CN106958641B - Planet differential variable-speed shaft - Google Patents
Planet differential variable-speed shaft Download PDFInfo
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- CN106958641B CN106958641B CN201710342832.5A CN201710342832A CN106958641B CN 106958641 B CN106958641 B CN 106958641B CN 201710342832 A CN201710342832 A CN 201710342832A CN 106958641 B CN106958641 B CN 106958641B
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- Prior art keywords
- wheel
- planet carrier
- input shaft
- inputting
- face
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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 shafts, variable-speed shaft includes the input shaft that rotation is driven by wheel for inputting, input shaft is equipped 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；By forming in the inner planets round and outer planet round of the connection rotated synchronously, inner planets round is engaged with sun gear and output wheel planetary gear respectively with outer planet round；Planetary differential be connected with wheel for inputting input torque increase to setting value or reach set revolving 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 with the speed change axis connection.The invention has the advantages that structure is simple, manufacture is easy；Compact-sized, long service life.
Description
The application is a divisional application, and parent application number corresponding to the divisional application is 201510294119.9, female
A kind of entitled planet differential variable-speed shaft and speed change system of case application, the applying date of parent application are 2015-06-02.
Technical field
The present invention relates to a kind of planet differential speed changing structure, in particular to a kind of planet differential variable-speed shaft.
Background technique
Planetary differential speed change is the differential principle using differential mechanism, by control device to the differential shape of planetary differential
State carries out control realization.But structure is complicated for existing control mechanism, processing difficulties, and manufacturing cost is high.In addition, existing electric vehicle is logical
It is all often the driving status conversion realizing vehicle by control motor positive and inverse and moving forward and backward, but due to vehicle in conversion process
Effect of inertia, the impact for be easy to causeing vehicle running state to convert.For this reason, it may be necessary to be further improved.
Summary of the invention
The first purpose of the object of the invention provides a kind of planet differential variable-speed shaft, the change aiming at the deficiencies in the prior art
Fast axis reduces manufacture difficulty and cost by simplified control apparatus structure.It includes row that the second object of the present invention, which is to provide a kind of,
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 that the first purpose, the present invention adopt the following technical scheme that.
A kind of planet differential variable-speed shaft, the input shaft including driving rotation by wheel for inputting, input shaft are equipped with conical gear
The planetary differential of transmission, the planetary differential include the output wheel of sun gear, planetary gear, planet carrier and composition 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 of inner planets round and outer planet round, and inner planets round is with outer planet round in synchronous
The connection structure of rotation, inner planets round are engaged with sun gear, and outer planet round is engaged with the input terminal 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, the planet carrier is formed and 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, first is that being turned round by input
Square control, second is that being controlled by input speed；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 planets round, and interior outer planet round retinue carrier is public
Turn, and drives output wheel and sun gear to form synchronous rotation by outer planet round, and then rotate synchronously with input shaft；In wheel for inputting
When input torque reaches setting value, speed-change control device forms the braking to planet carrier, at this point, outer planet round is dynamic in sun gear band
Synchronous rotation, outer planet round are driven output wheel rotation, are formed using the gear ratio between sun gear, interior outer planet round and output wheel
Slow down, output wheel is lower than the input shaft rotating speed with revolving speeds such as sun gears, and speed change is realized by way of input torque to realize.
When using input speed control, when input shaft rotating speed is lower than setting value, planet carrier is in on-position, exports wheel speed
Lower than the input shaft rotating speed with the revolving speeds such as sun gear, when input shaft rotating speed reaches setting value, planet carrier on-position is released from,
Sun gear drives planet carrier rotation, interior outer planet round with planetary carrier revolution by inner planets round, and is driven and exported by outer planet round
Wheel is formed with sun gear and is rotated synchronously, and then is rotated synchronously with input shaft.
Preferably, the speed-change control device includes the loading spring being connected between wheel for inputting and the axle journal of input shaft,
It is rotatably connected with brake disc on wheel for inputting, the anti-rotation structure for limiting its rotation by static component is formed in the brake disc,
The first end face clutch configuration of an end face tooth engagement is equipped between brake disc and planet carrier；The elastic force of loading spring is for making
The first end face clutch configuration between brake disc and planet carrier is detached from；The wheel for inputting by helical spline structure with it is defeated
Enter axis connection, the hand of spiral and angle of the helical spline structure have when wheel for inputting rotates in the forward direction, and wheel for inputting is to load bullet
Spring is formed with the movement tendency of compression-loaded spring, with when input torque increases to setting value, wheel for inputting overcomes loading spring
Elastic force, make brake disc in conjunction with the first end face clutch configuration between planet carrier.
In the prior art, helical spline fit structure has following fundamental characteristics, is mainly used for transmitting torque, have simultaneously
There is the corresponding characteristic moved on a large scale of Small-angle Rotation, therefore, the helix angle for helical spline is all inevitable larger, can pass through
Push cooperation in the mobile realization spline housing of spline housing of splined shaft or splined shaft rotation.This programme utilizes helical spline fit structure
Afore-mentioned characteristics, when wheel for inputting rotates forward, and when load torque and smaller corresponding input torque, wheel for inputting is rotated forward to loading spring shape
At compressing force 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 discrete state under the effect of loading spring pretightning force, to form the free state of planet carrier, output wheel and sun gear
It is rotated synchronously with input shaft.When wheel for inputting rotates forward and input torque reaches setting value, wheel for inputting rotating forward forms loading spring
Compressing force overcome the pretightning force of loading spring, and make at the first end face clutch configuration between brake disc and planet carrier
It in bonding state, is braked at this point, brake disc forms planet carrier, realizes speed change by way of input torque to realize.Its
Structure is simple, manufacturing cost and use cost is low, and motor output torque is made full use of to change automatically with the variation of load torque
The fluid drive of characteristic realization variable-speed shaft.
It is further preferred that the brake disc is in bell-jar structure, described first be equipped between brake disc and planet carrier
End face clutch structure is located at planet carrier end.To be formed in the control for brake of planet carrier end, braking is 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
Between wheel for inputting and planet carrier, output wheel is sleeved on input shaft and is located on a shaft part at sun gear rear and is located at institute sun wheel
It states in the bell jar of brake disc, the bell jar wall of brake disc is equipped with for receiving the power for forming power transmitting with output wheel to hold biography part
Gap.To facilitate laying of the variable-speed shaft in speed change system or gearbox, especially suitable for vehicle drive axle differential mechanism
Connection.
Still more preferably, the planet carrier is sleeved on the middle section of input shaft；The output wheel is sleeved on input shaft
On one shaft part of front end；The sun gear is between planet carrier and output wheel.Gap is set to avoid in brake disc, is suitable for
Lay the variable-speed shaft with positive and negative rotation Buffer output.
Still further preferably, the output wheel is grouped as by input terminal part and output end, and outlet end part is located at
Input end sub-headend, input terminal part are engaged on transition sleeve and with the outer planet round in the empty set of bell-jar, transition sleeve
It is coaxially rotatably sleeved on input shaft, transition sleeve is fixedly and coaxially connected with outlet end part formation, on transition sleeve also
It has been fixedly and coaxially connected end face disk, clock of the end face disk between input terminal part and the sun gear and positioned at input terminal part
In cover；Helical spline set is combined with by helical spline on the axle journal of the input terminal part, helical spline set be connected with one to
Its brake apparatus for applying frictional resistance；An end-tooth is respectively formed 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 terminal part respectively and pass through helical spline
Set drives outlet end part is synchronous to rotate forward and synchronous reversion；Helical spline set, which is located on the end face in the end face disk direction, to be formed with
The engagement pawl of multiple circumference uniform distributions；Multiple hollow holes passed through for engagement pawl are equipped at the top of the bell jar of the input terminal part；
Second end face clutch configuration between helical spline set and end face disk is formed in free end and the end face disk of engagement pawl
In corresponding end surface.By removing output wheel at input terminal part and outlet end part, and helical spline is formed between
The two-way of set is more than clutch configuration, so that the output of differential portion is when rotating and reverse, to pass through the mobile shape of screw-casing
At the time interval converted therebetween.For vehicle, when can effectively reduce the conversion of vehicle forward-reverse driving status, because of inertia
And impact is brought, impact is brought because of inertia to reduce, and plays good buffer function.
In double rolling key clutch structure above-mentioned, input terminal partial turn, helical spline is covered in brake apparatus application
Frictional resistance effect is lower to form the mobile comprehensive movement of certain relative rotation and axis with input terminal part, moving direction by
The hand of spiral and the rotation direction of input terminal part determine that direction of rotation and input end split-phase are same.Due to two second ends
Face clutch configuration be only respectively used to helical spline set directly drive or by transition sleeve drive outlet end part it is synchronous rotate forward with
Synchronous reversion, therefore, in input terminal partial turn, two give one of second end face clutch configuration to be in discrete state, separately
One is in bonding state.When setting the rotating forward of input terminal part for the hand of spiral, helical spline set directly drives output end
Part is synchronous to be rotated forward, when outlet end part revolving speed is greater than input terminal part and helical spline set revolving speed, outlet end part and spiral shell
Between rotation spline housing the and end face clutch structure is in and surmounts state., it can be achieved that the advance of vehicle is slided when for vehicle.
Preferably, the planet carrier is sleeved on the middle section 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 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 be further decreased, is convenient for
It is laid in gearbox.
The speed-change control device includes two balancing springs for being connected to wheel for inputting two sides, two balancing springs it is another
End passes through the axle journal of input shaft and locking nut and input axis connection respectively；Brake disc is rotatably set on wheel for inputting, it should
Brake disc is limited by static component and is rotated, and brake disc is respectively formed the clutch knot in conjunction with end face between the two sides of planet carrier
Structure；Two balancing springs are used to make two end faces of brake disc and planet carrier when the input torque of wheel for inputting is less than setting value
Clutch configuration is in discrete state；The wheel for inputting passes through helical spline structure and input axis connection, the helical spline structure
Spiral angle have when wheel for inputting is by setting rotation, wheel for inputting is formed with compression to one in two balancing springs, and this is flat
The movement tendency of weighing apparatus spring makes to brake so that when input torque increases to setting value, wheel for inputting overcomes the elastic force of balancing spring
Disk is in conjunction with the corresponding end face clutch structure between planet carrier.
Preferably, the speed-change control device includes two balancing springs for being connected to wheel for inputting two sides, two equilibrium bombs
The other end of spring pass through respectively input shaft axle journal and locking nut and input axis connection；System is rotatably set on wheel for inputting
Moving plate, the brake disc by static component limit rotate, brake disc be respectively formed between the two sides of planet carrier in conjunction with end face from
Clutch structure；Two balancing springs are used to make the two of brake disc and planet carrier when the input torque of wheel for inputting is less than setting value
A end face clutch structure is in discrete state；The wheel for inputting passes through helical spline structure and input axis connection, 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, with when input torque increases to setting value, wheel for inputting overcomes the elastic force of balancing spring,
Make brake disc in conjunction with the corresponding end face clutch structure between planet carrier.Two balancing springs make wheel for inputting in positive and negative rotation
Input torque when being less than setting value, planet carrier be in free state, output wheel in and the rotary regimes such as input shaft；Defeated
When entering forward and reverse input of wheel and reaching 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 is formed and is braked, at this point, output wheel passes through outer planet round rotation band
Turn is dynamic, to realize speed regulation purpose.I.e. this programme can realize positive and negative rotation speed change, it can be achieved that two kinds of speed when for vehicle
Reversing.
Preferably, 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 moved in fixing axle, should
Brake block and the planet carrier form end face clutch structure, and Self-resetting spring, Self-resetting are equipped between brake block and input shaft
The elastic force of spring is for making brake block in conjunction with the end face clutch structure between planet carrier；It is also connected on 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 be detached from.When input shaft rotating speed is lower than setting value, Self-resetting spring makes brake block and planet
End face clutch structure between frame combines, and planet carrier is rotated by limitation, and output wheel drives rotation by outer planet round rotation, reaches
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 is detached from, and planet carrier is in free state, and the rotational speeds such as output wheel and input shaft are turned 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 and planet carrier form end face clutch structure, and 7 font vertical sections of brake block are slidably fitted in what fixing axle was equipped with
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 two sides；Side and the input axis connection, the other side of ring flange and institute of the Self-resetting spring by ring flange
State centrifugal-block connection.It is convenient to be laid in gearbox to effectively reduce the radial dimension of variable-speed shaft, phase and speed Control structure
Simply, reliable 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 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 reasonable topology layout, further increases and laid in gearbox
Convenience.
Still further preferably, the centrifugal-block passes through the centrifugal-block bracket that is fixedly connected on the wheel for inputting trailing flank
On；Plane bearing is equipped between the ring flange of the brake block and the centrifugal-block.To make full use of the spatial position 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 prolonged the service life.
To realize that the second purpose, the present invention adopt the following technical scheme that.
A kind of planet gearing system, the vehicle drive axle differential mechanism including driving rotation by large fluted disc, large fluted disc and reality
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, due to using aforementioned planet differential variable-speed shaft, system passes through vehicle drive axle
It is exported with differential mechanism, the fluid drive suitable for tricycle or four-wheel electro-motive vehicle.Simple using speed-change control device structure,
The low feature of manufacturing cost and use cost, realizes the low cost of vehicle.
Preferably, the differential casing of vehicle drive axle differential mechanism is made of 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 rubs to its application
Wipe the second brake apparatus of resistance；The third of an end face tooth engagement is respectively formed between second helical spline set and left housing and right shell
End-engaging clutch structure, two third end-engaging clutch structures are only used for large fluted disc respectively and pass through two helical spline sets
Drive the differential casing of the vehicle drive axle differential mechanism is synchronous to rotate forward and synchronous reversion；Second helical spline set is located at institute
State the clutch pawl that multiple circumference uniform distributions are formed on the end face in large fluted disc web direction；The web of the large fluted disc is equipped 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
Third end-engaging clutch structure is formed on the free end and left housing or the corresponding end surface of right shell of clutch pawl.
Pass through the second helical spline set and end face tooth engagement knot between large fluted disc and the shell of vehicle drive axle differential mechanism
It is configured to helical spline shell type double rolling key clutch structure.Its working principle and beneficial effect and bidirectional overtaking clutch above-mentioned
Device structure is identical, and details are not described herein.
The invention has the advantages that speed change axle construction is simple, manufacture is easy, overall cost is low；Speed change system is small in size,
Rationally distributed, long service life is suitable for three-wheel and four-wheel electric motor car.
Detailed description of the invention
Fig. 1 is the structural schematic diagram 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 schematic diagram 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 schematic diagram of the embodiment of the present invention 4.
Fig. 6 is the structural schematic diagram of the embodiment of the present invention 5.
Fig. 7 is the structural schematic diagram of the embodiment of the present invention 6.
Fig. 8 is A-A cross-sectional view in Fig. 7 of the present invention.
Fig. 9 is the structural schematic diagram of brake block 16 in the embodiment of the present invention 6.
Figure 10 is the top view of Fig. 9 of the present invention.
Figure 11 is the bottom view of Fig. 9 of the present invention.
Figure 12 is the structural schematic diagram 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.
Specific embodiment
The present invention will be further described below with reference to the drawings, but does not therefore limit the present invention to the implementation
Among example range.
Embodiment 1 is referring to Fig. 1, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1, input
Axis 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, 5 and of planet carrier
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 2 rear end of input shaft, and planet carrier 5 can coaxially turn
Dynamic is sleeved on 2 front end of input shaft, and sun gear 3 is between wheel for inputting 1 and planet carrier 5, the coaxial rotatable suit of output wheel 7
On the shaft part that wheel for inputting 1 is located at 3 rear of sun gear.
Wherein, planetary gear is made of inner planets round 4 and outer planet round 4a, and inner planets round 4 is with outer planet round 4a in synchronous
The connection structure of rotation, inner planets round 4 are engaged with sun gear 3, and outer planet round 4a is engaged with the input terminal of the output wheel 7；Become
Velocity control device includes the loading spring 8 being made of disc spring being connected between wheel for inputting 1 and the axle journal of input shaft 2, wheel for inputting 1
On be rotatably set with the brake disc 9 of bell-jar structure, gear tongue 9a is formed on the outer wall of brake disc 9, which is constituted
The anti-rotation structure of brake disc 9, gear tongue 9a are used to limit 9 turns of brake disc by the sliding slot 6a on 6 class static component of gear box
It is dynamic, the first end face clutch configuration of an end face tooth engagement is equipped between brake disc 9 and planet carrier 5；The elastic force of loading spring 8
For being detached 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 connect with input shaft 2, and the hand of spiral and angle of the helical spline structure have when wheel for inputting 1 rotates in the forward direction, defeated
Enter the movement tendency that 1 pair of loading spring 8 of wheel is formed with compression-loaded spring 8, to input when input torque increases to setting value
Wheel 1 overcomes the elastic force of loading spring 8, makes brake disc 9 in conjunction with the first end face clutch configuration between planet carrier 5；
When wheel for inputting 1 inverts, wheel for inputting 1 passes through the locking nut 2a 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 is formed and is braked.
Wherein, output wheel 7 is located inside the bell jar of brake disc 9, described first be equipped between brake disc 9 and planet carrier 5
End face clutch structure is located at 5 end of planet carrier, and the bell jar wall of brake disc 9, which is equipped with, forms power with output wheel 7 for receiving
The power of transmitting holds the gap for passing part.
The anti-rotation structure of brake disc 9 can also be the anti-rotation groove being located on 9 outer wall of brake disc in the present embodiment, be become with passing through
Antirotation keys or stop pin limitation brake disc 9 in the static building of fast 6 class of box body rotate.
In the present embodiment, inner planets round 4 and outer planet round 4a are dual gear structure, and the two can also be independent knot certainly
Two gears of structure, when using two gears of absolute construction, the two is formed by spline housing class third component and is rotated synchronously
Connection structure, the two is sleeved on the axle journal of planet carrier 5 by spline housing.
Cylindrically coiled spring substitution also can be used in loading spring 8 in this implementation.
Referring to fig. 2, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1 inputs embodiment 2
Axis 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, 5 and of planet carrier
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 middle section of input shaft 2；7 sets of output wheel
On a shaft part of 2 front end of input shaft, so that the bell jar of brake disc 9 be avoided to block, it is not required to be arranged on the bell jar wall of brake disc 9
For receiving the power for forming power transmitting with output wheel 7 to hold the gap of biography part；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, and details are not described herein.
Embodiment 3 is referring to Fig. 3, Fig. 4, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1,
Input shaft 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, planet carrier
5 and 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 row
In carrier 5, planetary differential is connected with speed-change control device；Wherein, output wheel 7 is by input terminal part 71 and outlet end part 72
Composition, outlet end part 72 are located at 71 front end of input terminal part, and input terminal part 71 is in the empty set of bell-jar on transition sleeve 10
And engaged with the outer planet round 4a, transition sleeve 10 is coaxially rotatably sleeved on input shaft 2, transition sleeve 10 and the output
The formation of end part 72 is 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
Between end part 71 and the sun gear 3 and it is located in the bell jar of input terminal part 71；On the axle journal of the input terminal part 71
It is combined with helical spline set 12 by helical spline, helical spline set 12 is connected with a braking dress for applying frictional resistance to it
It sets；The second end face clutch of an end face tooth engagement is respectively formed between helical spline set 12 and outlet end part 72 and end face disk 11
Device structure, two second end face clutch configurations are only used for input terminal part 71 respectively and drive output end by helical spline set 12
Part 72 is synchronous to be rotated forward and synchronous reversion；Helical spline set 12, which is located on the end face in 11 direction of end face disk, is formed with multiple circles
The engagement pawl 12a of Zhou Junbu；Multiple hollow outs passed through for engagement pawl 12a are equipped at the top of the bell jar of the input terminal part 71
Hole；Second end face clutch configuration between the helical spline set 12 and end face disk 11 is formed in the free end of engagement pawl 12a
In the corresponding end surface of end face disk 11.
Wherein, brake apparatus includes the C-shaped retainer ring 24 with retainer ring handle 24a, which is embraced by C-shaped clamping part
It holds and is equipped in annular groove in helical spline set 12；C-shaped retainer ring 24 is equipped with the retainer ring handle 24a of U-shaped, two free end of U-shaped of retainer ring handle 24a
Corresponding with two free end of C-shaped of C-shaped retainer ring 24 to be fixedly connected, retainer ring handle 24a is used to prevent C-shaped retainer ring by gear box 6
24 rotate synchronously with helical spline set 12.
Remaining structure of the present embodiment is same as Example 2, and details are not described herein.
Following scheme substitution can be used in brake apparatus in the present embodiment, 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 bracket 28.
Embodiment 4 is referring to Fig. 5, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1, input
Axis 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, 5 and of planet carrier
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 middle section of input shaft 2, planet carrier
End face disk 5a is formed in the middle part of 5 sides；The output wheel 7, which is located at, to be sleeved on a shaft part of 2 front end of input shaft；The sun
Wheel 3 is 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 1 side of wheel for inputting, 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, and details are not described herein.
Embodiment 5 is referring to Fig. 6, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1, input
Axis 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, 5 and of planet carrier
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 1 two sides of wheel for inputting
Two balancing springs 13, the other end of two balancing springs 13 pass through respectively input shaft 2 axle journal and locking nut 2a and input
Axis 2 connects；It is rotatably set with brake disc 9 on wheel for inputting 1, gear tongue 9a, the gear tongue 9a structure are formed on the outer wall of brake disc 9
At the anti-rotation structure of brake disc 9, keeps off tongue 9a and be used to limit brake disc 9 by the sliding slot 6a on 6 class static component of gear box
Rotation, is respectively formed the end face clutch structure of end face tooth engagement between brake disc 9 and the two sides of planet carrier 5；Two equilibrium bombs
Spring 13 is used to make two end face clutch knots of brake disc 9 Yu planet carrier 5 when the input torque of wheel for inputting 1 is less than setting value
Structure is in discrete state；The wheel for inputting 1 is connect 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 wheel for inputting 1, which is formed with one in two balancing springs 13, compresses the balance
The movement tendency of spring 13 makes so that when input torque increases to setting value, wheel for inputting 1 overcomes the elastic force of balancing spring 13
Brake disc 9 is in conjunction with the corresponding end face clutch structure between planet carrier 5.
Remaining structure of the present embodiment is same as Example 2, and details are not described herein.
Embodiment 6 is referring to Fig. 7~12, a kind of planet differential variable-speed shaft, the input shaft 2 including driving rotation by wheel for inputting 1,
Input shaft 2 is equipped with the planetary differential of Bevel Gear Drive, which includes sun gear 3, planetary gear, planet carrier
5 and the output wheel 7 of output end is constituted, planetary gear is rotatably located on planet carrier 5, 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 of inner planets round 4 and outer planet round 4a, expert
Star-wheel 4 and outer planet round 4a are engaged in the connection structure rotated synchronously, inner planets round 4 with sun gear 3, outer planet round 4a with it is described
The input terminal of output wheel 7 engages；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 2 revolving speed of input shaft 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 moved in fixing axle 15, should
Brake block 16 and the planet carrier 5 form end face clutch structure, and Self-resetting spring is equipped between brake block 16 and input shaft 2
17, the elastic force of Self-resetting spring 17 is for making brake block 16 in conjunction with the end face clutch structure between planet carrier 5；It is described defeated
Enter to be also connected with multiple centrifugal-blocks 18 of circumference uniform distribution on axis 2, multiple centrifugal-blocks 18 are used to reach setting value in 2 revolving speed of input shaft
When, it is detached 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, the 7 font horizontal segments and planet carrier 5 of brake block 16 form end face clutch structure, and 7 fonts of brake block 16 are vertical
Section is slidably fitted in the keyway that fixing axle 15 is equipped with, and 7 font vertical section lower ends of brake block 16 are formed with ring flange 16a, system
The 7 font horizontal segments and ring flange 16a of motion block 16 are distributed in 5 two sides of planet carrier；The Self-resetting spring 17 passes through ring flange 16a
Side connect with the input shaft 2, the other side of ring flange 16a is connect with the centrifugal-block 18.7 font water of brake block 16
Flat section is located at 2 front end of input shaft；Wheel for inputting 1 is located at 2 rear end of input shaft；Output wheel 7 is 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 7 rear of output wheel in fixing axle 15；Centrifugal-block 18 is logical
It crosses on the centrifugal-block bracket 19 being fixedly connected on 1 trailing flank of wheel for inputting；The ring flange 16a of brake block 16 and the centrifugation
Plane bearing 14 is equipped between block 18.
Also three concrete conditions or four can be arranged according to structure size, strength of materials etc. in the 7 font pawls of the present embodiment
It is a.
Embodiment 7, referring to Figure 13, a kind of planet gearing system, the vehicle drive axle including driving rotation by large fluted disc 20
With differential mechanism, large fluted disc 20 engaged with the output end teeth portion of the output wheel 7 of planet differential variable-speed shaft described in embodiment 1 to be formed it is dynamic
A part of power transitive relation, large fluted disc 20 is goed deep into the bell jar of brake disc 9 by the gap that the bell jar wall of brake disc 9 is equipped with
The output end tooth engagement in portion and output wheel 7.
Wherein, the differential casing of vehicle drive axle differential mechanism is made of left housing 21 and right shell 22；In large fluted disc 20
Portion's hub portion a 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；An end face is respectively formed between second helical spline set 23 and left housing 21 and right shell 22
The third end-engaging clutch structure of tooth engagement, it is logical that two third end-engaging clutch structures are only used for large fluted disc 20 respectively
Crossing two helical splines set 23 drives the differential casing of the vehicle drive axle differential mechanism is synchronous 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 on the end face in the 20 web direction of large fluted disc；Institute
The web for stating large fluted disc 20 is equipped with multiple hollow holes passed through for clutch pawl 23a；Second helical spline set 23 with it is big
Third end-engaging clutch structure between the right shell 22 of 20 web respective side of fluted disc, is formed in the free end of clutch pawl 23a
In the corresponding end surface of right shell 22.
Wherein, brake apparatus includes the C-shaped retainer ring 24 with retainer ring handle 24a, which is embraced by C-shaped clamping part
It holds and is equipped in annular groove in the second helical spline set 23；C-shaped retainer ring 24 is equipped with the retainer ring handle 24a of U-shaped, and the U-shaped two of retainer ring handle 24a is certainly
It is fixedly connected by end is corresponding with two free end of C-shaped of C-shaped retainer ring 24, retainer ring handle 24a is used to prevent C-shaped by gear box 6
Retainer ring 24 is rotated synchronously with the second helical spline set 23.
Following scheme substitution can be used in brake apparatus in the present embodiment, 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 bracket 28.
Large fluted disc 20 can also be defeated with any one of embodiment 2~6 planet differential variable-speed shaft output wheel 7 in the present embodiment
Outlet teeth portion engages to form power transmission relationship.But when forming power transmission relationship with the output wheel of embodiment 37, vehicle can be formed
Advance buffered the two-stage converted between driving status is retreated, further decrease vehicle running state transitional impact.
The preferred embodiment of the present invention has been described in detail above.It should be appreciated that those skilled in the art without
It needs creative work according to the present invention can conceive and makes many modifications and variations.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 solution, all should be within the scope of protection determined by the claims.
Claims (1)
1. a kind of planet differential variable-speed shaft, the input shaft (2) including driving rotation by wheel for inputting (1), input shaft (2) are equipped with circle
The planetary differential of Bevel Gear Transmission, the planetary differential include sun gear (3), planetary gear, planet carrier (5) and constitute output
The output wheel (7) at end, planetary gear are rotatably located on planet carrier (5), and planetary differential is connected with speed-change control device；Its
It is characterized in that, the sun gear (3) is fixedly and coaxially connected on input shaft (2)；The planetary gear is by inner planets round (4) and outside
Planetary gear (4a) composition, inner planets round (4) and outer planet round (4a) are in the connection structure rotated synchronously, inner planets round (4) and too
Sun wheel (3) engagement, outer planet round (4a) are engaged with the input terminal 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 in wheel for inputting (1) input torque for increasing to
When setting value, the planet carrier (5) are formed and are braked；Or when input shaft (2) revolving 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 wheel for inputting (1) and the axle journal of input shaft (2), should
Loading spring (8) uses cylindrically coiled spring, brake disc (9) is rotatably connected on wheel for inputting (1), in the brake disc (9)
It is formed with the anti-rotation structure for limiting its rotation by static component, an end face tooth engagement is equipped between brake disc (9) and planet carrier (5)
First end face clutch configuration；Gear tongue (9a) is formed on the outer wall of the brake disc (9), which constitutes brake disc
(9) anti-rotation structure, gear tongue (9a) are used for through sliding slot (6a) limitation brake disc (9) rotation on gear box (6)；Load
The elastic force of spring (8) is for being detached from the first end face clutch configuration between brake disc (9) and planet carrier (5)；Institute
It states wheel for inputting (1) to connect by helical spline structure with input shaft (2), the hand of spiral and angle of the helical spline structure have
When wheel for inputting (1) rotates in the forward direction, wheel for inputting (1) is formed with the movement tendency of compression-loaded spring (8) to loading spring (8),
With when input torque increases to setting value, wheel for inputting (1) overcomes the elastic force of loading spring (8), make brake disc (9) and planet
The first end face clutch configuration between frame (5) combines；
The brake disc (9) is in bell-jar structure, the first end face clutch being equipped 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 middle section 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 of input terminal part (71) and outlet end part (72), and outlet end part (72) is located at input
End part (71) front end, input terminal part (71) in bell-jar empty set on transition sleeve (10) and with the outer planet round (4a)
Engagement, transition sleeve (10) are coaxially rotatably sleeved on input shaft (2), transition sleeve (10) and the outlet end part (72) shape
It at being fixedly and coaxially connected, has also been fixedly and coaxially connected on transition sleeve (10) end face disk (11), end face disk (11) is located at input end
Divide between (71) and the sun gear (3) and is located in the bell jar of input terminal part (71)；The axis of the input terminal part (71)
It is combined with helical spline set (12) on neck by helical spline, helical spline set (12) is connected with one and applies frictional resistance to it
Brake apparatus；The brake apparatus includes the C-shaped retainer ring (24) with retainer ring handle (24a), which passes through C clamp
It clasps in the annular groove of helical spline set (12) in the portion of holding；C-shaped retainer ring (24) is equipped with the retainer ring handle (24a) of U-shaped, retainer ring handle (24a)
Two free end of U-shaped it is corresponding with two free end of C-shaped of C-shaped retainer ring (24) be fixedly connected, retainer ring handle (24a) is for passing through gearbox
Cabinet (6) prevents C-shaped retainer ring (24) from rotating synchronously with helical spline set (12)；
An end face tooth engagement is respectively formed between the helical spline set (12) and 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 terminal part (71) respectively and pass through helical spline
Covering (12) drives outlet end part (72) are synchronous 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；It is equipped at the top of the bell jar of the input terminal part (71) more
A 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 is formed on the free end of engagement pawl (12a) and the corresponding end surface 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 |
|---|---|---|---|
| CN201710342832.5A CN106958641B (en) | 2015-06-02 | 2015-06-02 | Planet differential variable-speed shaft |
| CN201510294119.9A CN104913021B (en) | 2015-06-02 | 2015-06-02 | Planet differential speed change shaft and speed change system |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510294119.9A Division CN104913021B (en) | 2015-06-02 | 2015-06-02 | Planet differential speed change shaft and speed change system |
Publications (2)
| Publication Number | Publication Date |
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| CN106958641A CN106958641A (en) | 2017-07-18 |
| CN106958641B true CN106958641B (en) | 2019-04-19 |
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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 |
| 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 | Planet differential speed change 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 | Planet differential speed change shaft and speed change system |
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276096A (en) * | 2015-11-23 | 2016-01-27 | 中国航空动力机械研究所 | Planetary reduction mechanism |
| 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 |
| 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 | Adaptive pipeline robot under complex working conditions |
| 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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| WO1991016557A1 (en) * | 1990-04-14 | 1991-10-31 | Zahnradfabrik Friedrichshafen Ag | Steering axle with self-locking differential gear |
| US6293891B1 (en) * | 1999-12-23 | 2001-09-25 | Spicer Technologies, Inc. | Limited slip differential clutch pack |
| JP2003207026A (en) * | 2002-01-10 | 2003-07-25 | Tochigi Fuji Ind Co Ltd | Motive power transmission device |
| JP2006348983A (en) * | 2005-06-13 | 2006-12-28 | Fuji Heavy Ind Ltd | Differential unit with differential limiting mechanism |
| US7438661B2 (en) * | 2006-02-15 | 2008-10-21 | Eaton Corporation | Mechanical locking differential lockout mechanism |
| 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 |
| DE102007037676A1 (en) * | 2007-08-10 | 2009-02-12 | Bayerische Motoren Werke Aktiengesellschaft | Differential gear for vehicles, in particular for all-wheel drive vehicles |
| CN101290043B (en) * | 2008-04-18 | 2010-06-02 | 魏家斌 | Gear multilevel speed changer |
| CN201293084Y (en) * | 2008-08-01 | 2009-08-19 | 伊顿公司 | Improved lock stop differential mechanism comprising elastic disc apparatus |
| CN101871529B (en) * | 2010-06-01 | 2012-12-05 | 太原科技大学 | Automatic anti-slip tooth-embedded cone gear differential mechanism |
| TW201217669A (en) * | 2010-10-25 | 2012-05-01 | Sun Race Sturmey Archer Inc | Speed changing apparatus |
| CN203230809U (en) * | 2013-05-04 | 2013-10-09 | 陆天波 | Improved differential mechanism |
| CN103912653A (en) * | 2014-04-18 | 2014-07-09 | 杨洋 | Speed reducing device of torsion sensing differential planet gear system |
| CN204677720U (en) * | 2015-06-02 | 2015-09-30 | 傅元才 | Planet differential variable-speed shaft and speed variator system |
| DE102015223126A1 (en) * | 2015-11-24 | 2017-05-24 | Schaeffler Technologies AG & Co. KG | Differential gear with frictionally coupled power outputs |
-
2015
- 2015-06-02 CN CN201710346791.7A patent/CN107228175A/en active Pending
- 2015-06-02 CN CN201710342832.5A patent/CN106958641B/en active Active
- 2015-06-02 CN CN201510294119.9A patent/CN104913021B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN104913021B (en) | 2017-06-30 |
| CN104913021A (en) | 2015-09-16 |
| CN107228175A (en) | 2017-10-03 |
| CN106958641A (en) | 2017-07-18 |
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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 |
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