CN207921251U - Double rank planetary gears - Google Patents
Double rank planetary gears Download PDFInfo
- Publication number
- CN207921251U CN207921251U CN201820286938.8U CN201820286938U CN207921251U CN 207921251 U CN207921251 U CN 207921251U CN 201820286938 U CN201820286938 U CN 201820286938U CN 207921251 U CN207921251 U CN 207921251U
- Authority
- CN
- China
- Prior art keywords
- clutch
- gear
- sun gear
- planetary gear
- double rank
- 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.)
- Active
Links
Landscapes
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
Abstract
A kind of double rank planetary gears, are related to system of vehicle transmission technical field, select degree of freedom small the solution is to existing transmission gear ratio and bulky technical problem.The speed changer includes gearbox body, main motor, double rank planetary gear sets, first clutch, second clutch；Double rank planetary gear sets include planet carrier, ring gear, two sun gears；The planetary gear of two synchronous rotations is designed on each planet wheel spindle of planet carrier, first planetary gear therein is engaged with the first sun gear, second planetary gear is engaged with the second sun gear, and ring gear is fixed on gearbox body, and ring gear is engaged with each second planetary gear；The output shaft connection first clutch of the main motor, the driving shaft of second clutch, the driven shaft of first clutch couple the first sun gear, and the driven shaft of second clutch couples the second sun gear.Speed changer provided by the utility model is suitable for electronic or mixed electrical automobile.
Description
Technical field
The utility model is related to system of vehicle transmission technologies, more particularly to a kind of technology of double rank planetary gears.
Background technology
Existing mixed dynamic or pure electric vehicle speed changer mostly uses the fast structure of parallel-axis type two, but gear and bearing are because of single pair tooth
Stress is taken turns, load is higher, therefore the also therefore corresponding amplification in design size；Though also having once in a while using traditional two-row planetary gear group
Structure reduce design size, the speed changer of this planetary gear set structure is in speed ratio（Output/output of torque or speed
Than）Selection on degree of freedom very little, it is more difficult to cope with the demand of the structure and load-carrying ability of various deceleration transmission systems to gear ratio.
Utility model content
Defect present in for the above-mentioned prior art, the technical problem to be solved by the utility model is to provide a kind of teeth
Take turns the double rank planetary gears bigger and small than selection degree of freedom.
In order to solve the above-mentioned technical problem, a kind of double rank planetary gears provided by the utility model, feature exist
In：Including gearbox body, main motor, double rank planetary gear sets, first clutch, second clutch；
Double rank planetary gear sets include planet carrier, ring gear, sun gear；There are two the sun gears, this two too
Positive tooth number is different, and one of sun gear is the first sun gear, another sun gear is the second sun gear；The planet carrier
Each planet wheel spindle on be designed with first planetary gear and second planetary gear rotated synchronously with the first planetary gear；
Each first planetary gear is engaged with the first sun gear, and each second planetary gear is engaged with the second sun gear, and ring gear is fixed on change
On fast babinet, and ring gear is engaged with each second planetary gear；
The output shaft connection first clutch of the main motor, the driving shaft of second clutch, for driving the first clutch
The driving shaft rotation of device, second clutch；The driven shaft of first clutch couples the first sun gear, for driving the first sun gear
The driven shaft of rotation, second clutch couples the second sun gear, for driving the rotation of the second sun gear.
Further, further include third clutch, the driving shaft of the output shaft connection third clutch of the main motor, use
In the driving shaft rotation of driving third clutch, the planet carrier of the double rank planetary gear sets of driven shaft connection of third clutch is used
In driving planet carrier rotation.
Further, further include differential mechanism, the planet carrier in double rank planetary gear sets is connected to differential by transmission parts
Device exports power by differential mechanism.
Further, differential mechanism is equipped with the output side brake for differential output shaft braking.
Further, the main motor is arranged in gearbox body, or is arranged outside gearbox body.
Double rank planetary gears provided by the utility model use double rank planetary gear constructions, gear ratio selection
Degree of freedom is big, and relatively traditional double gear structure in structure is more closely, it is possible to reduce the axis of entire speed changer
To space, volume is also relatively small, and more activity spaces can be provided in the configuration of vehicle.
Description of the drawings
Fig. 1 is the structural schematic diagram of double rank planetary gears of the utility model first embodiment；
Fig. 2 is used between planet carrier and differential mechanism in double rank planetary gears of the utility model first embodiment
The schematic diagram of train of reduction gears transmission；
Fig. 3 is the structural schematic diagram of double rank planetary gears of the utility model second embodiment.
Specific implementation mode
The embodiments of the present invention are described in further detail below in conjunction with description of the drawings, but the present embodiment and are not had to
In limitation the utility model, every similar structure using the utility model and its similar variation should all be included in the utility model
Protection domain, the pause mark in the utility model indicates the relationship of sum.
As shown in Figure 1, a kind of double rank planetary gears that the utility model first embodiment is provided, feature exist
In：Including gearbox body（Do not show in figure）, main motor U1, double rank planetary gear sets, first clutch C1, second clutch C2；
Double rank planetary gear sets include planet carrier J1, ring gear R1, sun gear；There are two the sun gears, this two
A sun gear number of teeth is different, and one of sun gear is the first sun gear S1, another sun gear is the second sun gear S2；Institute
It states and is designed with a first planetary gear P1 on each planet wheel spindle of planet carrier J1 and one rotate synchronously with the first planetary gear
Second planetary gear P2；Each first planetary gear P1 is engaged with the first sun gear S1, each second planetary gear P2 and the second sun gear
P2 is engaged, and ring gear R1 is fixed on gearbox body, and ring gear R1 is engaged with each second planetary gear P2；
The output shaft connection first clutch C1 of the main motor U1, the driving shaft of second clutch C2, for driving the
The driving shaft rotation of one clutch C1, second clutch C2；The driven shaft of first clutch C1 couples the first sun gear S1, is used for
The first sun gear S1 rotations are driven, the driven shaft of second clutch C2 couples the second sun gear S2, for driving the second sun gear
S2 is rotated, and main motor U1 can be arranged according to the demand of layout in gearbox body, or be arranged outside gearbox body.
Further include differential mechanism U2 in the utility model first embodiment, differential mechanism U2, which is equipped with, is used for differential output shaft
The output side brake BK of braking, the planet carrier J1 in double rank planetary gear sets are connected to differential mechanism U2 by transmission parts, lead to
Cross differential mechanism output power, output side brake BK can to avoid when vehicle braking caused by differential output shaft rotates vehicle
Sliding.
For transmission parts in the present embodiment using transmission chain band N1, the present embodiment can also use shown in Fig. 2 subtract
Fast gear set N2 is as the transmission parts between planet carrier and differential mechanism；It, can be by chain when using transmission chain band as transmission parts
Wheel is placed on the support shaft of planet carrier and the output shaft of differential mechanism, and is coupled with transmission chain band, and reduction ratio can be according to the size of sprocket wheel
Ratio and two axis centers away from size etc. make suitable selection and adjustment, the design that such chain belt is slowed down be suitble to deceleration ratio compared with
It is small, and centre-to-centre spacing is shorter, the small vehicle of load, its advantage is that lightly, be easily assembled, and have high transmission efficiency, it is light-weight and
The advantage of low cost；In top load, deceleration ratio is high, when input and output shaft centre-to-centre spacing are larger, uses the double reduction of three axis
Gear set（With reference to figure 2）As transmission parts, durability can be more preferable.
The utility model first embodiment is suitable for electronic or mixed motor-car, can make the by the control mechanism of electric machine speed regulation
Division two notch speeds of the much smoother rapid realization output of one clutch C1, second clutch C2, so that vehicle drive system
Reach expected high turn round to start, quickly accelerate, functions, performance and the efficient demand such as run at high speed, and in the speed of gear
There is big selectivity more than relatively general common single, double rows of planetary gear set in apolegamy；Though the use in space, weight and at
The single, double rows of planetary gear set variation of present aspect, opposite conventional planetary is little, but has to vehicle functions, aspect of performance larger
Optimization.
When first clutch C1, second clutch C2 are totally separated, it is in neutral state；
First clutch C1 is closed, and when second clutch C2 separation, the power of main motor U1 outputs by first from
Clutch C1, the first sun gear S1, the first planetary gear P1 are transmitted on planet carrier J1, then are transmitted to differential mechanism U2 by planet carrier J1,
The output of the first notch speed is realized by differential mechanism U2；
Second clutch C2 is closed, and when first clutch C1 separation, the power of main motor U1 outputs by second from
Clutch C2, the second sun gear S2, the second planetary gear P2 are transmitted on planet carrier J1, then are transmitted to differential mechanism U2 by planet carrier J1,
The output of the second notch speed is realized by differential mechanism U2.
As shown in figure 3, the utility model second embodiment and first embodiment difference lies in：It further include third clutch
The driving shaft of the output shaft connection third clutch C3 of C3, the main motor U1, the driving shaft for driving third clutch C3
Rotation, the planet carrier J1 of the double rank planetary gear sets of driven shaft connection of third clutch C3, for driving planet carrier J1 to rotate.
The utility model second embodiment is by controlling first clutch C1, second clutch C2, third clutch C3
Division is, it can be achieved that three notch speeds export；
When first clutch C1, second clutch C2, third clutch C3 are totally separated, it is in neutral state；
First clutch C1 is closed, and when second clutch C2, the C3 separation of third clutch, main motor U1 outputs are moved
Power is transmitted on planet carrier J1 by first clutch C1, the first sun gear S1, the first planetary gear P1, then is transmitted by planet carrier J1
To differential mechanism U2, the output of the first notch speed is realized by differential mechanism U2；
Second clutch C2 is closed, and when first clutch C1, the C3 separation of third clutch, main motor U1 outputs are moved
Power is transmitted on planet carrier J1 by second clutch C2, the second sun gear S2, the second planetary gear P2, then is transmitted by planet carrier J1
To differential mechanism U2, the output of the second notch speed is realized by differential mechanism U2.
Third clutch C3 is closed, and when first clutch C1, second clutch C2 separation, main motor U1 outputs are moved
Power is transmitted to by third clutch C3 on planet carrier J1, then is transmitted to differential mechanism U2 by planet carrier J1, real by differential mechanism U2
Existing third notch speed output, third notch speed are served as due to inputting and exporting by planet carrier（That is direct-drive）, due to gear at this time
The gear set of system only locates idle conditions, therefore without any biography loss of energy, thus speedup, efficiency and it is energy saving on have compared with one, two grade
It is preferable to promote performance.
For reduce shifting shock power, from the first notch speed to the torque ratio difference of third notch speed should be maintained at as possible 2.0 hereinafter, because
This is with 4：2：1 ratio is preferred to make the design derivative of double rank planetary gear sets.
Claims (5)
1. a kind of double rank planetary gears, it is characterised in that：Including gearbox body, main motor, double rank planetary gear sets, first
Clutch, second clutch；
Double rank planetary gear sets include planet carrier, ring gear, sun gear；There are two the sun gears, two sun gears
The number of teeth is different, and one of sun gear is the first sun gear, another sun gear is the second sun gear；The planet carrier it is every
First planetary gear and second planetary gear rotated synchronously with the first planetary gear are designed on a planet wheel spindle；It is each
First planetary gear is engaged with the first sun gear, and each second planetary gear is engaged with the second sun gear, and ring gear is fixed on gearbox
On body, and ring gear is engaged with each second planetary gear；
The output shaft connection first clutch of the main motor, the driving shaft of second clutch, for driving first clutch, the
The driving shaft of two clutches rotates；The driven shaft of first clutch couples the first sun gear, for driving the rotation of the first sun gear,
The driven shaft of second clutch couples the second sun gear, for driving the rotation of the second sun gear.
2. double rank planetary gears according to claim 1, it is characterised in that：Further include third clutch, the master
The driving shaft of the output shaft connection third clutch of motor, for driving the driving shaft of third clutch to rotate, third clutch
The double rank planetary gear sets of driven shaft connection planet carrier, for driving planet carrier to rotate.
3. double rank planetary gears according to claim 1 or 2, it is characterised in that：Further include differential mechanism, double rank planets
Planet carrier in gear set is connected to differential mechanism by transmission parts, and power is exported by differential mechanism.
4. double rank planetary gears according to claim 3, it is characterised in that：Differential mechanism is equipped with defeated for differential mechanism
The output side brake of shaft braking.
5. double rank planetary gears according to claim 3, it is characterised in that：The main motor is arranged in gearbox body
It is interior, or be arranged outside gearbox body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820286938.8U CN207921251U (en) | 2018-03-01 | 2018-03-01 | Double rank planetary gears |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820286938.8U CN207921251U (en) | 2018-03-01 | 2018-03-01 | Double rank planetary gears |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN207921251U true CN207921251U (en) | 2018-09-28 |
Family
ID=63601967
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201820286938.8U Active CN207921251U (en) | 2018-03-01 | 2018-03-01 | Double rank planetary gears |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN207921251U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108240432A (en) * | 2018-03-01 | 2018-07-03 | 陈扬珑 | Double rank planetary gears |
-
2018
- 2018-03-01 CN CN201820286938.8U patent/CN207921251U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108240432A (en) * | 2018-03-01 | 2018-07-03 | 陈扬珑 | Double rank planetary gears |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8894536B2 (en) | Multistep gear mechanism | |
| CN206394434U (en) | A kind of many gear automotive trannsmission systems of integrated single motor | |
| US8944953B2 (en) | Multistep gear mechanism | |
| CN211525449U (en) | Parallel shaft type two-gear electric driving system | |
| CN105051414B (en) | Speed changer for motor vehicle | |
| CN105584349B (en) | A kind of hybrid-powered motor speed variator assembly | |
| CN106763565A (en) | It is suitable to the three gear planet speed change mechanisms that electric vehicle is used | |
| CN202872557U (en) | Motor and speed changer integrated transmission system for electric automobile | |
| CN206926509U (en) | A kind of more gear electric drive transmission devices | |
| CN102312966A (en) | Double-planetary-gear-set double-mode hybrid power transmission device | |
| CN201506247U (en) | Double planet-row four-axis hybrid speed variator | |
| CN101852278A (en) | Nine-gear planetary automatic transmission | |
| CN102616127A (en) | Hybrid power transmission device of dual-mode two-stage planet wheel | |
| CN110920367A (en) | Coaxial two-gear electric drive axle | |
| CN103066748A (en) | Integrated two-gear motor transmission for pure electric vehicle | |
| CN107599823A (en) | Differential multimodal fusion power car drive system | |
| CN105673783A (en) | Large-transmission-ratio two-gear planetary transmission | |
| CN205997708U (en) | A kind of electric drive axle system based on single planetary row two shift transmission | |
| CN202215683U (en) | Dual-planet row and dual-die hybrid power drive device | |
| CN106641135B (en) | A kind of 12 speed automatic transmissions | |
| CN206317685U (en) | A kind of four gear vehicle transmission devices of integrated single motor | |
| CN109203972B (en) | Transmission device of double-motor hybrid power system | |
| CN108240432A (en) | Double rank planetary gears | |
| CN207921251U (en) | Double rank planetary gears | |
| CN203039496U (en) | All-in-one two-shift motor transmission for pure electric automobile |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220215 Address after: Rooms 1808 and 1809, No. 1, Lane 1588, Wangyuan South Road, Fengxian District, Shanghai Patentee after: Shanghai Meihua Automobile Technology Co.,Ltd. Address before: No. 3728, Helen Road, Ann Arbor, Michigan, USA Patentee before: Chen Yanglong Patentee before: Zhou Shijian Patentee before: Yin Yusheng |