CN106958641A - Planet differential variable-speed shaft - Google Patents
Planet differential variable-speed shaft Download PDFInfo
- Publication number
- CN106958641A CN106958641A CN201710342832.5A CN201710342832A CN106958641A CN 106958641 A CN106958641 A CN 106958641A CN 201710342832 A CN201710342832 A CN 201710342832A CN 106958641 A CN106958641 A CN 106958641A
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- China
- Prior art keywords
- wheel
- planet carrier
- input shaft
- face
- inputting
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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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
- F16H48/38—Constructional details
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention discloses a kind of planet differential variable-speed shaft, variable-speed shaft includes driving the input shaft rotated by wheel for inputting, input shaft is provided with the planetary differential of Bevel Gear Drive, planetary differential includes sun gear, planetary gear, planet carrier and the output wheel for constituting output end, planetary gear is rotatably located on planet carrier, and sun gear is fixedly and coaxially connected on input shaft；Planet carrier and output wheel are coaxially rotatably sleeved on input shaft；Planetary gear is made up of the expert's star-wheel and layman's star-wheel of the connection in synchronous axial system, and expert's star-wheel is engaged with sun gear and output wheel respectively with layman's star-wheel；Planetary differential be connected with wheel for inputting input torque increase to setting value or reach set rotating speed when, to planet carrier be correspondingly formed braking or release on-position speed-change control device.Speed change system includes the vehicle drive axle differential mechanism being connected with the variable-speed shaft.The beneficial effects of the invention are as follows simple in construction, easy to manufacture；Compact conformation, long service life.
Description
The application is a divisional application, and the parent application number corresponding to the divisional application is 201510294119.9, female
Entitled a kind of the planet differential variable-speed shaft and speed change system of case application, the applying date of parent application is 2015-06-02.
Technical field
The present invention relates to a kind of planet differential speed changing structure, more particularly to a kind of planet differential variable-speed shaft.
Background technology
Planetary differential speed change is the differential principle using differential mechanism, passes through differential shape of the control device to planetary differential
State is controlled realization.But existing controlling organization complex structure, processing difficulties are more expensive to manufacture.In addition, existing electric motor car is logical
All it is often to realize that the transport condition that vehicle moves forward and backward is changed by controlled motor rotating, but due to vehicle in transfer process
Effect of inertia, easily causes the impact of vehicle running state conversion.For this reason, it may be necessary to further improve.
The content of the invention
There is provided a kind of planet differential variable-speed shaft, the change aiming at the deficiencies in the prior art for the purpose of the object of the invention first
Fast axle passes through simplify control apparatus structure, reduction manufacture difficulty and cost.The second object of the present invention is to provide a kind of including row
The speed change system of star differential variable-speed shaft, to adapt to tricycle or carriage drive axle, and then reduces vehicle manufacture difficulty and cost.
To realize the first purpose, the present invention is adopted the following technical scheme that.
A kind of planet differential variable-speed shaft, including the input shaft rotated is driven by wheel for inputting, input shaft is provided with conical gear
The planetary differential of transmission, the planetary differential includes sun gear, planetary gear, planet carrier and the output wheel for constituting output end,
Planetary gear is rotatably located on planet carrier, and planetary differential is connected with speed-change control device；The sun gear is coaxially fixed
It is connected on input shaft；The planetary gear is made up of expert's star-wheel and layman's star-wheel, and expert's star-wheel and layman's star-wheel are in synchronous
The attachment structure of rotation, expert's star-wheel is engaged with sun gear, and layman's star-wheel is engaged with the input of the output wheel；The planet
Frame and output wheel are coaxially rotatably sleeved on input shaft；The speed-change control device is used to increase in wheel for inputting input torque
When arriving setting value greatly, planet carrier formation is braked；Or when input shaft rotating speed reaches setting value, release to the planet
The braking of frame.
Using the present invention of preceding solution, speed-change control device includes two kinds of control modes, and one is turned round by inputting
Square is controlled, and two be by input speed control；When using input torque control, it is less than setting value in wheel for inputting input torque
When, planet carrier is in free state, and sun gear drives planet carrier to rotate by inner planet wheel, and inside and outside planetary gear is public with planet carrier
Turn, and drive output wheel and sun gear to form synchronous axial system by outer planet wheel, so with input shaft synchronous axial system；In wheel for inputting
When input torque reaches setting value, speed-change control device forms the braking to planet carrier, now, and planet moves in turn inside and outside sun gear band
Synchronous rotation, outer planet wheel drives output wheel to rotate, and is formed using the gear ratio between sun gear, inside and outside planetary gear and output wheel
Slow down, output wheel is less than the input shaft rotating speed with the rotating speed such as sun gear, and speed change is realized by way of input torque so as to realize.
When using input speed control, when input shaft rotating speed is less than setting value, planet carrier is in on-position, and it exports wheel speed
Less than the input shaft rotating speed with the rotating speed such as sun gear, when input shaft rotating speed reaches setting value, planet carrier on-position is released from,
Sun gear drives planet carrier to rotate by inner planet wheel, and inside and outside planetary gear revolves round the sun with planet carrier, and drives output by outer planet wheel
Wheel with sun gear formation synchronous axial system, and then with input shaft synchronous axial system.
It is preferred that, the speed-change control device includes the loading spring being connected between wheel for inputting and the axle journal of input shaft,
Brake disc rotatably is connected with wheel for inputting, the anti-rotation structure that its rotation is limited by static component is formed with the brake disc,
The first end face clutch configuration engaged between brake disc and planet carrier provided with end face tooth；The elastic force of loading spring is used to make
The first end face clutch configuration between brake disc and planet carrier departs from；The wheel for inputting by helical spline structure with it is defeated
Enter axle connection, the hand of spiral and angle of the helical spline structure have when wheel for inputting is rotated forward, and wheel for inputting is to loading bullet
Spring is formed with the movement tendency of compression-loaded spring, so that when input torque increases to setting value, wheel for inputting overcomes loading spring
Elastic force, combined the first end face clutch configuration between brake disc and planet carrier.
In the prior art, helical spline fit structure has following fundamental characteristics, and it is mainly used in transmitting torque, has simultaneously
There is the characteristic that Small-angle Rotation correspondence is moved on a large scale, therefore, the lead angle for helical spline is all inevitable larger, can pass through
Promote and coordinate the spline housing movement in splined shaft to realize that spline housing or splined shaft are rotated.This programme utilizes helical spline fit structure
Afore-mentioned characteristics, when wheel for inputting is rotated forward, and when load torque and smaller corresponding input torque, wheel for inputting is rotated forward to loading spring shape
Into compression stress be not enough to overcome the pretightning force of loading spring, the first end face clutch knot between brake disc and planet carrier
Structure is in released state under the effect of loading spring pretightning force, so as to form the free state of planet carrier, output wheel and sun gear
With input shaft synchronous axial system.When wheel for inputting is rotated forward and input torque reaches setting value, wheel for inputting rotates forward and loading spring is formed
Compression stress overcome the pretightning force of loading spring, and make at the first end face clutch configuration between brake disc and planet carrier
In bonding state, now, brake disc is braked to planet carrier formation, and speed change is realized by way of input torque so as to realize.Its
Simple in construction, manufacturing cost and use cost is low, and makes full use of what motor output torque changed automatically with the change of load torque
Characteristic realizes the fluid drive of variable-speed shaft.
It is further preferred that the brake disc is in bell-jar structure, described first be provided between brake disc and planet carrier
End face clutch structure is located at planet carrier end.To form the control for brake of planet carrier end, it brakes reliable.
Still more preferably, the wheel for inputting is located at input shaft rear end；The planet carrier is sleeved on input shaft front end, too
Sun wheel is located between wheel for inputting and planet carrier, and output wheel is sleeved on input shaft on a shaft part at sun gear rear and positioned at institute
State in the bell jar of brake disc, the bell jar wall of brake disc, which is provided with, to be used to receive the power with output wheel formation power transmission to hold biography part
Gap.To facilitate laying of the variable-speed shaft in speed change system or gearbox, it is particularly suitable for use in and vehicle drive axle differential mechanism
Connection.
Still more preferably, the planet carrier is sleeved on the stage casing of input shaft；The output wheel is sleeved on input shaft
On one shaft part of front end；The sun gear is located between planet carrier and output wheel.To avoid setting gap in brake disc, it is adaptable to
Lay the variable-speed shaft with rotating Buffer output.
Still further preferably, the output wheel is made up of input part and outlet end part, and outlet end part is located at
Input end sub-headend, input part in bell-jar empty set is on transition sleeve and is engaged with layman's star-wheel, transition sleeve
Coaxially rotatably it is sleeved on input shaft, transition sleeve is fixedly and coaxially connected with outlet end part formation, on transition sleeve also
End face disk is fixedly and coaxially connected, end face disk is located between input part and the sun gear and positioned at the clock of input part
In cover；Helical spline set is combined with by helical spline on the axle journal of the input part, helical spline set be connected with one to
It applies the brake apparatus of frictional resistance；End face tooth is formed respectively between helical spline set and outlet end part and end face disk to nibble
The second end face clutch configuration of conjunction, two second end face clutch configurations are only used for input part and pass through helical spline respectively
Set drives outlet end part synchronously to rotate forward and synchronous reversion；Helical spline set is formed with the end face in the end face disk direction
The engagement pawl of multiple circumference uniform distributions；Multiple hollow holes passed through for engagement pawl are provided with the top of the bell jar of the input part；
Second end face clutch configuration formation between helical spline set and end face disk is in the free end of engagement pawl and end face disk
On correspondence end face.By the way that output wheel is peeled off into input part and outlet end part, and helical spline is formed between
The two-way of set is more than clutch configuration, during so that differential portion being output as rotating and reverse, passes through the mobile shape of screw-casing
Into the time interval changed therebetween.For vehicle, when can effectively reduce the conversion of vehicle forward-reverse transport condition, because of inertia
And impact is brought, impact is brought because of inertia to reduce, good cushioning effect is played.
In foregoing double rolling key clutch structure, input partial turn, helical spline is enclosed within brake apparatus application
Frictional resistance effect is lower to form the integrated motion that certain relative rotation and axis are moved with input part, its moving direction by
The hand of spiral and the rotation direction of input part determine that its direction of rotation and input end split-phase are same.Due to two the second ends
Face clutch configuration be only respectively used to helical spline set directly drive or by transition sleeve drive outlet end part synchronously rotate forward and
Synchronous reversion, therefore, in input partial turn, two give one of second end face clutch configuration to be in released state, separately
One is in bonding state.When the hand of spiral is set into the rotating forward of input part, helical spline set directly drives output end
Partial synchronization is rotated forward, when outlet end part rotating speed is more than input part and helical spline set rotating speed, outlet end part and spiral shell
Between rotation spline housing the and end face clutch structure is in and surmounts state.During for vehicle, the advance that vehicle can be achieved is slided.
It is preferred that, the planet carrier is sleeved on the stage casing of input shaft, and planet carrier is formed with end face disk in the middle part of side；Institute
State output wheel be located at be sleeved on a shaft part of input shaft front end；The sun gear is located between planet carrier and output wheel；It is described
Brake disc is arranged on inside the wheel for inputting of support holder structure, and the anti-rotation structure of brake disc is stretched out by input wheel side, brake disc with
The end face disk of planet carrier forms the first end face clutch configuration.The radial dimension of variable-speed shaft can further be reduced, be easy to
Laid in gearbox.
The speed-change control device includes being connected to two balancing springs of wheel for inputting both sides, two balancing springs it is another
End is connected by the axle journal and locking nut of input shaft with input shaft respectively；Brake disc rotatably is set with wheel for inputting, should
Brake disc is limited by static component and rotated, and the clutch knot that end face is combined is respectively formed between brake disc and the two sides of planet carrier
Structure；Two balancing springs are used to, when the input torque of wheel for inputting is less than setting value, make two end faces of brake disc and planet carrier
Clutch configuration is in released state；The wheel for inputting is connected by helical spline structure with input shaft, the helical spline structure
Spiral angle have wheel for inputting by setting rotation when, wheel for inputting to one in two balancing springs be formed with compression this put down
The movement tendency of weighing apparatus spring, so that when input torque increases to setting value, wheel for inputting overcomes the elastic force of balancing spring, makes braking
A corresponding end face clutch structure between disk and planet carrier is combined.
It is preferred that, the speed-change control device includes two balancing springs for being connected to wheel for inputting both sides, two equilibrium bombs
The other end of spring is connected by the axle journal and locking nut of input shaft with input shaft respectively；Rotatably system is set with wheel for inputting
Moving plate, the brake disc is limited by static component and rotated, be respectively formed that end face combined between brake disc and the two sides of planet carrier from
Clutch structure；Two balancing springs are used to, when the input torque of wheel for inputting is less than setting value, make the two of brake disc and planet carrier
Individual end face clutch structure is in released state；The wheel for inputting is connected by helical spline structure with input shaft, the Turbo Flora
The spiral angle of bond structure has when wheel for inputting is by setting rotation, and wheel for inputting is formed with pressure to one in two balancing springs
Contract the movement tendency of the balancing spring, so that when input torque increases to setting value, wheel for inputting overcomes the elastic force of balancing spring,
Combine one between brake disc and planet carrier corresponding end face clutch structure.Two balancing springs make wheel for inputting in rotating
Input torque when less than setting value, planet carrier is in free state, and output wheel is in and the rotary regimes such as input shaft；Defeated
When the forward and reverse input for entering wheel reaches setting value, the balancing spring of one of input wheel compression, and make brake disc and planet carrier
Between a corresponding end face clutch structure combine, planet carrier formation is braked, now, output wheel passes through layman's star-wheel rotation band
It is dynamic to rotate, so as to realize speed governing purpose.I.e. this programme can realize rotating speed change, during for vehicle, achievable two kinds of speed
Reversing.
It is preferred that, the wheel for inputting is fixedly connected on the input shaft, the input shaft in tubular construction, tubular input shaft
Only it is rotatably coupled in fixing axle；The speed-change control device includes the brake block that connection is only may move in fixing axle, should
Brake block and planet carrier formation end face clutch structure, are provided with Self-resetting spring, Self-resetting between brake block and input shaft
The elastic force of spring is used to combined the end face clutch structure between brake block and planet carrier；It is also associated with the input shaft
Multiple centrifugal-blocks of circumference uniform distribution, multiple centrifugal-blocks are used for when input shaft rotating speed reaches setting value, make brake block and planet carrier
Between end face clutch structure depart from.When input shaft rotating speed is less than setting value, Self-resetting spring makes brake block and planet
End face clutch structure between frame is combined, and planet carrier is rotated by limitation, and output wheel is driven by the rotation of layman's star-wheel and rotated, and is reached
To deceleration purpose；When input shaft reaches setting value, centrifugal-block under the action of the centrifugal, makes the end face between brake block and planet carrier
Clutch configuration departs from, and planet carrier is in free state, and the rotational speed such as output wheel and input shaft is turned so as to realize by input shaft
The differential speed change of speed control.
It is further preferred that the brake block includes 7 font pawls of at least two circumference uniform distributions, 7 words of brake block
Shape horizontal segment is slidably fitted in what fixing axle was provided with planet carrier formation end face clutch structure, 7 font vertical sections of brake block
In keyway, 7 font vertical section lower ends of brake block are formed with ring flange, and the 7 font horizontal segments and ring flange of brake block are distributed in
Planet carrier both sides；The Self-resetting spring is connected by the side of ring flange with the input shaft, the opposite side of ring flange and institute
State centrifugal-block connection.It is convenient to be laid in gearbox so as to effectively reduce the radial dimension of variable-speed shaft, phase and speed Control structure
Simply, dependable performance.
Still more preferably, 7 font horizontal segments of the brake block are located at input shaft front end；The wheel for inputting is located at defeated
Enter shaft rear end；The output wheel is located between planet carrier and wheel for inputting；The method that 7 font vertical section lower ends of the brake block are formed
Blue disk is located at the output wheel rear in fixing axle.To obtain rational topology layout, further improve what is laid in gearbox
Convenience.
Still further preferably, the centrifugal-block passes through the centrifugal-block support that is fixedly connected on the wheel for inputting trailing flank
On；Plane bearing is provided between the ring flange of the brake block and the centrifugal-block.To make full use of the locus of wheel for inputting,
The reasonability of further reinforced structure；Meanwhile, the relative motion of centrifugal-block and brake block upper flange plate is eliminated using plane bearing,
Fretting wear is avoided, is increased the service life.
To realize the second purpose, the present invention is adopted the following technical scheme that.
A kind of planet gearing system, including the vehicle drive axle differential mechanism rotated, large fluted disc and reality are driven by large fluted disc
The output end teeth portion of the output wheel of existing first invention mesh planet differential variable-speed shaft engages to form power transmission relationship.
Using the present invention of aforementioned schemes, as a result of foregoing planet differential variable-speed shaft, system passes through vehicle drive axle
Exported with differential mechanism, it is adaptable to the fluid drive of tricycle or four-wheel electro-motive vehicle.Using speed-change control device it is simple in construction,
The characteristics of manufacturing cost and use cost is low, realizes the low cost of vehicle.
It is preferred that, the vehicle drive axle is made up of with the differential casing of differential mechanism left housing and right shell；The large fluted disc
Central hub portion a part be rotatably sleeved in left housing, another part is rotatably sleeved on large fluted disc；Large fluted disc
Central hub on the second helical spline set is combined with by helical spline, the second helical spline set is connected with one and rubbed to its application
Wipe the second brake apparatus of resistance；Second helical spline is covered with forming the end face tooth is engaged the 3rd between left housing and right shell respectively
End-engaging clutch structure, two the 3rd end-engaging clutch structures are only used for large fluted disc and pass through two helical spline sets respectively
The differential casing of the vehicle drive axle differential mechanism is driven synchronously to rotate forward and synchronous reversion；Second helical spline set is located at institute
The clutch pawl of multiple circumference uniform distributions is formed with the end face for stating large fluted disc web direction；The web of the large fluted disc is provided with multiple
The hollow hole passed through for clutch pawl；Between the second helical spline set and the left housing or right shell of large fluted disc web respective side
3rd end-engaging clutch structure, formed the free end of clutch pawl with the corresponding end face of left housing or right shell.
Large fluted disc and vehicle drive axle by the second helical spline set and end-tooth between the housing of differential mechanism with engaging knot
It is configured to helical spline shell type double rolling key clutch structure.Its operation principle and beneficial effect and foregoing bidirectional overtaking clutch
Device structure is identical, will not be repeated here.
The beneficial effects of the invention are as follows variable-speed shaft is simple in construction, easy to manufacture, integrated cost is low；Speed change system small volume,
Rationally distributed, long service life, it is adaptable to three-wheel and four-wheel electric motor car.
Brief description of the drawings
Fig. 1 is the structural representation of the embodiment of the present invention 1.
Fig. 2 is the schematic diagram of the structure of the embodiment of the present invention 2.
Fig. 3 is the structural representation of the embodiment of the present invention 3.
Fig. 4 is the axonometric schematic diagram of part-structure in the embodiment of the present invention 3.
Fig. 5 is the structural representation of the embodiment of the present invention 4.
Fig. 6 is the structural representation of the embodiment of the present invention 5.
Fig. 7 is the structural representation of the embodiment of the present invention 6.
Fig. 8 is A-A sectional views in Fig. 7 of the present invention.
Fig. 9 is the structural representation of brake block 16 in the embodiment of the present invention 6.
Figure 10 is Fig. 9 of the present invention top view.
Figure 11 is Fig. 9 of the present invention upward view.
Figure 12 is the structural representation of the embodiment of the present invention 7.
Figure 13 is another structure type schematic diagram of brake apparatus in the embodiment of the present invention 3 and 7.
Embodiment
The present invention is further illustrated below in conjunction with the accompanying drawings, but does not therefore limit the present invention to described implementation
Among example scope.
Embodiment 1 is referring to Fig. 1, a kind of planet differential variable-speed shaft, including drives the input shaft 2 of rotation by wheel for inputting 1, input
Axle 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, the and of planet carrier 5
The output wheel 7 of output end is constituted, sun gear 3 is fixedly and coaxially connected on input shaft 2；Planetary gear is rotatably located at planet carrier
On 5, planetary differential is connected with speed-change control device；Wherein, wheel for inputting 1 is located at the rear end of input shaft 2, and planet carrier 5 can coaxially turn
Dynamic is sleeved on the front end of input shaft 2, and sun gear 3 is located between wheel for inputting 1 and planet carrier 5, the coaxial rotatable suit of output wheel 7
It is located in wheel for inputting 1 on a shaft part at the rear of sun gear 3.
Wherein, planetary gear is made up of expert's star-wheel 4 and layman's star-wheel 4a, and expert's star-wheel 4 and layman's star-wheel 4a are in synchronous
The attachment structure of rotation, expert's star-wheel 4 is engaged with sun gear 3, and layman's star-wheel 4a is engaged with the input of the output wheel 7；Become
Velocity control device includes the loading spring 8 being made up of disc spring being connected between the axle journal of wheel for inputting 1 and input shaft 2, wheel for inputting 1
On be rotatably set with the brake disc 9 of bell-jar structure, the outer wall of brake disc 9 and be formed with gear tongue 9a, gear tongue 9a is constituted
The anti-rotation structure of brake disc 9, gear tongue 9a is used to limit 9 turns of brake disc by the chute 6a on the class static component of gear box 6
First end face clutch configuration that is dynamic, being engaged between brake disc 9 and planet carrier 5 provided with end face tooth；The elastic force of loading spring 8
For departing from the first end face clutch configuration between brake disc 9 and planet carrier 5；The wheel for inputting 1 passes through Turbo Flora
Bond structure is connected with input shaft 2, and the hand of spiral and angle of the helical spline structure have when wheel for inputting 1 is rotated forward, defeated
Enter the movement tendency that 1 pair of loading spring 8 of wheel is formed with compression-loaded spring 8, when input torque increases to setting value, to input
Wheel 1 overcomes the elastic force of loading spring 8, is combined the first end face clutch configuration between brake disc 9 and planet carrier 5；
When wheel for inputting 1 is inverted, wheel for inputting 1 passes through the locking nut 2a that is screwed togather on input shaft 2.Speed-change control device is used in input shaft
When 2 input torques increase to setting value, the planet carrier 5 formation is braked.
Wherein, output wheel 7 is located inside the bell jar of brake disc 9, described first be provided between brake disc 9 and planet carrier 5
End face clutch structure is located at the end of planet carrier 5, and the bell jar wall of brake disc 9, which is provided with, to be used to receive and the formation power of output wheel 7
The power of transmission holds the gap for passing part.
The anti-rotation structure of brake disc 9 can also be the anti-rotation groove being located on the outer wall of brake disc 9 in the present embodiment, with by becoming
Antirotation keys or stop pin limitation brake disc 9 on the static structure of the fast class of box body 6 are rotated.
In the present embodiment, expert's star-wheel 4 and layman's star-wheel 4a are dual gear structure, and the two can also be independent knot certainly
Two gears of structure, when two gears using absolute construction, the two passes through the component of spline housing class the 3rd formation synchronous axial system
Attachment structure, the two by spline housing be set with planet carrier 5 axle journal on.
Loading spring 8 in this implementation can also be substituted using cylindrically coiled spring.
Embodiment 2 is referring to Fig. 2, a kind of planet differential variable-speed shaft, including drives the input shaft 2 of rotation by wheel for inputting 1, input
Axle 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, the and of planet carrier 5
The output wheel 7 of output end is constituted, sun gear 3 is fixedly and coaxially connected on input shaft 2；Planetary gear is rotatably located at planet carrier
On 5, planetary differential is connected with speed-change control device；Wherein, planet carrier 5 is sleeved on the stage casing of input shaft 2；7 sets of output wheel
On a shaft part of the front end of input shaft 2, so as to avoid the bell jar of brake disc 9 from blocking, it is not required to set on the bell jar wall of brake disc 9
The gap of part is passed for receiving the power with the formation power transmission of output wheel 7 to hold；Sun gear 3 be located at planet carrier 5 and output wheel 7 it
Between.
Remaining structure of the present embodiment is same as Example 1, will not be repeated here.
Embodiment 3 is referring to Fig. 3, Fig. 4, a kind of planet differential variable-speed shaft, including drives by wheel for inputting 1 input shaft 2 of rotation,
Input shaft 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, planet carrier
5 are fixedly and coaxially connected on input shaft 2 with the output wheel 7 for constituting output end, sun gear 3；Planetary gear is rotatably located at row
In carrier 5, planetary differential is connected with speed-change control device；Wherein, output wheel 7 is by input part 71 and outlet end part 72
Composition, outlet end part 72 is located at the front end of input part 71, and input part 71 is in the empty set of bell-jar on transition sleeve 10
And engaged with layman's star-wheel 4a, transition sleeve 10 is coaxially rotatably sleeved on input shaft 2, transition sleeve 10 and the output
End part 72, which is formed, to be fixedly and coaxially connected, and end face disk 11 has also been fixedly and coaxially connected on transition sleeve 10, and end face disk 11 is located at input
Hold between part 71 and the sun gear 3 and in the bell jar of input part 71；On the axle journal of the input part 71
Helical spline set 12 is combined with by helical spline, helical spline set 12 is connected with one and filled to its braking for applying frictional resistance
Put；Helical spline set 12 with forming the second end face clutch that end face tooth is engaged respectively between outlet end part 72 and end face disk 11
Device structure, two second end face clutch configurations are only used for input part 71 and drive output end by helical spline set 12 respectively
Part 72 is synchronous to be rotated forward and synchronous reversion；Helical spline set 12, which is located on the end face in the direction of end face disk 11, is formed with multiple circles
Zhou Junbu engagement pawl 12a；Provided with multiple hollow outs passed through for engagement pawl 12a at the top of the bell jar of the input part 71
Hole；Second end face clutch configuration formation between the helical spline set 12 and end face disk 11 is in engagement pawl 12a free end
With on the corresponding end face of end face disk 11.
Wherein, brake apparatus includes the C-shaped collar 24 with collar handle 24a, and the C-shaped collar 24 is embraced by C-shaped clamping part
Hold in helical spline set 12 provided with annular groove；C-shaped collar 24 is provided with the collar handle 24a of U-shaped, the collar handle 24a free end of U-shaped two
Corresponding with the free end of C-shaped two of C-shaped collar 24 to be fixedly connected, collar handle 24a is used to prevent C-shaped collar by gear box 6
24 cover 12 synchronous axial systems with helical spline.
Remaining structure of the present embodiment is same as Example 2, will not be repeated here.
Brake apparatus in the present embodiment can be substituted using following scheme, and referring to Figure 13, brake apparatus includes and Turbo Flora
Key covers the brake shoe 26 of periphery frictional connection, and brake shoe 26 is connected to static brake by the way that brake spring 27 is telescopic
On support 28.
Embodiment 4 is referring to Fig. 5, a kind of planet differential variable-speed shaft, including drives the input shaft 2 of rotation by wheel for inputting 1, input
Axle 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, the and of planet carrier 5
The output wheel 7 of output end is constituted, sun gear 3 is fixedly and coaxially connected on input shaft 2；Planetary gear is rotatably located at planet carrier
On 5, planetary differential is connected with speed-change control device；Wherein, the planet carrier 5 is sleeved on the stage casing of input shaft 2, planet carrier
End face disk 5a is formed with the middle part of 5 sides；The output wheel 7, which is located at, to be sleeved on a shaft part of the front end of input shaft 2；The sun
Wheel 3 is located between planet carrier 5 and output wheel 7；The brake disc 9 is arranged on inside the wheel for inputting 1 of support holder structure, brake disc 9
Anti-rotation structure stretched out by the side of wheel for inputting 1, the end face disk 5a of brake disc 9 and planet carrier 5 forms the first end face clutch
Structure.
Remaining structure of the present embodiment is same as Example 2, will not be repeated here.
Embodiment 5 is referring to Fig. 6, a kind of planet differential variable-speed shaft, including drives the input shaft 2 of rotation by wheel for inputting 1, input
Axle 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, the and of planet carrier 5
The output wheel 7 of output end is constituted, sun gear 3 is fixedly and coaxially connected on input shaft 2；Planetary gear is rotatably located at planet carrier
On 5, planetary differential is connected with speed-change control device；Wherein, the speed-change control device includes being connected to the both sides of wheel for inputting 1
Two balancing springs 13, the other end of two balancing springs 13 is respectively by the axle journal and locking nut 2a of input shaft 2 with inputting
Axle 2 is connected；Rotatable be set with brake disc 9, the outer wall of brake disc 9 is formed with gear tongue 9a, the gear tongue 9a structures on wheel for inputting 1
Into the anti-rotation structure of brake disc 9, gear tongue 9a is used to limit brake disc 9 by the chute 6a on the class static component of gear box 6
Rotate, the end face clutch structure that end-tooth is engaged is respectively formed between brake disc 9 and the two sides of planet carrier 5；Two equilibrium bombs
Spring 13 is used to, when the input torque of wheel for inputting 1 is less than setting value, make two end face clutch knots of brake disc 9 and planet carrier 5
Structure is in released state；The wheel for inputting 1 is connected by helical spline structure with input shaft 2, the spiral of the helical spline structure
Angle has when wheel for inputting 1 is by setting rotation, and one in two balancing springs 13 of wheel for inputting 1 pair is formed with the compression balance
The movement tendency of spring 13, so that when input torque increases to setting value, wheel for inputting 1 overcomes the elastic force of balancing spring 13, makes
A corresponding end face clutch structure between brake disc 9 and planet carrier 5 is combined.
Remaining structure of the present embodiment is same as Example 2, will not be repeated here.
Embodiment 6 is referring to Fig. 7~12, a kind of planet differential variable-speed shaft, including drives by wheel for inputting 1 input shaft 2 of rotation,
Input shaft 2 is provided with the planetary differential of Bevel Gear Drive, and the planetary differential includes sun gear 3, planetary gear, planet carrier
5 are rotatably located on planet carrier 5 with the output wheel 7 for constituting output end, planetary gear, and planetary differential is connected with speed Control
Device；Sun gear 3 is fixedly and coaxially connected on input shaft 2；Planetary gear is made up of expert's star-wheel 4 and layman's star-wheel 4a, expert
Star-wheel 4 and layman's star-wheel 4a are in the attachment structure of synchronous axial system, and expert's star-wheel 4 is engaged with sun gear 3, layman's star-wheel 4a with it is described
The input engagement of output wheel 7；The planet carrier 5 and output wheel 7 are coaxially rotatably sleeved on input shaft 2；Speed change control
Device processed is used for when the rotating speed of input shaft 2 reaches setting value, releases the braking to the planet carrier 5.
Wherein, wheel for inputting 1 is fixedly connected on the input shaft 2, and in tubular construction, tubular input shaft 2 is only for the input shaft 2
It is rotatably coupled in fixing axle 15；Speed-change control device includes the brake block 16 that connection is only may move in fixing axle 15, should
Brake block 16 and the planet carrier 5 formation end face clutch structure, are provided with Self-resetting spring between brake block 16 and input shaft 2
17, the elastic force of Self-resetting spring 17 is used to combined the end face clutch structure between brake block 16 and planet carrier 5；It is described defeated
Enter to be also associated with multiple centrifugal-blocks 18 of circumference uniform distribution on axle 2, multiple centrifugal-blocks 18 are used to reach setting value in the rotating speed of input shaft 2
When, depart from the end face clutch structure between brake block 16 and planet carrier 5.Brake block 16 includes 7 words of two circumference uniform distributions
Shape pawl, 7 font horizontal segments and the formation end face clutch structure of planet carrier 5 of brake block 16,7 fonts of brake block 16 are vertical
Section is slidably fitted in the keyway that fixing axle 15 is provided with, and 7 font vertical section lower ends of brake block 16 are formed with ring flange 16a, system
7 font horizontal segments and ring flange 16a distribution planet carrier 5 both sides of motion block 16；The Self-resetting spring 17 passes through ring flange 16a
Side be connected with the input shaft 2, ring flange 16a opposite side is connected with the centrifugal-block 18.7 font water of brake block 16
Flat section is located at the front end of input shaft 2；Wheel for inputting 1 is located at the rear end of input shaft 2；Output wheel 7 is located between planet carrier 5 and wheel for inputting 1；System
The ring flange 16a that 7 font vertical section lower ends of motion block 16 are formed is located at the rear of output wheel 7 in fixing axle 15；Centrifugal-block 18 leads to
Cross on the centrifugal-block support 19 being fixedly connected on the trailing flank of wheel for inputting 1；The ring flange 16a of brake block 16 and the centrifugation
Plane bearing 14 is provided between block 18.
The 7 font pawls of the present embodiment can also set three concrete conditions or four according to physical dimension, strength of materials etc.
It is individual.
Embodiment 7, referring to Figure 13, a kind of planet gearing system, including drive by large fluted disc 20 vehicle drive axle of rotation
With differential mechanism, large fluted disc 20 engages to form dynamic with the output end teeth portion of the output wheel 7 of the planet differential variable-speed shaft described in embodiment 1
Power transitive relation, the gap that a part for large fluted disc 20 is provided with by the bell jar wall of brake disc 9 gos deep into the bell jar of brake disc 9
Engaged with the output end tooth of output wheel 7 in portion.
Wherein, the differential casing of vehicle drive axle differential mechanism is made up of left housing 21 and right shell 22；In large fluted disc 20
Portion's hub portion part is rotatably sleeved in left housing 21, and another part is rotatably sleeved on large fluted disc 20；Large fluted disc
The second helical spline set 23 is combined with by helical spline in 20 central hub, the second helical spline set 23 is connected with one to its
Apply the second brake apparatus of frictional resistance；End face is formed respectively between second helical spline set 23 and left housing 21 and right shell 22
3rd end-engaging clutch structure of tooth engagement, two the 3rd end-engaging clutch structures are only used for large fluted disc 20 and led to respectively
Crossing two helical splines set 23 drives the differential casing of the vehicle drive axle differential mechanism synchronously to rotate forward and synchronous reversion；Second
Helical spline set 23 is located at the clutch pawl 23a that multiple circumference uniform distributions are formed with the end face in the web direction of large fluted disc 20；Institute
The web of large fluted disc 20 is stated provided with multiple hollow holes passed through for clutch pawl 23a；Second helical spline covers 23 and big
The 3rd end-engaging clutch structure between the right shell 22 of the web respective side of fluted disc 20, is formed in clutch pawl 23a free end
With on the corresponding end face of right shell 22.
Wherein, brake apparatus includes the C-shaped collar 24 with collar handle 24a, and the C-shaped collar 24 is embraced by C-shaped clamping part
Hold in the second helical spline set 23 provided with annular groove；C-shaped collar 24 is provided with the collar handle 24a of U-shaped, and collar handle 24a U-shaped two is certainly
It is fixedly connected by end is corresponding with the free end of C-shaped two of C-shaped collar 24, collar handle 24a is used to prevent C-shaped by gear box 6
Collar 24 covers 23 synchronous axial systems with the second helical spline.
Brake apparatus in the present embodiment can be substituted using following scheme, and referring to Figure 13, brake apparatus includes and Turbo Flora
Key covers the brake shoe 26 of periphery frictional connection, and brake shoe 26 is connected to static brake by the way that brake spring 27 is telescopic
On support 28.
In the present embodiment large fluted disc 20 can also with embodiment 2~6 any one planet differential variable-speed shaft output wheel 7 it is defeated
Go out end tooth portion to engage to form power transmission relationship.But when forming power transmission relationship with the output wheel 7 of embodiment 3, car can be formed
Advance retreat transport condition between the two-stage changed buffer, further reduction vehicle running state transitional impact.
Preferred embodiment of the invention described in detail above.It should be appreciated that one of ordinary skill in the art without
Need creative work just can make many modifications and variations according to the design of the present invention.Therefore, all technologies in the art
Personnel are available by logical analysis, reasoning, or a limited experiment on the basis of existing technology under this invention's idea
Technical scheme, all should be in the protection domain being defined in the patent claims.
Claims (1)
1. a kind of planet differential variable-speed shaft, including the input shaft (2) rotated is driven by wheel for inputting (1), input shaft (2) is provided with circle
The planetary differential of Bevel Gear Transmission, the planetary differential includes sun gear (3), planetary gear, planet carrier (5) and constitutes output
The output wheel (7) at end, planetary gear is rotatably located on planet carrier (5), and planetary differential is connected with speed-change control device；Its
It is characterised by, the sun gear (3) is fixedly and coaxially connected on input shaft (2)；The planetary gear is by expert's star-wheel (4) and outside
Planetary gear (4a) is constituted, and expert's star-wheel (4) and layman's star-wheel (4a) are in the attachment structure of synchronous axial system, expert's star-wheel (4) and too
Sun wheel (3) engagement, layman's star-wheel (4a) is engaged with the input of the output wheel (7)；The planet carrier (5) and output wheel (7)
Coaxially rotatably it is sleeved on input shaft (2)；The speed-change control device is used to increase in wheel for inputting (1) input torque
During setting value, the planet carrier (5) formation is braked；Or when input shaft (2) rotating speed reaches setting value, release to the row
The braking of carrier (5)；
The speed-change control device includes the loading spring (8) being connected between the axle journal of wheel for inputting (1) and input shaft (2), should
Loading spring (8) to use and be rotatably connected with brake disc (9) on cylindrically coiled spring, wheel for inputting (1), in the brake disc (9)
The anti-rotation structure that its rotation is limited by static component is formed with, is engaged between brake disc (9) and planet carrier (5) provided with end face tooth
First end face clutch configuration；Gear tongue (9a) is formed with the outer wall of the brake disc (9), the gear tongue (9a) constitutes brake disc
(9) anti-rotation structure, gear tongue (9a) is used to limit brake disc by the chute (6a) on gear box (6) class static component
(9) rotate；The elastic force of loading spring (8) is used to make the first end face clutch between brake disc (9) and planet carrier (5)
Structure departs from；The wheel for inputting (1) is connected by helical spline structure with input shaft (2), the spiral side of the helical spline structure
Have to angle when wheel for inputting (1) is rotated forward, wheel for inputting (1) is formed with compression-loaded spring (8) to loading spring (8)
Movement tendency, so that when input torque increases to setting value, wheel for inputting (1) overcomes the elastic force of loading spring (8), makes braking
The first end face clutch configuration between disk (9) and planet carrier (5) is combined；
The brake disc (9) is in bell-jar structure, the first end face clutch being provided between brake disc (9) and planet carrier (5)
Device structure is located at planet carrier (5) end；The planet carrier (5) is sleeved on the stage casing of input shaft (2)；Output wheel (7) set
On a shaft part of input shaft (2) front end；The sun gear (3) is located between planet carrier (5) and output wheel (7)；
The output wheel (7) is made up of input part (71) and outlet end part (72), and outlet end part (72) is located at input
End part (71) front end, input part (71) in bell-jar empty set on transition sleeve (10) and with layman's star-wheel (4a)
Engagement, transition sleeve (10) is coaxially rotatably sleeved on input shaft (2), transition sleeve (10) and the outlet end part (72) shape
Into being fixedly and coaxially connected, end face disk (11) is also fixedly and coaxially connected on transition sleeve (10), end face disk (11) is located at input end
Divide between (71) and the sun gear (3) and in the bell jar of input part (71)；The axle of the input part (71)
Helical spline set (12) is combined with by helical spline on neck, helical spline set (12) is connected with one and applies frictional resistance to it
Brake apparatus；The brake apparatus includes the C-shaped collar (24) with collar handle (24a), and the C-shaped collar (24) passes through C clamp
Clasp in helical spline set (12) provided with annular groove in the portion of holding；C-shaped collar (24) is provided with the collar handle (24a) of U-shaped, collar handle
The free end of U-shaped two of (24a) is corresponding with the free end of C-shaped two of C-shaped collar (24) to be fixedly connected, and collar handle (24a) is used to pass through
Gear box (6) prevents C-shaped collar (24) with helical spline set (12) synchronous axial system；
The helical spline set (12) forms what end face tooth was engaged respectively between outlet end part (72) and end face disk (11)
Second end face clutch configuration, two second end face clutch configurations are only used for input part (71) by helical spline respectively
Covering (12) drives outlet end part (72) synchronously to rotate forward and synchronous reversion；Helical spline set (12) is located at the end face disk (11) side
To end face on be formed with the engagement pawls (12a) of multiple circumference uniform distributions；Provided with many at the top of the bell jar of the input part (71)
The individual hollow hole passed through for engagement pawl (12a)；Second end face between the helical spline set (12) and end face disk (11) from
Clutch structure formation the free end of engagement pawl (12a) with the corresponding end face of end face disk (11).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710342832.5A CN106958641B (en) | 2015-06-02 | 2015-06-02 | Planet differential variable-speed shaft |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510294119.9A CN104913021B (en) | 2015-06-02 | 2015-06-02 | A kind of planet differential variable-speed shaft and speed change system |
| CN201710342832.5A CN106958641B (en) | 2015-06-02 | 2015-06-02 | Planet differential variable-speed shaft |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510294119.9A Division CN104913021B (en) | 2015-06-02 | 2015-06-02 | A kind of planet differential variable-speed shaft and speed change system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106958641A true CN106958641A (en) | 2017-07-18 |
| CN106958641B CN106958641B (en) | 2019-04-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710346791.7A Pending CN107228175A (en) | 2015-06-02 | 2015-06-02 | Automobile planet differential variable-speed shaft |
| CN201710342832.5A Active CN106958641B (en) | 2015-06-02 | 2015-06-02 | Planet differential variable-speed shaft |
| CN201510294119.9A Active CN104913021B (en) | 2015-06-02 | 2015-06-02 | A kind of planet differential variable-speed shaft and speed change system |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710346791.7A Pending CN107228175A (en) | 2015-06-02 | 2015-06-02 | Automobile planet differential variable-speed shaft |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510294119.9A Active CN104913021B (en) | 2015-06-02 | 2015-06-02 | A kind of planet differential variable-speed shaft and speed change system |
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| CN (3) | CN107228175A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107487711A (en) * | 2017-09-08 | 2017-12-19 | 芜湖市长江起重设备制造有限公司 | A kind of OTC's trolley walking planetary gear differential steering mechanism |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105276096A (en) * | 2015-11-23 | 2016-01-27 | 中国航空动力机械研究所 | Planetary reduction mechanism |
| CN107504134A (en) * | 2017-09-18 | 2017-12-22 | 彭震远 | Gear and speed changer |
| CN107676570B (en) * | 2017-11-02 | 2023-09-01 | 西安石油大学 | Self-adaptive pipeline robot under complex working condition |
| CN110186677A (en) * | 2019-06-19 | 2019-08-30 | 苏州众源测试技术有限公司 | A kind of universal differential mechanism impact gear-box |
| CN112413065B (en) * | 2020-12-07 | 2024-07-23 | 吴佳妮 | Meshing type differential speed change structure |
| CN112871349B (en) * | 2021-01-08 | 2022-08-26 | 郑州铁路职业技术学院 | Environment-friendly kitchen garbage disposer and vibrating device with self-cleaning ability |
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| CN200978937Y (en) * | 2006-11-10 | 2007-11-21 | 湖北万山宏业汽车零部件有限公司 | Modified jaw type differential gear |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN104913021B (en) | 2017-06-30 |
| CN106958641B (en) | 2019-04-19 |
| CN107228175A (en) | 2017-10-03 |
| CN104913021A (en) | 2015-09-16 |
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Effective date of registration: 20190312 Address after: 325000 No. 1 Park Road, Xin Ao Industrial Park, Hongqiao Town, Yueqing, Wenzhou, Zhejiang Applicant after: WENZHOU SHENYI SHAFT INDUSTRIES Co.,Ltd. Address before: 404300 No. two, group two, along stream village, Wuyang Town, Zhongxian, Chongqing Applicant before: Hu Bing |
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Denomination of invention: Planetary differential transmission shaft Effective date of registration: 20221103 Granted publication date: 20190419 Pledgee: Wenzhou Financing Guarantee Co.,Ltd. Pledgor: WENZHOU SHENYI SHAFT INDUSTRIES Co.,Ltd. Registration number: Y2022110000296 |