CN107489737A - A kind of speed difference transmission mechanism and differential speed reducer - Google Patents
A kind of speed difference transmission mechanism and differential speed reducer Download PDFInfo
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- CN107489737A CN107489737A CN201710686328.7A CN201710686328A CN107489737A CN 107489737 A CN107489737 A CN 107489737A CN 201710686328 A CN201710686328 A CN 201710686328A CN 107489737 A CN107489737 A CN 107489737A
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- gear
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- outer ring
- dead axle
- wheel
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Classifications
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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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 technical field of mechanical transmission,Provide a kind of speed difference transmission mechanism and differential speed reducer,It includes central gear,Outer ring gear,Wheel and output gear between dead axle,Central gear drives outer ring pinion rotation by being taken turns between dead axle,Outer ring gear has different reference diameters from the part that wheel and the output gear are meshed between wheel and the part that is meshed of output gear and/or central gear and the dead axle between dead axle,So as to form a reference circle difference,Outer ring gear and central gear drive output gear to carry out rotation and revolved round the sun around central gear simultaneously,The ratio between the rotating speed of output gear revolution and the rotating speed of central gear are the fast ratio of the speed difference transmission mechanism,The size of fast ratio is inversely proportional with the difference,The difference is smaller,Fast ratio is bigger,The difference can be selected as needed,Compare size to reach corresponding speed,Being particularly suitable for use in needs the situation of super large speed ratio,Without setting cumbersome multi-stage speed-reducing transmission,Avoid overall volume excessively huge,Take great number of driving space.
Description
Technical field
The present invention relates to technical field of mechanical transmission, more particularly to a kind of speed difference transmission mechanism and differential speed reducer.
Background technology
Reductor is mechanically operated important component, and with the development of mechanization, plant equipment is towards small-sized, high
Effect, reliable, environmental protection direction are developed, and correspondingly, mechanical driving device is also towards small size, large speed ratio, efficient direction hair
Exhibition.In the prior art, reductor generally comprises gear reduction unit, planet-gear speed reducer, cycloidal planetary gear speed reducer, harmonic reduction
Machine and turbine worm reductor etc..Wherein, gear reduction unit has small volume, transmits the characteristics of moment of torsion is big, but single gear-stage velocity ratio is small；
The characteristics of planet-gear speed reducer structure is compact, and backhaul gap is small, and precision is higher, but it is smaller than speed (single-stage than speed for 3~
10)；Although cycloidal planetary gear speed reducer can reach relatively large speed than (9~87), but complicated；Harmonic wave speed reducing machine can also reach
To larger ratio fast (single-stage 50~300) and stronger bearing capacity, but during actual use, its flexbile gear is easy to produce fatigue rupture
And damage；Although turbine worm reductor also has a larger speed reducing ratio, transmission efficiency is poor.Several decelerations listed above
Machine, also one it is common the shortcomings that, be exactly, speed than and the contradictory relation between volume, specifically, when required speed is bigger
When, especially need in the case of realizing high-power large speed ratio, then need to design multi-stage speed-reducing transmission so that reductor is overall
Parts are various, and overall volume can be quite huge, and this does not occupy substantial amounts of space, are unfavorable for mechanical driving device to corpusculum
Product, large speed ratio, efficient direction are developed, and the increase of man power and material's cost such as cause to produce, assemble.
Therefore, it is necessary to be directed to above-mentioned problems of the prior art, there is provided a kind of technical scheme is to solve the above problems.
The content of the invention
The technical problems to be solved by the invention are to provide a kind of speed difference transmission mechanism of achievable large speed ratio and speed difference subtracts
Fast machine.
Technical scheme is used by the present invention solves above-mentioned technical problem：
A kind of speed difference transmission mechanism is provided, it includes wheel and output gear, institute between central gear, outer ring gear, dead axle
State between dead axle wheel and the output gear along the central gear axially arrangement and while engaged with the central gear, it is described fixed
Between centers wheel and the output gear engage with the outer ring gear simultaneously, and the central gear drives institute by being taken turns between the dead axle
Outer ring pinion rotation is stated, the outer ring gear and the central gear drive the output gear to carry out rotation and surround institute simultaneously
Central gear is stated to be revolved round the sun, the outer ring gear and wheel between the dead axle and the part that is meshed of the output gear and/or
The part that wheel and the output gear are meshed between the central gear and the dead axle has different reference diameters.
As the improvement of above-mentioned technical proposal, in addition to dead axle wheel carrier and output wheel carrier, it is provided with the outer ring gear
First ring gear and the second ring gear, first ring gear and second ring gear are arranged along the axial direction of the outer ring gear
Cloth, the outer ring gear mesh answer the part of first ring gear and second ring gear to have different reference circles straight respectively
Footpath, wheel is arranged on the dead axle wheel carrier between the dead axle, and wheel being located at the central gear and the outer ring tooth between the dead axle
Between wheel, and engaged with the central gear and first ring gear, the output gear be arranged on the outer ring gear and
Between the central gear, and engaged with the central gear and second ring gear, the output wheel carrier and the output
The wheel shaft of gear is fixedly connected.
As the further improvement of above-mentioned technical proposal, in addition to dead axle wheel carrier and output wheel carrier, the central gear bag
The first lap gear teeth and the second circle gear teeth are included, the first lap gear teeth and the second circle gear teeth are arranged along the axial direction of the central gear
Cloth, the central gear corresponds to the first lap gear teeth and the part of the second circle gear teeth has different reference circles straight respectively
Footpath, wheel is arranged on the dead axle wheel carrier between the dead axle, and wheel being located at the central gear and the outer ring tooth between the dead axle
Between wheel, and engaged with the first lap gear teeth of the central gear and the outer ring gear, the output gear is arranged on
Between the outer ring gear and the central gear, and the gear teeth and the outer ring gear are enclosed with described the second of the central gear
Engagement, the output wheel carrier are fixedly connected with the wheel shaft of the output gear.
As the further improvement of above-mentioned technical proposal, including take turns between several described dead axles, taken turns between the dead axle along institute
State the circumferential uniformly arrangement of central gear.
As the further improvement of above-mentioned technical proposal, including at least two output gears, the output gear edge
The circumferential uniformly arrangement of the central gear, the output wheel carrier are fixedly connected with the wheel shaft of the output gear.
A kind of differential speed reducer is additionally provided, it includes above-mentioned speed difference transmission mechanism.
As the improvement of above-mentioned technical proposal, in addition to shell, input shaft and output shaft, the input shaft and the center
Gear is conllinear and is fixedly connected or is integrally formed, and the output shaft is fixedly connected or is integrally formed with the output wheel carrier, described
Output shaft is conllinear with the rotary shaft of the output wheel carrier, and the speed difference transmission mechanism is arranged on the enclosure.
As the further improvement of above-mentioned technical proposal, in addition to shell, input shaft and output shaft, the input shaft and institute
State dead axle wheel carrier to be fixedly connected or be integrally formed, the output shaft is fixedly connected or is integrally formed with the output wheel carrier, described
Speed difference transmission mechanism is arranged on the enclosure.
The beneficial effects of the invention are as follows：
A kind of speed difference transmission mechanism of the present invention, it includes wheel and output gear between central gear, outer ring gear, dead axle, its
Including wheel and output gear between central gear, outer ring gear, dead axle, central gear drives outer ring gear in the same direction by being taken turns between dead axle
Constant Linear Velocity rotates, and outer ring gear and central gear drive output gear to carry out rotation and carried out around central gear public simultaneously
Turn, outer ring gear and wheel and described between wheel and the part that is meshed of output gear and/or central gear and the dead axle between dead axle
The part that output gear is meshed has different reference diameters so that two-part rotate produces speed difference, forms fast ratio, outside
Circle gear and/or central gear on set two different reference diameter parts reference diameter difference can pass through outer ring
The design of gear and/or central gear and realize, size and the difference of fast ratio are inversely proportional, and the difference is smaller, and fast ratio is bigger, tool
When body is implemented, the difference can be selected as needed, and to reach corresponding speed than size, being particularly suitable for use in needs the feelings of super large speed ratio
Condition, difference need to only be set, sizable fast ratio can be reached, meanwhile, the overall dimensions change of the speed difference transmission mechanism is small,
Without setting cumbersome multi-stage speed-reducing transmission, avoid overall volume excessively huge, take great number of driving space.
Brief description of the drawings
Technical scheme in order to illustrate the embodiments of the present invention more clearly, make required in being described below to embodiment
Accompanying drawing briefly describes：
Fig. 1 is the transmission principle schematic diagram of speed difference transmission mechanism of the present invention；
Fig. 2 is the structural representation of speed difference transmission mechanism one embodiment of the present invention；
Fig. 3 is the structural representation of outer ring gear in first embodiment of the invention；
Fig. 4 is the structural representation of central gear in second embodiment of the invention；
Fig. 5 is the internal structure schematic diagram of differential speed reducer one embodiment of the present invention；
Fig. 6 is the sectional view described in Fig. 5 at differential speed reducer A-A；
Fig. 7 is the sectional view described in Fig. 5 at differential speed reducer B-B.
Embodiment
Carried out below with reference to the design of embodiment and accompanying drawing to the present invention, concrete structure and caused technique effect clear
Chu, it is fully described by, to be completely understood by the purpose of the present invention, feature and effect.Obviously, described embodiment is this hair
Bright part of the embodiment, rather than whole embodiments, based on embodiments of the invention, those skilled in the art is not paying
The other embodiment obtained on the premise of creative work, belongs to the scope of protection of the invention.In addition, it is related in patent
All connection/annexations, not singly refer to component and directly connect, and refer to can according to specific implementation situation, by addition or
Couple auxiliary is reduced, to form more excellent draw bail.The orientation such as upper and lower, left and right involved by the present invention describe
For the mutual alignment relation of each part of the present invention in accompanying drawing.Each technical characteristic in the present invention, not
Can be with combination of interactions on the premise of conflicting conflict.
Fig. 1 is the transmission principle schematic diagram of speed difference transmission mechanism of the present invention；With reference to figure 1, speed difference transmission mechanism, including center
Wheel 3, output gear 4 between gear 1, outer ring gear 2, dead axle, axially arrangement is simultaneously along central gear 1 for wheel 3 and output gear 4 between dead axle
Engaged simultaneously with central gear 1, and wheel 3 and output gear 4 engage with outer ring gear 2 simultaneously between dead axle.It is defeated to central gear 1
Enter rotating speed so that central gear 1 rotates backward by taking turns 3 drive outer ring gears 2 between dead axle, now on the reference circle of outer ring gear 2
Point it is with the point linear velocity on the reference circle of central gear 1 equal, outer ring gear 2 is meshed with wheel 3 and output gear 4 between dead axle
Part and/or central gear 1 have different reference diameters from the part that wheel 3 and output gear 4 are meshed between dead axle so that
Output gear 4 can carry out rotation in the presence of outer ring gear 2 and central gear 1 and be revolved round the sun around central gear 1, and this is defeated
Go out the ratio of the angular speed and the angular speed of central gear 1 of the revolution of gear 4, the fast ratio of speed difference transmission mechanism as of the present invention.It is fixed
Between centers wheel 3 is installed by dead axle wheel carrier 5, and output gear 4 is installed by exporting wheel carrier 6, and output wheel carrier 6 can be with output
The revolution of gear 4 and rotate., can be by the way that rotating speed be passed through into center when carrying out deceleration transmission using speed difference transmission device of the present invention
Gear 1 is inputted, and dead axle wheel carrier 5 is fixed, you can exports rotating speed by exporting wheel carrier 6, now exports wheel carrier 6
Rotary shaft is conllinear with the central shaft of central gear 1.Rotating speed can also be inputted by dead axle wheel carrier 5, again by output
Wheel carrier 6 is exported rotating speed, and now the rotary middle spindle of dead axle wheel carrier 5 can be set with exporting the rotary middle spindle of wheel carrier 6
, can not also collinearly, suitable for input and output out-of-alignment situation to be conllinear.In order to make it easy to understand, the speed difference can be driven
Mechanism is divided into constant speed part I and speed difference part ii, as shown in figure 1, dotted line frame is only used for dividing I and II liang of region, the left side in figure
For constant speed part I, the right is speed difference part ii.
Definition：
The central gear reference diameter of constant speed part I is D1
The outer ring gear compound graduation circular diameter of constant speed part I is D2
The speed difference part ii output gear revolution a diameter of D in track3
Then the central gear of constant speed part I indexing circumference is D1π, output gear center of circle revolution track circumference is D3π。
(1) when reference circle of the central gear in speed difference part ii (part that i.e. central gear 1 is meshed with output gear 4)
Difference be present with its reference diameter at constant speed part I (i.e. central gear 1 and the part that wheel 3 is meshed between dead axle) in diameter
X, outer ring gear is when speed difference part ii is identical in the reference diameter divided of constant speed part I with it, speed difference part ii centre tooth
It is x π that wheel indexing circumference differs with constant speed part I, and now, the fast ratio of the speed difference transmission mechanism is：
It can be seen that when x values are smaller, fast ratio is bigger, as long as control x values are sufficiently small, the speed difference transmission mechanism can reach quite big
Fast ratio, on the basis of feasible process, x values can be arbitrarily set as needed, you can obtain needed for fast ratio.
(2) when outer ring gear (part that i.e. outer ring gear 2 is meshed with output gear 4) reference circle of speed difference part ii is straight
Difference be present with central gear (i.e. outer ring gear 2 and the part that wheel 3 is meshed between dead axle) reference diameter of constant speed part I in footpath
Y, central gear 1 is when speed difference part ii is identical in the reference diameter divided of constant speed part I with it, the rotation of central gear 1 one
The speed difference part ii of outer ring gear 2 and its long phase difference of reference circle rotary arc in constant speed part I are (D when all1/D2) π y, now,
The fast ratio of the speed difference transmission mechanism is：
It can be seen that when y values are smaller, fast ratio is bigger, as long as control y values are sufficiently small, the speed difference transmission mechanism can reach quite big
Fast ratio, on the basis of feasible process, y values can be arbitrarily set as needed, you can obtain needed for fast ratio.
If above-mentioned x values and y values are all 0, i.e., outer ring gear 2 and wheel 3 between dead axle and the part that is meshed of output gear 4 and
Central gear 1 all has identical reference diameter with the part that wheel 3 and output gear 4 are meshed between dead axle, then output gear 4
The revolution motion around central gear 1 does not occur, only carries out rotation.
Fig. 2 is the structural representation of speed difference transmission mechanism one embodiment of the present invention, with reference to Fig. 1 and Fig. 2, this reality
Applying example includes wheel 3, output gear 4, dead axle wheel carrier 5 and output wheel between speed difference transmission mechanism central gear 1, outer ring gear 2, dead axle
Frame 6.
Wherein, the first ring gear 21 and the second ring gear 22 are provided with outer ring gear 2, first ring gear 21 and second
Axial arranging of the ring gear 22 along outer ring gear 2, outer ring gear 2 to should the first ring gear 21 and the second ring gear 22 part
There is different reference diameters respectively, can by setting different moduluses and/or the number of teeth to realize different reference diameters, in
The part reference diameter that wheel 3 and output gear 4 engage respectively between dead axle on heart gear 1 is identical.The position of dead axle wheel carrier 5 is consolidated
It is fixed, 3 are taken turns between dead axle and is arranged on by its wheel shaft on dead axle wheel carrier 5, taken turns between dead axle 3 located at central gear 1 and outer ring gear 2 it
Between, and engaged with the ring gear 21 of central gear 1 and first, output gear 4 is arranged between outer ring gear 2 and central gear 1, and
Engaged with the ring gear 22 of central gear 1 and second.It is set to be rotated with a fixed angular speed to the input speed of central gear 1, centre tooth
Wheel 1 drives outer ring gear 2 to rotate backward by the ring gear 21 of wheel between dead axle 3 and first, corresponding first ring gear of outer ring gear 2
The linear velocity of point on 21 part reference circles is v21, the point linear velocity on the reference circle of central gear 1 is v1, now v21=v1, outside
When enclosing pinion rotation, the angular velocity omega of the second ring gear 2222With the angular velocity omega of the first ring gear 2121Equal (ω22=ω21),
Due to the two different reference diameter of tool, so when the 2 corresponding part of second ring gear 22 of outer ring gear reference circle on point
Linear velocity be v21, now v21≠v21, v21≠v1, therefore output gear 4 is in the presence of the second ring gear 22 and central gear 1
Rotation can be carried out and revolved round the sun around central gear 1, the angular velocity omega of the revolution4With the ratio of the angular velocity omega of central gear 1
Value, is the fast ratio of the speed difference transmission mechanism, and output wheel carrier 6 is fixedly connected with the wheel shaft of output gear 4 and with the public affairs of gear 4
Then rotate, when the reference diameter of the second ring gear 22 is more than the reference diameter of the first ring gear 21, the public affairs of output gear 4
Turn that direction is identical with the rotation direction of central gear 1, conversely, the revolution direction of output gear 4 and the rotation side with central gear 1
To opposite.The number that 3 are taken turns in the present embodiment, between dead axle is preferably 3, and to increase strength and stability, three is around central gear week
To uniform arrangement；Similarly, the number of output gear 4 is preferably 3, and three is around the circumferential uniformly arrangement of central gear.
Fig. 3 is the structural representation of outer ring gear in first embodiment of the invention, with reference to figure 3, is set on outer ring gear 2
There are the first ring gear 21 and the second ring gear 22, the ring gear 22 of the first ring gear 21 and second is arranged along the axial direction of outer ring gear 2
Cloth, the outside of outer ring gear 2 are additionally provided with bearing erecting bed 23, in order to install and fixing bearing.First ring gear 21 in figure
Spacer region 24 is provided with among the second ring gear 22, is easy to process operation, in practical operation, in the first ring gear 21 and second
Gear ring 22 can also be continuous structure.In order that the first ring gear 21 and the second ring gear 22 have different reference circles straight
Footpath, only different moduluses and/or the number of teeth need to be set, so, in the case that a ring gear is constant wherein, only need basis
Reference circle difference corresponding to required speed ratio sets the modulus and/or the number of teeth of another ring gear, is not required to do in volume too big
Change, less with accelerating, implementation is simply efficient.
Fig. 4 is the structural representation of central gear in second embodiment of the invention, with reference to figure 4, speed difference transmission of the present invention
The difference of second embodiment and above-mentioned one embodiment of mechanism is, 3 and output are taken turns between outer ring gear 2 and dead axle
The part reference diameter that gear 4 engages respectively is identical, and central gear 1 includes the first lap gear teeth 11 and second and encloses the gear teeth 12,
The first lap gear teeth 11 and second enclose axial arranging of the gear teeth 12 along central gear 1, and the corresponding first lap gear teeth 11 of central gear 1
There is different reference diameters respectively with the part of the second circle gear teeth 12.
To the input speed of central gear 1, the linear velocity of the point at the corresponding first lap gear teeth 11 of central gear 1 on reference circle is
v11, the linear velocity of the point at the corresponding first lap gear teeth 11 of central gear 1 on reference circle is v12, due to central gear 1 corresponding first
The part that the circle gear teeth 11 and second enclose the gear teeth 12 has different reference diameters, therefore during rotation, v11≠v12, central gear 1
Wheel 3 rotates and drives outer ring gear 2 to rotate backward between the first lap gear teeth 11 drive dead axle, the point on the reference circle of outer ring gear 2
Linear velocity is v2, now v2=v11, therefore output gear 4 is in the presence of outer ring gear 2 and central gear 1 second enclose the gear teeth 12
Rotation can be carried out and revolved round the sun around central gear 1, the angular velocity omega of the revolution4With the ratio of the angular velocity omega of central gear 1
Value, is the fast ratio of the speed difference transmission mechanism, and output wheel carrier 6 is fixedly connected with the wheel shaft of output gear 4 and with the public affairs of gear 4
Then rotate, when the reference diameter of the second circle gear teeth 12 is more than the reference diameter of the first lap gear teeth 11, output gear 4
Revolution direction it is identical with the rotation direction of central gear 1, conversely, output gear 4 revolution direction with central gear 1 turn
It is dynamic in opposite direction.
Central gear 1 includes the first lap gear teeth 11 and second and encloses the gear teeth 12, and the first lap gear teeth 11 and second enclose the edge of the gear teeth 12
The axial arranging of central gear 1, and the part that the corresponding first lap gear teeth 11 and second of central gear 1 enclose the gear teeth 12 has respectively
Different reference diameters.The first lap gear teeth 11 and second enclose among the gear teeth 12 and are provided with spacer region 13 in figure, are easy to processing to grasp
Make, in practical operation, it can also be continuous structure that the first lap gear teeth 11 and second, which enclose the gear teeth 12,.In order that the first lap gear teeth 11
There is different reference diameters with the second circle gear teeth 12, only different moduluses and/or the number of teeth need to be set, so, at it
In one circle the gear teeth it is constant in the case of, only need to according to it is required speed corresponding to than reference circle difference set it is another enclose the gear teeth modulus
And/or the number of teeth, it is not required to do too big variation in volume, less with accelerating, implementation is simply efficient.
The difference of 3rd embodiment and above-mentioned one embodiment of speed difference transmission mechanism of the present invention is, outer ring
It is straight to be provided with different reference circles for the corresponding part engaged from wheel 3 between dead axle and output gear 4 on gear 2 and central gear 1
Footpath.Specifically, the first ring gear 21 and the second ring gear 22 are provided with outer ring gear 2, in first ring gear 21 and second
Axial arranging of the gear ring 22 along outer ring gear 2, outer ring gear 2 to should the first ring gear 21 and the second ring gear 22 part point
Reference diameter that Ju You be not different.Central gear 1 includes the first lap gear teeth 11 and second and encloses the gear teeth 12, the He of the first lap gear teeth 11
Axial arranging of the second circle gear teeth 12 along central gear 1, and the corresponding first lap gear teeth 11 and second of central gear 1 enclose the gear teeth 12
Part there is different reference diameters respectively.With said one embodiment and second embodiment similarly, output gear 4 exists
Second ring gear 22 and the second circle gear 12 act on lower generation rotation and the revolution motion around central gear 1 simultaneously, the revolution
The ratio of the angular speed of angular speed and idler gear and the fast ratio for the present embodiment speed difference transmission mechanism, realize that speed difference exports.
Fig. 5 is the internal structure schematic diagram of differential speed reducer one embodiment of the present invention, and Fig. 6 is that speed difference described in Fig. 5 is slowed down
Sectional view at machine A-A, Fig. 7 are the sectional view described in Fig. 5 at differential speed reducer B-B, with reference to Fig. 5-7, the present embodiment speed
Poor reductor includes shell 100, input shaft 200, output shaft 300 and above-mentioned speed difference transmission mechanism.Input shaft 200 and centre tooth
Wheel 1 is conllinear and is fixedly connected or is integrally formed, and output shaft 300 is fixedly connected or is integrally formed with output wheel carrier 6, output shaft 300
Conllinear with the rotary shaft for exporting wheel carrier 6, now, output shaft 300 is conllinear with input shaft 200, and speed difference transmission mechanism is arranged on shell
Inside 100.
Shell 100 includes housing 110, the first end cap 120 and the second end cap 130, the first end cap 120 and the second end cap 130
Be fixedly mounted on the both ends of housing 110, and an inner chamber 140 surrounded jointly with housing 110, the end cap 120 of input shaft 200 and first it
Between carried by clutch shaft bearing 150, carried between the end cap 130 of output shaft 300 and second by second bearing 160,
Second bearing 160 is compressed by trim ring 170 and oil sealing 180 to the second end cap 130.The side wall of outer ring gear 2 and inner chamber 140 it
Between be provided with 3rd bearing 190 for carrying outer ring gear 2.
The difference of another embodiment of differential speed reducer of the present invention and embodiment illustrated in fig. 5 is, input shaft 200 with
Dead axle wheel carrier 5 is fixedly connected or is integrally formed, and now, output shaft 300 is conllinear with central gear 1, input shaft 200 and centre tooth
Wheel can collinearly can not also collinearly, so, the present embodiment can be according to the input shaft feelings conllinear or not conllinear with output shaft
Condition is set accordingly.
The reference circle difference and/or central gear 1 of first ring gear 21 and the second ring gear 22 on outer ring gear 2 of the present invention
The difference that the upper first lap gear teeth 11 and second enclose the reference circle of the gear teeth 12 can be by the design of outer ring gear and/or central gear and reality
Existing, size and the difference of fast ratio are inversely proportional, and the difference is smaller, and fast ratio is bigger, when it is implemented, the difference can be selected as needed
Value, to reach corresponding speed than size, being particularly suitable for use in needs the situation of super large speed ratio.When needing super large speed ratio, only need by
The difference is set enough to small, you can to reach sizable fast ratio, meanwhile, the overall dimensions change of the speed difference transmission mechanism
It is small, without setting cumbersome multi-stage speed-reducing transmission, avoid overall volume excessively huge, take great number of driving space.
Presently preferred embodiments of the present invention is above are only, but the present invention is not restricted to the embodiment, is familiar with this area
Technical staff can also make a variety of equivalent variations or replacement on the premise of without prejudice to spirit of the invention, these equivalent deformations
Or replace and be all contained in the application claim limited range.
Claims (8)
- A kind of 1. speed difference transmission mechanism, it is characterised in that：Including wheel and output gear, institute between central gear, outer ring gear, dead axle State between dead axle wheel and the output gear along the central gear axially arrangement and while engaged with the central gear, it is described fixed Between centers wheel and the output gear engage with the outer ring gear simultaneously, and the central gear drives institute by being taken turns between the dead axle Outer ring pinion rotation is stated, the outer ring gear and the central gear drive the output gear to carry out rotation and surround institute simultaneously Central gear is stated to be revolved round the sun, the outer ring gear and wheel between the dead axle and the part that is meshed of the output gear and/or The part that wheel and the output gear are meshed between the central gear and the dead axle has different reference diameters.
- 2. speed difference transmission mechanism according to claim 1, it is characterised in that：Also include dead axle wheel carrier and output wheel carrier, institute State and the first ring gear and the second ring gear are provided with the gear of outer ring, first ring gear and second ring gear are described in The axial arranging of outer ring gear, the outer ring gear mesh answer first ring gear and the part of second ring gear to have respectively There is different reference diameters, take turns and be arranged on the dead axle wheel carrier between the dead axle, wheel being located at the center between the dead axle Between gear and the outer ring gear, and engaged with the central gear and first ring gear, the output gear is set Engaged between the outer ring gear and the central gear, and with the central gear and second ring gear, it is described defeated The wheel shaft for going out wheel carrier with the output gear is fixedly connected.
- 3. speed difference transmission mechanism according to claim 1, it is characterised in that：Also include dead axle wheel carrier and output wheel carrier, institute Stating central gear includes the first lap gear teeth and the second circle gear teeth, and the first lap gear teeth and described second enclose the gear teeth along the center The axial arranging of gear, the central gear corresponds to the first lap gear teeth and the part of the second circle gear teeth to be had not respectively With reference diameter, wheel is arranged on the dead axle wheel carrier between the dead axle, and wheel being located at the central gear between the dead axle Engaged between the outer ring gear, and with the first lap gear teeth of the central gear and the outer ring gear, it is described defeated Go out gear to be arranged between the outer ring gear and the central gear, and with the central gear it is described second circle the gear teeth and The outer ring gear engagement, the output wheel carrier are fixedly connected with the wheel shaft of the output gear.
- 4. the speed difference transmission mechanism according to any one of claims 1 to 3, it is characterised in that：Including described in several Taken turns between dead axle, circumferential uniformly arrangement of the wheel along the central gear between the dead axle.
- 5. the speed difference transmission mechanism according to any one of claims 1 to 3, it is characterised in that：Including at least two institutes Output gear is stated, the output gear is described to export wheel carrier and the output gear along the circumferential uniformly arrangement of the central gear Wheel shaft be fixedly connected.
- A kind of 6. differential speed reducer, it is characterised in that：Including a kind of speed difference transmission described in any one of Claims 1 to 5 Mechanism.
- 7. differential speed reducer according to claim 6, it is characterised in that：Also include shell, input shaft and output shaft, it is described Input shaft is conllinear with the central gear and is fixedly connected or is integrally formed, and the output shaft is fixedly connected with the output wheel carrier Or be integrally formed, the output shaft is conllinear with the rotary shaft of the output wheel carrier, and the speed difference transmission mechanism is arranged on described outer Inside shell.
- 8. differential speed reducer according to claim 6, it is characterised in that：Also include shell, input shaft and output shaft, it is described Input shaft is fixedly connected or is integrally formed with the dead axle wheel carrier, and the output shaft is fixedly connected with the output wheel carrier or one Shaping, the speed difference transmission mechanism are arranged on the enclosure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710686328.7A CN107489737A (en) | 2017-08-11 | 2017-08-11 | A kind of speed difference transmission mechanism and differential speed reducer |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710686328.7A CN107489737A (en) | 2017-08-11 | 2017-08-11 | A kind of speed difference transmission mechanism and differential speed reducer |
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| Publication Number | Publication Date |
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| CN107489737A true CN107489737A (en) | 2017-12-19 |
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| CN201710686328.7A Pending CN107489737A (en) | 2017-08-11 | 2017-08-11 | A kind of speed difference transmission mechanism and differential speed reducer |
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| CN109538701A (en) * | 2018-03-07 | 2019-03-29 | 深圳市奇诺动力科技有限公司 | Differential planetary transmission |
| CN112743567A (en) * | 2020-12-28 | 2021-05-04 | 深圳市优必选科技股份有限公司 | Steering wheel module and robot |
| CN114216430A (en) * | 2021-11-17 | 2022-03-22 | 盾构及掘进技术国家重点实验室 | Real-time monitoring method for roller strain of main drive bearing of large-scale tunneling machine |
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