CN205298430U - Two separation and reunion fourth speed automatic gearbox of planetary geared - Google Patents
Two separation and reunion fourth speed automatic gearbox of planetary geared Download PDFInfo
- Publication number
- CN205298430U CN205298430U CN201620069615.4U CN201620069615U CN205298430U CN 205298430 U CN205298430 U CN 205298430U CN 201620069615 U CN201620069615 U CN 201620069615U CN 205298430 U CN205298430 U CN 205298430U
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- China
- Prior art keywords
- clutch coupling
- gear
- seat
- clutch
- sun
- 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.)
- Withdrawn - After Issue
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Abstract
The utility model discloses a two separation and reunion fourth speed automatic gearbox of planetary geared, including power input shaft (1) and power output shaft (23), the first output of power input shaft (1) is connected with the input of second clutch (3) and third clutch (4) respectively through first clutch (2), the output of second clutch (3) is connected with front -seat ring gear (8) of planetary gear mechanism, the output of third clutch (4) is connected with front -seat sun gear (6) of planetary gear mechanism. The utility model discloses an automatic gearbox adopts planetary gear structure, except that the advantage that has two separation and reunion automatic gearbox, has still for parallel shaft type gear structure that compact structure, long service life, operation are more steady, the noise low, the characteristics of technology maturation.
Description
Technical field
The utility model relates to two clutch four speed automatic transmission of a kind of planetary gear type.
Background technology
Automatic transmission generally comprises the friction engagement element of such as planetary gear unit, clutch coupling and stopper. Automatic transmission is carried out energy transformation and transmission of power, utilize the component such as oil pump, oil circuit loop, clutch coupling, planetary set, multiple magnetic valves to realize automatic transmission, drive for the automobile of people to bring and easily easy control impression.
And existing double-clutch automatic gearbox has two power input clutch, the power input of odd number shelves is responsible for by one of them clutch coupling, and the power input of even gear is responsible for by another clutch coupling, and it has, and gearshift property steady, comfortable is good, the advantage of fuel-economizing. At present, existing double-clutch automatic gearbox generally adopts parallel-axis type gear structure, and the automatic transmission structure of this structure is compact not, runs steady not, and noise is bigger, it may also be useful to the life-span is low.
Practical novel content
The utility model object is that the defect existed for prior art provides a kind of five gear planetary gear automatic transmissions.
The utility model for achieving the above object, adopts following technical scheme: two clutch four speed automatic transmission of a kind of planetary gear type, it is characterised in that,
Comprise power input shaft 1 and power output shaft 23;
First output terminal of described power input shaft 1 is connected with the input terminus of the 2nd clutch coupling 3 and the 3rd clutch coupling 4 respectively by the first clutch coupling 2, the described output terminal of the 2nd clutch coupling 3 is connected with the front-seat gear ring 8 of sun and planet gear mechanism, and the described output terminal of the 3rd clutch coupling 4 is connected with the front-seat sun gear 6 of sun and planet gear mechanism;
2nd output terminal of described power input shaft 1 is connected with the input terminus of the 5th clutch coupling 12 and the 6th clutch coupling 13 respectively by the 4th clutch coupling 11, the described output terminal of the 5th clutch coupling 12 is connected with the rear ring gear 17 of sun and planet gear mechanism, and the output terminal of described 6th clutch coupling 13 is connected with rear row's sun gear 15 of sun and planet gear mechanism;
Wherein, the front-seat planet carrier 9 of the front-seat sun and planet gear 7 of band it is provided with between described front-seat sun gear 6 and front-seat gear ring 8;
The rear seniority among brothers and sisters carrier 18 of the rear rows of planetary gear 16 of band it is provided with between row's sun gear 15 and rear ring gear 17 after described;
First input terminus of described power output shaft 23 is connected by the output terminal of the 7th clutch coupling 22 with described front-seat planet carrier 9, its the 2nd input terminus is connected with the output terminal of described 5th clutch coupling 12 by the 8th clutch coupling 21, and its 3rd input terminus is connected by the output terminal of the 9th clutch coupling 20 with described rear seniority among brothers and sisters carrier 18.
Further, it is provided with the first stopper 5 that described front-seat gear ring 8 is braked between described 2nd clutch coupling 3 and front-seat gear ring 8, it is provided with the 2nd stopper 10 that described front-seat sun gear 6 is braked between described 3rd clutch coupling 4 and front-seat sun gear 6, the 3rd stopper 14 to the braking of described rear ring gear 17 it is provided with between described 5th clutch coupling 12 and rear ring gear 17, it is provided with the 4th stopper 24 that described rear row's sun gear 15 is braked between described 6th clutch coupling 13 and rear row's sun gear 15, it is provided with between described 9th clutch coupling 20 and rear seniority among brothers and sisters carrier 18 the 5th stopper 19 that described rear seniority among brothers and sisters carrier 18 is braked.
The beneficial effects of the utility model: automatic transmission of the present utility model adopts planetary gear construction, except the advantage with double-clutch automatic gearbox, relative to parallel-axis type gear structure also have compact construction, long service life, running more steadily, noise is low, the feature of technology maturation.
Accompanying drawing explanation
Fig. 1 structural representation of the present utility model.
Embodiment
Shown in Fig. 1, it relates to two clutch four speed automatic transmission of a kind of planetary gear type, comprises power input shaft 1 and power output shaft 23;
First output terminal of described power input shaft 1 is connected with the input terminus of the 2nd clutch coupling 3 and the 3rd clutch coupling 4 respectively by the first clutch coupling 2, the described output terminal of the 2nd clutch coupling 3 is connected with the front-seat gear ring 8 of sun and planet gear mechanism, and the described output terminal of the 3rd clutch coupling 4 is connected with the front-seat sun gear 6 of sun and planet gear mechanism;
2nd output terminal of described power input shaft 1 is connected with the input terminus of the 5th clutch coupling 12 and the 6th clutch coupling 13 respectively by the 4th clutch coupling 11, the described output terminal of the 5th clutch coupling 12 is connected with the rear ring gear 17 of sun and planet gear mechanism, and the output terminal of described 6th clutch coupling 13 is connected with rear row's sun gear 15 of sun and planet gear mechanism;
Wherein, the front-seat planet carrier 9 of the front-seat sun and planet gear 7 of band it is provided with between described front-seat sun gear 6 and front-seat gear ring 8;
The rear seniority among brothers and sisters carrier 18 of the rear rows of planetary gear 16 of band it is provided with between row's sun gear 15 and rear ring gear 17 after described;
First input terminus of described power output shaft 23 is connected by the output terminal of the 7th clutch coupling 22 with described front-seat planet carrier 9, its the 2nd input terminus is connected with the output terminal of described 5th clutch coupling 12 by the 8th clutch coupling 21, and its 3rd input terminus is connected by the output terminal of the 9th clutch coupling 20 with described rear seniority among brothers and sisters carrier 18.
In further scheme, it is provided with the first stopper 5 that described front-seat gear ring 8 is braked between described 2nd clutch coupling 3 and front-seat gear ring 8, it is provided with the 2nd stopper 10 that described front-seat sun gear 6 is braked between described 3rd clutch coupling 4 and front-seat sun gear 6, the 3rd stopper 14 to the braking of described rear ring gear 17 it is provided with between described 5th clutch coupling 12 and rear ring gear 17, it is provided with the 4th stopper 24 that described rear row's sun gear 15 is braked between described 6th clutch coupling 13 and rear row's sun gear 15, it is provided with between described 9th clutch coupling 20 and rear seniority among brothers and sisters carrier 18 the 5th stopper 19 that described rear seniority among brothers and sisters carrier 18 is braked.
During use, it is assumed that the front-seat sun gear number of teeth is ZBefore 1, the gear ring number of teeth is ZBefore 2, then �� can be madeBefore=ZBefore 2/ZBefore 1; Rear row's sun gear number of teeth is ZAfter 1, the gear ring number of teeth is ZAfter 2, then �� can be madeAfter=ZAfter 2/ZAfter 1; And ��After> ��Before. It is below each gear power transmission line and gear ratio calculation.
1 gear: the 4th clutch coupling 11, the 6th clutch coupling 13, the 3rd stopper 14, the 9th clutch coupling 20 work. Power from power input shaft 1 through the 4th clutch coupling 11, the 6th clutch coupling 13 by after arrange sun gear 15 and input, through after rows of planetary gear 16, after rank carrier 18, the 9th clutch coupling 20, power output shaft 23 outputting power. Calculate according to movement relation formula, 1 gear transmitting ratio i1=1+ ��After��
2 gears: the first clutch coupling 2, the 3rd clutch coupling 4, first stopper 5, the 7th clutch coupling 22 work. Power is inputted by front-seat sun gear 6 from power input shaft 1 through the first clutch coupling 2, the 3rd clutch coupling 4, premenstrual rows of planetary gear 7, front-seat planet carrier 9, the 7th clutch coupling 22, power output shaft 23 outputting power. Calculate according to movement relation formula, 2 gear transmitting ratio i2=1+ ��Before��
3 gears: the 4th clutch coupling 11, the 5th clutch coupling 12, the 9th clutch coupling 20, the 4th stopper 24 work. Power passes to rear ring gear 17 from power input shaft 1 through the 4th clutch coupling 11, the 5th clutch coupling 12, then through after rows of planetary gear 16, after rank carrier 18, the 9th clutch coupling 20, power output shaft 23 outputting power. Calculate according to movement relation formula, 3 gear transmitting ratio i3=1+1/ ��After��
4 gears: the first clutch coupling 2, the 2nd clutch coupling 3, the 3rd clutch coupling 4, the 7th clutch coupling 22 work. Power from power input shaft 1 through the first clutch coupling 2, pass to front-seat gear ring 8 by the 2nd clutch coupling 3 simultaneously, pass to front-seat sun gear 6 by the 3rd clutch coupling 4, more premenstrual rows of planetary gear 7, front-seat planet carrier 9, the 7th clutch coupling 22, power output shaft 23 outputting power. Calculate according to movement relation formula, 4 gear transmitting ratio i4=1.
Reverse gear [R gear]: the 4th clutch coupling 11, the 6th clutch coupling 13, the 5th stopper 19, the 8th clutch coupling 21 work. Power arranges sun gear 15 through the 4th clutch coupling 11, the 6th clutch coupling 13 after passing to by power input shaft 1, through after rows of planetary gear 16, rear ring gear 17, the 8th clutch coupling 21, power output shaft 23 outputting power. Calculating according to movement relation formula, reverse gear transmitting ratio iR=-��After��
The foregoing is only better embodiment of the present utility model, not in order to limit the utility model, all within spirit of the present utility model and principle, any amendment of doing, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (2)
1. two clutch four speed automatic transmission of planetary gear type, it is characterised in that,
Comprise power input shaft (1) and power output shaft (23);
First output terminal of described power input shaft (1) is connected with the input terminus of the 2nd clutch coupling (3) and the 3rd clutch coupling (4) respectively by the first clutch coupling (2), the described output terminal of the 2nd clutch coupling (3) is connected with the front-seat gear ring (8) of sun and planet gear mechanism, and the described output terminal of the 3rd clutch coupling (4) is connected with the front-seat sun gear (6) of sun and planet gear mechanism;
2nd output terminal of described power input shaft (1) is connected with the input terminus of the 5th clutch coupling (12) and the 6th clutch coupling (13) respectively by the 4th clutch coupling (11), the described output terminal of the 5th clutch coupling (12) is connected with the rear ring gear (17) of sun and planet gear mechanism, and the output terminal of described 6th clutch coupling (13) is connected with rear row's sun gear (15) of sun and planet gear mechanism;
Wherein, the front-seat planet carrier (9) of the front-seat sun and planet gear (7) of band it is provided with between described front-seat sun gear (6) and front-seat gear ring (8);
The rear seniority among brothers and sisters carrier (18) being provided with the rear rows of planetary gear (16) of band between sun gear (15) and rear ring gear (17) is arranged after described;
First input terminus of described power output shaft (23) is connected by the output terminal of the 7th clutch coupling (22) with described front-seat planet carrier (9), its the 2nd input terminus is connected with the output terminal of described 5th clutch coupling (12) by the 8th clutch coupling (21), its 3rd input terminus pass through the 9th clutch coupling (20) with described after rank carrier (18) output terminal be connected.
2. two clutch four speed automatic transmission of a kind of planetary gear type as claimed in claim 1, it is characterized in that, it is provided with the first stopper (5) that described front-seat gear ring (8) is braked between described 2nd clutch coupling (3) and front-seat gear ring (8), it is provided with the 2nd stopper (10) that described front-seat sun gear (6) is braked between described 3rd clutch coupling (4) and front-seat sun gear (6), the 3rd stopper (14) braked by described rear ring gear (17) it is provided with between described 5th clutch coupling (12) and rear ring gear (17), it is provided with the 4th stopper (24) arranged sun gear (15) after described and brake between described 6th clutch coupling (13) and rear row's sun gear (15), it is provided with between described 9th clutch coupling (20) and rear seniority among brothers and sisters carrier (18) the 5th stopper (19) ranked carrier (18) after described and brake.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620069615.4U CN205298430U (en) | 2016-01-19 | 2016-01-19 | Two separation and reunion fourth speed automatic gearbox of planetary geared |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620069615.4U CN205298430U (en) | 2016-01-19 | 2016-01-19 | Two separation and reunion fourth speed automatic gearbox of planetary geared |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205298430U true CN205298430U (en) | 2016-06-08 |
Family
ID=56426568
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620069615.4U Withdrawn - After Issue CN205298430U (en) | 2016-01-19 | 2016-01-19 | Two separation and reunion fourth speed automatic gearbox of planetary geared |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205298430U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546060A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Planetary gear type double-clutch four-gear automatic transmission |
-
2016
- 2016-01-19 CN CN201620069615.4U patent/CN205298430U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546060A (en) * | 2016-01-19 | 2016-05-04 | 无锡商业职业技术学院 | Planetary gear type double-clutch four-gear automatic transmission |
| CN105546060B (en) * | 2016-01-19 | 2017-09-19 | 无锡商业职业技术学院 | A kind of double speed automatic transmissions of clutch four of planetary gear type |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20160608 Effective date of abandoning: 20170919 |