CN108488335A - A kind of speed changer based on small teeth number difference planet gear - Google Patents
A kind of speed changer based on small teeth number difference planet gear Download PDFInfo
- Publication number
- CN108488335A CN108488335A CN201810724518.8A CN201810724518A CN108488335A CN 108488335 A CN108488335 A CN 108488335A CN 201810724518 A CN201810724518 A CN 201810724518A CN 108488335 A CN108488335 A CN 108488335A
- Authority
- CN
- China
- Prior art keywords
- planet gear
- number difference
- small teeth
- teeth number
- difference planet
- 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.)
- Granted
Links
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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
A kind of speed changer based on small teeth number difference planet gear, include the differential type small teeth number difference planet gear of shell and the bent axle being arranged in shell and plural serial stage on bent axle, it is connected by the first crank structure between adjacent differential formula small teeth number difference planet gear, differential type small teeth number difference planet gear is connect by bearing with crank rotation, further includes power input shaft and power output shaft；Power input shaft is connect with housing into rotation, and power input shaft one end is located at hull outside, and the other end is connect with the ring gear of bent axle and first order differential type small teeth number difference planet gear respectively by first clutch and second clutch；The shell is equipped with the one-to-one brake of ring gear with multipole differential formula small teeth number difference planet gear, power output shaft is connect with housing into rotation, power output shaft one end is connect with the external tooth Cycloidal Wheel of afterbody differential type small teeth number difference planet gear by the second crank structure, and the power output shaft other end is located at hull outside.
Description
Technical field
The present invention relates to a kind of transmission mechanism more particularly to a kind of speed changers based on small teeth number difference planet gear.
Background technology
Gear-shift mechanism is a kind of to be widely used general mechanical device.And with the high speed development of modern industry, machine
The continuous improvement of tool and automatization level, the requirement to speed changer are also higher and higher.Small, light weight, slewing range be big,
Developing direction efficient, bearing capacity is strong, long lifespan becomes modern speed changer.Either traditional manual transmission China and foreign countries
General simpson planetary gear transmission, all cannot have grade change in realization in meshed gears transmission or modern automatic transmission
Large speed ratio transmission is realized while fast, and only there is smaller transmission ratio, general transmission ratio to be not more than 10.
The planet-gear transmission technology gradually promoted out from nineteen sixties has in the following aspects
It is advantageous：（1）It is driven bigger.The range of single-stage planet-gear transmission transmission ratio is 10-1000；（2）Structure
It is compact, it is small.With with transmission ratio, compared with the common cylinder gear drive of power, volume and quality can be obviously reduced；
（3）Transmission efficiency is higher.Rational in design, manufacture, assembly, little gear difference planetary driving mechanism efficiency is about in 0.8-
Between 0.94；（4）It is high to overload and impact bearing performance, long lifespan.The internal gear pair conjugated greatly is used, to improve
Contact strength and bending strength, service life can greatly extend.
But the current planet-gear transmission technology overwhelming majority applies in deceleration device, it can not
Easily step speed change is realized while realizing large transmission ratio, limit further genralrlization and the application of technique, such as
Application No. is the Chinese invention patents of CN201510827603.3, cannot realize multistep speed regulation.
Invention content
For the defects in the prior art, the purpose of the present invention is to provide a kind of speed changes based on small teeth number difference planet gear
Device, can multistep speed regulation.
For achieving the above object, the technical solution adopted by the present invention is：A kind of change based on small teeth number difference planet gear
Fast device includes the differential type small teeth number difference planet gear of shell and the bent axle and plural serial stage that are arranged in shell on bent axle,
It is connected by the first crank structure between adjacent differential formula small teeth number difference planet gear, differential type small teeth number difference planet gear passes through bearing
It is connect with crank rotation, further includes power input shaft and power output shaft；Power input shaft is connect with housing into rotation, power input
Axis one end is located at hull outside, and the other end is few with bent axle and first order differential type respectively by first clutch and second clutch
The ring gear of differential teeth planetary gear connects；The shell is equipped with the ring gear of multipole differential formula small teeth number difference planet gear one by one
Corresponding brake, power output shaft are connect with housing into rotation, power output shaft one end and afterbody differential type few teeth difference row
The external tooth Cycloidal Wheel of star gear is connected by the second crank structure, and the power output shaft other end is located at hull outside.
First crank structure and the second crank structure include cylindrical connecting pole, differential type small teeth number difference planet gear
External tooth Cycloidal Wheel be equipped with circular shaft bore corresponding with cylindrical connecting pole, the cylindrical connecting pole of the first crank structure is vertical
The ring gear side of the rear stage differential type small teeth number difference planet gear in adjacent differential formula small teeth number difference planet gear, and first are set
The cylindrical connecting pole of crank structure is inserted into previous stage differential type fewer differential teeth planetary tooth in adjacent differential formula small teeth number difference planet gear
On wheel in the circular shaft bore of external tooth Cycloidal Wheel, the cylindrical connecting pole and the circular shaft bore of external tooth Cycloidal Wheel of the first crank structure are inclined
The heart is arranged, and the distance between axis and circular shaft bore axis of the first crank structure cylinder connecting pole are a, differential type few teeth difference
The distance between the planetary external tooth Cycloidal Wheel center of circle and the differential type small teeth number difference planet gear ring gear center of circle are b, a and b phases
Deng；The cylindrical connecting pole of second crank structure is fixed at the end of power output shaft, the cylinder of the second crank structure
Connecting pole is inserted into the circular shaft bore in afterbody differential type small teeth number difference planet gear external tooth Cycloidal Wheel, installation and cooperation side
Formula is identical as the first crank structure.
The first clutch and second clutch are multiple-piece hydraulic friction clutches.
The brake is pneumatic tube brake.
The shell includes the cylindrical tube of left and right ends opening, and cylindrical tube left and right ends are covered with " canopy " shape
End cap.
" canopy " the shape end cap is connect by bolt with cylindrical tube.
The differential type small teeth number difference planet gear is three-level, and differential type small teeth number difference planet gear structure at different levels is identical.
The external tooth Cycloidal Wheel of first order differential type small teeth number difference planet gear and third level differential type small teeth number difference planet gear
External tooth Cycloidal Wheel is eccentric downwards, and the external tooth Cycloidal Wheel of second level differential type small teeth number difference planet gear is eccentric upwards.
Structure of the invention is compact, and the small cooperation by first clutch, second clutch and brake can be achieved more
Grade speed governing, to meet different rate requests.
Figure of description
Fig. 1 is schematic structural view of the invention；
Fig. 2 is sectional view of the present invention；
Fig. 3 is the first crank structure structural schematic diagram of the invention；
Fig. 4 is structure of the invention schematic diagram.
Specific implementation mode
As shown in Figures 1 to 4, a kind of speed changer based on small teeth number difference planet gear, including shell and setting are in shell
Differential type small teeth number difference planet gear of the interior bent axle 1 and thtee-stage shiplock on bent axle 1, and differential type small teeth number difference planet gear at different levels
Structure is identical, is connected by the first crank structure between adjacent differential formula small teeth number difference planet gear, differential type fewer differential teeth planetary tooth
Wheel is rotatablely connected by bearing and bent axle 1, further includes power input shaft 2 and power output shaft 3；Power input shaft 2 turns with shell
Dynamic connection, 2 one end of power input shaft are located at hull outside, the other end by first clutch 4 and second clutch 5 respectively with song
The ring gear 6 of axis 1 and first order differential type small teeth number difference planet gear connects；It is few with three-level differential type respectively there are three being set on shell
The one-to-one brake 7 of ring gear of differential teeth planetary gear, power output shaft 3 are connect with housing into rotation, power output shaft 3 one
The external tooth Cycloidal Wheel 8 with third level grade differential type small teeth number difference planet gear is held to be connect by the second crank structure, power output shaft 3
The other end is located at hull outside.
First crank structure and the second crank structure include cylindrical connecting pole 9, three-level differential type fewer differential teeth planetary tooth
Circular shaft bore 10 corresponding with cylindrical connecting pole 9 is equipped in the external tooth Cycloidal Wheel of wheel, the cylindrical of the first crank structure connects
Connect the ring gear side that column 9 is vertically set on rear stage differential type small teeth number difference planet gear in adjacent differential formula small teeth number difference planet gear
Face, and previous stage differential type is few in the insertion adjacent differential formula small teeth number difference planet gear of cylindrical connecting pole 9 of the first crank structure
On differential teeth planetary gear in the circular shaft bore 10 of external tooth Cycloidal Wheel, cylindrical connecting pole 9 and the external tooth cycloid of the first crank structure
10 eccentric setting of circular shaft bore of wheel, between 10 axis of axis and circular shaft bore of the first crank structure cylinder connecting pole 9
Distance is a, the external tooth Cycloidal Wheel center of circle and the differential type small teeth number difference planet gear ring gear center of circle of differential type small teeth number difference planet gear
The distance between for b, a and b it is equal；The cylindrical connecting pole 9 of second crank structure is fixed at the end of power output shaft 3
Portion, the cylindrical connecting pole 9 of the second crank structure are inserted into the circle in third level differential type small teeth number difference planet gear external tooth Cycloidal Wheel 8
In shape axis hole 10, installation and fit system are identical as the first crank structure, constitute multicrank parallelogram sturcutre.
First clutch 4 and second clutch 5 are multiple-piece hydraulic friction clutches.Brake 7 is pneumatic tube brake.
Shell includes the cylindrical tube 11 of left and right ends opening, and 11 left and right ends of cylindrical tube are covered with " canopy " shape
End cap 12." canopy " shape end cap 12 is connect by bolt with cylindrical tube 11, installation easy to disassemble.
The external tooth Cycloidal Wheel 13 of first order differential type small teeth number difference planet gear and third level differential type small teeth number difference planet gear
External tooth Cycloidal Wheel 8, the external tooth Cycloidal Wheel 14 of second level differential type small teeth number difference planet gear is eccentric upwards, when the present apparatus works
The vibrations of the present apparatus can be reduced.
The external tooth Cycloidal Wheel number of teeth of three differential type small teeth number difference planet gears being connected on bent axle 1 is identical, is z1；Three
The ring gear number of teeth of a differential type small teeth number difference planet gear being connected on bent axle 1 is identical, is z2, wherein z2With z1Difference
It is 1,2,3 or 4, while the cogged modulus of institute is identical.
Embodiment 1
z1=103, modification coefficient x1=1.013； z2=104, modification coefficient x2=1.784.2 input speed of power input shaft is
2930r/min。
For originally when starting first clutch 4 and brake 7 corresponding with third level differential type small teeth number difference planet gear simultaneously
First grade of device, power input shaft 2 is connect with bent axle 1, and the rotating speed of bent axle 1 is identical as the rotating speed of power input shaft 2, the third level
The ring gear 15 of differential type small teeth number difference planet gear is locked with cylindrical tube 11, third level differential type small teeth number difference planet gear
The revolution in the ring gear 15 of third level differential type small teeth number difference planet gear with bent axle 1 of external tooth Cycloidal Wheel 8, while the third level is differential
The external tooth Cycloidal Wheel 8 of formula small teeth number difference planet gear generates rotation, drives power output shaft 3 to rotate by the second crank structure, moves
The rotating speed of power output shaft 3 is identical as the rotating speed of 8 rotation of external tooth Cycloidal Wheel of third level differential type small teeth number difference planet gear, transmission ratio
3 rotation direction of power output shaft is represented with power input shaft 2 for, negative sign on the contrary, the rotating speed of power output shaft 3 is ﹣ 28.4 at this time
r/min。
For originally when starting first clutch 4 and brake 7 corresponding with second level differential type small teeth number difference planet gear simultaneously
The second gear of device, power input shaft 2 are connect with bent axle 1, and the rotating speed of bent axle 1 is identical as the rotating speed of power input shaft 2, the second level
The ring gear 16 of differential type small teeth number difference planet gear is locked with cylindrical tube 11, second level differential type small teeth number difference planet gear
External tooth Cycloidal Wheel 14 generates revolution under the drive of bent axle 1, due to the ring gear 16 of second level differential type small teeth number difference planet gear
Fixed, also rotation while revolution of external tooth Cycloidal Wheel 14 of second level differential type small teeth number difference planet gear, second is differential
The external tooth Cycloidal Wheel 14 of dynamic formula small teeth number difference planet gear drives third level differential type fewer differential teeth planetary tooth by the first crank structure
The ring gear 15 of wheel rotates, and the ring gear 15 of third level differential type small teeth number difference planet gear drives third level differential type few teeth difference row
The external tooth Cycloidal Wheel 8 of 8 rotation of external tooth Cycloidal Wheel of star gear, third level differential type small teeth number difference planet gear passes through the second crank knot
Structure drives power output shaft 3 to rotate, and transmission ratio is that the rotating speed of power output shaft 3 is -57.2 r/min.
For originally when starting first clutch 4 and brake 7 corresponding with first order differential type small teeth number difference planet gear simultaneously
The third gear of device, power input shaft 2 are connect with bent axle 1, and the rotating speed of bent axle 1 is identical as the rotating speed of power input shaft 2, the first order
The ring gear 6 of differential type small teeth number difference planet gear is locked with cylindrical tube 11, and with reference to the operation principle of second gear, first is differential
The external tooth Cycloidal Wheel 13 of dynamic formula small teeth number difference planet gear revolves round the sun under the action of bent axle 1 and rotation, first order differential type few teeth difference
Planetary external tooth Cycloidal Wheel 13 passes sequentially through second level differential type small teeth number difference planet gear and third level differential type few teeth difference
Planetary gear drives power output shaft 3 to rotate, and transmission ratio is that the rotating speed of power output shaft 3 is -86.2 r/min.
For originally when starting second clutch 5 and brake 7 corresponding with third level differential type small teeth number difference planet gear simultaneously
The fourth speed of device, power input shaft 2 are connect with the ring gear 6 of first order differential type small teeth number difference planet gear, and the first order is differential
The rotating speed of the ring gear 6 of formula small teeth number difference planet gear is identical as the rotating speed of power input shaft 2, third level differential type fewer differential teeth planetary
The external tooth Cycloidal Wheel 8 of gear drives power output shaft 3 to rotate, and transmission ratio is that this formula derives from：Cymbals shake guiding principle planetary gears biography
Dynamic Beijing design [M]：Chemical Industry Press, 2014, the rotating speed of power output shaft 3 is -1486.4 r/min.
For originally when starting second clutch 5 and brake 7 corresponding with second level differential type small teeth number difference planet gear simultaneously
The fifth speed of device, power input shaft 2 are connect with the ring gear 6 of first order differential type small teeth number difference planet gear, and the first order is differential
The rotating speed of the ring gear 6 of formula small teeth number difference planet gear is identical as the rotating speed of power input shaft 2, first order differential type fewer differential teeth planetary
The external tooth Cycloidal Wheel 13 of gear rotation and revolution under the action of ring gear 6 of first order differential type small teeth number difference planet gear, the
The external tooth Cycloidal Wheel 13 of level-one differential type small teeth number difference planet gear band dynamic crankshaft 1 while revolution rotates, second level differential type
The external tooth Cycloidal Wheel 14 of small teeth number difference planet gear revolves round the sun under the drive of bent axle 1, while also rotation, and the work with reference to second gear is former
The external tooth Cycloidal Wheel 14 of reason, second level differential type small teeth number difference planet gear drives power output shaft 3 to rotate, and transmission ratio is power
The rotating speed of output shaft 3 is -5888.4 r/min.
Start first clutch 4 and second clutch 5 simultaneously, power input shaft 2 drives first order differential type to lack tooth simultaneously
The ring gear 6 and bent axle 1 of difference planet gear rotate synchronously, at this time three-level differential type small teeth number difference planet gear as a whole with
Power input shaft 2 rotates synchronously, and power output shaft 3 is driven to rotate simultaneously, and the rotating speed of transmission ratio 1, power output shaft 3 is
2930 r/min。
Claims (8)
1. a kind of speed changer based on small teeth number difference planet gear, including shell and the bent axle and plural serial stage that are arranged in shell
Differential type small teeth number difference planet gear on bent axle passes through the first crank structure between adjacent differential formula small teeth number difference planet gear and connects
It connects, differential type small teeth number difference planet gear is connect by bearing with crank rotation, it is characterised in that：Further include power input shaft and dynamic
Power output shaft；Power input shaft is connect with housing into rotation, and power input shaft one end is located at hull outside, the other end by first from
Clutch and second clutch are connect with the ring gear of bent axle and first order differential type small teeth number difference planet gear respectively；On the shell
Equipped with the one-to-one brake of ring gear with multipole differential formula small teeth number difference planet gear, power output shaft connects with housing into rotation
It connects, power output shaft one end and the external tooth Cycloidal Wheel of afterbody differential type small teeth number difference planet gear are connected by the second crank structure
It connects, the power output shaft other end is located at hull outside.
2. a kind of speed changer based on small teeth number difference planet gear according to claim 1, it is characterised in that：Described first is bent
Handle structure and the second crank structure include cylindrical connecting pole, and the external tooth Cycloidal Wheel of differential type small teeth number difference planet gear is equipped with
Circular shaft bore corresponding with cylindrical connecting pole, it is few that the cylindrical connecting pole of the first crank structure is vertically set on adjacent differential formula
The ring gear side of rear stage differential type small teeth number difference planet gear in differential teeth planetary gear, and the cylindrical of the first crank structure connects
Connect the circle that column is inserted into external tooth Cycloidal Wheel on previous stage differential type small teeth number difference planet gear in adjacent differential formula small teeth number difference planet gear
In shape axis hole, the cylindrical connecting pole of the first crank structure and the circular shaft bore eccentric setting of external tooth Cycloidal Wheel, the first crank knot
The distance between axis and circular shaft bore axis of structure cylinder connecting pole are a, and the external tooth of differential type small teeth number difference planet gear is put
The distance between the line wheel center of circle and the differential type small teeth number difference planet gear ring gear center of circle are that b, a and b are equal；Second crank structure
Cylindrical connecting pole is fixed at the end of power output shaft, and the cylindrical connecting pole of the second crank structure is inserted into afterbody
In circular shaft bore in differential type small teeth number difference planet gear external tooth Cycloidal Wheel, installation and fit system and the first crank structure phase
Together.
3. a kind of speed changer based on small teeth number difference planet gear according to claim 1, it is characterised in that：Described first from
Clutch and second clutch are multiple-piece hydraulic friction clutches.
4. a kind of speed changer based on small teeth number difference planet gear according to claim 1, it is characterised in that：The brake
For pneumatic tube brake.
5. a kind of speed changer based on small teeth number difference planet gear according to claim 1, it is characterised in that：The shell packet
The cylindrical tube of left and right ends opening is included, cylindrical tube left and right ends are covered with " canopy " shape end cap.
6. a kind of speed changer based on small teeth number difference planet gear according to claim 5, it is characterised in that：" canopy "
Shape end cap is connect by bolt with cylindrical tube.
7. a kind of speed changer based on small teeth number difference planet gear according to claim 1, it is characterised in that：The differential type
Small teeth number difference planet gear is three-level, and differential type small teeth number difference planet gear structure at different levels is identical.
8. a kind of speed changer based on small teeth number difference planet gear according to claim 7, it is characterised in that：The first order is differential
The external tooth Cycloidal Wheel of formula small teeth number difference planet gear and the external tooth Cycloidal Wheel of third level differential type small teeth number difference planet gear are eccentric downwards,
The external tooth Cycloidal Wheel of second level differential type small teeth number difference planet gear is eccentric upwards.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810724518.8A CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810724518.8A CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108488335A true CN108488335A (en) | 2018-09-04 |
| CN108488335B CN108488335B (en) | 2020-01-31 |
Family
ID=63343335
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810724518.8A Expired - Fee Related CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108488335B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2167236Y (en) * | 1993-05-24 | 1994-06-01 | 徐至辉 | Planetary transmission withless leeth difference of dynamic shifting type |
| CN1090024A (en) * | 1993-01-19 | 1994-07-27 | 徐至辉 | Epicyclic variable-speed gear with less difference of number of teeth |
| JP2005016695A (en) * | 2003-06-30 | 2005-01-20 | Hirokazu Tanaka | Reduction gear |
| CN201348024Y (en) * | 2008-12-05 | 2009-11-18 | 天津市正平机械新技术有限公司 | Compound small teeth difference reducing gear |
| CN101881322A (en) * | 2009-05-06 | 2010-11-10 | 徐至辉 | Series-connection type small tooth number difference speed-change mechanism |
| CN105276097A (en) * | 2015-11-25 | 2016-01-27 | 重庆大学 | Double-level differential movement type few-tooth-difference planetary gear transmission mechanism |
-
2018
- 2018-07-04 CN CN201810724518.8A patent/CN108488335B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1090024A (en) * | 1993-01-19 | 1994-07-27 | 徐至辉 | Epicyclic variable-speed gear with less difference of number of teeth |
| CN2167236Y (en) * | 1993-05-24 | 1994-06-01 | 徐至辉 | Planetary transmission withless leeth difference of dynamic shifting type |
| JP2005016695A (en) * | 2003-06-30 | 2005-01-20 | Hirokazu Tanaka | Reduction gear |
| CN201348024Y (en) * | 2008-12-05 | 2009-11-18 | 天津市正平机械新技术有限公司 | Compound small teeth difference reducing gear |
| CN101881322A (en) * | 2009-05-06 | 2010-11-10 | 徐至辉 | Series-connection type small tooth number difference speed-change mechanism |
| CN105276097A (en) * | 2015-11-25 | 2016-01-27 | 重庆大学 | Double-level differential movement type few-tooth-difference planetary gear transmission mechanism |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108488335B (en) | 2020-01-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2016011921A1 (en) | Reduction ratio variable hub motor for electric bicycle | |
| CN102420494B (en) | Variable speed wheel-disc integrated mid-motor in electrical bicycle | |
| CN201667582U (en) | Motor-driven speed changing device | |
| CN201166096Y (en) | Circular body gear box and shifting device | |
| US20220107017A1 (en) | Continuously variable transmission | |
| CN1199696A (en) | Built-in variable speed wheel hub for bicycle | |
| CN201177029Y (en) | Planet type few teeth difference decelerator | |
| CN108488335A (en) | A kind of speed changer based on small teeth number difference planet gear | |
| CN100458217C (en) | Single inputting and double outputting planetary speed reducer | |
| CN1442569A (en) | Fully automatic speed reducing clutch of washing machine | |
| CN204805447U (en) | Automatic transmission | |
| CN201080990Y (en) | Two ends output movable teeth reduction driver | |
| CN109624689A (en) | A kind of hub motor of electronic hovercar | |
| CN101320928A (en) | Driving motor and automatic transmission | |
| CN104165214B (en) | A kind of double dynamical synthesizer | |
| CN209781587U (en) | Speed change device based on small-tooth-difference planetary gear | |
| EP4309988A1 (en) | Hub motor having integrated transmission mechanism | |
| CN210559044U (en) | Precise and efficient electric winding drum | |
| CN111503230A (en) | Multi-stage speed change gear box | |
| CN201031942Y (en) | Satellite gear stepless gear based on variable crank length crank-rocker mechanism | |
| CN201118352Y (en) | Shift bearing deceleration wheel hub electromotor for electric car | |
| CN1393354A (en) | Multi-gear mechanical automatic transmission for automobile | |
| CN102705453A (en) | Internal-vibration multi-crankshaft small-tooth difference speed reducer | |
| CN2661744Y (en) | Full automatic deceleration clutch for washing machine | |
| CN201401485Y (en) | Reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200131 Termination date: 20200704 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |