KR100267309B1 - Up-shift control device and method - Google Patents

Abstract

PURPOSE: A gear shifting control device and the method when an automatic transmission is in up-shift is provided achieve a stable gear shifting by controlling a duty ratio of hydraulic control signals according to rotary speed of a turbine of a torque converter. CONSTITUTION: A torque converter converts an engine torque to a rotary force of fluid and output the torque, and is equipped with a detecting device of rotary speed in a turbine. A detecting device of travelling condition detects a vehicle speed, a throttle angle, a transmission temperature and so on, and outputs the signals. A gear shifting control device calculates a rotary speed of the turbine of the torque converter and outputs signals of duty pattern for hydraulic control according to a fixed table map. A hydraulic control system constrains a clutch and a brake by operating each solenoid valve for gear shifting according to the signals of duty pattern and shifts up an aimed speed step according to a vehicle speed, a throttle angle, and the rotary speed of the turbine of the torque converter.

Description

Shift control device and method for upshift of automatic transmission

FIG. 1 is a block diagram of an upshift shift control device of an automatic transmission according to an embodiment of the present invention,

FIG. 2 is a configuration diagram of a hydraulic control system according to the present invention,

FIG. 3 is a graph showing a change in the number of revolutions of the turbine shaft during a power-up upshift operation according to an embodiment of the present invention.

FIG. 4 is a diagram illustrating a duty pattern according to a shift state in the course of performing an upshift operation at power-on according to an embodiment of the present invention;

5 (a) and 5 (b) are flowcharts for realizing an upshift shift control method at power-on of an automatic transmission according to an embodiment of the present invention.

FIG. 6 is a flowchart for realizing duty control in a period "b" during a shift process of an upshift at power-on according to an embodiment of the present invention.

[Industrial Applications]

The present invention relates to a shift control method for an automatic transmission, and more particularly, to a shift control method for an automatic transmission in which, when an upshift shift operation is performed to an arbitrary target shift stage according to power-on, Shift speed control of the automatic transmission in which the duty ratio of the hydraulic control signal for synchronizing the speed change is adjusted in accordance with the rotational speed of the automatic transmission.

[0003]

Generally, an automobile equipped with an automatic transmission controls the hydraulic pressure flowing into each of the clutches and the brakes within a predetermined shift range according to the opening ratio of the throttle valve, which adjusts the running speed of the car and the amount of air sucked, So that the shift gear of the target speed change stage can be operated.

Such an automatic transmission controls the output power of the engine through the torque converter through the torque converter and controls the transmission control device according to the traveling speed of the vehicle, the opening ratio of the throttle valve, A duty signal for oil pressure control is output so that the shift gear can be operated, and the target shift stage is synchronized through the corresponding solenoid valve.

Therefore, the automatic transmission performs port conversion according to the range of the shift lever selected by the driver and receives the fluid pressure from the oil pump. Depending on the fluid pressure through the solenoid valve controlled according to the duty ratio, And is operated to select the speed change stage to control the operation state of the hydraulic operation friction element.

The operation of the planetary gear set is switched according to the selective operation of the friction element composed of the clutch and the brake, and the gear is transmitted to the drive gear after an appropriate gear ratio is performed.

When the power transmitted to the drive gear is transmitted, the shifted power is transmitted to a driven gear which is gear-engaged with the longitudinal reduction gear by a driven gear which is gear-engaged with the drive gear, thereby controlling the turning operation of the wheel.

The automatic transmission that automatically performs the shift operation to the target shift stage that is appropriate for the running state of the vehicle according to the above-described operating principle is configured such that, when performing the shift operation to each corresponding target shift stage, A control operation for increasing the shift feeling is executed by reducing the shift shock which occurs at the time of the change of the operation of the friction element that is converted from the state to the operating state.

Therefore, in a vehicle equipped with an automatic transmission in which the target speed change stage is controlled in accordance with the hydraulic pressure, it is not necessary to operate the clutch pedal for interrupting the power to the engine in order to change the speed change stage according to the driven vehicle speed. The driving fatigue can be alleviated and the engine stall due to malfunction of the driver during running and insufficient driving can be prevented. Therefore, the driving operation can be facilitated even for a beginner.

In the conventional control method of controlling the duty ratio according to the vehicle speed in the automatic transmission as described above, the characteristics of the inherent torque of the engine are set in the memory means as data and then the vehicle speed of the driven vehicle, The opening rate of the throttle valve which is opened or closed according to the rotational speed and the driving of the accelerator pedal is detected and the corresponding gear range is changed according to the set data.

[Problems to be solved by the present invention]

In such a conventional automatic transmission, the control method of the speed change end is not sensitive to the variation in the opening rate of the throttle valve, the friction element, and the reaction occurring in the repetitive operation of the clutch and the brake, So that a shock is generated in the course of shifting, and a stable ride feeling can not be provided to a driver and a pilfered occupant.

[Object of the Invention for Solving the Problem]

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and it is an object of the present invention to provide an internal combustion engine which is capable of performing upshifting from a lower end to a higher end in a power-on state caused by an increase in opening rate of a throttle valve, And the duty of each solenoid valve is controlled by detecting the target speed change stage from the rotation speed of the turbine in the torque converter for outputting the converted torque, And the response of the shift is improved by the progress of the shift according to the load.

[MEANS FOR SOLVING PROBLEMS]

According to an aspect of the present invention, there is provided an automatic transmission for a motor vehicle,

A torque converter which converts a drive torque of the engine into a rotational force of the fluid and outputs the rotational torque, and a rotational speed detecting means at a predetermined position of the turbine;

A traveling state detecting means for detecting a vehicle speed, an opening rate of a throttle valve, a temperature of a transmission and the like in accordance with traveling of the vehicle and outputting an electrical signal corresponding thereto;

Shift control means for calculating a turbine rotational speed of the torque converter when a power-on is detected and an upshift of the upshift is to be executed, and then outputting a signal of a duty pattern for controlling the hydraulic pressure according to data of the set map table; And

The solenoid valves for the gear stage synchronization are driven in accordance with the duty pattern signal to constrain the arbitrary clutches and the brakes to upshift the target gear stage according to the opening ratio of the throttle valve and the turbine rotational speed in the vehicle speed and torque converter And a hydraulic control system.

Here, the hydraulic control system of the present invention includes an oil pump that is driven together with an engine to generate hydraulic pressure;

A pressure regulating valve that receives the hydraulic pressure from the oil pump and changes the hydraulic pressure according to the traveling state of the vehicle;

A solenoid supply valve for supplying the line pressure supplied from the pressure regulating valve along the line pressure line to the first, second and third solenoid valves;

A manual valve for supplying hydraulic pressure from the "D" range to the drive pressure pipe, and supplying hydraulic pressure from the "R"

A torque control regulator valve that receives drive pressure of the manual valve and converts the torque pressure by duty control of the third solenoid valve;

A control switch valve for supplying a torque pressure alternately to a first torque pressure line and a second torque pressure line by on / off action of a fourth solenoid valve by receiving a torque pressure from the torque control regulator valve;

The torque pressure is preferentially supplied to the fifth friction element that is operated with the first friction element that is operated by directly receiving the initial line pressure of the shift during the range conversion from the neutral mode to the running mode, Control valve;

When the speed change from the first speed range to the second speed range is made in the "D" range, the port pressure is converted by the on / off control of the fifth solenoid valve, so that the torque pressure supplied from the first and second torque pressure pipes, To the fifth friction element via the second clutch valve;

When shifting from the second speed to the third speed in the "D" range, the port pressure is converted by the on / off control of the sixth solenoid valve and the torque pressure supplied from the 1-2 shift valve, Quot; L "range < RTI ID = 0.0 > 1 < / RTI > to the second friction element via a third clutch valve -3 shift valve;

When the shift is made from the third speed to the fourth speed in the "D" range, the port pressure is converted by the on / off control of the seventh solenoid valve, so that the torque pressure supplied from the 2-3 shift valve Quot; D "range 4 to the" 2 "range 2, the second friction element is supplied with a part of the hydraulic pressure through the fourth clutch valve to the third friction element, A 3-4 shift valve for supplying a torque pressure supplied to the torque pressure line to the seventh friction element via the third clutch valve and the second clutch valve;

And an N-R control valve for supplying, to the sixth friction element, the hydraulic pressure supplied from the manual valve through the after-pressure pipe in the "R" range under the control of the third solenoid valve.

According to another aspect of the present invention, there is provided a shift control method for an automatic transmission,

(a) maintaining a control signal of a first engagement duty (Da) set in the map table for a predetermined time (ta) when a shift command is detected in the shift control means;

(b) if the control signal holding time ta has elapsed in the step (a), the second engagement duty ratio Db is set from the map table, and then the duty ratio of the first slope ramp-Db Detecting the slip ratio of the torque converter and checking whether the number of revolutions of the turbine has been changed to the set state;

(c) when the rotational speed of the turbine is changed to the set state in the step (b), the shift control means sets the third engagement duty ratio Dc from the map table and holds the predetermined engagement time tc;

(d) performing open loop control or feedback control according to the selected control state when the time (tc) set in the step (c) has elapsed, and checking whether the shift synchronization for the target speed change stage is completed; And

(e) when the shift speed synchronization of the target speed change stage is completed, decreasing the duty ratio by the amount DELTA De set in the map table at the engagement duty ratio at the time of completion of the shift, and maintaining the duty ratio for a predetermined time (te).

[Example]

Hereinafter, the most preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

As can be seen from FIG. 1, the upshift shift control torque converter 10 of the automatic transmission according to the present invention, the running state sensing unit 20, the shift control unit 30 and the hydraulic control system 40 The torque converter 10 includes an impeller which generates a rotational force identical to the driving speed of the engine and is directly connected to the output of the engine, a stator which guides the flow of the fluid generated by the rotation of the impeller, And a detecting means for detecting the rotational speed at a predetermined position of the turbine is provided. The turbine rotates the driving torque of the engine to a rotational force of the fluid.

The running state detecting unit 20 detects an overall state such as a vehicle speed detected according to running of the vehicle, an opening rate of the throttle valve, a temperature of the transmission, and outputs a predetermined electrical signal corresponding thereto.

The shift control unit 30 determines the overall state of the vehicle driven from the signal applied from the running state sensing unit 20. When the power-on is detected and the upshift shift control is to be executed, And outputs a duty pattern signal for oil pressure control based on the data of the map table set in accordance with the rotational speed of the turbine.

The hydraulic control system 40 drives each solenoid valve for the speed change stage synchronization in accordance with a control signal applied from the speed change control section 2 to restrain any clutches and brakes so that the opening ratio of the throttle valve and the vehicle speed and torque converter Up or down-shifts the target speed change stage according to the rotational speed of the turbine in the engine 10.

2, the hydraulic control system according to the present invention includes an oil pump 2 for pumping oil by the driving force of the engine, a torque converter (not shown) for transmitting the power of the engine to the input shaft of the transmission, A damper clutch 6 installed in the torque converter for increasing the power transmission efficiency, a pressure regulating valve 8 for varying the hydraulic pressure generated in the oil pump according to the traveling state of the vehicle, A converter feed valve 10 for supplying a hydraulic pressure passing through the valve 8 to a working oil pressure and a lubricating point of the torque converter and a converter clutch control valve 12 for controlling the operation of the damper clutch.

The pressure regulating valve 8 and the converter clutch regulating valve 12 are port-switched by the first and second solenoid valves S1 and S2, respectively, whose duty is controlled by the transmission control unit TCU.

The pressure regulating valve 8 is connected to the solenoid supply valve 16 through the line pressure line 14 to supply the hydraulic pressure to the solenoid supply valve 16. The hydraulic pressure passing through the solenoid supply valve 16 And is supplied to the first and second solenoid valves S1 and S2 and connected to the third solenoid valve S3 through the conduit 18 to supply the hydraulic pressure.

The third solenoid valve S3 is connected to the port control of the torque control regulator valve 20. The torque control regulator valve 20 receives the hydraulic pressure from the line pressure line 14, And is connected to the manual valve 22 through which the port is changed according to the position of one selection lever, by the drive pressure pipeline 24, so that the hydraulic pressure can be supplied.

The torque control regulator valve 20 supplies the torque pressure controlled by the third solenoid valve S3 to the control switch valve 26 and the torque control valve valve 26 when the shift from the neutral position N to the forward So that torque pressure can be transmitted to the ND control valve 28 that alleviates a shift shock.

The ND control valve 28 supplies the torque pressure to the first friction element C1 which is operated together with the fourth friction element B1 which receives the line pressure directly at the beginning of the shift, The operating pressure of the first friction element C1 is changed to reduce the shift shock.

In order to selectively supply the torque pressure supplied to the control switch valve 26 to the first torque pressure line 30 and the second torque line 32, the fourth solenoid valve S4 is connected to the transmission control unit And can be controlled to be turned on / off by the ON / OFF control.

The first and second torque pressure pipelines 30 and 32 perform port conversion in accordance with ON / OFF control of the fifth solenoid valve S5 controlled by the transmission unit at the time of shifting from first speed to second speed And is connected to the 1-2 shift valve 34 which supplies the drive pressure supplied from the drive pressure line 24 to the fifth friction element B2.

The 2-3 shift valve 36, in which the port is changed according to the ON / OFF control of the sixth solenoid valve S6 controlled by the transmission control unit at the third speed gear, is connected to the fifth friction element B2 A part of the supplied hydraulic pressure is supplied to the second friction element C2 to realize the third speed shift control, and the seventh solenoid S7 controlled by the transmission control unit performs the 3-4 shift The valve 38 supplies a part of the hydraulic pressure supplied to the second friction element C2 to the third friction element C3.

The second clutch valve 40, which is supplied with the hydraulic pressure from the 1-2 shift valve 34 in the "D" range 2, supplies the hydraulic pressure to the fifth friction element B2 and the 2-3 shift valve And is connected to the third clutch valve 42 connected to the 3-4 shift valve 38 so as to be supplied to the sixth friction element B3 or the seventh friction element B4 .

The third clutch valve 42 receives the hydraulic pressure from the 2-3 shift valve 36 and supplies the hydraulic pressure to the second friction element C2 to operate the friction element, (38).

The fourth clutch valve 44 is connected to the line 46 branched from the line pressure line 14 while operating the third friction element C3 by receiving the hydraulic pressure from the 3-4 shift valve 38, , And operates the fourth friction element (Bl) operated in the "D" range 1, 2, 3 speed operation with the hydraulic pressure supplied thereto.

Shift operation of the upshift according to the power-on will be described in the present invention having the above-described functions.

In order to start the operation of the vehicle, the oil pump 2 of the hydraulic control system shown in FIG. 2 attached to the engine is started or operated, and the pressure of the line applied to each pressure control valve side .

At this time, before the speed change stage is selected, the transmission control section 30 maintains the duty state for synchronizing the target speed change stage via the hydraulic pressure control system 40 to "0% " .

In this way, in the waiting state of the speed change stage selection, the transmission control section 30 judges whether or not the speed change stage selection command S for the upshift or the progress of the shift from the running state detection section 20 is detected (step 10).

When the selection command SS of the speed change stage or progress of the speed change is detected in step 10, the transmission control unit 30 controls the hydraulic control system 40 to execute the duty control on the side of the fourth solenoid valve S4 of FIG. Signal to apply a predetermined pressure through the control switch valve 26 to the clutch and the brake side.

At this time, the shift control portion 30 determines whether or not the first finish flag for detecting whether the routine for engaging the clutch of the target speed change stage has elapsed according to the shift command SS or the progress of the shift (Step 11 ).

In the step 11, the engagement timing of the target speed change stage is determined as the execution of the second finish flag for determining whether the routine for selecting the shift control solenoid valve (SCSV) is in progress if the first finish flag is not terminated (Step 12).

If it is determined in the step 12 that the second finishing flag is not being executed, an SCSV selection routine for applying an on / off drive control signal to the solenoid valve side for clutch and brake operation for the purpose of speed change synchronization of the target speed change stage And then sets the second finish flag for completing the SCSV selection routine (step 13) (step 14).

At this time, the transmission control section 30 outputs a control signal to the fourth solenoid valve S4 to keep the solenoid valve S4 in the ON state if the transmission is shifted from the first speed to the second speed in the "D" The solenoid valve S4 is turned off and the solenoid valve S4 is turned on when the speed is shifted from the third speed to the fourth speed.

As can be seen from the section "a" in the attached drawing, the transmission control section 30 sets the initial duty to "Da ", and determines the rotation speed of the engine, the delay time of each solenoid valve operation, Quot; ta "calculated by correcting various delay times generated according to the traveling time and temperature of the clutch (step 15).

If the shift command S for executing the shift operation is not detected in step 10, the process returns to the main program.

If it is determined in step 12 that the SCSV selection routine is already completed and the completion of the second finishing flag is detected, the step 15 is executed to output the duty of "Da ".

3 and 4, in the state in which the control of the section "a" in which the duty of the shift command SS is controlled is progressed, the shift control section 30 judges, from each of the detection signals, it is determined whether the delay time of "ta " has elapsed (step 16).

When the vehicle reaches the IF point with the lapse of the "ta" delay time of the clutch engaging in the step 16, the first finish flag is set to " 1 "and at the same time, the start flag for detecting the progress of the subroutine for the shift change- Is set to "0" (step 17) and it is detected whether the third finishing flag is set to "1 " in order to judge whether or not the routine for section" b & Step 18).

If the routine for the section "b" is not completed in the step 18, the transmission control section 30 transmits the "ramp- Quot; b "region to which the control signal of " Db" is applied (step 19).

Thereafter, the transmission control unit 30 calculates the slip ratio of the impeller and the turbine of the torque converter 10 to determine whether the duty control for the region "b" is completed (Step 20) (Step 45). If the control of the duty for the area "b" is completed, the third finishing flag is set to "1 " The start flag for execution is set to "0" (step 21).

The third finishing flag indicating the completion of the routine for the section "b" region is detected as "1 " in the step 18, or after the execution of the step 21, the transmission control section 30 controls the duty for the section & The initial engagement duty value is kept constant for a predetermined time "t" by setting the initial engagement duty value to " Dc " in the section "c" obtained by adding the correction value to the end duty value of the section "b" quot; tc "has elapsed (step 22).

At this time, the initial engagement duty value "Dc" applied in the section "c &

Dc = (duty value D +? Dc + DbL of all the sections) Ka + Dt

Here,? Dc is the set duty value, DbL is the engagement duty learning value of the interval c, Dt is the duty ratio correction value according to the oil temperature, and Ka is the torque-duty conversion coefficient.

If the elapse of the hold time "tc" is not detected in accordance with the detection of the fourth finishing flag in step 22, the shift control section 30 proceeds to a routine for continuously holding the hold time "tc"

Thereafter, it is continuously detected whether or not the hold time "tc" for the section "c" has elapsed (step 24), and the elapsed time for the hold time " tc & tc ", the fourth finishing flag is set to " 1 " and the start flag for executing the subroutine is set to "0" (step 25).

Thereafter, it is judged whether or not the fifth finishing flag for judging whether or not the section "c" and the section " d " .

If the fifth finish flag "1" is not detected in step 26, the shift control section 30 determines the value of the open flag to determine the control method of the feedback control section (step 27).

If the value of the open flag is set to "1 " in the step 27, the shift control section 30 goes to the open loop control routine (step 28) and executes the control operation of the feedback control section in the open loop control state 28).

That is, the duty ratio of the feedback control section is decreased by a predetermined value by a predetermined time interval to change the duty ratio.

If the value of the open flag is "0 " in the step 27, the transmission control unit 30 executes the feedback control routine to change the duty ratio of the feedback control period (step 29).

In this case, since the feedback section in which the corresponding control operation is performed according to the value of the open flag is divided into the section "c" region and the section "d" region for the number of revolutions Nt of the turbine shaft, When the turbine shaft revolution speed Nt is decreased by the set rotation speed Ntc, the control operation of the section "c" is completed and the operation of the section "d" The controlled duty ratio "D _n " is calculated and controlled by the following equation.

_{D n: = (Di) n} -1 -K p × e n - K D × (e n -e n-1) -K I × e n

Here, e _n = Ni (target turbine change rate) - (Nt) _n (actual turbine change rate) and e _n-1 = Ni - (Nt) _n-1 .

The target turbine change rate Ni of the section "c" uses the value of "Nt-? Ns" determined at the point FB and the target turbine change rate Ni of the section "d" "Value.

The turbine shaft rotational speed? N _F for determining completion of synchronization is determined to be a value obtained by subtracting the number of rotations calculated by multiplying the gear ratio by the output shaft rotational speed No at the turbine shaft rotational speed Nt of 100 rpm .

As described above, after the duty ratio control operation of the feedback control section executes the shift operation in accordance with the corresponding control method in accordance with the value of the open flag, it is determined whether or not the shift speed synchronization to the target speed change stage is completed (step 30).

If it is determined in step 30 that the shift-speed synchronization to the target speed change stage has been completed, the shift control section 30 sets the fifth finish flag to "1" indicating that the control of the section "c" and the section "d" , A start flag for executing the subroutine is set to "0", a change flag is set to "0" (step 31), and a final routine of the section "d" is executed And the initial engagement duty ratio is determined by decreasing the duty ratio DELTA De set at the last duty ratio of the feedback control section (step 32).

At this time, by maintaining the duty ratio reduced by the set duty ratio DELTA De at the last duty ratio during the set time "te ", the operation of the hydraulic control apparatus 40 is controlled to maintain the safe shifting completion operation 36).

Then, when the elapse of the set time "te" is detected, the state of each control solenoid valve for the upshift operation is converted into the set state, the variable values used are initialized, Return.

Then, the elapsed time is counted by elapsing the time (ta, tb, tc) set in the step 16, the step 24 and the step 33, and the elapsed time is detected And compares the elapsed time (total-time) with the maximum shift time t-max set for the shift operation (step 43).

If the total elapsed time tota1-time determined in step 43 exceeds the set maximum shift time t-max, the value of the forced-shift-flag is set to "1 & The operation of the pressure control device 40 is controlled with a duty ratio decreasing at a constant slope to complete the shifting operation.

Therefore, it is possible to prevent a problem that occurs when the shifting operation of the target speed change stage ends and the shifting operation to the target speed change stage is performed beyond the set time.

Referring to FIG. 6, the engagement duty control for synchronizing the target speed change stage in the section "b " will be described below.

First, it is determined whether the duty control operation of the region "b" region is completed (Step 100). If the duty control is not completed, A subroutine for detecting the number of revolutions of the turbine is executed (step 101).

Then, it is determined whether a start flag for determining whether the subroutine for detecting the number of revolutions of the turbine is terminated is detected as "1 " (step 102).

If the subroutine is not terminated at step 102, the shift control section 30 sets the initial engagement duty value "Db" of the section "b " to execute the up-engagement duty routine.

At this time, the initial engagement duty value "Db"

Db = (Dbo + DbL) xKe + Dt, and Dbo = Dbi - Ka x Tt x Kat.

Here, Dbo is an initial duty of engagement, Tt is a turbine torque, Ka is a torque duty conversion coefficient, Kat is a torque capacity coefficient, and Dt is a duty ratio correction value according to an oil temperature. , DbL: initial engagement duty learning value.

As described above, when the initial engagement duty value "Db" for controlling the section "b " is set, the slope for decreasing the duty ratio is set to" 0 ", and the start flag for execution of the subroutine Quot; 1 "(step 103), and it is detected whether or not the target speed change stage to be shifted is in the" 4 "

If the target speed change stage is "4" in step 104, the initial engagement duty DbL is set to 34, the torque duty conversion coefficient Ka is set to 34, and the torque capacity coefficient Kat is set to 34 And outputs it to the hydraulic control system 40 side (step 108).

If the target speed change stage is not "4" in step 104, it is determined whether the target speed change stage for the speed change synchronization is "3" (step 105).

When the target speed change stage is "3" in step 105, the initial engagement duty DbL is set to 23, the torque duty conversion coefficient Ka is set to 23, and the torque capacity coefficient Kat is set to 23 And outputs it to the hydraulic control system 40 side (step 106).

If the target speed change stage is not "3" in step 105, the initial engagement duty DbL is set to 12, the torque duty conversion coefficient Ka is set to 12, the torque capacity coefficient Kat is set to 12, And outputs it to the hydraulic control system 40 side (step 107).

Subsequently, the transmission control section 30 determines whether the range of the initial engagement duty "DbL " is included within the lowest engagement duty" DbL_min "and the maximum engagement duty" DbL_max "

When it is within the minimum engagement duty "DbL_min" and the maximum engagement duty "DbL_max" in step 109, it is judged whether or not the flag of the operation power source for completing the shift synchromesh and the flag of the ignition are set The initial engagement duty "DbL" is set to the current duty value, and if the flag is not set, the learning routine for setting the engagement duty value is executed (step 112).

The routine for setting the engagement duty value detects whether the number of revolutions of the calculated turbine is included in the reference value of the set table and calculates the initial value of the engagement duty. At this time, Dbo = Dbi - Ka × number of rotations of the input torque And is calculated as D = (Dbo + DbL) x "number of revolutions of the turbine" (step 113).

When the engagement value is set in step 113, the duty value of the section "b" is calculated. At this time, D is calculated as the slope (ramp_Db) of the final D + calculated turbine engagement value-initial engagement value, And is applied to each solenoid valve side through the control system 40 to complete the synchronization of the target speed change stage (step 114).

After the duty control of the area "b" is completed in step 100 and the FB point is detected, the engagement duty control for the completion of the stable synchronization of the target speed change stage is executed (step 115), and the slope of the duty engagement for the speed change synchronization Quot; ramp-Db ", which is the duty slope of the initial engagement, and drives each solenoid valve through the hydraulic control system 40. [

If it is determined in step 102 that the start flag for executing the subroutine is set to "1 ", it is determined whether the slip flag for detecting the slip ratio of the impeller and the turbine in the torque converter 10 is set to" 1 " 117).

At this time, when the slip flag is detected as being set to "1 " and the change state of the duty ratio reaches the FB point and the state of the section" b "section control operation is completed, the main routine is executed. (Step 118) for determining the set time "tb " to calculate the slip rate of the turbine and the setting of the start flag for setting the end of subroutine execution (step 119).

If it is determined in step 118 that the set time has elapsed for the calculation of the slip ratio, or if it is determined in step 119 that the subroutine is set, the aforementioned step 116 and step 114 are executed to control the final engagement duty of the section "b & Is not set, a duty value setting routine for engagement is executed.

Then, it is determined whether or not the target speed change stage for the speed change synchronization is "4" (step 120). If the target speed change stage is "4", the slope "ramp-Db" It is determined whether the target speed change stage is in the "4" or "3" (step 121).

The slope " ramp-Db " of the duty for engagement is set to "23 " if the target speed change stage is the" 3 " The start flag for the subroutine is terminated, and the above-mentioned step 112 is executed to execute the learning of the engagement duty.

At this time, the completion of the control of the section "b " is the time when the number of rotations of the turbine in the torque converter 10 has been changed by the set change amount Ns and the output shaft speed No at the turbine speed Nt, And the number of revolutions minus the number of revolutions calculated is 35 rpm.

As described above, according to the present invention, the duty ratio for the shift control of the upshift by power-on is calculated as the slip ratio of the torque converter, and the duty value for the speed change synchronization of the target speed change stage is controlled according to the number of revolutions of the turbine Shocks are prevented from occurring due to the progress of shifting, the transmission feeling is improved, the shock of line pressure is eliminated, and the durability of the automatic transmission is improved.

Claims (9)

In an automatic transmission of an automobile, A torque converter which converts a drive torque of the engine into a rotational force of the fluid and outputs the rotational torque, and a rotational speed detecting means at a predetermined position of the turbine; A traveling state detecting means for detecting a vehicle speed, an opening rate of a throttle valve, a temperature of a transmission and the like in accordance with traveling of the vehicle and outputting an electrical signal corresponding thereto; Shift control means for calculating a turbine rotational speed of the torque converter when a power-on is detected and an upshift of the upshift is to be executed, and then outputting a signal of a duty pattern for controlling the hydraulic pressure according to data of the set map table; And The solenoid valves for the gear stage synchronization are driven in accordance with the duty pattern signal to constrain the arbitrary clutches and the brakes to upshift the target gear stage according to the opening ratio of the throttle valve and the turbine rotational speed in the vehicle speed and torque converter Hydraulic control system Shift control device for an upshift of an automatic transmission. The method according to claim 1, The hydraulic control system includes: An oil pump which is driven together with the engine to generate oil pressure; A pressure regulating valve that receives hydraulic pressure from the oil pump and varies the hydraulic pressure according to the running state of the vehicle; A solenoid supply valve for supplying the line pressure supplied from the pressure regulating valve along the line pressure line to the first, second and third solenoid valves; Manual valve that supplies hydraulic pressure from the "D" range to the drive pressure line, and supplies hydraulic pressure from the "R" range to the back pressure line, A torque control regulator valve that receives drive pressure of the manual valve and converts the torque pressure by duty control of the third solenoid valve; A control switch valve for supplying a torque pressure alternately to a first torque pressure line and a second torque pressure line by on / off action of a fourth solenoid valve by receiving a torque pressure from the torque control regulator valve; The torque pressure is preferentially supplied to the fifth friction element that is operated with the first friction element that is operated by directly receiving the initial line pressure of the shift during the range conversion from the neutral mode to the running mode, Control valve; When shifting from the first speed to the second speed in the "D" speed range, the port pressure is converted by the ON / OFF control of the fifth solenoid valve, so that the torque pressure supplied from the first and second torque pressure pipes, A 1-2 shift valve for supplying pressure to the fifth friction element via the second clutch valve; When shifting from the second speed to the third speed in the "D" range, the port pressure is converted by the on / off control of the sixth solenoid valve and the torque pressure supplied from the 1-2 shift valve, Quot; L "range < RTI ID = 0.0 > 1 < / RTI > to the second friction element via a third clutch valve -3 shift valve; When the shift is made from the third speed to the fourth speed in the "D" range, the port pressure is converted by the on / off control of the seventh solenoid valve, so that the torque pressure supplied from the 2-3 shift valve Quot; D "range 4 to the" 2 "range 2, the second friction element is supplied with a part of the hydraulic pressure through the fourth clutch valve to the third friction element, A 3-4 shift valve for supplying a torque pressure supplied to the torque pressure line to the seventh friction element via the third clutch valve and the second clutch valve; An N-R control valve for supplying hydraulic pressure supplied from the manual valve through the after-pressure pipe to the sixth friction element in the "R" range under the control of the third solenoid valve, Shift-time control device of an automatic transmission. A shift control method for an automatic transmission, (a) maintaining a control signal of a first engagement duty (Da) set in the map table for a predetermined time (ta) when a shift command is detected in the shift control means; (b) when the control signal holding time ta has elapsed in the step (a), the second engagement duty ratio Db is set from the map table, and the duty ratio Db is converted into the first slope duty ratio Db Detecting a slip ratio of the torque converter and checking whether the number of revolutions of the turbine has been changed to the set state; (c) when the rotational speed of the turbine is changed to the set state in the step (b), the shift control means sets the third engagement duty ratio Dc from the map table and holds the predetermined engagement time tc; (d) performing open loop control or feedback control according to the selected control state when the time (tc) set in the step (c) has elapsed, and checking whether the shift synchronization for the target speed change stage is completed; And (e) decreasing the duty ratio by the amount DELTA De set in the map table at the engagement duty ratio at the time of completion of the shift when the shift synchronization of the target speed change stage is completed and maintaining the duty ratio for a predetermined time te Shifting control of the automatic transmission. The method of claim 3, The step (a) Wherein said solenoid control valve selection routine determines whether or not a solenoid control valve (SCSV) is selected and executed to determine whether to execute a solenoid control valve selection routine. The method of claim 3, The initial second engagement duty ratio (Db) Db = (DbO + DbL) xKe + Dt (Where "Dbi" is the initial value of the engagement duty, "Ka" is the torque-duty conversion coefficient, "Tt" is the torque of the turbine, "Kat" is the torque capacity coefficient), Dbo = Dbi-Ka × Tt × Kat "DbL" is a learned value of the initial engagement duty, "Dt" is a duty ratio correction value according to the oil temperature) Shift-up control of the automatic transmission. The method of claim 3, The step (b) (b-1) calculating the number of revolutions of the turbine by executing the subroutine to determine a first slope duty ratio (ramp-Db); (b-2) calculating the number of revolutions of the turbine after the execution of the step (b-1) and determining whether a start flag that has executed the subroutine is set; (b-3) After the execution of the step (b-2), the target shift stage is detected and the torque-capacity conversion coefficient Ka, the torque capacity coefficient Kat and the learning value of the initial engagement duty Determining whether the learned value DbL of the initial engagement duty is included within the set maximum and minimum ranges after setting DbL; And (b-4) If the learned value DbL of the initial engagement duty is within the set maximum and minimum ranges in the step (b-3), the initial engagement duty value Dbo is calculated to control the duty control signal of the interval Step of outputting to the means Shifting control of the automatic transmission. The method of claim 3, The initial third engagement duty ratio Dc set in the step (c) Dc is the set duty value, "DbL" is the engagement duty learning value in the section, and "Ke" is the set duty value of the torque- Quot; Dt "is a duty ratio correction value according to the oil temperature) Shift-up control of the automatic transmission. The method of claim 6, wherein If the start flag that has completed the execution of the subroutine in the step (b-2) is detected as "1 ", and if the lapse of the set time is not detected, the target speed change stage is detected and the duty control Outputting a signal to the hydraulic pressure control means Speed shift control of an automatic transmission. The method according to claim 6, The initial engagement duty value calculated in the step (b-4) is calculated as Dbo = Dbi - K × number of rotations of the input torque × Kat (where "Dbi" is the initial value of the engagement duty, "Ka" ., Dt = ramp_Db (where "Dt" is the duty ratio correction value "ramp_Db" according to the oil temperature is the duty ratio of the first slope) Shift-up control of the automatic transmission.