CN1616853A - Dual Clutch Automatic Transmission - Google Patents
Dual Clutch Automatic Transmission Download PDFInfo
- Publication number
- CN1616853A CN1616853A CN 200410011060 CN200410011060A CN1616853A CN 1616853 A CN1616853 A CN 1616853A CN 200410011060 CN200410011060 CN 200410011060 CN 200410011060 A CN200410011060 A CN 200410011060A CN 1616853 A CN1616853 A CN 1616853A
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- Prior art keywords
- gear
- clutch
- power
- shifting
- automatic transmission
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- 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.)
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- 230000005540 biological transmission Effects 0.000 title claims description 37
- 230000009977 dual effect Effects 0.000 title 1
- 238000000034 method Methods 0.000 abstract description 10
- 230000000694 effects Effects 0.000 abstract description 4
- 230000008569 process Effects 0.000 abstract description 2
- 230000001360 synchronised effect Effects 0.000 abstract 1
- 206010009232 Clang associations Diseases 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 238000011161 development Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- IXSZQYVWNJNRAL-UHFFFAOYSA-N etoxazole Chemical compound CCOC1=CC(C(C)(C)C)=CC=C1C1N=C(C=2C(=CC=CC=2F)F)OC1 IXSZQYVWNJNRAL-UHFFFAOYSA-N 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
Images
Classifications
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- 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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- 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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
Abstract
The present invention belongs to the field of mechanical automatic speed variator for vehicle, and is especially one kind of double clutch type automatic gear box in new structure. The automatic gear box includes various setting gear pairs, synchronous shifting unit and shifting control system, and features that each of the power input shaft and the power output shaft is provided with one wet clutch, all the setting gear pairs are divided into odd number set and even number set connected separately to the driven sheet of one of the clutches, and two clutches transmit the work power alternately to realize setting switching. The shift process has no power interruption, short shifting time, greatly raised shifting comfort and excellent shifting power performance and quality of vehicle. The present invention has simple and compact parallel shaft structure, low cost but the same effect as automatic rotary shaft gear box in complicated structure.
Description
Technical field
The invention belongs to the double-clutch automatic transmission of the automatic transmission in the vehicle, particularly a kind of new structure.
Technical background
Fast development along with automotive engineering, the automatic gear for vehicle that various ways occurred, mainly contain: hydraulic mechanical type automatic transmission (AT), mechanical continuously-variable transmission (CVT), and exerting both at home and abroad the electric control mechanical type automatic speed variator (AMT) studied in recent years.The particularly development of electric control mechanical type automatic speed variator because it has the advantage of the existing manual transmission production investment of the desired high fuel economy of present automobile industry development, low emission and protection, just has been subjected to the attention of each big automobile factory.
The generation of electric control mechanical type automatic speed variator is based on the development of traditional parallel-axis type manual transmission and comes.Among developmental research process to electric control mechanical type automatic speed variator, also discovery gradually its some shortcomings, power interruption when the problem of its maximum is exactly gear shift, this power character to vehicle, travelling comfort and fuel economy and discharging have brought certain influence.AMT plucks neutral gear with speed changer then because its structural principle has determined it at first to want cut-off clutch in gearshift procedure, gear selecting, gear shift again, last engaging clutch.Like this, after clutch separation, before clutch engages again again, the power of motor can not be passed to wheel and go the powered vehicle operation, so produced the interruption of transmission of power in the gearshift procedure, vehicle certainly leads to retardation, and shift time is long, brings adverse effect for the acceleration, travelling comfort etc. of vehicle.
Double-clutch automatic transmission (DCT) is emerging in recent years a kind of automatic transmission form, it can solve the power interruption problem that present automobile electric control mechanical type automatic speed variator produces effectively in gearshift procedure, present double-clutch automatic transmission structure as shown in Figure 4, though it has solved the power interruption problem in the gearshift procedure, but its complex structure, be difficult to manufacturing, particularly double clutch device, manufacture cost is very high.
Summary of the invention
The objective of the invention is to propose the double-clutch automatic transmission that a kind of structure is simple and direct, manufacture cost is lower, safe and reliable, to overcome the shortcoming that present various automatic transmission exists.
Double-clutch automatic transmission of the present invention, comprise each shifting gear pair, gear shift synchronizer and shift control, it is characterized in that respectively being provided with on its power input shaft and the output shaft wet clutch, each shifting gear is secondary to be divided by strange, even number gear, be connected with the driven plate of a clutch among these two wet clutches respectively, two clutches alternately transmit operation power to realize gear switch.
Working principle of the present invention is: when vehicle moves with a certain gear that links to each other with a clutch, control system is prejudged next gear that links to each other with another clutch that is about to the work of entering, because of this gear transferring power not also, so can instruct the self-clanging gear-shift gear of substituting in advance very easily, when vehicle operating reaches shift point, with the clutch separation of working,, automobile is travelled with next gear simultaneously with another clutch.In gearshift procedure, the power of motor constantly is passed to wheel all the time, so the gearshift procedure of finishing like this is the uninterrupted gear shift of power.
Good effect of the present invention is:
1. because double-clutch automatic transmission is to handle according to the principle of power shfit, it has the advantage of the two concurrently between AT automatic transmission and two kinds of automatic gearboxes of AMT.There is not power interruption in double-clutch automatic gearbox in gear shift work, do not produce so significantly slow down during gear shift.And it has shortened shift time, has improved the gear shift travelling comfort greatly, has guaranteed that vehicle has good power character and property of automatic shft.The inside transmission of double-clutch automatic transmission is the pure mechanical transmission of gear type, and the transmission efficiency during its operation is equal to electric control mechanical type automatic speed variator (AMT).Carry out work though this double-clutch automatic transmission also needs extra power to control it, internal structure that it is specific and decision-making capability have than the better fuel economy of traditional speed changer this speed changer.And because the improvement of control mode, the shortening of shift time also makes moderate progress to aspects such as vehicle oil consumption and dischargings.
2. because double-clutch automatic transmission is to carry out automation on former traditional manual transmission basis, thereby reached the effect of baroque running shaft (planetary pinion) formula automatic transmission with parallel-axis type structure simple in structure, but structure is compact more, and cost is lower.Its cost is well below automatic transmission such as AT, CVT.
3. double clutch of the present invention is made up of two independent single clutch, and its structure does not need otherwise designed, and single wet clutch is matured product, good reliability, and cost is low.
4. the double-clutch automatic transmission of structure of the present invention is simple in structure, is easy to processing.
Description of drawings
Fig. 1 is a double-clutch automatic transmission structural drawing of the present invention;
Working state schematic representation when Fig. 2 begins with one grade of operation for double-clutch automatic transmission of the present invention;
Working state schematic representation when Fig. 3 moves with second gear for double-clutch automatic transmission of the present invention changes;
Fig. 4 figure is present double-clutch automatic transmission structural representation.
Embodiment
The embodiment who provides below in conjunction with accompanying drawing is further elaborated technical solution of the present invention.
Among Fig. 1 to 3: 1 is input shaft, 2 is the fourth gear driving gear, 3 be two, the fourth gear synchronizer, 4 is the second gear driving gear, 5 is one, three, reverse clutch, 6 is third speed drive gear, 7 is one grade of driving gear, and 8 is reverse driving gear, and 19 is the reverse gear mesomerism gear, 9 is output shaft, 10 be reverse gear in conjunction with gear ring, 11 is the reverse gear combined cover, 12 is the reverse gear driven gear, 13 is first speed driven gear, 14 be one, the third gear synchronizer, 15 is the third gear driven gear, 16 is the second gear driven gear, 17 is the fourth gear driven gear, 18 is two, the fourth gear clutch.
With reference to Fig. 1, has five speed change gears double-clutch automatic transmission of (comprising the back reverse gear), mainly by forming: two independent wet clutches, five speed change gear gear pairs and corresponding gear shift synchronizer, control system and gearshift mechanism (not drawing among the figure) thereof with the bottom.One, three, reverse clutch 5 is arranged on the input shaft 1 its concrete structure is:, the driven plate of clutch 5 and third speed drive gear 6, one grade of driving gear 7 are connected with reverse driving gear 8.Two, fourth gear clutch 18 is arranged on the output shaft 9, and the driven plate of clutch 18 is connected with second gear driven gear 16, fourth gear driven gear 17.Second gear driving gear 4 and fourth gear driving gear 2 between them are two, fourth gear synchronizer 3 on input shaft 1.And first speed driven gear 13 and third gear driven gear 15 are positioned on the output shaft 9, between them are one, third gear synchronizer 14.Reverse gear driven gear 12 also is positioned on the output shaft 9, engages in conjunction with gear ring 10 with reverse gear on being fixed on output shaft 9 or separates by reverse gear combined cover 11.Reverse gear mesomerism gear 19 and reverse driving gear 8 and 12 engagements of reverse gear driven gear, transferring power.
With reference to Fig. 2, when vehicle was in vehicle stop state, two clutches were all often opened, and promptly all were in separated state, not transferring power at two clutches at ordinary times.When vehicle is started to walk with one grade, two, fourth gear clutch 18 is a separated state, self-clanging gear-shift with one, third gear synchronizer 14 is engaged to first speed driven gear 13, gear switch is the I shelves, then one, three, reverse clutch 5 engages, vehicle begins with one grade of operation, and this moment, power transmission line was: input shaft 1 →, three, 5 → one grades of driving gear 7 → first speed driven gears 13 → of reverse clutch, third gear synchronizer 14 → output shaft 9.
Vehicle is when one grade of operation, because this moment two, fourth gear clutch 18 is in separated state, transferring power not, when vehicle quickens, when reaching the shift point near second gear, self-clanging gear-shift can change to second gear in advance with gear, be about to two, fourth gear synchronizer 3 is engaged to second gear driving gear 4, then one, three, reverse clutch 5 begins to separate, the while two, fourth gear clutch 18 begins to engage, and two clutches alternately switch, up to one, three, reverse clutch 5 separates fully, two, fourth gear clutch 18 engages fully, and whole gearshift procedure finishes, and vehicle changes to second gear.
With reference to Fig. 3, the power transmission line of second gear is: input shaft 1 → two, fourth gear synchronizer 3 → second gear driving gear 4 → second gear driven gear 16 → two, fourth gear clutch 18 → output shaft 9.
After vehicle enters the second gear operation, the vehicular automatic transmission ECU (Electrical Control Unit) can be known the current running state of vehicle according to relevant sensor signals, and then judge that vehicle is about to enter the gear of operation, if vehicle quickens, then next gear is a third gear, if vehicle deceleration, then next gear is one grade.And one grade and third gear all are connected in one, three, on the reverse clutch 5, because this clutch is in separated state, transferring power not, be about to the gear of the work of entering so can instruct self-clanging gear-shift to substitute in advance very easily, when vehicle operating reaches shift point, only need to work two, fourth gear clutch 18 separates, simultaneously one, three, reverse clutch 5 engages, the work good switching sequence of two clutches, whole gear shift action is all finished.The handoff procedure of other gear that advances also is like this.
During reverse gear, two, fourth gear clutch 18 separates, one, three, reverse clutch 2 engages, one, third gear synchronizer 14 mediates, reverse gear combined cover 11 combines gear ring 10 combinations with reverse gear driven gear 12 with reverse gear, drive driven shaft 9 and export reverse gears.
The structural principle of below only just have one, two, three, four, the embodiment of totally five gear speed changers for example understanding technical solution of the present invention; can realize more speed change gear or modification set-up mode fully by this design; but so long as form double clutch construction with two independent wet clutches; connect each Transmission gear respectively step by step; realize the alternate type gear switch, all belong to the claim protection domain of the technology of the present invention design.
Claims (2)
1. double-clutch automatic transmission, comprise each shifting gear pair, gear shift synchronizer and shift control, it is characterized in that respectively being provided with on its power input shaft and the output shaft wet clutch, each shifting gear is secondary to be divided by strange, even number gear, be connected with the driven plate of a clutch among these two wet clutches respectively, two clutches alternately transmit operation power to realize gear switch.
2. double-clutch automatic transmission according to claim 1, it is characterized in that the described driven plate that is arranged on the wet clutch (5) on the input shaft (1) is connected with third speed drive gear (6), one grade of driving gear (7) and reverse driving gear (8), the driven plate that is arranged on the wet clutch (18) on the output shaft (9) is connected with second gear driven gear 16, fourth gear driven gear 17.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410011060 CN1616853A (en) | 2004-08-24 | 2004-08-24 | Dual Clutch Automatic Transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410011060 CN1616853A (en) | 2004-08-24 | 2004-08-24 | Dual Clutch Automatic Transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1616853A true CN1616853A (en) | 2005-05-18 |
Family
ID=34763170
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200410011060 Pending CN1616853A (en) | 2004-08-24 | 2004-08-24 | Dual Clutch Automatic Transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1616853A (en) |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100408882C (en) * | 2005-10-21 | 2008-08-06 | 强井鑫 | Speed variator with starting function need not stepping on clutch to regulate gear |
| CN101846175A (en) * | 2009-04-14 | 2010-09-29 | 杨伟斌 | Double-clutch automatic gear shifting mechanism capable of avoiding negative torque phenomenon in gear shifting process |
| CN101852289A (en) * | 2010-06-13 | 2010-10-06 | 程秀生 | Heavy-duty and rear-drive automobile wet-type double-clutch automatic speed-change power transmission device |
| CN102080721A (en) * | 2009-11-30 | 2011-06-01 | 中国第一汽车集团公司 | Novel dual-clutch automatic transmission system |
| CN102141143A (en) * | 2010-02-03 | 2011-08-03 | 本田技研工业株式会社 | Shift control apparatus |
| CN101096990B (en) * | 2006-06-28 | 2012-07-04 | 福特环球技术公司 | Output reduction dual clutch transmission with clutch coupler |
| CN101713448B (en) * | 2009-03-13 | 2012-07-04 | 浙江吉利汽车研究院有限公司 | Double clutch type automatic gearbox |
| CN101545523B (en) * | 2008-02-08 | 2012-07-18 | 通用汽车公司 | Multi-speed split dual clutch transmission |
| CN101504060B (en) * | 2008-02-08 | 2012-07-18 | 通用汽车公司 | Multi-speed split dual clutch transmission |
| CN102808904A (en) * | 2011-05-31 | 2012-12-05 | 北京理工大学 | Double-wet type dead axle and planet compound type mechanical speed change mechanism used for high-speed vehicle |
| CN101251171B (en) * | 2007-02-23 | 2012-12-05 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
| CN101809319B (en) * | 2007-10-15 | 2013-01-09 | 腓特烈斯港齿轮工厂股份公司 | Dual clutch transmission |
| CN103438160A (en) * | 2013-08-02 | 2013-12-11 | 浙江吉利汽车研究院有限公司 | Automobile dual-clutch automatic transmission |
| CN104930134A (en) * | 2015-05-13 | 2015-09-23 | 雷胜林 | Multiwheel axle-structured transmission |
| CN105240524A (en) * | 2015-11-16 | 2016-01-13 | 张庆法 | Hydraulic automatic control transmission |
| CN109630566A (en) * | 2019-01-30 | 2019-04-16 | 陈奇 | A kind of wet clutch unit assembly |
-
2004
- 2004-08-24 CN CN 200410011060 patent/CN1616853A/en active Pending
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100408882C (en) * | 2005-10-21 | 2008-08-06 | 强井鑫 | Speed variator with starting function need not stepping on clutch to regulate gear |
| CN101096990B (en) * | 2006-06-28 | 2012-07-04 | 福特环球技术公司 | Output reduction dual clutch transmission with clutch coupler |
| CN101251171B (en) * | 2007-02-23 | 2012-12-05 | 通用汽车环球科技运作公司 | Multi-speed transmission with countershaft gearing |
| CN101809319B (en) * | 2007-10-15 | 2013-01-09 | 腓特烈斯港齿轮工厂股份公司 | Dual clutch transmission |
| CN101545523B (en) * | 2008-02-08 | 2012-07-18 | 通用汽车公司 | Multi-speed split dual clutch transmission |
| CN101504060B (en) * | 2008-02-08 | 2012-07-18 | 通用汽车公司 | Multi-speed split dual clutch transmission |
| CN101713448B (en) * | 2009-03-13 | 2012-07-04 | 浙江吉利汽车研究院有限公司 | Double clutch type automatic gearbox |
| CN101846175A (en) * | 2009-04-14 | 2010-09-29 | 杨伟斌 | Double-clutch automatic gear shifting mechanism capable of avoiding negative torque phenomenon in gear shifting process |
| CN102080721A (en) * | 2009-11-30 | 2011-06-01 | 中国第一汽车集团公司 | Novel dual-clutch automatic transmission system |
| CN102141143B (en) * | 2010-02-03 | 2014-03-12 | 本田技研工业株式会社 | Shift control apparatus |
| CN102141143A (en) * | 2010-02-03 | 2011-08-03 | 本田技研工业株式会社 | Shift control apparatus |
| CN101852289A (en) * | 2010-06-13 | 2010-10-06 | 程秀生 | Heavy-duty and rear-drive automobile wet-type double-clutch automatic speed-change power transmission device |
| CN102808904B (en) * | 2011-05-31 | 2014-12-24 | 北京理工大学 | Double-wet type dead axle and planet compound type mechanical speed change mechanism used for high-speed vehicle |
| CN102808904A (en) * | 2011-05-31 | 2012-12-05 | 北京理工大学 | Double-wet type dead axle and planet compound type mechanical speed change mechanism used for high-speed vehicle |
| CN103438160A (en) * | 2013-08-02 | 2013-12-11 | 浙江吉利汽车研究院有限公司 | Automobile dual-clutch automatic transmission |
| CN103438160B (en) * | 2013-08-02 | 2016-05-18 | 浙江吉利汽车研究院有限公司 | Automobile double clutch automatic transmission |
| CN104930134A (en) * | 2015-05-13 | 2015-09-23 | 雷胜林 | Multiwheel axle-structured transmission |
| CN104930134B (en) * | 2015-05-13 | 2018-05-01 | 雷胜林 | More wheel wheel shaft structure speed changers |
| CN105240524A (en) * | 2015-11-16 | 2016-01-13 | 张庆法 | Hydraulic automatic control transmission |
| CN105240524B (en) * | 2015-11-16 | 2017-06-16 | 张庆法 | Hydraulic pressure automatic control of transmission |
| CN109630566A (en) * | 2019-01-30 | 2019-04-16 | 陈奇 | A kind of wet clutch unit assembly |
| CN109630566B (en) * | 2019-01-30 | 2024-04-05 | 浙江海天机械有限公司 | Wet clutch unit assembly |
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