CN106015501A - Differential gear reducer - Google Patents
Differential gear reducer Download PDFInfo
- Publication number
- CN106015501A CN106015501A CN201610667455.8A CN201610667455A CN106015501A CN 106015501 A CN106015501 A CN 106015501A CN 201610667455 A CN201610667455 A CN 201610667455A CN 106015501 A CN106015501 A CN 106015501A
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- CN
- China
- Prior art keywords
- gear
- input
- external
- internal
- group
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention discloses a differential gear reducer. The differential gear reducer is characterized in that the reducer is composed of an input gear set and an output gear set, wherein four gears are arranged in the input gear set and the output gear set and are a set of engaged inner gears and a set of engaged outer gears respectively. The inner gear or the outer gear of the input gear set can serve as a power input end, and the corresponding outer gear or the corresponding inner gear of the output gear set serves as an output gear. When one gear in the input gear set serves as the input end, the other gear is fixedly connected with the non-output gear of the output gear set. The input gear set and the output gear set are different in pitch circle diameter, and a large reduction ratio is achieved through cooperation between the gears for speed reduction. The reducer is simple in structure, compact in layout, good in rigidity and large in reduction ratio, and no flexible part is arranged.
Description
Technical field
The present invention relates to mechanical engineering field, particularly to mechanical reduction transmission field.
Background technology
Decelerator is one of assembly conventional in machine driving.At present, main groups of reducers has planetary gear speed-reduction
A few class decelerators such as device, RV decelerator and harmonic speed reducer.Wherein, planetary reducer stable transmission, driving torque is big, nothing
Compliant member, can realize slowing down and speedup simultaneously, but decelerator volume is relatively big, and speed reducing ratio improves difficulty；RV decelerator slows down
Bigger, stable transmission, but drive disk assembly is more, and system is complex；Harmonic speed reducer gear ratio is big, simple in construction, but tool
Having compliant member, be on the one hand unfavorable for controlling, on the other hand lifetime of system is shorter.
Summary of the invention
For solving gear big retarding ratio, long-life problem, the present invention provides a kind of decelerator without compliant member, and this subtracts
Speed device realizes speed reducing ratio control by controlling pitch circle diameter.
Decelerator of the present invention at least includes one group of input gear group, one group of output gear wheels and a ball axle
Hold.
Described input gear group includes intermeshing first gear and the second gear；Output gear wheels include engaging each other
The 3rd gear and the 4th gear.
Described first gear is external gear, and the second gear is internal gear, and the 3rd gear is external gear, and the 4th gear is internal tooth
Wheel.
Described first gear and the second gear are meshed, and it is poor to have certain number of teeth.
Described 3rd gear and the engagement of the 4th gear, and it is poor to have certain number of teeth.
The pitch diameter difference of described 3rd gear and the 4th gear and the pitch diameter difference phase of the first gear and the second gear
With.
Described first gear or the second gear can be as power input shafts.
When described first gear is power intake, ball bearing is positioned at the first gear, coaxial with the first gear；Second
Gear is fixing shaft gear.
When described second gear is power intake, ball bearing is positioned at the second gear, coaxial with the second gear；First
Gear is fixing shaft gear.
When described 3rd gear is clutch end, the fixing shaft gear of the 4th gear and input gear group coaxially and is mutually consolidated
Even.
When described 4th gear is clutch end, the fixing shaft gear of the 3rd gear and input gear group coaxially and is mutually consolidated
Even.
The present invention realizes different size of deceleration by controlling the pitch diameter of the first gear, the second gear and the 3rd gear
Ratio.
The present invention has an advantage that
Described decelerator does not use compliant member, it is simple to the accurate control of transmission process, and improves the decelerator life-span；
Described reducer structure is compact, and volume is little；
Described decelerator carries out speed reducing ratio control by controlling pitch diameter, and design space is big, and speed reducing ratio is big.
Accompanying drawing explanation
Fig. 1 is the decelerator first embodiment profile according to present invention design.
Fig. 2 is decelerator the second embodiment profile according to present invention design.
Fig. 3 is the first pitch circle diameter-gear ratio change curve under first embodiment under canonical parameter.
Fig. 4 is the second pitch circle diameter-gear ratio change curve under first embodiment under canonical parameter.
Fig. 5 is the 3rd pitch circle diameter-gear ratio change curve under first embodiment under canonical parameter.
Detailed description of the invention
Fig. 1 is first embodiment of the present invention.With reference to Fig. 1, the decelerator described in the present embodiment includes power shaft 1, rolling
Pearl bearing 2, external gear 3, internal gear 4, fixing bar 5, internal gear 6 and external gear 7.
Wherein, power shaft 1, ball bearing 2, external gear 3 and external gear 7 are coaxial.Power shaft 1 is positioned at ball bearing 2,
External gear 3 is connected with ball bearing 2.Power shaft 1 is connected with outer eccentric wheel, and under motor drives, power shaft 1 drives external gear
3 rotate.By ball bearing 2, external gear 3 can freely rotate around power shaft 1.
Internal gear 4 is fast pulley, and to have a small amount of tooth poor with external gear 3, and two gears are meshed.Limit by internal gear 4
System, the eccentric motion radius of power shaft 1 is that internal gear 4 is poor with the pitch radius of external gear 3.
Under the driving of input motor, external gear 3 rotates around internal gear 4.Poor owing to having certain tooth between two gears, therefore outward
Gear 3, while the axis around internal gear 4 revolves round the sun, has certain spin velocity, spin velocity size and external gear 3
Relevant with the tooth difference between internal gear 4.
Described fixing connecting rod 5 has at least 3, and one end of each fixing connecting rod 5 is fixed on external gear 3, the other end
It is fixed on external gear 7.By connection rod set 5 so that external gear 7 position relative with external gear 3, attitude are fixed and two gears are same
Axle.Under the drive of external gear 3, external gear 7 has the revolution angular velocity identical with external gear 3 and spin velocity.
External gear 7 is positioned at above external gear 3, and to have certain pitch diameter poor with external gear 3.
Internal gear 6 is positioned at outside external gear 7, and coaxial with internal gear 4.
Described internal gear 6 is power output shaft.
It is poor that internal gear 6 and external gear 7 have certain tooth, and the tooth difference of two gears and external gear 3 and the tooth of internal gear 4
Difference is identical.Therefore, external gear 7 revolves round the sun around internal gear 4 when, it is ensured that be meshed with external gear 7.
Owing to external gear 7 has certain rotation while revolution, by rationally selecting the number of teeth poor, internal gear 6 is at external tooth
Start under the driving of wheel 7 to rotate, thus export power.
With reference to Fig. 1, if the diameter of gear 3, gear 4, gear 6 and gear 7 is respectivelyd 3 、d 4 、d 6Withd 7.External tooth
Wheel 3 has revolution speedAnd rotational velocity, whereinFor input speed.External gear 7 has revolution speedAnd from rotating speed
Degree, internal gear 4 is fixed gear, and rotating speed is 0, and internal gear 6 is output gear, only has rotating speed and isRevolution speed.
Owing to gear 3, gear 4 engage each other, modulus is identical；Gear 6 and gear 7 engage each other, and modulus is identical.But gear
6 can be different from the modulus of gear 4.Respectively engage each other the number of teeth of gear, diameter and Zhou Changwei linear relationship.Use diameter generation herein
For the number of teeth, then to directly translate into pitch diameter poor for number of gear teeth difference.
?In time, external gear 3 rotates a circle around internal gear 4, arrives starting point, now has:
(1)
(2)
Owing to external gear 7 and external gear 3 have identical revolution and spin velocity, i.e.
(3)
(4)
And now internal gear 6 rotating speed is, have
(5)
Had by geometrical relationship again:
(6)
Simultaneous is above-mentioned various, can solve:
(7)
This is decelerator speed reducing ratio computing formula of the present invention.
According to the embodiment shown in Fig. 1, taking gear 3 pitch diameter 95, gear 4 pitch diameter 100, gear 6 pitch circle is straight
Footpath 66, now speed reducing ratio is 1881；When adjustment gear 3 pitch diameter is 98, keep remaining gear constant, then speed reducing ratio is
4851.Limiting case, gear 6 diameter is identical with gear 4, then gear 7 does not rotates, and speed reducing ratio is it is believed that be infinitely great.
Fig. 2 is second embodiment of the present invention.In the present embodiment, described decelerator includes fixing axle 1, ball bearing
2, external gear 3, internal gear 4, internal gear 5, external gear 6 and ring flange.
Power shaft 1 and ball bearing 2 and internal gear 4 are coaxial.Power shaft 1 is positioned at ball bearing 2, internal gear 4 and ball
Bearing 2 is connected.
External gear 3 is positioned at the inner side of internal gear 4, for fast pulley.It is poor that external gear 3 and internal gear 4 have a small amount of tooth, and two
Gear is meshed.
Internal gear 4 is wheel for inputting, is connected with outer eccentric wheel by power shaft 1, under outside driven by motor, and internal gear 4
Rotate around external gear 3.
By ball bearing 2, internal gear 4 can freely rotate around power shaft 1.Limited by external gear 3, power shaft 1 inclined
Heart moving radius is the semidiameter of internal gear 4 and external gear 3.
Under the driving of input motor, internal gear 4 rotates around external gear 3.Poor owing to having certain tooth between two gears, thus interior
Gear 4, while the axis around external gear 3 revolves round the sun, has certain spin velocity, spin velocity size and external gear 3
Relevant with the tooth difference between internal gear 4.
Described internal gear 5 is positioned at above internal gear 4, fixing and on internal gear 4 and same with internal gear 4 by ring flange 7
Axle.Under the drive of internal gear 4, internal gear 5 has the revolution angular velocity identical with internal gear 4 and spin velocity.
Described ring flange 7, between internal gear 4 and internal gear 5, is used for be connected internal gear 4 and internal gear 5.
It is internal that described external gear 6 is positioned at internal gear 5, and coaxial with internal gear 4.External gear 6 and internal gear 5 have a small amount of
Tooth is poor.And two the tooth difference of gear identical with the tooth difference of external gear 3 and internal gear 4.Therefore, public around internal gear 5 at external gear 6
Turn and time rotational, it is ensured that be meshed with external gear 6.Under the driving of internal gear 5, external gear 6 starts to rotate, and exports dynamic
Power.
Described external gear 6 is power output wheel.
For the embodiment shown in Fig. 2, the solution procedure in reference example 1 can be tried to achieve, and speed reducing ratio computing formula is
(8)。
Claims (11)
1. decelerator described at least includes one group of input gear group, one group of output gear wheels and a ball bearing.
2. input gear group described in includes intermeshing first gear and the second gear；Output gear wheels include intermeshing
3rd gear and the 4th gear.
3. the first gear described in is external gear, and the second gear is internal gear, and the 3rd gear is external gear, and the 4th gear is internal tooth
Wheel.
4. the first gear described in and the second gear are meshed, and it is poor to have certain number of teeth.
5. the 3rd gear described in and the engagement of the 4th gear, and it is poor to have certain number of teeth.
6. the pitch diameter difference of the 3rd gear and the 4th gear described in and the pitch diameter difference of the first gear and the second gear are identical.
7. the first gear described in or the second gear can be as power input shafts.
8. when described in, the first gear is power intake, ball bearing is positioned at the first gear, coaxial with the first gear；Second tooth
Wheel is fixing shaft gear.
9. when described in, the second gear is power intake, ball bearing is positioned at the second gear, coaxial with the second gear；First tooth
Wheel is fixing shaft gear.
10., when described in, the 3rd gear is clutch end, the input end gear of the 4th gear and input gear group coaxially and is mutually consolidated
Even.
When described in 11., the 4th gear is clutch end, the input end gear of the 3rd gear and input gear group coaxially and is mutually consolidated
Even.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610667455.8A CN106015501A (en) | 2016-08-15 | 2016-08-15 | Differential gear reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610667455.8A CN106015501A (en) | 2016-08-15 | 2016-08-15 | Differential gear reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106015501A true CN106015501A (en) | 2016-10-12 |
Family
ID=57135372
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610667455.8A Pending CN106015501A (en) | 2016-08-15 | 2016-08-15 | Differential gear reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106015501A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111577841A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | External-engagement planetary gear type output power amplifier |
| CN111577839A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | Planet wheel type output power amplifier |
| CN111577840A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | Internal-meshing planetary gear type output power amplifier |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1743704A (en) * | 2004-08-31 | 2006-03-08 | 王维民 | Direct-driving (external-toothing) gear speed reducer |
| CN1982745A (en) * | 2005-12-13 | 2007-06-20 | 王维民 | Positive and negative differential gear reducer |
| CN101509538A (en) * | 2009-03-25 | 2009-08-19 | 孟凡才 | Double-system differential speed reducer |
| CN102141118A (en) * | 2011-03-29 | 2011-08-03 | 重庆大学 | Differential speed reducer |
| JP5348182B2 (en) * | 2011-06-07 | 2013-11-20 | 株式会社安川電機 | Motor with reduction gear |
| CN105402321A (en) * | 2015-12-21 | 2016-03-16 | 肖立峰 | Eccentric double-tooth-difference speed-changing device |
-
2016
- 2016-08-15 CN CN201610667455.8A patent/CN106015501A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1743704A (en) * | 2004-08-31 | 2006-03-08 | 王维民 | Direct-driving (external-toothing) gear speed reducer |
| CN1982745A (en) * | 2005-12-13 | 2007-06-20 | 王维民 | Positive and negative differential gear reducer |
| CN101509538A (en) * | 2009-03-25 | 2009-08-19 | 孟凡才 | Double-system differential speed reducer |
| CN102141118A (en) * | 2011-03-29 | 2011-08-03 | 重庆大学 | Differential speed reducer |
| JP5348182B2 (en) * | 2011-06-07 | 2013-11-20 | 株式会社安川電機 | Motor with reduction gear |
| CN105402321A (en) * | 2015-12-21 | 2016-03-16 | 肖立峰 | Eccentric double-tooth-difference speed-changing device |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111577841A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | External-engagement planetary gear type output power amplifier |
| CN111577839A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | Planet wheel type output power amplifier |
| CN111577840A (en) * | 2020-05-19 | 2020-08-25 | 于永利 | Internal-meshing planetary gear type output power amplifier |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| DD01 | Delivery of document by public notice | ||
| DD01 | Delivery of document by public notice |
Addressee: Pan Lei Document name: Notification of Approving Refund |
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| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20161012 |