CN107514445A - Based on improvement lever method six speed transmission - Google Patents
Based on improvement lever method six speed transmission Download PDFInfo
- Publication number
- CN107514445A CN107514445A CN201710749531.4A CN201710749531A CN107514445A CN 107514445 A CN107514445 A CN 107514445A CN 201710749531 A CN201710749531 A CN 201710749531A CN 107514445 A CN107514445 A CN 107514445A
- Authority
- CN
- China
- Prior art keywords
- row
- gear
- seat
- input
- change
- 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
- 230000005540 biological transmission Effects 0.000 title claims abstract description 25
- 238000000034 method Methods 0.000 title claims abstract description 15
- 230000006872 improvement Effects 0.000 title claims abstract description 9
- 238000009499 grossing Methods 0.000 abstract description 3
- 230000007246 mechanism Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 241000233855 Orchidaceae Species 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H57/00—General details of gearing
- F16H2057/0087—Computer aided design [CAD] specially adapted for gearing features ; Analysis of gear systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to one kind based on improvement lever method six speed transmission, including front-seat input gear assembly, middle row's change-speed gearing component and heel row change-speed gearing component, the front-seat input gear assembly is single row configuration, and middle row's change-speed gearing component is in parallel into two-row structure with heel row change-speed gearing component；The input of the front-seat input gear assembly is connected with the input shaft, and middle row's change-speed gearing component is connected output shaft jointly with the output end of heel row change-speed gearing component；The output end of the front-seat input gear assembly is connected by first clutch and the 3rd clutch with middle row's change-speed gearing component and heel row change-speed gearing component respectively, and the heel row change-speed gearing component is connected by second clutch with the input shaft.The present invention has the advantages that transmission efficiency, a gear gearratio is big, transmission amplitude is big, speed is small, fast smaller than step interval than Spline smoothing fluctuation.
Description
Technical field
The present invention relates to one kind based on improvement lever method six speed transmission.
Background technology
Transmission market occupation rate highest is six speed transmission at present, and corresponding six speed planetary gear mechanism is by three rows
Composition, general front row are single, and middle heel row is in parallel double, according to the annexation of double and single output in parallel, six speed
Planetary gears shares two classes, 6 kinds of schemes.The speed vector figure established according to lever method is improved, six speed planetary gear mechanism
It is rational that two 6 kinds of class schemes, which only have two kinds, and because every row can be single-stage or multistage two kinds of situations, so in theory most
More shared 2x23=16 seed schemes.
Currently used two kinds of reasonable plans of six speed planetary gear mechanism.
The row's relation of six speed planetary gear mechanism three is：Front row is single (being joined directly together with input shaft), and middle heel row is in parallel
Double, front-seat output element and in parallel certain double one or two input element are generally by clutch (or without clutch
Device, but there has been the brake of phase same-action at front row) connected, it is that connection is closed that front-seat output and parallel connection are double when clutch works
System, front-seat output and in parallel double there is no annexation when clutch does not work.Front row output and double this connection in parallel
Mode, the bad expression of traditional lever method, so need to make traditional lever method some improvement, it is specific as follows：Three rows continue to make
With in parallel four double node equivalent levers, but the input of equivalent lever has two class modes, and one kind is connected with front-seat export
Equivalent inpnt in ', equivalent inpnt speed be m (because the main function of speed changer be slow down, front-seat output speed namely
Equivalent inpnt speed m<1), another kind of is the input in being joined directly together with input shaft, and input speed is 1.
Fig. 1 is the speed vector figure of two class reasonable plans of six speed planetary gear mechanism.Jth keeps off rotating speed line and out lines
Intersection point abscissa value is the output speed value n of the gearj(j=1,2 ..., 7), it is to reverse gear corresponding to j=7.Can from figure
Arrive：Scheme one has direct gear, 3 gears that slow down, 2 overgears and 1 to reverse gear；Scheme two does not have direct gear, there are 4 decelerations to keep off,
2 overgears and 1 are reversed gear.The characteristics of this two classes scheme speed vector figure, is as follows：1) it is equivalent that scheme one, which only has a component,
In ' is inputted, this component corresponding node is the end points (D nodes) away from output point；2) it is equivalent inpnt that scheme two, which has two components,
In ', node corresponding to them is two end points (A and D node)；3) the rotating speed line starting and terminal point of this two classes scheme is all identical, its
Middle rotating speed line 1. -4. have a common ground, it is exactly the velocity terminal of end points adjacent with output point.
According to Fig. 1 speed vector figure, it is easy to which diagram obtains two class reasonable plan gearratio formula shown in table 1, sees
Table 1. can see from table 1：As the overgear (the 5th~6 gear) of two class schemes with the gearratio formula to reverse gear is, and the 1st
~4 gear gearratio formula are different.
The gearratio formula of 1 liang of class reasonable plan of table
Know that six speed planetary gear mechanism has a two class reasonable plans by knowledge above, but due to every row can be single-stage or
Multistage two kinds of situations, so at most shared 2x2 in theory3=16 seed schemes.The conventional subscheme of scheme one has at present：(1)
Front row is single-stage, double parallel connection is Ravigneaux formula (scheme one：Single-stage+Ravigneaux), U660E that Toyota Camry carries and wide
Vapour Toyota Highlander U760E speed changers are all this seed schemes；(2) front row be twin-stage, it is in parallel it is double be classical Simpson
CR-SS (schemes one：Twin-stage+classical Simpson), A760E the and A761E speed changers carried on Toyota Lexus GS430 are
This seed scheme.
The conventional subscheme of scheme two is that front row is single-stage, and double parallel connection is Ravigneaux formula (scheme two：Single-stage+La Wei
Na), the AT6 speed changers of Japanese Ai Xin companies production are this seed schemes, and AT6 is Duo Jia motor corporations (such as Toyota, Buick, snow
Buddhist orchid etc.) it is supporting.It is twin-stage that design, which has a row, above, and the present invention devises a kind of three rows of the subscheme using scheme two
All it is the planetary gears (scheme two of single-stage：Single-stage+modified Simpson), wherein it is in parallel it is double be modified Simpson
Formula CR-CR, because three rows are single-stages, transmission efficiency is than using the high of twin-stage.Corresponding relation is arranged too in the A in Fig. 1 corresponding
Sun wheel S2, carrier and rear ring gear component PC are ranked during B is corresponding2-R3, C corresponds to intermediate row teeth circle and heel row planet carrier component R2-
PC3, D corresponds to heel row sun gear S3。
In above two scheme, gear number is less, and the transmission efficiency of six speed planetary gear mechanism need to be improved.
The content of the invention
In consideration of it, applicant is studied and improved, there is provided a kind of three row be all single-stage six speed planetary gear mechanism with
And speed changer.
In order to solve the above problems, the present invention uses following scheme：
One kind based on improve lever method six speed transmission, including front-seat input gear assembly, middle row's change-speed gearing component and
Heel row change-speed gearing component, the front-seat input gear assembly are single row configuration, and middle row's change-speed gearing component becomes with heel row
Fast gear assembly is in parallel into two-row structure；The input of the front-seat input gear assembly is connected with the input shaft, described
Middle row's change-speed gearing component is connected output shaft jointly with the output end of heel row change-speed gearing component；The front-seat input gear group
The output end of part passes through first clutch and the 3rd clutch and middle row's change-speed gearing component and heel row change-speed gearing component respectively
It is connected, the heel row change-speed gearing component is connected by second clutch with the input shaft；The front-seat input gear assembly
Output end and heel row change-speed gearing component input between the first brake is installed, the input shaft and heel row speed change
Second brake and one-way clutch are installed between the input of gear assembly.
Further improvement as above-mentioned technical proposal：
The front-seat input gear assembly includes the front-seat planetary gear being installed on front-seat planet carrier and the preceding rows of planetary
Take turns external toothing front-seat sun gear, with the front-seat gear ring of the front-seat planetary gear internal messing, the input of the front-seat gear ring with
The input shaft is connected；Middle row's change-speed gearing component includes middle seniority among brothers and sisters carrier, the middle seniority among brothers and sisters being installed in middle seniority among brothers and sisters carrier
Star-wheel, the intermediate row teeth circle with the middle middle row's sun gear for ranking star-wheel external toothing, with the middle seniority among brothers and sisters star-wheel internal messing；Institute
Stating heel row change-speed gearing component includes heel row planet carrier, the heel row planetary gear being installed on heel row planet carrier and the rear seniority among brothers and sisters
The heel row sun gear of star-wheel external toothing, the rear ring gear with the heel row planetary gear internal messing；
The input of the front-seat gear ring is connected with the input shaft, and the input of middle row's sun gear passes through described
One clutch is connected with the output end of front-seat planet carrier, the input of the heel row sun gear by the 3rd clutch with
The output end of front-seat planet carrier is connected and is provided with the first brake, and the intermediate row teeth circle and heel row planet carrier are directly connected into
The input of integral and described heel row planet carrier passes through the second clutch and the input axis connection and the braking of installation second
Device and one-way clutch, the middle seniority among brothers and sisters carrier and rear ring gear are directly connected to integral and its output end and the output shaft
It is connected.
The technical effects of the invention are that：
The gear transmission of the present invention is big, that is, the driving force of maximum can be obtained during vehicle starting, and the biography of the present invention
It is also maximum to move than amplitude；Speed is than in terms of step, interval fluctuation is small, and present invention speed compares conventional transmissions than step during bottom gear
Bigger, present invention speed is very gentler than step during top gear because automobile high-speed gear with it is more when, the present invention is advantageous；
The row of six speed transmission three of the present invention is single-stage, the two-row structure in parallel of middle heel row so that the present invention has transmission efficiency
A advantages that high, gear gearratio is greatly, transmission amplitude is big, speed is small, fast smaller than step interval than Spline smoothing fluctuation.
Brief description of the drawings
Fig. 1 is the speed vector figure of two class reasonable plans.
Fig. 2 is the speed vector figure of the speed changer of the present invention.
Fig. 3 is the structural representation of the present invention.
Tetra- kinds of transmission ratios of Fig. 4.
Tetra- kinds of transmission gear ratio steps of Fig. 5.
Tetra- kinds of transmission gear ratio step intervals of Fig. 6.
Embodiment
The embodiment of the present invention is described further below in conjunction with the accompanying drawings, how skill is applied to the present invention whereby
Art means solve technical problem, and the implementation process for reaching technique effect can fully understand and implement according to this.Need what is illustrated
It is that, as long as not forming conflict, each embodiment in the present invention and each feature in each embodiment can be combined with each other,
The technical scheme formed is within protection scope of the present invention.
As shown in Figure 2 and Figure 3, the present embodiment based on improving lever method six speed transmission, including front-seat input gear assembly
1st, middle row's change-speed gearing component 2 and heel row change-speed gearing component 3, front-seat input gear assembly 1 are single row configuration, middle row's speed change
Gear assembly 2 is in parallel into two-row structure with heel row change-speed gearing component 3；It is defeated described in the input of front-seat input gear assembly 1
Enter axle in be connected, middle row's change-speed gearing component 2 is connected output shaft out jointly with the output end of heel row change-speed gearing component 3；Before
The output end of row's input gear assembly 1 passes through first clutch C1 and the 3rd clutch C3 and middle row's change-speed gearing component 2 respectively
And heel row change-speed gearing component 3 is connected, heel row change-speed gearing component 3 is connected by second clutch C2 with the input shaft in；
First brake B1, institute are installed between the output end of front-seat input gear assembly 1 and the input of heel row change-speed gearing component 3
State and second brake B2 and one-way clutch F is installed between the input of input shaft in and heel row change-speed gearing component 3.
Front-seat input gear assembly 1 includes being installed on front-seat planet carrier PC1On front-seat planetary gear P1And front-seat planetary gear
P1The front-seat sun gear S of external toothing1And front-seat planetary gear P1The front-seat gear ring R of internal messing1, front-seat gear ring R1Input described in
Input shaft in connections；Middle row's change-speed gearing component 2 includes middle seniority among brothers and sisters carrier PC2, be installed on middle seniority among brothers and sisters carrier PC2On middle seniority among brothers and sisters
Star-wheel P2And middle seniority among brothers and sisters star-wheel P2Middle row's sun gear S of external toothing2And middle seniority among brothers and sisters star-wheel P2The intermediate row teeth circle R of internal messing2；Afterwards
Row's change-speed gearing component 3 includes heel row planet carrier PC3, be installed on heel row planet carrier PC3On heel row planetary gear P3And rear seniority among brothers and sisters
Star-wheel P3The heel row sun gear S of external toothing3And heel row planetary gear P3The rear ring gear R of internal messing3；The front-seat gear ring R1It is defeated
Enter end to be connected with the input shaft in, middle row's sun gear S2Input pass through the first clutch C1 and preceding seniority among brothers and sisters
Carrier PC1Output end connection, the heel row sun gear S3Input pass through the 3rd clutch C3 and front-seat planet carrier
PC1Output end connect and the first brake B1, the intermediate row teeth circle R be installed2With heel row planet carrier PC3It is directly connected into one
Body and the heel row planet carrier PC3Input be connected by the second clutch C2 with the input shaft in and install
Two brake B2 and one-way clutch F, the middle seniority among brothers and sisters carrier PC2With rear ring gear R3It is directly connected to integral and its output end
It is connected with the output shaft out.
In order to obtain multiple gears, planetary gears is required for multiple shifting elements.Scheme two in Fig. 1 of the invention
On the basis of be improved, the double shifting element arrangement in parallel of use is：(1) have on A, C, D node speed polar plot one it is defeated
Enter speed, so setting a clutch before them；(2) D nodes forward gear have speed be 0 when, so being set before it
Put a brake, it is to be noted that D nodes are simultaneously when having brake and clutch, brake than clutch closer to node,
It is exactly whether brake is not worked by clutch and influenceed；(3) C nodes forward gear and reversing gear all exist speed for 0 when, so
One brake one-way clutch in parallel is set before it, braked when brake is responsible for reversing gear, one-way clutch is responsible for
Brake or worked in engine braking during forward gear.Speed changer of the present invention as shown in Figure 2 can so be obtained (using this
The speed changer of the planetary gears of invention) speed vector figure (containing shifting element), engaging element shares 6 (3 clutches
Device (C1, C2, C3), 2 brakes (B1, B2) and 1 one-way clutch (F)), each working law such as table for keeping off shifting element
Shown in 2, black circle expression bonding state, namely the shifting element are in running order.
Each gear shifting element working law of 2 speed changer of the present invention of table
In the present invention, the structure and the number of teeth of speed changer and being calculated as follows for gearratio.
Fig. 3 is the structural representation of the of the present invention speed changer corresponding with Fig. 2, and front row is single-stage, and front-seat in represents it
It is connected with input shaft in, middle heel row is in parallel double, using modified Simpson CR-CR.Each row's parameter is as follows：ZS1=
ZS2=45, ZS3=39, ZR1=ZR2=ZR3=81, ZP1=ZP2=18, ZP3=21, α1=α2=81/45=1.8, α3=81/
39=2.077, K1=α1=1.8, K2=α2=1.8, K3=α3=2.077, m=K1/ (1+K1)=0.643.
Wherein Z represents the number of teeth, and subscript is corresponding gear, such as ZS1=45 represent sun gear S1The number of teeth be 45；αjRepresent
The gear ratio of jth toothrow circle and sun gear, subscript 1,2,3 correspond to front-seat, middle row, heel row respectively；Kj represents that jth parallelism example is normal
Number, j implications are the same；M represents equivalent inpnt speed.
With reference to table 2 and Fig. 2, it is as follows that diagram obtains the method that speed changer of the present invention respectively keeps off gearratio：
(1) 1 gear：C1 and F work
C1 work makes S2Speed be in ', namely nS2=m, F work make nR2=nPC3=0, connect the two velocities
Terminal can obtain rotating speed line 1. with output speed n1, had by similar triangles：
(2) 2 gears：C1 and B1 work
C1 work makes nS2=m, B1 work make nS3=0,2. and n rotating speed line can be obtained2, had by similar triangles：
(3) 3 gears：C1 and C3 work
C1 work makes nS2=m, C3 work make nS33. and n=m, rotating speed line can be obtained3=m, so having：
(4) 4 gears：C1 and C2 work
C1 work makes nS2=m, C2 work make nR2=nPC3=1,4. and n rotating speed line can be obtained4, had by similar triangles：
(5) 5 gears：C2 and C3 work
C2 work makes nR2=nPC3=1, C3 work make nS35. and n=m, rotating speed line can be obtained5, had by similar triangles：
(6) 6 gears：C2 and B1 work
C2 work makes nR2=nPC3=1, B1 work make nS3=0,6. and n rotating speed line can be obtained6, had by similar triangles：
(7) reverse gear R：C3 and B2 work
C3 work makes nS3=m, B2 work make nR2=nPC3=0,7. and the output speed n that reverses gear rotating speed line can be obtained7, from Fig. 6
In it can be seen that n7It is negative, direction is with input direction on the contrary, being had by similar triangles：
4) contrast of four kinds of speed changers is as shown in table 3.
The contrast of 3 four kinds of speed changers of table
It is gearratio to evaluate one of index of speed changer quality, and gearratio amplitude (is equal to i1/i6, it is also equal to speed and multiplies than step
Product) it is the bigger the better；And the gear speed per hour that requires to slow down is than step (ratio of the gearratio of adjacent two gear) relatively large, overgear
Speed per hour is more relatively small than step, is so advantageous to steady and raising dynamic property of shifting gears；Because bottom gear is generally used for starting to walk, vapour
Car owner's is top gear, so the speed of top gear is more the smaller the better than step interval, because interval is smaller more to reduce gearshift
Switching time.
Evaluation index can also be dimensional parameters and technological parameter etc..Dimensional parameters are that have with planet row appearance profile size
The parameter of pass, represented with each row's gear ratio α, α ∈ (1.4,4.5), when α=2.7 are best.Technological parameter is the system with speed changer
The parameter of technique is made, with T=αmin/αmaxTo represent, αminAnd αmaxGear ratio α, the T ∈ (0.33,1) of minimum and maximum respectively,
T is more near better from 1.
Table 3 is Toyota U760E (schemes one：Single-stage+Ravigneaux), Toyota A761E (schemes one：Twin-stage+classical Simpson),
Love letter AT6 (schemes two：Single-stage+Ravigneaux) and speed changer of the present invention (scheme two：Single-stage+improvement Simpson) it is many-sided right
Than Fig. 4~Fig. 6 is the gearratio of four kinds of speed changers, speed than step and the fast comparison diagram than step interval.
It can see from Fig. 4~6 and table 3：In terms of forward gear gearratio, the Toyota U760E and A761E of scheme one are almost
Overlapping, scheme two (AT6 and the present invention) is bigger than the gearratio of one identical gear of scheme, and of the invention one gear gearratio is maximum,
Namely vehicle starting when can obtain the driving force of maximum, and the gearratio amplitude of the present invention is also maximum；Speed is than step side
Face, present invention speed is more bigger than other three kinds of speed changers than step during bottom gear, and the present invention is fast very gentler than step during top gear,
Because when automobile high-speed gear is used more, the present invention is advantageous；Speed than in terms of step interval, the fluctuation of present invention interval is small,
It and can like that letter AT6 and Toyota A761E compares favourably.So in terms of gearratio, the present invention is good, especially gearratio amplitude
A big and gear gearratio is big.
In terms of dimensional parameters, Toyota A761E three row's gear ratio α are not very close to and being too remote from 2.7, so phase
To best；Two row's gear ratio α of the present invention are the same, due to from 2.7 farther out, belonging to medium so considering；Other two kinds
Three row's gear ratio α have gap, and some has greatly small, and master-plan is also medium.In terms of technological parameter, the present invention and Toyota
A761E T is close to 0.9, and other two kinds of speed changers, less than 0.70, the present invention is advantageous.In a word from dimensional parameters and
Technological parameter, the present invention is good.
The row of six speed transmission three of the present invention is single-stage, middle heel row it is in parallel it is double be modified Simpson CR-CR, it
Belong to the subscheme of scheme two.With Toyota U760E (schemes one：Single-stage+Ravigneaux), Toyota A761E (schemes one：Twin-stage+warp
Allusion quotation Simpson) and love letter AT6 (schemes two：Single-stage+Ravigneaux) to compare, speed changer of the present invention has transmission efficiency, a gear
The advantages that gearratio is big, transmission amplitude is big, speed is small, fast smaller than step interval than Spline smoothing fluctuation.
Embodiment provided above is the better embodiment of the present invention, is only used for the convenient explanation present invention, not to this hair
It is bright to make any formal limitation, any those of ordinary skill in the art, if putting forward skill not departing from the present invention
In the range of art feature, using the equivalent embodiment locally changed or modified made by disclosed technology contents, and
Without departing from the technical feature content of the present invention, in the range of still falling within the technology of the present invention feature.
Claims (2)
1. one kind is based on improvement lever method six speed transmission, it is characterised in that：Become including front-seat input gear assembly (1), middle row
Fast gear assembly (2) and heel row change-speed gearing component (3), the front-seat input gear assembly (1) are single row configuration, the middle row
Change-speed gearing component (2) is in parallel into two-row structure with heel row change-speed gearing component (3)；The front-seat input gear assembly (1)
Input be connected with the input shaft (in), middle row's change-speed gearing component (2) is defeated with heel row change-speed gearing component (3)
Go out the common connection output shaft (out) in end；The output end of the front-seat input gear assembly (1) passes through first clutch (C1) respectively
And the 3rd clutch (C3) be connected with middle row's change-speed gearing component (2) and heel row change-speed gearing component (3), the heel row gear teeth
Wheel assembly (3) is connected by second clutch (C2) with the input shaft (in)；The output of the front-seat input gear assembly (1)
The first brake (B1), the input shaft (in) and heel row are installed between end and the input of heel row change-speed gearing component (3)
Second brake (B2) and one-way clutch (F) are installed between the input of change-speed gearing component (3).
It is 2. according to claim 1 based on improvement lever method six speed transmission, it is characterised in that：The front-seat input gear
Component (1) includes being installed on front-seat planet carrier (PC1) on front-seat planetary gear (P1) and the front-seat planetary gear (P1) external toothing
Front-seat sun gear (S1) and the front-seat planetary gear (P1) internal messing front-seat gear ring (R1), the front-seat gear ring (R1) it is defeated
Enter end with the input shaft (in) to be connected；Middle row's change-speed gearing component (2) includes middle seniority among brothers and sisters carrier (PC2), be installed on
Rank carrier (PC2) on middle seniority among brothers and sisters star-wheel (P2) and the middle seniority among brothers and sisters star-wheel (P2) external toothing middle row's sun gear (S2) and
The middle seniority among brothers and sisters star-wheel (P2) internal messing intermediate row teeth circle (R2)；The heel row change-speed gearing component (3) includes heel row planet carrier
(PC3), be installed on heel row planet carrier (PC3) on heel row planetary gear (P3) and the heel row planetary gear (P3) external toothing heel row
Sun gear (S3) and the heel row planetary gear (P3) internal messing rear ring gear (R3)；Front-seat gear ring (the R1) input with
The input shaft (in) is connected, middle row's sun gear (S2) input pass through the first clutch (C1) and preceding rows of planetary
Frame (PC1) output end connection, the heel row sun gear (S3) input pass through the 3rd clutch (C3) and preceding rows of planetary
Frame (PC1) output end connect and the first brake (B1) be installed, the intermediate row teeth circle (R2) and heel row planet carrier (PC3) straight
Connect and link into an integrated entity and the heel row planet carrier (PC3) input pass through the second clutch (C2) and the input shaft
(in) connect and second brake (B2) and one-way clutch (F) are installed, the middle seniority among brothers and sisters carrier (PC2) and rear ring gear (R3)
Integral and its output end is directly connected to the output shaft (out) to be connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710749531.4A CN107514445B (en) | 2017-08-28 | 2017-08-28 | Six-speed transmission based on improved lever method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710749531.4A CN107514445B (en) | 2017-08-28 | 2017-08-28 | Six-speed transmission based on improved lever method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107514445A true CN107514445A (en) | 2017-12-26 |
| CN107514445B CN107514445B (en) | 2024-01-09 |
Family
ID=60724305
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710749531.4A Active CN107514445B (en) | 2017-08-28 | 2017-08-28 | Six-speed transmission based on improved lever method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107514445B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20080016158A (en) * | 2006-08-17 | 2008-02-21 | 현대자동차주식회사 | A six-speed power train of an automatic transmission for a vehicle |
| JP2009174642A (en) * | 2008-01-24 | 2009-08-06 | Honda Motor Co Ltd | Automatic transmission |
| CN103438164A (en) * | 2013-07-27 | 2013-12-11 | 顺德职业技术学院 | Multi-speed gearbox transmission mechanism |
| CN103953699A (en) * | 2014-03-31 | 2014-07-30 | 北京航空航天大学 | Multi-gear transmission with planetary gear structure |
| CN105485271A (en) * | 2014-09-19 | 2016-04-13 | 西安双特智能传动有限公司 | Automatic transmission and planetary gear train thereof |
| CN207229684U (en) * | 2017-08-28 | 2018-04-13 | 无锡职业技术学院 | Based on improvement lever method six speed transmission |
-
2017
- 2017-08-28 CN CN201710749531.4A patent/CN107514445B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20080016158A (en) * | 2006-08-17 | 2008-02-21 | 현대자동차주식회사 | A six-speed power train of an automatic transmission for a vehicle |
| JP2009174642A (en) * | 2008-01-24 | 2009-08-06 | Honda Motor Co Ltd | Automatic transmission |
| CN103438164A (en) * | 2013-07-27 | 2013-12-11 | 顺德职业技术学院 | Multi-speed gearbox transmission mechanism |
| CN103953699A (en) * | 2014-03-31 | 2014-07-30 | 北京航空航天大学 | Multi-gear transmission with planetary gear structure |
| CN105485271A (en) * | 2014-09-19 | 2016-04-13 | 西安双特智能传动有限公司 | Automatic transmission and planetary gear train thereof |
| CN207229684U (en) * | 2017-08-28 | 2018-04-13 | 无锡职业技术学院 | Based on improvement lever method six speed transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107514445B (en) | 2024-01-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9777802B2 (en) | Multi-speed transmission | |
| US6926635B2 (en) | Multi-speed transmission | |
| US6991578B2 (en) | Multistep gear | |
| US9291244B2 (en) | Nine speed automatic transmission | |
| CN206159382U (en) | 11 fast automatic gearbox drive mechanism | |
| CN103148180A (en) | Planetary gear train of automatic transmission for vehicles | |
| CN103807372A (en) | Planetary gear train of automatic transmission for vehicle | |
| CN103807371B (en) | Epicyclic train for the automatic transmission of vehicle | |
| CN104728368A (en) | Six-gear planetary automatic transmission | |
| CN104903616A (en) | Eight-speed powertrain of automatic transmission for vehicle | |
| US20130217534A1 (en) | Multispeed transmission | |
| CN103953699B (en) | A kind of multi-shifting speed variator of planetary gear construction | |
| CN106838153B (en) | A kind of seven previous planetary transmissions of falling four-degree-of-freedom | |
| CN106438878A (en) | Nine-gear planet automatic transmission | |
| CN105485271B (en) | A kind of automatic transmission and its epicyclic train | |
| CN207229684U (en) | Based on improvement lever method six speed transmission | |
| CN104033549B (en) | Eight shift transmissions | |
| CN205383228U (en) | Ten grades of automatic gearbox drive mechanism | |
| CN205503881U (en) | Novel ten grades of automatic gearbox drive mechanism | |
| CN107514445A (en) | Based on improvement lever method six speed transmission | |
| CN107477155B (en) | Four planet row automatic transmission and vehicle | |
| CN207349376U (en) | Based on lever method parallel connection compound planetary gearing | |
| CN110030335A (en) | Complete single schedule speed changer in center of the same race | |
| CN110500390A (en) | One kind seven keeps off planetary automatic transmission | |
| CN102808906B (en) | A kind of automatic transmission and motor vehicles |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 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 |