CN203176273U - Nine-gear automatic transmission - Google Patents
Nine-gear automatic transmission Download PDFInfo
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- CN203176273U CN203176273U CN 201320195746 CN201320195746U CN203176273U CN 203176273 U CN203176273 U CN 203176273U CN 201320195746 CN201320195746 CN 201320195746 CN 201320195746 U CN201320195746 U CN 201320195746U CN 203176273 U CN203176273 U CN 203176273U
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Abstract
The utility model discloses a nine-gear automatic transmission which is in a double-intermediate-shaft structure and transfers power by combining a planetary gear with a conventional gear and a synchronizer. The nine-gear automatic transmission comprises the planetary gear, intermediate shafts, a driving gear, a driving-gear gear, a main speed reducer, a differential mechanism, a gear operating component and an electronic-control power unit, wherein the power coming from an engine is input from the planetary gear and then transferred to the driving gear, the driving gear drives the driving-gear gear to rotate, the power is transferred to the intermediate shafts through the synchronizer, then transferred to the main speed reducer through the intermediate shafts and finally output by the differential mechanism, the electronic-control power unit controls the gear operating component to work cooperatively to finish gear shifting according to driving conditions, and the power is transferred by the double intermediate shafts alternately.
Description
Technical field
The utility model belongs to automobile power transmission device technical field, relates to the automotive transmission production technology, exactly is a kind of nine speed automatic transmissions.
Background technique
Automobile speed in the process of moving constantly changes, and requires the gear ratio of automobile power transmission constantly to change, and just requires speed change gear that as much as possible gear is arranged.At present, most of automobile is equipped with five retainings or six retaining speed change gears, has only the minority vehicle to use the above speed change gear of seven retainings.
Multi-form speed changer has its advantage and deficiency, and MT is simple in structure, efficient is high, power is big, but the frequent operation of manual shift and pin stepping on clutch pedal must be arranged, the labor intensity height, and be difficult to guarantee that motor is in work in the best speed range; AMT is parent with the manual transmission, by electronic or hydraulic power clutch separation and the shift control of manual transmission are realized automation, but its control parameter is many, interrupts transmission of power during gearshift, is difficult to realize high-quality gearshift control; AT is with the planetary pinion transmission and add fluid torque converter, and each driving retaining gear is in engagement all the time, and smooth gear shifting is good, and is simple to operate laborsaving, but its efficient is low, complex structure, cost height, maintenance difficult; CVT is the target that automotive transmission is chased all the time, but has CVT now with the friction mode transferring power, and transmission efficiency is low, and the ablation of easily skidding must have enough big stiction to driving belt, realize very difficulty of powerful stepless transmission; DSG adopts the two jack shaft technology of double clutch, can there be two gears to be in engagement simultaneously, the fast sensitivity of shifting gears, the sensation that does not have power interruption is accelerated powerful slyness, has good driving enjoyment, but double clutch construction complexity, the manufacture process requirement height, maintenance difficulty is big, can not fundamentally satisfy automobile to the requirement of speed changer.
In general, gear is more to make speed changer have the Speed Ratio Distribution between bigger ratio coverage and the finer and closely woven gear, can improve power character, fuel economy and the smooth gear shifting of automobile, but, more many its gearbox designs of automobile shift can be more complicated, volume and weight is also more big, takies space, more cabin, brings difficulty for the installment work of motor integral arrangement.
The model utility content
The purpose of this utility model is to gather every advantage of existing MT, AMT, AT, DSG speed changer, design a kind of compact structure, can realize that gearshift rapidly also can obtain the variable speed drive of more gears, it is more fast that vehicle is accelerated, it is more smooth-going to shift gears, and fuel consume still less.
The utility model is achieved through the following technical solutions.
Speed changer described in the utility model adopts two jack shaft structures, the mode transferring power that combines with conventional gear and synchronizer with planetary pinion, it mainly comprises planetary pinion, jack shaft, actuation gear, driving retaining gear, main reducing gear, differential mechanism, gear operating component and automatically controlled power unit, power from motor is imported from planetary pinion, be delivered to actuation gear then, actuation gear drives driving retaining gear and rotates, via synchronizer transmission of power is arrived jack shaft, by jack shaft transmission of power is arrived main reducing gear, at last by the differential mechanism outputting power, automatically controlled power unit is controlled the collaborative work of gear operating component according to the driving operating mode and is finished the gear conversion, replaces transferring power by two jack shafts.
Jack shaft described in the utility model comprises first jack shaft (1) and second jack shaft (15), and first jack shaft (1) is enclosed within and forms revolute pair in first hollow shaft (3), and second jack shaft (15) is enclosed within and forms revolute pair in second hollow shaft (13).
Described actuation gear comprises low gear actuation gear (9) and high gear actuation gear (7), described driving retaining gear comprises the first driving retaining gear (12), second driving retaining gear (5), the third line car bumper gear (11) and the reverse gear (4), and described main reducing gear comprises first reduction gear (2), second reduction gear (14) and final gear (18).
Described gear operating component comprises first synchronizer (A1), second synchronizer (A2), first break (B1), second break (B2), first clutch (C1), second clutch (C2), three-clutch (C3) and four clutches (C4), wherein, first clutch (C1) and second clutch (C2) have the synchrolock locking apparatus.
Sun wheel shaft described in the utility model (10) place axis is the power input shaft axis, first jack shaft (1) place axis is the first jack shaft axis, second jack shaft (15) place axis is the second jack shaft axis, final gear axle (20) place axis is the pto axis, above-mentioned four axis are space parallel and distribute, thus, speed changer described in the utility model constitutes two jack shaft structural types.
First reduction gear (2) is installed on first jack shaft described in the utility model (1), at first hollow shaft (3) reverse gear (4), first synchronizer (A1) and the second driving retaining gear (5) are installed, reverse gear (4) and the second driving retaining gear (5) can be gone up at first hollow shaft (3) and freely rotate, first synchronizer (A1) can mesh with reverse gear (4) and the second driving retaining gear (5) respectively, between first jack shaft (1) and first hollow shaft (3) first clutch (C1) is installed.
Second reduction gear (14) is installed on second jack shaft described in the utility model (15), at second hollow shaft (13) first driving retaining gear (12), second synchronizer (A2) and the third line car bumper gear (11) is installed, the first driving retaining gear (12) and the third line car bumper gear (11) can be gone up at second hollow shaft (13) and freely rotate, second synchronizer (A2) can mesh with the first driving retaining gear (12) and the third line car bumper gear (11) respectively, between second jack shaft (15) and second hollow shaft (13) second clutch (C2) is installed.
Planetary gear ring axle described in the utility model (16) and planet carrier axle (8) are hollow shaft, sun wheel shaft (10) is enclosed within gear ring axle (16) and the planet carrier axle (8) and forms revolute pair, at planet carrier axle (8) low gear actuation gear (9) and high gear actuation gear (7) is installed.
Between the planet carrier axle (8) of speed changer described in the utility model and first hollow shaft (3) reverse idler gear (6) is installed, low gear actuation gear (9) meshes with the first driving retaining gear (12) and reverse idler gear (6) simultaneously, reverse idler gear (6) meshes with reverse gear (4) again, high gear actuation gear (7) meshes with the second driving retaining gear (5) and the third line car bumper gear (11) simultaneously, final gear (18) meshes with first reduction gear (2) and second reduction gear (14) simultaneously, and final gear (18) is fixedlyed connected with the housing of differential mechanism (19).
First break (B1) is installed on the planetary gear ring axle described in the utility model (16), in sun wheel shaft (10) second break (B2) is installed, three-clutch (C3) and four clutches (C4) are combined the formation double clutch, planetary gear ring axle (16) is connected to engine power output shaft (17) by three-clutch (C3), and sun wheel shaft (10) is connected to engine power output shaft (17) by four clutches (C4).
First clutch described in the utility model (C1) has the synchrolock locking apparatus, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, second clutch (C2) has the synchrolock locking apparatus, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, first clutch (C1) and second clutch (C2) interlock each other, and both only allow one of them in running order at one time.
Speed changer described in the utility model has nine forward gears and two and reverses gear, one retaining, two retainings and three retainings share the first driving retaining gear (12), four retainings, six retainings and eight retainings share the second driving retaining gear (5), five retainings, seven retainings and nine retainings share the third line car bumper gear (11), a retaining and two retainings that fall share reverse gear (4), one keep off, two retainings and four that fall keep off, six retainings, the transmission of power of eight retainings is undertaken by first jack shaft (1), one retaining, two retainings, three retainings, with five retainings, seven retainings, the transmission of power of nine retainings is undertaken by second jack shaft (15), and automatically controlled power unit is according to driving operating mode control gear operating component collaborative work self shifter.
Transmission gear operating component working state relation described in the utility model sees the following form:
Sense of rotation with engine power output shaft (17) is forward, and the working state of each gear is described below:
Neutral: first clutch (C1) and second clutch (C2) all are in off working state, and be neutral this moment.
One keep off: first synchronizer (A1) and reverse gear (4) engagement, first clutch (C1) engages, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, first break (B1) produces braking, four clutches (C4) engages, low gear actuation gear (9) drives reverse gear (4) by reverse idler gear (6) and rotates, and by first jack shaft (1) transferring power, this moment is for falling a retaining state.
Two keep off: first synchronizer (A1) and reverse gear (4) engagement, first clutch (C1) engages, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, second break (B2) produces braking, three-clutch (C3) engages, low gear actuation gear (9) drives reverse gear (4) by reverse idler gear (6) and rotates, and by first jack shaft (1) transferring power, this moment is for falling two retaining states.
One retaining: second synchronizer (A2) and first driving retaining gear (12) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, first break (B1) produces braking, four clutches (C4) engages, low gear actuation gear (9) drives the first driving retaining gear (12) and rotates, and by second jack shaft (15) transferring power, be a retaining state this moment.
Two retainings: second synchronizer (A2) and first driving retaining gear (12) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, second break (B2) produces braking, three-clutch (C3) engages, low gear actuation gear (9) drives the first driving retaining gear (12) and rotates, and by second jack shaft (15) transferring power, be two retaining states this moment.
Three retainings: second synchronizer (A2) and first driving retaining gear (12) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, three-clutch (C3) and four clutches (C4) engage simultaneously, make the planetary pinion unitary rotation, low gear actuation gear (9) drives the first driving retaining gear (12) and rotates, and by second jack shaft (15) transferring power, be three retaining states this moment.
Four retainings: first synchronizer (A1) and second driving retaining gear (5) engagement, first clutch (C1) engages, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, first break (B1) produces braking, four clutches (C4) engages, high gear actuation gear (7) drives the second driving retaining gear (5) and rotates, and by first jack shaft (1) transferring power, be four retaining states this moment.
Five retainings: second synchronizer (A2) and the third line car bumper gear (11) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, first break (B1) produces braking, four clutches (C4) engages, high gear actuation gear (7) drives the third line car bumper gear (11) and rotates, and by second jack shaft (15) transferring power, be five retaining states this moment.
Six retainings: first synchronizer (A1) and second driving retaining gear (5) engagement, first clutch (C1) engages, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, second break (B2) produces braking, three-clutch (C3) engages, high gear actuation gear (7) drives the second driving retaining gear (5) and rotates, and by first jack shaft (1) transferring power, be six retaining states this moment.
Seven retainings: second synchronizer (A2) and the third line car bumper gear (11) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, second break (B2) produces braking, three-clutch (C3) engages, high gear actuation gear (7) drives the third line car bumper gear (11) and rotates, and by second jack shaft (15) transferring power, be seven retaining states this moment.
Eight retainings: first synchronizer (A1) and second driving retaining gear (5) engagement, first clutch (C1) engages, first jack shaft (1) is also locked rapidly synchronously with first hollow shaft (3) to be connected as a single entity, three-clutch (C3) and four clutches (C4) engage simultaneously, make the planetary pinion unitary rotation, high gear actuation gear (7) drives the second driving retaining gear (5) and rotates, and by first jack shaft (1) transferring power, be eight retaining states this moment.
Nine retainings: second synchronizer (A2) and the third line car bumper gear (11) engagement, second clutch (C2) engages, second jack shaft (15) is also locked rapidly synchronously with second hollow shaft (13) to be connected as a single entity, three-clutch (C3) and four clutches (C4) engage simultaneously, make the planetary pinion unitary rotation, high gear actuation gear (7) drives the third line car bumper gear (11) and rotates, and by second jack shaft (15) transferring power, be nine retaining states this moment.
Description of drawings
Fig. 1 is that the utility model embodiment critical piece is arranged schematic representation.
Fig. 2 is that the utility model embodiment main reducing gear is arranged schematic representation.
Fig. 3 is the utility model embodiment transmission shaft spatial relation schematic representation.
Among Fig. 1 to Fig. 3:
1. first jack shaft, 2. first reduction gear, 3. first hollow shaft, 4. reverse gear, 5. second driving retaining gear, the 6. reverse idler gear, 7. high gear actuation gear, 8. planet carrier axle, 9. low gear actuation gear, 10. sun wheel shaft, 11. the third line car bumper gears, 12. first driving retaining gears, 13. second hollow shaft, 14. second reduction gear, 15. second jack shafts, 16. gear ring axle, 17. engine power output shaft, 18. final gears, 19. differential mechanisms, 20. final gear axle, 21. the differential mechanism output shaft, A1. first synchronizer, A2. second synchronizer, B1. first break, B2. second break, C1. first clutch, C2. second clutch, C3. three-clutch, the C4. four clutches
Embodiment
Provide a kind of mode of execution of the present utility model below in conjunction with accompanying drawing, and the technical solution of the utility model is described.
With reference to Fig. 1, Fig. 2 and Fig. 3, press and arrange first jack shaft (1), second jack shaft (15), sun wheel shaft (10) and the spatial position of final gear axle (20) in mission case shown in the figure.
With reference to shown in Figure 1, first reduction gear (2) is installed on first jack shaft (1), with reverse gear (4), first synchronizer (A1) and the second driving retaining gear (5) are installed on first hollow shaft (3), reverse gear (4) and the second driving retaining gear (5) can be gone up at first hollow shaft (3) freely to rotate, first synchronizer (A1) can mesh with reverse gear (4) and the second driving retaining gear (5) respectively, first jack shaft (1) is enclosed within first hollow shaft (3), support first jack shaft (1) and first hollow shaft (3) with bearing, above-mentioned parts are installed in the mission case, and make first jack shaft (1) and first hollow shaft (3) extend the mission case rear end.
With reference to shown in Figure 1, second reduction gear (14) is installed on second jack shaft (15), with the first driving retaining gear (12), second synchronizer (A2) and the third line car bumper gear (11) are installed on second hollow shaft (13), the first driving retaining gear (12) and the third line car bumper gear (11) can be gone up at second hollow shaft (13) freely to rotate, second synchronizer (A2) can mesh with the first driving retaining gear (12) and the third line car bumper gear (11) respectively, second jack shaft (15) is enclosed within second hollow shaft (13), support second jack shaft (15) and second hollow shaft (13) with bearing, above-mentioned parts are installed in the mission case, and make second jack shaft (15) and second hollow shaft (13) extend the mission case rear end.
With reference to shown in Figure 1, sun wheel shaft (10) is enclosed within gear ring axle (16) and the planet carrier axle (8), low gear actuation gear (9) and high gear actuation gear (7) are installed on the planetary planet carrier axle (8), with bearing supporting gear ring axle (16) and planet carrier axle (8), planetary pinion is installed in the mission case, and make planetary gear ring axle (16) and sun wheel shaft (10) extend the mission case front end, simultaneously, make sun wheel shaft (10) extend the mission case rear end.
With reference to shown in Figure 1, between planet carrier axle (8) and first hollow shaft (3), arrange the reverse idler gear axle, reverse idler gear (6) is installed thereon.
With reference to shown in Figure 2, final gear (18) is fixedlyed connected with the housing of differential mechanism (19), final gear axle (20) is hollow shaft, differential mechanism output shaft (21) is enclosed within the final gear axle (20), with bearing supporting final gear axle (20), final gear (18) and differential mechanism (19) are installed in the mission case.
With reference to Fig. 1, Fig. 2 and shown in Figure 3, above-mentioned layout is installed the following condition that meets: low gear actuation gear (9) meshes with the first driving retaining gear (12) and reverse idler gear (6) simultaneously, reverse idler gear (6) and reverse gear (4) engagement, high gear actuation gear (7) meshes with the second driving retaining gear (5) and the third line car bumper gear (11) simultaneously, final gear (18) while and first reduction gear (2) and second reduction gear (14) engagement.
With reference to shown in Figure 1, in the mission case rear end, connect first jack shaft (1) and first hollow shaft (3) with first clutch (C1), connect second jack shaft (15) and second hollow shaft (13) with second clutch (C2), in sun wheel shaft (10) second break (B2) is installed.
With reference to shown in Figure 1, three-clutch (C3) and four clutches (C4) are combined the formation double clutch, and double clutch is installed on the engine power output shaft (17).
With reference to shown in Figure 1, at the mission case front end, at gear ring axle (16) first break (B1) is installed, sun wheel shaft (10) is by splined four clutches (C4), and gear ring axle (16) is by splined three-clutch (C3).
Installation comprises the automatically controlled power unit of gear actuator.
Each gear number of teeth of the utility model is chosen as follows:
The planetary planetary pinion quantity of speed changer described in the utility model is 4, and the number of teeth of each small gear is 15 teeth, and reverse idler gear (6) is idle pulley, and its number of teeth can according to circumstances be selected.
By above gear parameter, the total gear ratio of each gear of speed changer described in the utility model that calculates is as follows:
| One retaining | Two retainings | Three retainings | Four retainings | Five retainings | Six retainings | Seven retainings | Eight retainings | Nine retainings |
| 28.401 | 17.336 | 10.765 | 8.414 | 6.643 | 5.136 | 4.055 | 3.189 | 2.518 |
| One keep off | Two keep off | ? | ? | ? | ? | ? | ? | ? |
| 24.214 | 14.780 | ? | ? | ? | ? | ? | ? | ? |
Speed changer described in the utility model has been gathered every advantage of MT, AMT, AT, DSG speed changer in one, a plurality of gears are arranged for sharing gear, compact structure is saved the space, having nine forward gears and two reverses gear, first speed speed ratio height, gear range wide (greater than 11), tooth is close than little, it is fast smooth-going to shift gears, and can greatly improve power performance and the fuel-economy performance of car load.
Under driving states forward, first synchronizer (A1) meshes with the second driving retaining gear (5) all the time, second synchronizer (A2) only four retainings during states fibrous root select the engagement object of next gear in advance according to the driving operating mode, reduced the gear shift operation step, make the speed changer operation more reliable and stable.
The utility model can be continued to use the ripe manufacturing process of traditional speed changer, and is compatible fully with existing production technology, need not increase new manufacturing mechanism, and cost of production and user cost all can remain on low-level.
A kind of embodiment of the present utility model has below been described by reference to the accompanying drawings; but only be preferred embodiment of the present utility model; be not in order to limit protection domain of the present utility model; utilize the utility model anyly to be equal to change, to revise or to the change of gear parameter, also in protection domain of the present utility model what above-described embodiment was made.
Claims (9)
1. speed automatic transmission, comprise planetary pinion, jack shaft, actuation gear, driving retaining gear, main reducing gear, differential mechanism, gear operating component and automatically controlled power unit, it is characterized in that: this speed changer adopts two jack shaft structures, the mode transferring power that combines with conventional gear and synchronizer with planetary pinion, having nine forward gears and two reverses gear, power from motor is imported from planetary pinion, be delivered to actuation gear then, actuation gear drives driving retaining gear and rotates, via synchronizer transmission of power is arrived jack shaft, again by jack shaft with transmission of power to main reducing gear, at last by the differential mechanism outputting power, automatically controlled power unit is controlled the collaborative work of gear operating component according to the driving operating mode and is finished the gear conversion, replaces transferring power by two jack shafts.
2. a kind of nine speed automatic transmissions according to claim 1, it is characterized in that: described jack shaft comprises first jack shaft (1) and second jack shaft (15), described actuation gear comprises low gear actuation gear (9) and high gear actuation gear (7), described driving retaining gear comprises the first driving retaining gear (12), the second driving retaining gear (5), the third line car bumper gear (11) and reverse gear (4), described main reducing gear comprises first reduction gear (2), second reduction gear (14) and final gear (18), described gear operating component comprises first synchronizer (A1), second synchronizer (A2), first break (B1), second break (B2), first clutch (C1), second clutch (C2), three-clutch (C3) and four clutches (C4).
3. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: first jack shaft (1) of this speed changer is enclosed within and forms revolute pair in first hollow shaft (3), at first jack shaft (1) first reduction gear (2) is installed, at first hollow shaft (3) reverse gear (4) is installed, first synchronizer (A1) and the second driving retaining gear (5), reverse gear (4) and the second driving retaining gear (5) can be gone up at first hollow shaft (3) and freely rotate, first synchronizer (A1) can be respectively and reverse gear (4) and second driving retaining gear (5) engagement, has first clutch (C1) to connect between first jack shaft (1) and first hollow shaft (3).
4. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: second jack shaft (15) of this speed changer is enclosed within and forms revolute pair in second hollow shaft (13), at second jack shaft (15) second reduction gear (14) is installed, at second hollow shaft (13) the first driving retaining gear (12) is installed, second synchronizer (A2) and the third line car bumper gear (11), the first driving retaining gear (12) and the third line car bumper gear (11) can be gone up at second hollow shaft (13) and freely rotate, second synchronizer (A2) can be respectively and the first driving retaining gear (12) and the third line car bumper gear (11) engagement, has second clutch (C2) to connect between second jack shaft (15) and second hollow shaft (13).
5. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: first clutch (C1) has the synchrolock locking apparatus, first clutch (C1) can make first jack shaft (1) also lock synchronously rapidly with first hollow shaft (3) and be connected as a single entity, second clutch (C2) has the synchrolock locking apparatus, second clutch (C2) can make second jack shaft (15) also lock synchronously rapidly with second hollow shaft (13) and be connected as a single entity, first clutch (C1) and second clutch (C2) interlock each other, and both only allow one of them in running order at one time.
6. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: described planetary gear ring axle (16) and planet carrier axle (8) are hollow shaft, sun wheel shaft (10) is enclosed within gear ring axle (16) and the planet carrier axle (8) and forms revolute pair, at planet carrier axle (8) low gear actuation gear (9) and high gear actuation gear (7) are installed, at gear ring axle (16) first break (B1) is installed, in sun wheel shaft (10) second break (B2) is installed.
7. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: three-clutch (C3) and four clutches (C4) are combined the formation double clutch, planetary gear ring axle (16) connects with three-clutch (C3) by spline, and sun wheel shaft (10) connects with four clutches (C4) by spline.
8. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: between the planet carrier axle (8) of this speed changer and first hollow shaft (3) reverse idler gear (6) is installed, low gear actuation gear (9) meshes with the first driving retaining gear (12) and reverse idler gear (6) simultaneously, reverse idler gear (6) meshes with reverse gear (4) again, high gear actuation gear (7) meshes with the second driving retaining gear (5) and the third line car bumper gear (11) simultaneously, final gear (18) while and first reduction gear (2) and second reduction gear (14) engagement.
9. a kind of nine speed automatic transmissions according to claim 1 and 2, it is characterized in that: a retaining of this speed changer, two retainings and three retainings share the first driving retaining gear (12), four retainings, six retainings and eight retainings share the second driving retaining gear (5), five retainings, seven retainings and nine retainings share the third line car bumper gear (11), and a retaining and two retainings that fall share reverse gear (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320195746 CN203176273U (en) | 2013-04-18 | 2013-04-18 | Nine-gear automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320195746 CN203176273U (en) | 2013-04-18 | 2013-04-18 | Nine-gear automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203176273U true CN203176273U (en) | 2013-09-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320195746 Expired - Fee Related CN203176273U (en) | 2013-04-18 | 2013-04-18 | Nine-gear automatic transmission |
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| CN (1) | CN203176273U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105370817A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| CN105370816A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| CN105370814A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| WO2019129210A1 (en) * | 2017-12-29 | 2019-07-04 | 比亚迪股份有限公司 | Transmission, power drive system and vehicle |
| CN110822031A (en) * | 2018-08-10 | 2020-02-21 | 现代自动车株式会社 | Power transmission apparatus for vehicle |
| CN111365436A (en) * | 2020-04-17 | 2020-07-03 | 丁红涛 | Automatic gearbox of power switch |
| CN112867621A (en) * | 2018-10-18 | 2021-05-28 | 采埃孚股份公司 | Transmission and drive system for a motor vehicle |
| CN113795689A (en) * | 2019-04-23 | 2021-12-14 | Hj变速器株式会社 | Power transmission device |
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2013
- 2013-04-18 CN CN 201320195746 patent/CN203176273U/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105370817A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| CN105370816A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| CN105370814A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Multi-gear double-clutch transmission and vehicle |
| CN105370816B (en) * | 2014-08-29 | 2017-12-19 | 广州汽车集团股份有限公司 | More gear double-clutch speed changers and vehicle |
| CN105370817B (en) * | 2014-08-29 | 2017-12-19 | 广州汽车集团股份有限公司 | More gear double-clutch speed changers and vehicle |
| CN105370814B (en) * | 2014-08-29 | 2017-12-19 | 广州汽车集团股份有限公司 | More gear double-clutch speed changers and vehicle |
| WO2019129210A1 (en) * | 2017-12-29 | 2019-07-04 | 比亚迪股份有限公司 | Transmission, power drive system and vehicle |
| CN110822031A (en) * | 2018-08-10 | 2020-02-21 | 现代自动车株式会社 | Power transmission apparatus for vehicle |
| CN110822031B (en) * | 2018-08-10 | 2023-10-03 | 现代自动车株式会社 | Power transmission apparatus for vehicle |
| CN112867621A (en) * | 2018-10-18 | 2021-05-28 | 采埃孚股份公司 | Transmission and drive system for a motor vehicle |
| CN112867621B (en) * | 2018-10-18 | 2024-05-24 | 采埃孚股份公司 | Transmission and drive system for a motor vehicle |
| CN113795689A (en) * | 2019-04-23 | 2021-12-14 | Hj变速器株式会社 | Power transmission device |
| CN113795689B (en) * | 2019-04-23 | 2023-07-18 | Hj变速器株式会社 | Power transmission device |
| CN111365436A (en) * | 2020-04-17 | 2020-07-03 | 丁红涛 | Automatic gearbox of power switch |
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