CN1335235A - Variable speed control method for automatic speed transmission - Google Patents
Variable speed control method for automatic speed transmission Download PDFInfo
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- CN1335235A CN1335235A CN 01118209 CN01118209A CN1335235A CN 1335235 A CN1335235 A CN 1335235A CN 01118209 CN01118209 CN 01118209 CN 01118209 A CN01118209 A CN 01118209A CN 1335235 A CN1335235 A CN 1335235A
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Abstract
A shift control method for an automatic transmission is provided with a process determining whether the input rotation speed of the automatic transmission is lowered to a rotation speed or less higher than the input rotation speed of the high speed gear by a prescribed value or not, a process determining whether the input rotation speed is lowered to the input rotation speed of the high speed gear during an interval elapsing a prescribed time from the determination or not, when the input rotation speed is determined to be lowered to the rotation speed or less higher than the input rotation speed of the high speed gear by the prescribed value; a process fastening the frictional engagement element by increasing the engagement hydraulic pressure of the frictional engagement element, when the input rotation speed after elapsing the prescribed time is more than the input rotation speed of the high speed gear; and a process increasing the engagement hydraulic pressure of the frictional engagement element at a slope slightly gentler than the increase slope in the fastening, when the input rotation speed is lowered from the input rotation speed of the high speed gear.
Description
The present invention relates to a kind of shifting control method of automatic transmission with hydraulic torque converter, particularly about the invention of the control method of the frictional fit part when rising speed change.
Usually, the operating condition of the automatic transmission with hydraulic torque converter response speed of a motor vehicle or throttle opening etc. automatically determines gear by the speed change line chart, carries out speed change.In such automatic transmission with hydraulic torque converter, when the walking of acceleration pedal limit is stepped on the limit, slow down acceleration pedal suddenly, because of the speed of a motor vehicle almost enters full cut-off at the fast state throttle opening, then the operating point in the speed change line chart has surpassed the speed change point, just to high speed gear side speed change.This is called from rising speed change.
In rising speed change, because air door is closed, is the power closed condition such, and the turbine rotation number descends naturally.Usually, for the change of the input current value of the electromagnetic valve of the oil pressure of control frictional fit part, the response of oil pressure is slow, thereby considers that in advance it is slow, synchronous judgement to judging that the frictional fit parts match postpones is necessary to make the position that drops to high speed gear turbine rotation number.In a word, turbine is imported rotation number to do synchronous judgement than high speed gear turbine rotation number with only high than institute definite value rotation number usually.
Yet, because of the descending speed of turbine rotation number not necessarily, can not predict it whether is to be in the state that cooperates of being about to the frictional fit part that cooperates side when judging synchronously.
Fig. 1 shows that the turbine rotation number when rising speed change (for example 1 speed → 2 speed), the received current of electromagnetic valve, the time of frictional fit parts match oil pressure change.
The solid line of Fig. 1 is the descending speed of turbine rotation number and the situation that the frictional fit parts match postpones fine cooperation, when the turbine rotation number is reduced to the turbine rotation number of high speed gear as making frictional fit part perfect fitting, can finish not have impact, speed change sleekly.
The dotted line of Fig. 1 is, the descending speed of turbine rotation is big, the state when the frictional fit part does not reach cooperation and will reach when judging synchronously, the example that the turbine rotation number descends from the turbine rotation number of high speed gear (with call in the following text down towards).At this moment, dash the back owing to make frictional fit part perfect fitting down, promote oil pressure rapidly, the lifting that the turbine rotation just takes place is impacted.
Open in the flat 10-181386 communique the spy, disclose, become the target rotation number, motor torque is carried out the content of controlled reset for making the turbine rotation number when when rising speed change.
At this moment, can prevent that the following of turbine rotation from dashing itself, but be necessary, to have the confined shortcoming of employed driving engine along with control becomes complicated to the centralized control of driving engine and automatic transmission with hydraulic torque converter.
Therefore, the objective of the invention is, utilize control frictional fit parts match oil pressure, a kind of shifting control method that can prevent by the automatic transmission with hydraulic torque converter of the following cooperation impact of dashing when rising speed change is provided.
For achieving the above object, provided by the invention with the full cut-off throttle opening or near the state of full cut-off, by to fixed frictional fit component delivery cooperate oil pressure, carry out moving to high speed gear from low gear, it is characterized in that having the input rotation number of judging automatic transmission with hydraulic torque converter and whether dropped to and only be the operation below the high rotation number of institute's definite value than the input rotation number of high speed gear; When judging that the input rotation number of described input rotation number than high speed gear only dropped to below the rotation number high for institute's definite value, between judgement begins to fix time to the institute of process from judgement, the input rotation number whether than the input rotation number step-down of above-mentioned high speed gear operation; When fix time in more than the input rotation number of above-mentioned input rotation number later at high speed gear, make frictional fit parts match oil pressure rise the operation of concluding the frictional fit part; With in the input rotation number step-down of described input rotation number than high speed gear, the operation that the gradient that relaxes with the rising gradient when concluding frictional fit parts match oil pressure rises.
At first, the input rotation number is judged synchronously with the high rotation number of rotation number institute definite value than high speed gear only.By synchronous judgement, when below the input rotation number is only reduced to than the input rotation number of high speed gear the rotation number high for institute's definite value, being determined, then from synchronous judgement between fixing time through institute, judge to dash down whether taken place.
Fix time through later input rotation number be more than the input rotation number of high speed gear in, judge not dash down and take place, and frictional fit parts match oil pressure is risen with common heavy gradient, the frictional fit part is concluded also can.At this moment, the input rotation number is almost consistent with the input rotation number of high speed gear, thereby does not impact.
On the other hand, when the input rotation number is lower than the input rotation number of high speed gear (down towards time),, follow the impact of cooperation when when the oil pressure state of concluding the frictional fit part rises with heavy gradient.Here, instantly towards the time, the gradient slow with the rising gradient when concluding frictional fit parts match oil pressure rises.In a word, carry out scan control.Thus, the impact of raising of the turbine rotation that disappears can be separated, speed change can be finished sleekly.
In addition, as the input rotation number among the present invention, be the rotation number of the input shaft of automatic transmission with hydraulic torque converter, in the situation of the automatic transmission with hydraulic torque converter that possesses torque converter, be equivalent to the turbine rotation number.
In the shifting control method of above-mentioned automatic speed variator of the present invention, preferably also comprise, the input rotation number become than high speed gear input rotation number low after, judge that above-mentioned input rotation number transfers the operation of rising to from decline; Input is after rotation number transfers rising to from decline, judges whether input rotation number by high speed gear rises to the operation more than the only low rotation number; With rise to rotation number that only institute's definite value is low when above in the input rotation number than the input rotation number of high speed gear, rising frictional fit parts match oil pressure, the operation of concluding the frictional fit part.
In a word, under the input rotation number takes place towards the time, judge that the input rotation number for to transfer rising to from decline, rises to thereafter more than the input rotation number rotation number that only institute's definite value is low than high speed gear, that is, judge synchronously again.Judge synchronously and conclude the frictional fit part rapidly and not have the end of impact speed change again by this.
In the shifting control method of the automatic speed variator of the invention described above, in the input rotation number during than the input rotation number step-down of high speed gear, the maximum slippage of input rotation number or input rotation number become in the setting range like that than the time integral value of input rotation number from step-down to the slippage that transfers rising to of high speed gear, and the initial stage oil pressure of learning control frictional fit part is desirable.
In automatic transmission with hydraulic torque converter, by its individual difference, following momentum also has deviation.When following momentum is big, carry out control of the present invention, speed change ends the possibility of delay.Following momentum, is that the piston of frictional fit part can be changed by the oil pressure of the state that contacts clutch plate as initial beginning at the initial stage oil pressure of frictional fit part.In addition.Can judge by the time integral value that is flushed to the slippage that transfers rising to down.As following momentum, the maximum slippage of input rotation number or input rotation number
Here, following momentum by learning control initial stage oil pressure, is removed individual difference as in being in setting range, realized cooperating impacting and lacked, and speed change postpones few automatic transmission with hydraulic torque converter.
In the shifting control method of the automatic speed variator of the invention described above, in the input rotation number step-down of input rotation number than high speed gear, continue to make frictional fit parts match oil pressure to rise, when the input rotation number transfers to when rising from decline, make that to cooperate oil pressure rising gradient ratio rising gradient so far will be desirable for a short time.In a word, behind the input input rotation number step-down of rotation number than high speed gear, monitoring input rotation number, the input rotation number makes to cooperate the rising gradient of oil pressure to diminish after decline transfers to when rising, and thus, the impact of raising of turbine rotation number is further alleviated.
Below drawing is carried out simple declaration.
Fig. 1 is the time variation diagram of turbine rotation number, coil current and cooperation oil pressure when rising speed change in the past.
Fig. 2 is the pie graph about the present invention's one routine automatic transmission with hydraulic torque converter.
Fig. 3 is the synoptic map of speed-changing mechanism of the automatic transmission with hydraulic torque converter of displayed map 1.
Fig. 4 is the action schedule of each mating parts shown in Figure 3 and electromagnetic valve.
Fig. 5 is from the diagram of circuit that rises variable speed control about an example of the present invention.
Fig. 6 be do not take place down towards the time turbine rotation number, coil current and cooperate the time variation diagram of oil pressure.
Fig. 7 be take place down towards the time turbine rotation number, coil current and cooperate the time variation diagram of oil pressure.
Fig. 8 is the time variation diagram for turbine rotation number, coil current and the cooperation oil pressure of explanation learning control.
Fig. 9 is the diagram of circuit of a routine learning control.
Among the figure, B1-drg (frictional fit part), the electromagnetic valve of SOL1-B1 drg control usefulness, 2-controller.
Fig. 2 illustrates about of the present invention one routine automatic transmission with hydraulic torque converter.
Automatic transmission with hydraulic torque converter 1 has speed change structure and torque converter as described later, and speed change structure basis is from the instruction control of AT controller 2 gear arbitrarily.At AT controller 2, by throttle opening sensor 3, car speed sensor 4, turbine rotation number sensor 5, when importing throttle opening, the speed of a motor vehicle, turbine rotation number respectively, from shift position signals such as shift position sensor 6 input " P ", " R ", " N ", " D ".In addition, the signal of AT controller 2 inputs is not limited to described signal.The described incoming signal of AT controller 2 responses, control variable speed control electromagnetic valve SOL1～SOL3.
Fig. 3 illustrates an in-built example of automatic transmission with hydraulic torque converter 1.
This automatic transmission with hydraulic torque converter 1 has, torque converter 20,21,3 power-transfer clutch C1～C3 of input shaft, 2 drg B1 by torque converter 20 transmission engine powers, B2, free-wheel clutch F, Lapie Buddhist nun's type star gear mechanism 22, output shaft 24, differential attachment 25 etc.
The forward fixed star driving device 22a of star gear mechanism 22 links input shaft 21 by the C1 power-transfer clutch, and forward fixed star driving device 22a links change-speed box case 26 by the B1 drg.And rear portion fixed star driving device 22b links input shaft 21 by the C2 power-transfer clutch.Transmission gear 22c links input shaft 21 by tween drive shaft 27 and C3 power-transfer clutch.In addition, transmission gear 22c is by the B2 drg and only allow that transmission gear 22c just changes (hand engine rotation) free-wheel clutch F, links change-speed box case 26.Transmission gear 22c supports 2 kinds auxiliary gear 22d, 22e, and forward fixed star driving device 22a stings the long auxiliary gear 22d with axial length, and rear portion fixed star driving device 22b stings and long auxiliary gear 22d by the short short auxiliary gear 22e of axial length.Only can sting and the annular gear 22f of long auxiliary gear 22d is incorporated into output transmission 23.Output transmission 23 is by output shaft 24 differential attachment 25 that continues.
Fig. 4 shows power-transfer clutch C1, C2, C3, the action of drg B1, B2 and free-wheel clutch F, realize advancing 4 grades, retreat 1 grade gear.In Fig. 4, ● the active state of expression oil pressure, in addition, the B2 drg is matched with when retreating and during the 1st speed, but when cooperating the 1st speed only be the L district time.
In Fig. 4, also show (the action of the common state of SOL1～SOL3) of the 1st～the 3rd electromagnetic valve.Zero expression "on" position, * the expression non-power status.The 1st electromagnetic valve SOL1 has B1 drg control usefulness concurrently, and the 2nd electromagnetic valve SOL2 has C2 clutch control usefulness concurrently, and the 3rd electromagnetic valve SOL3 has C3 clutch control usefulness concurrently and the control of B2 drg is used.The 3rd electromagnetic valve SOL3 has the reason that the C3 clutch control is used and the B2 drg is used concurrently, is that the B2 drg is failure to actuate in D, 2 districts, only in the Jake brake control in L district and the transition control usefulness of Zone R, thereby does not disturb the C3 power-transfer clutch that moves in the D district.
The the 1st～the 3rd electromagnetic valve SOL1～SOL3 carries out careful oil pressure control, functions of use electromagnetic valve or linear solenoid valve because of needs.And, in this embodiment, the 1st electromagnetic valve SOL1 closed type, the 2nd, the 3rd electromagnetic valve SOL2,3 uses open type.
Below, to controlling with reference to Fig. 5 explanation to the oil pressure of the B1 drg (frictional fit part) of 2 speed when rising speed change from 1 speed.Turbine rotation number when Fig. 6, Fig. 7 point out to implement shown in Figure 5 control, B1 drg changed with the received current of electromagnetic valve SOL1, the time that the B1 drg is pressed, and Fig. 6 is the situation of dashing under not taking place, and Fig. 7 is the situation that generation is dashed down.
Control is differentiated whether 1 speed (step S1) of present gear at the beginning.Situation beyond 1 speed is returned.Then, differentiating power closes, is whether full cut-off or near full cut-off (step S2) of throttle opening.When the power closed condition, the controller 2 response speed of a motor vehicle and the throttle opening gear (at this moment being 2 speed) of being wished by the decision of speed change line chart at that time is to electromagnetic valve SOL1 output (step S3) gear-shift command (from rising instruction).Output according to gear-shift command, at first, the gap of B1 drg makes (step S4) behind the ON of the electromagnetic valve place state because stopping up only certain hour, for the initial stage oil pressure of supplying with the B1 drg makes coil current certain (step S5), thereafter for the cooperation oil pressure of B1 drg is risen gradually, with coil current from certain gradient A rise (step S6).
During the aftermentioned gap is stopped up, during the initial stage oil pressure, gradient A during, constitute the control period that cooperates the state before the B1 drg together.That is, during the gap is stopped up,, only during certain, make the ON of coil current place state, make piston during the clutch plate direction moves rapidly for the piston chamber that removes the B1 drg as early as possible and the gap (invalid air door) of clutch plate.This gap is stopped up response and need and be implemented.The initial stage oil pressure, be above-mentioned make like that piston reach with initial clutch plate state of contact mobile during, the B1 drg is supplied with the oil pressure higher slightly than return spring power.The pressure of initial stage oil pressure is variable by the aftermentioned learning control, during it by operative condition (as from low gear to the length of turbine rotation number fall time of high speed gear etc.) and variable.During the gradient A piston that moves to the state that contacts initial clutch plate is further pushed away it, whole clutch plates move to during the preceding state of contact (preceding state takes place in torque), by the gradient A that delays oil pressure are risen.It is irrelevant always certain during this gradient A reaches with operative condition.
Owing to make to be in the power closed condition, the turbine rotation number begins to descend.Whether the rotation number when judging the turbine rotation number from 2 speed here, drops to only is (step S7) below the high rotation number of certain value.In a word, judge synchronously.Declare timer-operated rotation number synchronously, for example preferably than the high value of turbine rotation number 30～50rpm degree when 2 speed.
In judging synchronously, when being judged to be synchronously, when the turbine rotation number that is the turbine rotation number when being in 2 speed drops to below the high rotation number of certain value only, the cooperation of beginning B1 drg, thereby coil current is with certain gradient B rise (step S8).Gradient B and described gradient A also can be equal, but in this embodiment, with A＜B.Its reason is dashed when not detecting under aftermentioned, has shortened the time of ending to speed change.
Below, descend towards detecting (step S9).Detect as dashing down, the turbine rotation number when detecting the turbine rotation number whether than 2 speed becomes low, after judging synchronously, continues to implement then (step S10) during certain.As during this certain, for example about 100～300msec.
After judging synchronously, both made through during certain, dash down when not being detected, as shown in Figure 6, the turbine rotation number means in the turbine rotation number convergence of desirable state during to 2 speed, so judge the state that has reached the speed change that to end, coil current is risen (step S11) with certain gradient C, and process during certain is after having continued (step S12), conclude the B1 drg, finish speed change (step S13).The gradient C of described coil current is for concluding the control of B1 drg, and is bigger than so far gradient A, B.
C＞A、B
During gradient C certain, take precautions against to conclude to impact betiding during the possible trouble, do not establish gradient C during, also can conclude the B1 drg at once.
After judging synchronously, detect in during certain dash down in, as shown in Figure 7, coil current is risen (step S14) by certain gradient D, to the cooperation oil pressure rising that suppresses to continue on the direction of dashing down to make the B1 drg.In addition, during certain in owing to often monitor the turbine rotation number, dash if detect down, end during not waiting necessarily and just can move to step S14.During the described gradient D, be aftermentioned turbine rotation number for alleviate from decline transfer that counter-rotating when rising impacts to during, gradient D can equate with gradient A, B, or than its little also can, littler than gradient C at least.
With gradient D coil current is risen, the limit is risen the cooperation oil pressure of B1 drg slowly, and frontier inspection goes out the turbine rotation number and transfers rising point (step S15) to from decline.The turbine rotation number makes coil current by certain gradient E rising (step S16) after the counter-rotating of rising.During this gradient E, during impacting in order to relax again synchronously, in an embodiment, set E＜D.Its reason is, after the turbine rotation number turns to rising, in order to control to lentamente the rotation number near 2 speed.In addition, also can set E equates with its preceding gradient D.
Below, judge synchronously that again the rotation number when promptly judging the turbine rotation number whether from 2 speed rises to more than the low rotation number of certain value only (step S17).Declaring timer-operated rotation number more synchronously, for example is low value about turbine rotation number 30～50rp during than 2 speed again.In judging synchronously again, the turbine rotation number rises to rotation number that only certain value is low when above being judged to be from the rotation number in 2 whens speed, be judged to be the state of speed change finally that reached, coil current is risen (step S18), (step S19) after continuing through certain hour, conclude the B1 drg and stop speed change (step S20) from certain gradient C.The control of described step S18～S20, same with step S11～S13 control, omit step S18, S19 according to necessity, it is also passable to conclude the B1 drg immediately.
As mentioned above, when the turbine rotation number takes place to dash down, to the cooperation oil pressure of B1 drg is not to make its sharply rise (with reference to Fig. 1) resembling in the past, owing to implemented to have the mitigation rising scan control of gradient B, D, E, just can eliminate the impact of raising of turbine rotation number, can stop speed change sleekly.
Fig. 8, Fig. 9 show the 2nd embodiment of the present invention.
In automatic transmission with hydraulic torque converter, because its individual difference, following momentum is also variant.When momentum is excessive instantly, implement described scan control, stop needing the time to speed change.Among the embodiment here, the following momentum of turbine rotation number is in the setting range when rising, and is the amount of the initial stage oil pressure (being illustrated by Pi among Fig. 8) of learning control frictional fit part.The initial stage oil pressure pi of frictional fit part is to make above-mentioned plug cock move to oil pressure with initial clutch plate contact condition, changes this oil pressure, because state can change the frictional fit parts match when judging synchronously before, following momentum also can change.In addition, initial stage oil pressure Pi because of proportional with coil current Ia, then can control initial stage oil pressure Pi by coil current Ia.
As following momentum, the maximum slippage of turbine rotation number (representing with Δ T among Fig. 8), perhaps turbine rotation number uses the time integral value (representing with oblique line among Fig. 8) that forwards the slippage till the rising behind the turbine rotation number step-down by high speed gear to define.Particularly, the turbine rotation number detects from decline and transfers turbine rotation number when rising to, and fixed this rotation number is maximum slippage Δ T, and the time integral that transfers to when perhaps the turbine rotation number of turbine rotation number when becoming 2 speed is following till the rising is also passable.Following momentum like this constitutes the initial stage oil pressure of the frictional fit part of setting range by learning control, can remove individual difference, and can realize removing and impact and the change-speed box of speed change delay.
Fig. 9 illustrates a routine learning control of initial stage oil pressure.This example is as descending momentum to be to use the example of the maximum amount of the falling Δ T of turbine rotation number.
Learning control one starts, and at first differentiates whether exported (step S21) from the gear-shift command that rises.When the gear-shift command that rises is exported, then export initial stage oil pressure (current value) Ia (step S22).This initial stage oil pressure Ia is redefined for the oil pressure that generation is dashed down.Experienced at first when rising, the output of the initial value of initial stage oil pressure Ia has been experienced several times after liter, resembles aftermentioned because initial stage oil pressure Ia upgrades, and it is also passable to export the initial stage oil pressure Ia that last time was updated.
Then, detect down towards the time turbine rotation number maximum slippage Δ T (step S23).
Then, maximum slippage Δ T and setting value Nmin, Nmax are compared (step S24).If maximum slippage Δ T when being Nmin≤Δ T≤Nmax, not upgrading initial stage oil pressure Ia and promptly stops in setting range.In addition, when Δ T＞Nmax, following momentum is judged as excessive, for initial stage oil pressure Ia value so far, and the certain value α that only adds, and upgrade initial stage oil pressure Ia (step S25).On the contrary, when Δ T＜Nmin, following momentum is judged as too small, to initial stage oil pressure Ia value so far, only subtracts and calculates certain value α, the initial stage oil pressure Ia (step S26) that upgrades.Next time when rising, use the initial stage oil pressure Ia upgraded, control frictional fit parts match oil pressure also can.In addition,, with maximum slippage Δ T and upper lower limit value relatively, as in upper lower limit value the time, show the example of not upgrading at step S24, but also passable near the such frequent renewal of setting value.
During upgrading initial stage oil pressure Ia repeatedly in this wise, following momentum is by in deciding scope inner control, can realize not having impacting stable speed change.
In described embodiment, be for from 1 speed to 2 speed from rising speed change, promptly control is illustrated about the oil pressure of B1 drg, but in other the oil pressure control that can be applicable to the frictional fit part in rising speed change (as 2 speed to 3 speed, 3 speed to 4 speed) too.
In addition, automatic transmission with hydraulic torque converter of the present invention is not limited only to the automatic transmission with hydraulic torque converter that 3 power-transfer clutch C1～C3,2 drg B1, B2 arranged shown in Figure 3.
In sum, by the present invention, in rising speed change, judge following the dashing of back judgement turbine rotation synchronously, down towards the time because to rise than concluding the slow gradient of frictional fit parts match oil pressure rising gradient, can remove down towards the time turbine rotation raise impact, make the effect of the speed change that obtains ending sleekly.
Thereby,,, and the driving engine that can use is not restricted yet so control is simple owing to control the control of unifying of driving engine and change-speed box there is no need to resemble in the past.
Claims (4)
1. the automatic gear shifting method of an automatic transmission with hydraulic torque converter, during in the throttle opening full cut-off or near the state of full cut-off, frictional fit component delivery by Xiang Suoding cooperates oil pressure, carry out moving to high speed gear from low gear, it is characterized in that having: whether the input rotation number of judging automatic transmission with hydraulic torque converter has only dropped to than the operation below the high rotation number of institute's definite value of the input rotation number of high speed gear; Be judged as in described input rotation number and only dropped to the rotation number higher when following than the institute definite value of the input rotation number of high speed gear, from judge fix time to the institute of process between, judge the input rotation number whether than the input rotation number step-down of described high speed gear operation; Fix time when later the described input rotation number input rotation number that is high speed gear is above, the operation that makes frictional fit parts match oil pressure rise and conclude the frictional fit part; When becoming lower in described input rotation number than the input rotation number of high speed gear, the operation that the gradient that relaxes with the rising gradient when concluding frictional fit parts match oil pressure rises.
2. according to the described self-shifting shifting control method of claim 1, it is characterized in that also having: behind the input rotation number step-down of described input rotation number than high speed gear, judge that described input rotation number transfers the operation of rising to from reduction; After described input rotation number transfers rising to from decline, judge whether rise to than the operation more than the input rotation number rotation number that only institute's definite value is low of high speed gear; Described input rotation number rises to when above than the input rotation number rotation number that only institute's definite value is low of high speed gear, rising frictional fit parts match oil pressure, the operation of concluding the frictional fit part.
3. according to claim 1 or 2 described self-shifting shifting control methods, it is characterized in that, in described input rotation number during than the input rotation number step-down of high speed gear, the maximum slippage of described input rotation number or input rotation number are from being in the setting range like that the initial stage oil pressure of the described frictional fit part of learning control to the time integral value of the slippage that transfers rising to than the input rotation number step-down of high speed gear.
4. according to claim 1,2 or 3 described self-shifting shifting control methods, it is characterized in that, in described input rotation number during than the input rotation number step-down of high speed gear, make described frictional fit parts match oil pressure continue to rise, transfer to when rising from decline in the input rotation number, make to cooperate the rising gradient ratio rising gradient so far of oil pressure to diminish.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP220005/2000 | 2000-07-21 | ||
| JP2000220005A JP3492295B2 (en) | 2000-07-21 | 2000-07-21 | Shift control method for automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1335235A true CN1335235A (en) | 2002-02-13 |
| CN1231369C CN1231369C (en) | 2005-12-14 |
Family
ID=18714688
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01118209 Expired - Fee Related CN1231369C (en) | 2000-07-21 | 2001-05-22 | Variable speed control method for automatic speed transmission |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3492295B2 (en) |
| CN (1) | CN1231369C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100416139C (en) * | 2002-12-23 | 2008-09-03 | 范多尔内斯变速器公司 | Method for operating a continuously variable transmission |
| CN100436891C (en) * | 2004-02-06 | 2008-11-26 | 五十铃自动车株式会社 | Engine control device of power transmission device for vehicle |
| CN105518352A (en) * | 2013-09-13 | 2016-04-20 | 加特可株式会社 | Oil pressure controller for automatic transmission |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3900049B2 (en) * | 2002-09-12 | 2007-04-04 | トヨタ自動車株式会社 | Hydraulic control device for automatic transmission for vehicle |
| JP4716743B2 (en) * | 2005-01-28 | 2011-07-06 | ダイハツ工業株式会社 | Shift control method and apparatus for automatic transmission |
-
2000
- 2000-07-21 JP JP2000220005A patent/JP3492295B2/en not_active Expired - Fee Related
-
2001
- 2001-05-22 CN CN 01118209 patent/CN1231369C/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100416139C (en) * | 2002-12-23 | 2008-09-03 | 范多尔内斯变速器公司 | Method for operating a continuously variable transmission |
| CN100436891C (en) * | 2004-02-06 | 2008-11-26 | 五十铃自动车株式会社 | Engine control device of power transmission device for vehicle |
| CN105518352A (en) * | 2013-09-13 | 2016-04-20 | 加特可株式会社 | Oil pressure controller for automatic transmission |
| CN105518352B (en) * | 2013-09-13 | 2017-07-07 | 加特可株式会社 | The hydraulic pressure control device of automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002039346A (en) | 2002-02-06 |
| CN1231369C (en) | 2005-12-14 |
| JP3492295B2 (en) | 2004-02-03 |
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