CN1558125A - Clutch-coupling type automatic transmission - Google Patents
Clutch-coupling type automatic transmission Download PDFInfo
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- CN1558125A CN1558125A CNA2004100151544A CN200410015154A CN1558125A CN 1558125 A CN1558125 A CN 1558125A CN A2004100151544 A CNA2004100151544 A CN A2004100151544A CN 200410015154 A CN200410015154 A CN 200410015154A CN 1558125 A CN1558125 A CN 1558125A
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- gear
- transmission shaft
- clutch
- transmission
- fluid coupling
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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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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Control Of Transmission Device (AREA)
Abstract
The present invention relates to electrically controlled automatic shifting and speed varying device for automobile, and is one kind of automatic clutch-coupler type speed variator, superior to available planetary wheel automatic speed variator and electrically controlled mechanical speed variator and automatic double-clutch speed variator. The design thoughts include adopting combined hydraulic coupler and double-coupler in shifting; adopting fluid friction to replace solid surface friction between clutch plates, lower the slippage and material requirement and avoid the excessive power consumption and additional cooling system; and maintaining the continuity, comfort and high efficiency of the said three kinds of automatic speed variator. The present invention also proposes a four-step shifting process and three-step initiating process to reduce the complexity of automatic control.
Description
Technical field the present invention relates to a kind of novel from the coupler type automatic transmission, is the electric controlled automatic shift formula speed change gear that is applied in car transmissions.
Usually in an automatic shifting transmission with planetary gear train, fluid torque converter is absolutely necessary background of invention.Fluid torque converter not only can be regulated output torque and speed within the specific limits automatically according to the size of input speed and power; and because the buffering of fluid; absorbing and flexibly connect effect; make when load takes place to change suddenly; when for example shifting gears; guarantee the travelling comfort of automobile passenger and the continuity of transmission of power, simultaneously motor and speed changer are played a protective role.Yet, because fluid torque converter also can be lost a part of moment of torsion and speed, cause that the loss of energy causes hydraulic fluid temperature to raise, make the efficient of this automatic transmission lower.Technology by electronic locking reduces this energy loss on automatic transmission though have both at home and abroad at present, because structure and control technique are complicated and expensive, not every gear can both be locked, and the effect of raising the efficiency is still limited.
Except the planetary gear train automatic transmission, electric control mechanical type automatic speed variator (AMT) has also obtained extensive use to a certain degree.This speed changer characteristics are generally not adopt fluid torque converter, thereby have saved very big power consumption parts, and efficient is improved.Its another one advantage is to adopt the parallel-axis type train, thereby manufacturing assembly technology and widely used manual transmission are similar, is easy to equally produce with manual transmission.Its gearshift principle is similar to manual shift, and only electricity consumption prosecutor formula realizes that automatically promptly cut-off clutch is plucked neutral gear, and gear selecting gear shift again is at last in conjunction with clutch.Shortcoming is and since clutch from being separated to combination, thereby be raised to required torque again after causing the moment of torsion of its transmission almost to reduce to zero.This power interruption process must increase the impact of gear shift, and the acceleration performance of vehicle is caused negative effect, and is unfavorable to the travelling comfort of travelling.
There is the automatic transmission of a new generation to come out in recent years both at home and abroad again, i.e. double-clutch automatic gearbox (D.B.P. 19711820, U. S. Patent 5950781 and U. S. Patent 6463821).The structure of this speed changer is, do not adopt fluid torque converter, and motor is by two clutch transmits power, and gear is contained in respectively on two axles that respectively have a clutch.Its principle is that vehicle is when a certain gear engaged, by a clutch transmission torque.When the needs gear shift, hang next gear that is positioned on the other transmission shaft earlier, then with clutch combination on this transmission shaft, this moment, double clutch all was in bonding state.Interfere owing to two gear ratios are different, must cause some clutches or two clutches to skid, do not interrupt, finish gearshift procedure thereby last one grade clutch is broken away from this moment at this transition period power.The advantage of double-clutch automatic gearbox is under the situation of accurately control, both can prevent that machinery driving efficiency was very high because the impact that power interruption causes needn't adopt the big fluid torque converter of power consumption to realize a smooth transition again.In addition, it is also little that its structure and manual transmission differ, and the manufacturing assembling of component of machine is also more easy to implement.Yet, can produce frictional heat when skidding in the transitional period owing to double clutch, high frictional heat can reduce the reliability and the working life of clutch plate.If wet clutch also will be provided with a cooling oil pump usually again and be cooled off.If dry clutch, then transmitting torque be restricted and the radial dimension of clutch relatively large so that reduce positive pressure on the clutch plate.No matter be wet type or dry type, to the requirement of clutch plate material also than higher.Another shortcoming of this automatic transmission is that the complexity of electronic control system has surpassed above-mentioned any two kinds of speed changers.Domestic patent (Chinese patent CN1415876A) is with external slightly different, the main distinction is that two clutches are non-slip, but when gear shift, clutch broken away from simultaneously in conjunction with another clutch, such advantage is that control is simple, but can produce impact during gear shift.
Summary of the invention
The objective of the invention is to propose a kind of novel from the coupler type automatic transmission, replace friction between clutch plate with the contactless fluid friction of fluid coupling, skidding relatively of clutch plate reduced greatly, thereby avoid consuming extra energy and use new spare system to cool off, guarantee the continuity stationarity and the high efficiency of transmission of power, also can reduce requirement simultaneously the clutch plate material.In addition, the present invention's four step gear shift methods that propose and three steps that start to walk also can reduce the complexity of automatic control relatively.
Description of drawings Fig. 1 six speed are from coupler type automatic transmission schematic diagram of mechanism
Fig. 2 is from one grade of drive path sketch of coupler type automatic transmission
Fig. 3-1 one grade is changed second gear probationary period explanation: the unloaded second gear of hanging
Fig. 3-2 one grade is changed first transitional period of second gear: HC and drives the second gear transmission
Fig. 3-3 one grade is changed second transitional period of second gear: C2 three combinations, and E drives the second gear transmission, and HC does not break away from
Fig. 3-4 one grade is changed second gear and finish the phase: E directly drives the second gear transmission, and HC breaks away from
Fig. 4-1 odd number shelves change the even number shelves from the coupler action specification
Fig. 4-2 even number shelves change the odd number shelves from the coupler action specification
Fig. 5-1 is from shifting from slow to fast motor and transmission shaft speed discrepancy change procedure
Fig. 5-2 is from shifting from fast to slow motor and transmission shaft speed discrepancy change procedure
Fig. 6 four speed are from coupler type automatic transmission schematic diagram of mechanism
Fig. 7 five speed are from coupler type automatic transmission schematic diagram of mechanism
Fig. 8 seven speed are from coupler type automatic transmission schematic diagram of mechanism
Embodiment: structure of the present invention can illustrate from coupler type automatic transmission schematic diagram of mechanism with six speed among Fig. 1.Working principle of the present invention can be come labor to what Fig. 3-4 illustrated from one grade of example of changing to second gear with Fig. 3-1.
Six speed are made up of following element from the coupler type automatic transmission:
1: transmission shaft 1
2: transmission shaft 2
3: output shaft 3
C
1: the duplex clutch
C
2: the duplex clutch
E: motor
HC: fluid coupling
I: the pump impeller of fluid coupling
RD: retarder and differential mechanism (not drawing among the figure)
S
R: the one-way synchronization device that is used for reverse gear
S
13: the bi-directional synchronization device that is used for a third gear
S
25: be used for two or five grades bi-directional synchronization device
S
46: be used for four or six grades bi-directional synchronization device
T: the turbine of fluid coupling
Z
11: one grade of gear on the transmission shaft 1
Z
13: the intermediate gear on the transmission shaft 1
Z
15: the three-range transmission on the transmission shaft 1
Z
1R: the reverse gear on the transmission shaft 1
Z
22: the fourth gear on the transmission shaft 2
Z
24: five grades of gears on the transmission shaft 2
Z
26: the six shift of gears on the transmission shaft 2
Z
31: one grade of gear on the transmission shaft 3
Z
32: the intermediate gear on the transmission shaft 3
Z
33: the three-range transmission on the transmission shaft 3
Z
34: the fourth gear on the transmission shaft 3
Z
35: five grades of gears on the transmission shaft 3
Z
36: the six shift of gears on the transmission shaft 3
Z
3R: the reverse gear on the transmission shaft 3
Z
i: the mesomerism gear that is used for reverse gear
Transmission shaft 1 is a hollow shaft, and gear Z promptly is housed
1R, Z
11, Z
13And Z
15Transmission shaft.Dress transmission shaft 2 within it is a solid shaft, and gear Z promptly is housed
22, Z
24And Z
26Transmission shaft.Transmission shaft 1 and transmission shaft 2 do not retrain mutually, but independence and freedom is rotated.Gear on the transmission shaft 1 removes Z
15Outside being cemented on the transmission shaft 1, Z
1R, Z
11And Z
13All free to rotate.And Z
22, Z
24And Z
26Then be cemented on the transmission shaft 2, can only rotate with axle 2.Two synchronizer S are arranged on the transmission shaft 1
RAnd S
13, also two synchronizer S are arranged on the transmission shaft 3
25And S
46, they are that circumferencial direction is cemented on the axle, can or gear are cemented on the axle along the axis translation under the promotion of shift fork (being omitted in Fig. 1), or make gear break away from the constraint of axle.In like manner, the gear Z on the transmission shaft 3
32, Z
34, Z
35And Z
36Can on axle, freely rotate Z
3R, Z
31And Z
33Then be cemented on the transmission shaft 3.Wherein, Z
3RBe connected with differential mechanism with retarder, and pass to the left and right wheels of automobile rotatablely moving by it.
HC is the fluid coupling that only contains pump impeller (initiatively) and turbine (passive).Pump impeller is connected with motor E, turbine then with duplex clutch C
1And C
2Link.The power of motor can be passed on the turbine with pressure by the mobile of hydraulic oil by the pump impeller of fluid coupling.
Duplex clutch C1 and C2 are two parts independently mutually.Any one clutch all can produce following four kinds of Placements:
1. make the turbine of fluid coupling HC connect transmission shaft
2. make the pump impeller (motor E) of fluid coupling HC connect transmission shaft
3. above-mentioned two kinds of connections are implemented simultaneously
4. interrupt any connection
Above-mentioned transmission shaft is to C
1Refer to transmission shaft 1, to C
2Refer to transmission shaft 2.
Gear shift working principle of the present invention can describe in detail with the example of changing to second gear from one grade.One grade state at first, is described.As shown in Figure 2, when speed changer was in a gear and puts, the rotating speed of the output of motor and moment of torsion were by duplex clutch C
1Be delivered to axle 1, and by synchronizer S
13Be delivered to gear Z
11Because gear Z
11With Z
31Engagement, gear Z
31And Z
3RFixed with axle 3, then the power of motor E can pass to retarder and differential mechanism via axle 3.To be divided into five steps below and describe gearshift procedure in detail.For simplicity, the rotating speed when rotating speed during one grade of velocity ratio of speed changer employing and employing second gear velocity ratio is abbreviated as one grade of rotating speed and second gear rotating speed respectively.
Change the probationary period of second gear, shown in Fig. 3-1, power train control module (PCM) is sent the instruction control hydraulic system and is started shift fork (being omitted among the figure) with synchronizer S
25Stir to the right and make gear Z
32Fixed under unloaded state with axle 3.Handle duplex clutch C then
2The turbine of fluid coupling HC is linked to each other with axle 2.At this moment, Z
11With Z
31Engagement be in one grade of state, and gear Z
22And Z
32Engagement then be in second gear, the velocity ratio of two pairs of gears is different and transferring power simultaneously but can not interfere.This is to skid owing between the pump impeller of fluid coupling HC and the turbine contactless liquid friction taking place, and output speed remains one grade rotating speed.
Change first transitional period of second gear, shown in Fig. 3-2, power train control module (PCM) is sent the instruction control hydraulic system and is made duplex clutch C
1Break away from gradually and make synchronizer S
13Break away from Z
11, make it and one grade of gear Z
11With Z
31It doesn't matter.At this moment transmission is by fluid coupling HC and Z
22And Z
32Engagement realize that the rotating speed of output begins to increase from one grade of rotating speed basis and be approaching to the second gear rotating speed gradually.
Change second transitional period of second gear, shown in Fig. 3-3, power train control module (PCM) is sent the instruction control hydraulic system and is made duplex clutch C
2When pump impeller (motor E) was directly combined gradually with axle 2, the while is combining of retainer shaft 2 and fluid coupling HC and turbine still.Power continues by intermediate gear Z
22And Z
32Engagement transmit.Because C during this
2Combination gradually and the hydraudynamic drive of HC, make output speed near the second gear rotating speed to finally reaching the second gear rotating speed.
Change finishing the phase of second gear, shown in Fig. 3-5, power train control module (PCM) is sent the instruction control hydraulic system makes duplex clutch C2 that the turbine of pump impeller (motor E) with fluid coupling HC broken away from, this moment, fluid coupling HC no longer worked, and engine output shaft directly reaches power intermediate gear Z
22And Z
32, the second gear rotating speed is maintained and don't must uses fluid coupling.
Above-mentioned gear shift steps except from neutral gear to a grade or reverse gear, is equally applicable to transform to from a certain shelves the situation of its contiguous shelves.Change the combination of synchronizer, can obtain different gears.Table 1 expression be for obtaining different gears, the position of synchronizer when reverse gear and one to six grade.
Table 1 is from the position of coupler type automatic transmission synchronizer
| The synchronizer title | ||||
| The gear title | ????S R | ????S 13 | ????S 25 | ????S 46 |
| Reverse gear | Left side combination | Break away from | Break away from | Break away from |
| One grade | Break away from | Left side combination | Break away from | Break away from |
| Second gear | Break away from | Break away from | Right combination | Break away from |
| Third gear | Break away from | Right combination | Break away from | Break away from |
| Fourth gear | Break away from | Break away from | Break away from | Left side combination |
| Five grades | Break away from | Break away from | Left side combination | Break away from |
| Six grades | Break away from | Break away from | Break away from | Right combination |
Here it needs to be noted, change to the even number shelves and change to odd number shelves principle from the even number shelves identical from the odd number shelves, but C
1And C
2Clutch order slightly different, its difference can be used Fig. 4-1 and Fig. 4-2 explanation.
Fig. 4-the 1st, when the odd number shelves are changed to the even number shelves, fluid coupling HC and duplex clutch C
1And C
2Action description, can reduce following steps:
1. probationary period: C
1Double combination is changed unloaded even number shelves, C
2The transmission simultaneously of double combination odd and even number shelves, HC partly carries and skids
2. transitional period: C
1Break away from C
2Double combination even number shelves are by the HC transmission, and the odd number shelves are out of supply
3. second transitional period: C
1Break away from C
2Three mobilize E directly by the transmission of even number shelves in conjunction with , and HC does not break away from
4. finish the phase: C
1Break away from C
2Double combination motor E is directly by the transmission of even number shelves, and HC breaks away from
Fig. 3-1 to Fig. 3-4 pair only be the special case of Fig. 4-1 from one grade of explanation of changing to second gear.
Fig. 4-2 expression be when the even number shelves are changed to the odd number shelves, fluid coupling HC and duplex clutch C
1And C
2Action description, can reduce following steps:
1. probationary period: C
1Double combination is changed unloaded odd number shelves, C
2The transmission simultaneously of double combination odd and even number shelves, HC partly carries and skids
2. first transitional period: C
2Break away from C
1Double combination odd number shelves are by the HC transmission, and the even number shelves are out of supply
3. second transitional period: C
2Break away from C
1Three in conjunction with motor E directly by the transmission of odd number shelves, HC does not break away from
4. finish the phase: C
2Break away from C
1Double combination motor E is directly by the transmission of odd number shelves, and the double combination more than HC breaks away from the explanation and the implication of three combinations are as follows:
Double combination: transmission shaft or link to each other with the pump impeller (motor E) of fluid coupling HC, or link to each other with the turbine of HC
Three combinations: transmission shaft links to each other with turbine with the pump impeller (motor E) of fluid coupling HC
And one grade or the reverse gear of starting stage promptly shift to first gear or reverse gear from neutral gear illustrated in Figure 1, and its gearshift procedure is four step gear shift and do not need the first above-mentioned transitional period, and all the other processes are then similar.Be the example explanation with one grade below.
One grade probationary period, as shown in Figure 1, power train control module (PCM) is sent the instruction control hydraulic system and is started shift fork (being omitted among the figure) with synchronizer S
13Stir left and make gear Z
11Fixed and make duplex clutch C under unloaded state with axle 1
1In conjunction with.At this moment, one grade power transmission is by duplex clutch C
1, fluid coupling HC, gear Z
11And Z
31To retarder and differential mechanism output.The buffer function of fluid coupling make rotating speed gradually from zero to one grade of rotating speed transition.
One grade transitional period, power train control module (PCM) is sent the instruction control hydraulic system makes duplex clutch C1 with pump impeller (motor E), and turbine and axle 1 combine.Power is by one grade of gear Z
11And Z
31Engagement transmit, make output speed near one grade of rotating speed to finally reaching one grade of rotating speed.
One grade finish the phase, power train control module (PCM) are sent the instruction control hydraulic system and are made duplex clutch C
1Pump impeller (motor E) and fluid coupling HC are broken away from, and pump impeller this moment (motor E) directly reaches power one grade of gear Z
11And Z
31, this moment, fluid coupling HC did not participate in transmission, and one grade transmission of power only depends on gear to finish.
The gearshift procedure and the said process of reverse gear are similar, and its description can be with a grade in above-mentioned, S
13, Z
11And Z
31Change reverse gear respectively into, S
R, Z
1RAnd Z
iCan become reverse gear describes.
The detailed description of above-mentioned gear shift steps can be referred to as four step gear shift methods and starting three steps respectively, it can be write as computer language and be cured to and make the standard submodule on the integrated circuit, as the electronic control component from the coupler type automatic transmission.
Because above a series of successive relay trips from coupler, speed and moment of torsion when making gear shift are able to smooth transition, and the fluid absorbing of fluid coupling and buffering effect greatly reduce the impact of gear shift, thus protection motor and speed changer.Different with double-clutch automatic transmission, mainly replace the friction between clutch plate to realize a smooth transition from the coupler type automatic transmission with the contactless fluid friction of fluid coupling.This soft gearshift procedure will make the output speed of speed changer change very gentlely in less than one second time, make the people be difficult to feel to obtain, thereby reach the requirement of travelling comfort.Fig. 5-1 expression be transient process from the low grade to the top grade, Fig. 5-2 expression be transient process from the top grade to the low grade.
According to above principle, six speed among Fig. 1 can develop into various ways from the coupler type automatic transmission, to be applicable to different applications.Fig. 6 is the sketches of a kind of four speed from the coupler type automatic transmission, and Fig. 7 is the sketches of a kind of five speed from the coupler type automatic transmission, and Fig. 8 is the sketches of a kind of seven speed from the coupler type automatic transmission.
In sum, owing to utilized the contactless fluid friction of fluid coupling, the friction of clutch plate significantly reduces, and has promptly reduced frictional heat, has prevented the inordinate wear and the scuffing failure of clutch plate, and has kept powerdriven travelling comfort of not interrupting with gear shift.Therefore the material requirements of clutch plate also decreases, and helps improving the reliability of part and keeps low-cost.Because fluid coupling is hydraudynamic drive, has adaptive characteristic, thereby do not need sensing system complicated as double-clutch automatic transmission and loaded down with trivial details calculating to obtain parameter control whole system, therefore fairly simple from the control of coupler type automatic transmission.What be worth particularly pointing out is, the fluid coupling that the present invention adopts only just is used when gear shift, and the power transmission after the gear shift needn't be undertaken by it, thereby the high efficiency of transmission is guaranteed.This automatic transmission with the band fluid torque converter that generally efficient of employing is lower both at home and abroad has basic difference.
Claims (5)
1. from the coupler type automatic transmission, a kind of six shift automatic variable speed devices that are applied to car transmissions, this device comprises: a fluid coupling HC.This fluid coupling has initiatively pump impeller and passive turbine, and it uses and has hydraulic oil concurrently, cooling liquid, and the automatic transmission fluid of friction lubricating function is a medium.Be used for assisted gearshift, its effective use can reduce clutch plate surface friction and wearing and tearing, prevents to guarantee the power continuity and the travelling comfort of gear shift because friction makes clutch plate cross thermogenetic scuffing failure.
Two duplex clutch C
1And C
2Each clutch all can also can be connected with pump impeller being connected with the turbine of above-mentioned fluid coupling with 2 with transmission shaft 1, and also can be with three element, i.e. pump impeller, and turbine and transmission shaft all connect or all disconnect.
The transmission system of a gear.This transmission system is arranged in the parallel drive shaft mode, is used to be mounted to meshed gears, and its driving gear is by being assemblied in respectively on the transmission shaft 1, this axle be hollow and transmission shaft 2 on, this axle is for being sleeved in the transmission shaft 1 concentric and transmission shaft independently with it.All driven gear then is assemblied on the transmission shaft 3, and Jie's gear Zi that is used for reverse gear then is contained in the independent axle of another root.
Be installed in several synchronizers on transmission shaft 1 and the transmission shaft 3 respectively.The purpose of this synchronizer is to be used for gear shift, and they can be stirred fixed with transmission shaft with gear by shift fork or separate.
The hydraulic system of controlled clutch and above-mentioned synchronizer promptly comprises oil pump, spool, valve body, control valve, the system of spring and Sealing etc.;
The electronic control system that comprises a power train control module PCM.This system can handle by position transducer, temperature transducer, and the data of sensing systems such as velocity transducer input are carried out analytical calculation and contrast, make the gear shift decision and send instruction.
The component function of system zero described in the claim 1 and since function that various Placement provided comprise
By two duplex clutch C
1And C
2With the connection of fluid coupling HC, make two pairs to have the gear engagement of different drive ratios and do not interfere with different transmission shafts;
Contactless liquid friction by fluid coupling HC replaces the friction between clutch plate, so that reduce the friction and wear on clutch plate surface;
Utilize the turbine of fluid coupling HC, the output shaft of motor E and the transmission shaft of gear train 1 and transmission shaft 2 are by duplex clutch C
1And C
2Double combination, three in conjunction with and not combinations, realize the gear shift transition, prevent power interruption and avoid impacting;
Utilize the diverse location combination of synchronizer described in the claim 1, realize the conversion of different gears.
3. with system described in the claim 1, from any one grade of gear shift method (removing from neutral gear to a grade or reverse gear) to its contiguous shelves, i.e. four step gear shift methods, its four steps comprise probationary period, first transitional period, second transitional period with finish the phase.
4. application rights requires system described in 1, shift to first gear or the method for starting of reverse gear from neutral gear, and three steps that promptly start to walk, its three steps comprise probationary period, transitional period and finishing the phase.
5. the multi-form system of being derived out by the described system of claim 1 comprises four speed from the coupler type automatic transmission, five speed from coupler type automatic transmission and seven speed from the coupler type automatic transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100151544A CN100392289C (en) | 2004-01-16 | 2004-01-16 | Clutch-coupling type automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100151544A CN100392289C (en) | 2004-01-16 | 2004-01-16 | Clutch-coupling type automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1558125A true CN1558125A (en) | 2004-12-29 |
| CN100392289C CN100392289C (en) | 2008-06-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100151544A Expired - Fee Related CN100392289C (en) | 2004-01-16 | 2004-01-16 | Clutch-coupling type automatic transmission |
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| CN101566203B (en) * | 2009-05-11 | 2011-02-02 | 湘潭大学 | Intermediate shaft brake of hydraulic retarding type automatic speed changer |
| CN102080714A (en) * | 2010-12-11 | 2011-06-01 | 大连交通大学 | Novel variable speed fluid coupling |
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| CN108644341A (en) * | 2018-06-29 | 2018-10-12 | 吉林大学 | One kind is based on the more hydraulic transmission gear boxes of speed identification rail engineering automobile and its control method |
| CN109500590A (en) * | 2018-08-23 | 2019-03-22 | 湖南吉盛国际动力传动系统有限公司 | Automatic transmission valve general assembly method |
| CN112984056A (en) * | 2021-02-26 | 2021-06-18 | 淮阴工学院 | Six grades of AMT speed change systems of diaxon |
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| DE19711820A1 (en) * | 1996-08-08 | 1998-09-24 | Volkswagen Ag | Method for shifting a double clutch transmission and double clutch transmission |
| CN1349902A (en) * | 2000-10-20 | 2002-05-22 | 韩培洲 | Shifting speed variator with hydraulic coupler |
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- 2004-01-16 CN CNB2004100151544A patent/CN100392289C/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100585237C (en) * | 2004-06-11 | 2010-01-27 | 特纳动力系统有限公司 | Transmission and shift method |
| CN101720296B (en) * | 2007-05-30 | 2012-08-22 | 施奥泰尔有限公司 | Rudder propeller drive, and rudder propeller driving method |
| CN101463897B (en) * | 2007-12-17 | 2013-11-27 | 现代自动车株式会社 | Automatic transmission for vehicles |
| CN102144114B (en) * | 2008-09-03 | 2014-08-06 | 罗伯特·博世有限公司 | Method for changing gear stages and transmission arrangement |
| CN101865247B (en) * | 2009-04-14 | 2013-09-11 | 腓特烈斯港齿轮工厂股份公司 | Double clutch transmission |
| CN101865247A (en) * | 2009-04-14 | 2010-10-20 | 腓特烈斯港齿轮工厂股份公司 | Dual-clutch transmission |
| CN101566203B (en) * | 2009-05-11 | 2011-02-02 | 湘潭大学 | Intermediate shaft brake of hydraulic retarding type automatic speed changer |
| CN102483107A (en) * | 2009-07-16 | 2012-05-30 | 舍弗勒技术股份两合公司 | Clutch contact points |
| CN102483107B (en) * | 2009-07-16 | 2014-12-03 | 舍弗勒技术股份两合公司 | Clutch contact points |
| CN102310760A (en) * | 2010-06-30 | 2012-01-11 | 比亚迪股份有限公司 | Driving method of hybrid driving system |
| CN102080714A (en) * | 2010-12-11 | 2011-06-01 | 大连交通大学 | Novel variable speed fluid coupling |
| CN102080714B (en) * | 2010-12-11 | 2012-11-07 | 大连交通大学 | Novel variable speed fluid coupling |
| CN104712718B (en) * | 2013-12-13 | 2018-05-25 | 现代自动车株式会社 | Transmission for a vehicle |
| CN104712718A (en) * | 2013-12-13 | 2015-06-17 | 现代自动车株式会社 | Transmission for vehicle |
| CN104728426A (en) * | 2013-12-18 | 2015-06-24 | 现代自动车株式会社 | Clutch failure diagnostic method for dual clutch transmission |
| CN106594214A (en) * | 2015-10-20 | 2017-04-26 | 熵零股份有限公司 | Power transmission system |
| CN108180261A (en) * | 2018-02-01 | 2018-06-19 | 淮阴工学院 | A kind of automatic mechanical transmission speed change system |
| CN108180261B (en) * | 2018-02-01 | 2023-12-22 | 淮阴工学院 | Speed changing system of mechanical automatic transmission |
| CN108644341A (en) * | 2018-06-29 | 2018-10-12 | 吉林大学 | One kind is based on the more hydraulic transmission gear boxes of speed identification rail engineering automobile and its control method |
| CN109500590A (en) * | 2018-08-23 | 2019-03-22 | 湖南吉盛国际动力传动系统有限公司 | Automatic transmission valve general assembly method |
| CN112984056A (en) * | 2021-02-26 | 2021-06-18 | 淮阴工学院 | Six grades of AMT speed change systems of diaxon |
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| CN100392289C (en) | 2008-06-04 |
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