CN205745168U - A kind of dual planetary gear mechanical differential - Google Patents
A kind of dual planetary gear mechanical differential Download PDFInfo
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- CN205745168U CN205745168U CN201620460690.3U CN201620460690U CN205745168U CN 205745168 U CN205745168 U CN 205745168U CN 201620460690 U CN201620460690 U CN 201620460690U CN 205745168 U CN205745168 U CN 205745168U
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- planetary gear
- gear set
- groups
- retainer
- overall structure
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Abstract
The utility model discloses a kind of dual planetary gear mechanical differential, including two groups of planetary gear set, each planetary gear set all comprises sun gear, multiple planetary gear and comprises the outer rotor of engagement inner ring, the planetary gear of each planetary gear set engages with the inner ring of corresponding sun gear, outer rotor respectively, and multiple planetary gears of each planetary gear set are connected in outer rotor inner position by retainer；Described sun gear, outer rotor, retainer are three transmission key elements, when a transmission key element in one of them planetary gear set is fixed, then corresponding in another planetary gear set transmission key element is arranged to output shaft, and identical transmission key element correspondence is fixedly connected as a kind of overall structure in two groups of planetary gears, power shaft is the fixed connection structure of one of them transmission key element.This utility model uses the planetary gear of two groups of difference speed reducing ratio can realize large speed ratio to slow down transmission, can meet high pulling torque, the working condition requirement of high rotating speed input simultaneously, and have technique be simple to manufacture, low cost and the high advantage of reliability.
Description
Technical field
This utility model relates to mechanical transmission fields, specifically a kind of dual planetary gear mechanical differential.
Background technology
The high-power reducer with big speed ratio of current industrial use is usually and is made up of plural serial stage, and take up room big, fortune
Turn that stationarity is poor, cost high；And small-power large speed ratio Cycloidal Wheel reductor and harmonic wave speed reducing machine have eccentric shaft mechanism, limit defeated
Entering the raising of rotating speed and the transmission of high pulling torque, it is the biggest that speed reducing ratio is not easy to do.
Utility model content
The technical problems to be solved in the utility model is to provide a kind of dual planetary gear mechanical differential, utilizes two groups of speed reducing ratio
Differ less planetary gear set, it is achieved bigger speed reducing ratio output, the need that input speed is high, transmission moment of torsion is big can be met simultaneously
Ask, and operate steadily.
The technical solution of the utility model is:
A kind of dual planetary gear mechanical differential, including two groups of planetary gear set, each planetary gear set all comprises sun gear, multiple
Planetary gear and comprise the outer rotor of engagement inner ring, the planetary gear of each planetary gear set respectively with corresponding sun gear, outer rotor
Inner ring engages, and multiple planetary gears of each planetary gear set are connected in outer rotor inner position by retainer；Described sun gear, outer
Rotor, retainer are three transmission key elements, when a transmission key element in one of them planetary gear set is fixed, then another
The transmission key element correspondence that transmission key element corresponding in planetary gear set is arranged to identical in output shaft, and two groups of planetary gears is fixing even
Connecing as a kind of overall structure, power shaft is the fixed connection structure of one of them transmission key element.
In two groups of described planetary gear set, the sun gear of one of them planetary gear set is fixed, and another planetary gear set is too
Sun wheel is set to output shaft, and the outer rotor of two groups of planetary gear set is fixedly connected as an overall structure outer ring, two groups of planetary gear set
Retainer is fixedly connected as an overall structure retainer, and overall structure retainer is set to power shaft.
In two groups of described planetary gear set, the sun gear of one of them planetary gear set is fixed, and another planetary gear set is too
Sun wheel is set to output shaft, and the outer rotor of two groups of planetary gear set is fixedly connected as an overall structure outer ring, two groups of planetary gear set
Retainer is fixedly connected as an overall structure retainer, and overall structure outer ring is set to power shaft.
In two groups of described planetary gear set, the outer rotor of one of them planetary gear set is fixed, outside another planetary gear set
Rotor is set to output shaft, and the sun gear of two groups of planetary gear set is fixedly connected as an overall structure sun gear, two groups of planetary gear set
Retainer be fixedly connected as that an overall structure retainer, an overall structure sun gear and power shaft are fixing to be connected.
In two groups of described planetary gear set, the outer rotor of one of them planetary gear set is fixed, outside another planetary gear set
Rotor is set to output shaft, and the sun gear of two groups of planetary gear set is fixedly connected as an overall structure sun gear, two groups of planetary gear set
Retainer be fixedly connected as an overall structure retainer, overall structure retainer is set to power shaft.
Described transmission key element is fixed i.e. to be fixed on housing or is integrative-structure or to be fixed on other static with housing
On part.
The described overall structure that is fixedly connected as i.e. is structure as a whole or stiff assembly structure.
The engagement system of described planetary gear is gear engagement or friction pulley engagement.
The parameter (such as: wheel radius, wheel form and speed reducing ratio etc.) of two groups of described planetary gears can separate configurations.
Advantage of the present utility model:
This utility model uses the planetary gear of two groups of difference speed reducing ratio can realize large speed ratio deceleration transmission, can meet big simultaneously
The working condition requirement of moment of torsion, high rotating speed input, and have technique be simple to manufacture, low cost and the high advantage of reliability.
Accompanying drawing explanation
Fig. 1 is the relativeness figure of this utility model sun gear, planetary gear and outer rotor.
Fig. 2 is the structural representation of this utility model embodiment 1.
Fig. 3 is the structural representation of this utility model embodiment 2.
Fig. 4 is the structural representation of this utility model embodiment 3.
Fig. 5 is the structural representation of this utility model embodiment 4.
Fig. 6 is the structural representation of this utility model embodiment 5.
Detailed description of the invention
This utility model provides multiple embodiment, its objective is to provide multiple selections, to meet different works for application
Condition needs.
Embodiment main formulas for calculating of the present utility model is according to below equation (1), the Transfer Formula of single planetary bevel gear system:
N1+a*n2-(1+a) * n3=0 (1),
In formula, n1 is sun gear rotating speed, and n2 is outer rotor rotating speed, and n3 is planetary gear retainer rotating speed, and a is the inner ring number of teeth
Divided by solar wheeling tooth numerical value (if frictional wheel drive, a is then that the inner radii of outer rotor is divided by sun gear radius value).
Embodiment 1
Seeing Fig. 1 and Fig. 2, a kind of dual planetary gear mechanical differential, including two groups of planetary gear set, is first planet wheels respectively
With the second planetary gear set, first planet wheels comprise 4, three the first row star-wheels of the first sun gear 8 and the first inner ring 6, the second row
Star-wheel group comprises the second sun gear 5, three second planetary gears 9 and the second inner rings 7, and the planetary gear of each planetary gear set is respectively with right
Sun gear, the inner ring answered engage, and three the first row star-wheels 8 of first planet wheels pass through the first retainer 10 at the first inner ring 6
Inner position connects, and three the second planetary gears 9 of the second planetary gear set are by the second retainer 11 in the second inner ring 7 inner position even
Connect；First sun gear 4 and housing 1 is fixing to be connected, and the second sun gear 5 and output shaft 12 are fixedly connected as an overall structure, and first
Inner ring 6 and the inner ring that the second inner ring 7 is outer rotor 3, the first retainer 10 and the second retainer 1 are fixedly connected as an overall structure
Retainer, overall structure retainer and power shaft 2 are fixedly connected as an overall structure.
First planet wheels choose Planetary Gear Transmission pattern, and delivery number is 0.5, wherein number of teeth z11 of the first sun gear 4
=60, number of teeth z13=60 of the first row star-wheel 8, number of teeth z12=180 of the first ring gear 6；Second planetary gear set chooses planetary gear
Transmission mode, delivery number is 0.5, number of teeth z21=60 of the second sun gear 5, number of teeth z23=59 of the second planetary gear 9, the second internal tooth
Number of teeth z22=178 of circle 7.
First planet wheels are under the input of power shaft 2, and the velocity of rotation of the first inner ring 6 of outer rotor 3 is:
N12=n1* (1+a1)/a1 (2),
(2) in formula, a1=z12/z11, n1 are the rotating speed of power shaft 2, and n12 is the rotating speed of the first inner ring 6.
Owing to retainer and the inner ring rotating speed of two groups of planetary gear set are equal, so the second sun gear 5 of the second planetary gear set
Rotating speed be:
N2=(1+a2) * n1-a2*n1* (1+a1)/a1 (3),
(3) in formula: a2=z22/z21, n2 are the second sun gear 5 i.e. rotating speed of output shaft 12, formula (3) draw output
The speed ratio of rotating speed and input speed is i:
I=n1/n2=1/ [(1+178/60)-(178/60) * (1+180/60)/(180/60) ≈-90.1, (4),
Result is that negative value represents the in opposite direction of output speed and input speed, same when second planetary gear of the present embodiment
Speed reducing ratio more than the speed reducing ratio of the first row star-wheel time, the rotation speed difference result of calculating be on the occasion of, show the outfan after deceleration
Rotation direction identical with the rotation direction of input.
Embodiment 2
Seeing Fig. 1 and Fig. 3, a kind of dual planetary gear mechanical differential, including two groups of planetary gear set, is first planet wheels respectively
With the second planetary gear set, first planet wheels comprise 4, three the first row star-wheels of the first sun gear 8 and the first inner ring 6, the second row
Star-wheel group comprises the second sun gear 5, three second planetary gears 9 and the second inner rings 7, and the planetary gear of each planetary gear set is respectively with right
Sun gear, the inner ring answered engage, and three the first row star-wheels 8 of first planet wheels pass through the first retainer 10 at the first inner ring 6
Inner position connects, and three the second planetary gears 9 of the second planetary gear set are by the second retainer 11 in the second inner ring 7 inner position even
Connect；First sun gear 4 and housing 1 is fixing to be connected, and the second sun gear 5 and output shaft 12 are fixedly connected as an overall structure, and first
Inner ring 6 and the inner ring that the second inner ring 7 is outer rotor 3, the first retainer 10 and the second retainer 1 are fixedly connected as an overall structure
Retainer, outer rotor 3 and power shaft 2 are fixedly connected as an overall structure.
First planet wheels choose Planetary Gear Transmission pattern, and delivery number is 0.5, wherein number of teeth z11 of the first sun gear 4
=60, number of teeth z13=60 of the first row star-wheel 8, number of teeth z12=180 of the first inner ring 6；Second planetary gear set is chosen planetary gear and is passed
Dynamic model formula, delivery number is 0.5, number of teeth z21=60 of the second sun gear 5, number of teeth z23=59 of the second planetary gear 9, the second inner ring 7
Number of teeth z22=178.By formula (4) through calculating:
I=n1/n2 ≈ 120,
Wherein, n1 is the rotating speed of power shaft 2, and n2 is the rotating speed of output shaft 12, and result value is for just representing output rotation side
To with input direction of rotation in the same direction.
Embodiment 3
Seeing Fig. 1 and Fig. 4, a kind of dual planetary gear mechanical differential, including two groups of planetary gear set, is first planet wheels respectively
With the second planetary gear set, first planet wheels comprise 4, three the first row star-wheels of the first sun gear 8 and the first inner ring 6, the second row
Star-wheel group comprises the second sun gear 5, three second planetary gears 9 and the second inner rings 7, and the planetary gear of each planetary gear set is respectively with right
Sun gear, the inner ring answered engage, and three the first row star-wheels 8 of first planet wheels pass through the first retainer 10 at the first inner ring 6
Inner position connects, and three the second planetary gears 9 of the second planetary gear set are by the second retainer 11 in the second inner ring 7 inner position even
Connect；First inner ring 6 is fixing with housing 1 to be connected, and the second inner ring 7 is fixedly connected as an overall structure, first sun with output shaft 12
Wheel 4 and the second sun gear 5 are fixedly connected as an overall structure sun gear, and a retainer 10 and the second retainer 1 are fixedly connected as
One overall structure retainer, an overall structure sun gear and power shaft 2 are fixedly connected as an overall structure.
First planet wheels choose Planetary Gear Transmission pattern, and delivery number is 0.5, wherein number of teeth z11 of the first sun gear 4
=60, number of teeth z12=180 of the first ring gear 6；Second planetary gear set chooses Planetary Gear Transmission pattern, and delivery number is 0.6, the
Number of teeth z21=58 of two sun gears 5, number of teeth z22=178 of the second ring gear 7.By formula (4) through calculating:
I=n1/n2 ≈ 19,
Wherein, n1 is the rotating speed of power shaft 2, and n2 is the rotating speed of output shaft 12, and result value is for just representing output rotation side
To with input direction of rotation in the same direction.
Embodiment 4
Seeing Fig. 1 and Fig. 5, a kind of dual planetary gear mechanical differential, including two groups of planetary gear set, is first planet wheels respectively
With the second planetary gear set, first planet wheels comprise 4, three the first row star-wheels of the first sun gear 8 and the first inner ring 6, the second row
Star-wheel group comprises the second sun gear 5, three second planetary gears 9 and the second inner rings 7, and the planetary gear of each planetary gear set is respectively with right
Sun gear, the inner ring answered engage, and three the first row star-wheels 8 of first planet wheels pass through the first retainer 10 at the first inner ring 6
Inner position connects, and three the second planetary gears 9 of the second planetary gear set are by the second retainer 11 in the second inner ring 7 inner position even
Connect；First inner ring 6 is fixing with housing 1 to be connected, and the second inner ring 7 is fixedly connected as an overall structure, first sun with output shaft 12
Wheel 4 and the second sun gear 5 are fixedly connected as an overall structure sun gear, and a retainer 10 and the second retainer 1 are fixedly connected as
One overall structure retainer, an overall structure retainer and power shaft 2 are fixedly connected as an overall structure.
First planet wheels choose Planetary Gear Transmission pattern, and delivery number is 0.5, wherein number of teeth z11 of the first sun gear 4
=60, number of teeth z12=180 of the first ring gear 6；Second planetary gear set chooses Planetary Gear Transmission pattern, and delivery number is 0.5, the
Number of teeth z21=60 of two sun gears 5, number of teeth z22=178 of the second ring gear 7.By formula (4) through calculating:
i = n1/n2 ≈ - 89
Wherein, n1 is the rotating speed of power shaft 13, and n2 is the rotating speed of output shaft 12, and result value represents output rotation side for negative
To contrary with input direction of rotation.
Embodiment 5
See Fig. 6, be that overall structure changes the first sun gear 4 into and controls electricity the first sun gear 4 in embodiment 1 and shell
Machine 13 is overall structure, and controlling motor 13 with housing 1 is integrally-built embodiment.
Due to the second sun gear 5 relative to the speed reducing ratio of power shaft 2 based on reference to the first sun gear 4, so changing
First sun gear 4 i.e. changes the second sun gear 5 i.e. output shaft 12 relative to the deceleration of power shaft 2 to the relative rotation speed of object
Ratio.
Claims (8)
1. a dual planetary gear mechanical differential, it is characterised in that: including two groups of planetary gear set, each planetary gear set all comprises too
Sun wheel, multiple planetary gear and comprise engagement inner ring outer rotor, the planetary gear of each planetary gear set respectively with corresponding sun gear,
The inner ring engagement of outer rotor, multiple planetary gears of each planetary gear set are connected in outer rotor inner position by retainer；Described
Sun gear, outer rotor, retainer are three transmission key elements, when a transmission key element in one of them planetary gear set is fixed
Time, then corresponding in another planetary gear set transmission key element is arranged to transmission identical in output shaft, and two groups of planetary gears and wants
Element correspondence is fixedly connected as a kind of overall structure, and power shaft is the fixed connection structure of one of them transmission key element.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: two groups of described planetary gear set
In the sun gear of one of them planetary gear set fixed, the sun gear of another planetary gear set is set to output shaft, two groups of planets
The outer rotor of wheels is fixedly connected as an overall structure outer ring, and the retainer of two groups of planetary gear set is fixedly connected as an overall structure
Retainer, overall structure retainer is set to power shaft.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: two groups of described planetary gear set
In the sun gear of one of them planetary gear set fixed, the sun gear of another planetary gear set is set to output shaft, two groups of planets
The outer rotor of wheels is fixedly connected as an overall structure outer ring, and the retainer of two groups of planetary gear set is fixedly connected as an overall structure
Retainer, overall structure outer ring is set to power shaft.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: two groups of described planetary gear set
In the outer rotor of one of them planetary gear set fixed, the outer rotor of another planetary gear set is set to output shaft, two groups of planets
The sun gear of wheels is fixedly connected as an overall structure sun gear, and the retainer of two groups of planetary gear set is fixedly connected as an overall knot
Structure retainer, an overall structure sun gear and power shaft are fixing to be connected.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: two groups of described planetary gear set
In the outer rotor of one of them planetary gear set fixed, the outer rotor of another planetary gear set is set to output shaft, two groups of planets
The sun gear of wheels is fixedly connected as an overall structure sun gear, and the retainer of two groups of planetary gear set is fixedly connected as an overall knot
Structure retainer, overall structure retainer is set to power shaft.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: described transmission key element is consolidated
Fixed i.e. it be fixed on housing or be integrative-structure with housing or be fixed on other static elements.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: described is fixedly connected as one
Overall structure is i.e. structure as a whole or stiff assembly structure.
A kind of dual planetary gear mechanical differential the most according to claim 1, it is characterised in that: the engagement of described planetary gear
Mode is gear engagement or friction pulley engagement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620460690.3U CN205745168U (en) | 2016-05-14 | 2016-05-14 | A kind of dual planetary gear mechanical differential |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620460690.3U CN205745168U (en) | 2016-05-14 | 2016-05-14 | A kind of dual planetary gear mechanical differential |
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| CN205745168U true CN205745168U (en) | 2016-11-30 |
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| CN201620460690.3U Expired - Fee Related CN205745168U (en) | 2016-05-14 | 2016-05-14 | A kind of dual planetary gear mechanical differential |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822746A (en) * | 2016-05-14 | 2016-08-03 | 袁廷华 | Double-planet-gear differential speed reducer |
| CN110315113B (en) * | 2019-06-19 | 2020-06-05 | 北京理工大学 | Design and assembly method of single-shaft input planetary composite milling tool |
-
2016
- 2016-05-14 CN CN201620460690.3U patent/CN205745168U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822746A (en) * | 2016-05-14 | 2016-08-03 | 袁廷华 | Double-planet-gear differential speed reducer |
| CN110315113B (en) * | 2019-06-19 | 2020-06-05 | 北京理工大学 | Design and assembly method of single-shaft input planetary composite milling tool |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20161130 Termination date: 20180514 |