CN2487592Y - Automatic speed changing box planetary gear train - Google Patents
Automatic speed changing box planetary gear train Download PDFInfo
- Publication number
- CN2487592Y CN2487592Y CN 01218755 CN01218755U CN2487592Y CN 2487592 Y CN2487592 Y CN 2487592Y CN 01218755 CN01218755 CN 01218755 CN 01218755 U CN01218755 U CN 01218755U CN 2487592 Y CN2487592 Y CN 2487592Y
- Authority
- CN
- China
- Prior art keywords
- gear
- star
- gear shift
- wheel
- housed
- 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.)
- Expired - Fee Related
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Abstract
An automatic speed changing box planetary gear train comprises two planetary platoons which are arranged on a box body, a power inputting axle, a power outputting axle, three gear shift clutches and three gear shift arresters. The variable speed requirements of four forward gears and one reverse gear are achieved through controlling the different working states of the gear shift clutch and the gear shift arrester. Compared with the prior various gear trains of same performance, the utility model has a simple and compact structure and fewer parts and can reduce the producing cost, using and maintenance cost of the automatic speed changing box.
Description
The utility model relates to a kind of automatic gearbox of vehicles planet circular system (dividing f-w-d type and two kinds of structures of back-wheel drive type).
At present, the Automatic Transmission of the better performances that automobile adopts four D Drives, the automatic speed changing trains of a reverse gear of adopting more.But their complex structure, maintenance difficult has increased the productive costs of Automatic Transmission and has used service expenditure.
The purpose of this utility model provides a kind of simple and compact for structure, and amount of parts significantly reduces, and can reduce production costs and use the novel train of service expenditure significantly.Can install a kind of energy saver that surmounts in addition as required additional, can reduce consumption of fuel about 20%, improve pollution simultaneously air.
The purpose of this utility model is achieved in that in container body of outer cover, two star rows is housed, a power input shaft, a power take-off shaft, three gear shift sleeves and three gear shift drgs.By preceding center gear, preceding star frame and three preceding star-wheels that are contained on the preceding star frame, star row before front ring gear is formed.By rear center wheel, back star frame and be contained on the star frame of back three after star-wheel, star was arranged after back gear ring was formed.Power input shaft and preceding center gear combine and constitute the power input component of train.Before star frame and back gear ring combine, during D Drive, it is preceding star row's a takeoff output spare, is again simultaneously back star row's power input component; It is the total brake operation spare of front and back star row during reverse gear.Power take-off shaft and back star frame combine and constitute the takeoff output spare of train.Between the front end of preceding star frame and the power input shaft gear shift sleeve C is housed
1, and gear shift drg B is housed between the housing
1Gear shift drg B is housed between front ring gear and the housing
2, and between rear center's wheel shift clutch C is housed
2Rear center's wheel is contained on the power take-off shaft, and gear shift sleeve C is housed between the power take-off shaft
3And gear shift drg B is housed between the housing
3
The principle of work of following each grade of surface analysis:
A, neutral gear:
All not combinations of actuating unit, power can not pass on the output shaft from input shaft.
B, one grade of principle of work (seeing one grade of transmission sketch Fig. 5):
Braking B
2, B
3Power is passed to preceding center gear from input shaft, because front ring gear is by B
2The star-wheel rotation of between center gear and gear ring, rolling on the one hand before braking, power then drive, simultaneously around the center gear revolution, and star frame and back gear ring rotate together before driving, and this motion has been played to slow down and has been increased the effect of turning round; Because rear center's wheel is by B
3Braking, back star-wheel then under the drive of back gear ring, the rotation of rolling on the one hand, simultaneously around rear center's wheel revolution, and star frame and power take-off shaft rotate together after driving, power here is decelerated again to increase has sent change speed gear box after turning round.
The transmitting ratio formula that can obtain one grade according to star row's the equation of motion and constraint equation:
The equation of motion: n
T1+ kn
Q1-(1+k
1) n
J1=0 (1)
n
t2+kn
q2-(1+k
2)n
j2＝0 (2)
N in the formula
T1, n
T2The rotating speed of center gear before and after being respectively.
n
Q1, n
Q2The rotating speed of gear ring before and after being respectively.
n
J1, n
J2The rotating speed of star frame before and after being respectively.
k
1, k
2The ratio of number of teeth of center gear and front and back gear ring before and after being respectively.
One grade of constraint equation: n
Q1=0, n
T2=0 n
J1=n
Q2
One grade of constraint equation substitution equation of motion (1) and (2) are got one grade of transmitting ratio formula:
i
1＝n
t1/n
j2＝(1+k
1)(1+k
2)/k
2
C, second gear principle of work (seeing second gear transmission sketch Fig. 6):
Braking B
2, in conjunction with C
3Power is passed to preceding center gear from input shaft, because front ring gear is by B
2Star-wheel and preceding star frame were done to slow down to increase and are passed to the back gear ring after turning round motion before braking, power then drove.C
3In conjunction with will back star row locking, back star is arranged and is only made transport motion power is passed to output shaft.Therefore, preceding star row's transmitting ratio is exactly the transmitting ratio of second gear.
Second gear constraint equation: n
Q1=0
With n
Q1=0 substitution (1) formula gets second gear transmission formula:
i
2＝n
t1/n
j1＝1+K
D, third gear principle of work (seeing third gear transmission sketch Fig. 7):
In conjunction with C
1, braking B
3Because C
1Combination make before star row locking.Power passes through C from input shaft
1Star frame and back gear ring before passing to.Because rear center's wheel is by B
3Braking, power then drive back star-wheel and back star frame and do to slow down to increase to turn round and pass to power take-off shaft after the motion and send change speed gear box.Therefore, back star row's transmitting ratio is exactly the three-speed transmitting ratio.
Third gear constraint equation: n
T2=0
With n
T2=0 substitution equation (2) then obtains this formula of third gear transmission.
i
3＝n
q2/n
j2＝(1+k
2)/k
2
E, fourth gear principle of work (seeing fourth gear sketch Fig. 8):
In conjunction with C
1, in conjunction with C
3C
1And C
3Combination make before and after all lockings of star row, all parts all have only transport motion, power passes through C from input shaft
1, preceding star frame, back gear ring, back star-wheel and back star frame, C
3Enter output shaft, do not make variable-speed motion midway.So the four-speed transmitting ratio is i
4=1.
F, reverse gear principle of work (seeing reverse gear transmission sketch Fig. 9):
Braking B
1, in conjunction with C
2B
1Braking braked preceding star frame and back gear ring two parts simultaneously.C
2Combination front ring gear and rear center wheel is combined, power enters preceding center gear from input shaft.Because preceding star frame is braked, power then drives the nipper backward rotation by preceding star-wheel, and having played simultaneously slows down increases torsion effect.This moment, rear center's wheel was followed the front ring gear backward rotation, because of the back gear ring is braked, power then drives the back star-wheel rotation of rolling on the one hand, simultaneously around rear center's wheel revolution, and driving back star frame and output shaft rotates together, power here is decelerated again to increase to turn round with backward rotation sends change speed gear box with power.
Reverse gear constraint equation: n
J1=n
Q2=0 n
Q1=n
T2
With the reverse gear constraint equation substitution equation of motion (1) and (2), get the reverse gear ratio formula:
i
R＝n
t1/n
j2＝-K(1+K
2)
Owing to adopted above-mentioned transmission scheme, when having reduced amount of parts, kept the super performance of a reverse gear of four D Drives.Because it is simple and compact for structure, use parts few, so greatly reduce productive costs and use service expenditure.
Below in conjunction with drawings and Examples the utility model is further specified.
Fig. 1 is a rear-guard type transmission sketch of the present utility model;
Fig. 2 is forerunner's type transmission sketch of the present utility model;
Fig. 3 is that the utility model rear-guard type installs the transmission sketch that surmounts energy saver additional;
Fig. 4 is that the utility model forerunner type installs the transmission sketch that surmounts energy saver additional;
Fig. 5 is one grade of transmission sketch;
Fig. 6 is a second gear transmission sketch;
Fig. 7 is a third gear transmission sketch;
Fig. 8 is the fourth gear sketch;
Fig. 9 is a reverse gear transmission sketch.
Among the figure 1, preceding star frame, 2, back star frame, 3, drg B
3, 4, power-transfer clutch C
2, 5 power-transfer clutch C
3, 6, power input shaft, 7, turbine transformer, 8, power-transfer clutch C
1, 9, preceding center gear, 10, preceding star-wheel, 11, drg B
1, 12 drg B
2, 13 front ring gears, 14, power take-off shaft, 15, back gear ring, 16, the back star-wheel, 17, rear center wheel, 18, surmount the energy saver lockup clutch, 19, surmount energy saver, 20, transmission shaft, 21, transmission gear, 22, transmission ring gear, 23, main deceleration driving gear, 24, main deceleration ring gear, 25, differential assembly.
In the embodiment in figure 1, the power of power input shaft (6) comes from turbine transformer (7).Power input shaft (6) and preceding center gear (9) combine, and form the power input component of train.Star was arranged before three preceding star-wheels (10) on the star frame (1) and front ring gear were formed by preceding center gear (9), preceding star frame (1) and before being contained in.Before star frame (1) and back gear ring (1 5) be combined into an assembly set, during D Drive, it is preceding star row's a takeoff output spare, also is simultaneously back star row's power input component, during reverse gear it be before and after the brake operation spare that has of star row.By back gear ring (15), back star frame (2) and after being contained on back star frame (2) three star-wheel (16) and be contained in rear center's wheel (17) on the power take-off shaft (14) forms after star arrange.Back star frame (2) and power take-off shaft (14) are combined as a whole, and it is the takeoff output spare of train.In order to control the drive path of different gear power, between the front end of preceding star frame (1) and power input shaft (6), gear shift sleeve C is housed
1And gear shift drg B is housed between the casing (8),
1(11).Between front ring gear (13) and rear center's wheel (17), gear shift sleeve C is housed
2And gear shift drg B is housed between the casing (4),
2(12).Between rear center's wheel (17) and power take-off shaft (14), gear shift sleeve C is housed
3And gear shift drg B is housed between the casing (5),
3(3).
In Fig. 2, the variable part is identical with Fig. 1, and difference is to have added driving device after the variable part, main reduction gear and diff, and wherein running part comprises transmission gear (21), transmission ring gear (22) and transmission shaft (20).The main deceleration comprises that transmission shaft (20) hold the main deceleration driving gear of adorning (23) and be contained in main deceleration ring gear (24) on the diff (25).
In Fig. 3, be on the power take-off shaft of Fig. 1 change speed gear box, to have added a cover to surmount energy saver (18) and (19).Its detail principle of work is seen the Energy-saving gearbox specification sheets of declaring in person.The number of declaring: 01218754.2
In Fig. 4, be between the transmission ring gear (22) of Fig. 2 change speed gear box and transmission shaft (20), to have installed a cover additional to surmount energy saver (18) and (19).
Claims (3)
1, a kind of planet circular system that is used for automatic gearbox of vehicles, it is that two star rows are housed in casing, a power input shaft, a power take-off shaft, three gear shift sleeves and three gear shift drgs are formed, it is characterized in that: power input shaft and preceding center gear are combined as a whole, by preceding center gear, before the star frame and be contained in before three preceding star-wheels on the star frame and front ring gear form before star row: preceding star frame and back gear ring are combined into a combination, by the back gear ring, star-wheel and rear center's wheel of being contained on the power take-off shaft are formed back star row after three on back star frame and the back star frame, and back star frame and power take-off shaft are combined into one.
2, planet circular system according to claim 1 is characterized in that: between preceding star frame and the power input shaft gear shift sleeve C is housed
1, between front ring gear and the rear center's wheel gear shift sleeve C is housed
2, between rear center's wheel and the power take-off shaft gear shift sleeve C is housed
3
3, planet circular system according to claim 1 is characterized in that: gear shift drg B is housed between preceding star frame and the casing
1, gear shift drg B is housed between front ring gear and the casing
2, between rear center's wheel and the casing gear shift drg B is housed
3
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01218755 CN2487592Y (en) | 2001-04-03 | 2001-04-03 | Automatic speed changing box planetary gear train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01218755 CN2487592Y (en) | 2001-04-03 | 2001-04-03 | Automatic speed changing box planetary gear train |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2487592Y true CN2487592Y (en) | 2002-04-24 |
Family
ID=33636727
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01218755 Expired - Fee Related CN2487592Y (en) | 2001-04-03 | 2001-04-03 | Automatic speed changing box planetary gear train |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2487592Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101473147B (en) * | 2006-06-23 | 2012-12-12 | 腓特烈斯港齿轮工厂股份公司 | Dual-clutch transmission |
-
2001
- 2001-04-03 CN CN 01218755 patent/CN2487592Y/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101473147B (en) * | 2006-06-23 | 2012-12-12 | 腓特烈斯港齿轮工厂股份公司 | Dual-clutch transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |