JPS601463A - Slip controlling apparatus for torque converter - Google Patents

Abstract

PURPOSE:To prevent an overshoot and noise and improve follow-up characteristics, by setting two threshold values for the PID operation and adapting, when the result of the operation does not fall within the range between the two threshold values, one of the threshold value closer to the result to be changed into the PID operational value. CONSTITUTION:A threshold value setting means (g) for setting two threshold values for the PID operation is connected to an operaional value changing means (h) which is connected to the PID operational means (e) and defines either threshold value closer to the limit of range to PID operational value, if the result of operation stays outside the range limited by these threshold values. Thus , the slip controlling is executed with the threshold value which is closer to the PID- operated value when the slip error is too large and the PID-operated value exceeds that threshold value. Hence, it can be prevented that an overshoot becomes too large and the follow-up characteristics become poorer. Such things can also be prevented that the torque converter makes a vibration and the prime mover a makes a noise at a transient period of the slip controlling.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torque converter inserted into a power transmission system such as an automatic transmission, and in particular to a slip control type torque converter which can limit the relative rotation (slip) between its input and output elements. The present invention relates to a slip control device for a torque converter.

A normal torque converter transmits power by driving an output runner (usually a turbine runner) through working fluid stirred by an input element (usually a pump impeller) driven by a prime mover, so it has a torque increasing function. Although the torque fluctuation absorber 1j and the torque fluctuation absorber 1j can be obtained, the relative amount ik (slip of the torque converter) between the input and output elements cannot be avoided, resulting in poor power transmission efficiency.

Therefore, the above slip can be adjusted as appropriate depending on the operating condition of the prime mover.
A slip 1tjll J-type torque converter is being put into practical use in which the power transmission 1'' and the child 6 are made the same by limiting the torque increasing function and the necessary minimum amount of the culm that meets the requirements of the torque increasing function.

This kind of early-acting torque converter is constructed by mechanically directly connecting its input and output elements as appropriate to a normal torque converter, or adding a lock amplifier clutch that adjusts this direct connection appropriately. When the up clutch is released, the torque converter functions in a so-called converter state in which slip is not limited, and when the lock up clutch is fully engaged, the torque converter is operated in a state where there is no slip (Nil lock amplifier type)'J! ', and lock amplifier clutch engagement '6 Force i[ill [11itl
IIη The so-called slip Fr1ll iaU in which the slip of the torque converter is limited to 1ljlJ to the target 11″
It can be made to function in this state.

By the way, when the torque converter is operated in a slip-limited state, the slip if;
PID calculation is performed based on the error of each actual slip with respect to target slip) 41, and the coupling force of the lock amplifier clutch written in 1\iJ is proportional to CP) - integral (I) - i machine so that the error is eliminated based on the calculation result. Outside (D) 1lrl
Conventionally, a system is known in which the slip i'j1 of the torque converter is feedback-controlled d1. In this slip slip control device, the duty of the electromagnetic valve is set to 1 based on the above calculation result, and thereby the pressure involved in the coupling force of the lock-up clutch is made to be equal to the slip slip error.

But it takes! IJ fil! In method 1, when the converter state force) shifts to slip 1IiJ (4) 1 state (... - when the slip slip error is large, the PID
It is possible to judge the calculation based on this slip error.
The rate of change of the calculated value is large, and the calculated value quickly becomes one that corresponds to the target slip m. However, the above type ma
Actual slip 1 for duty 1ljlJ Z of r
There was a time lag before fiiJ 1all was performed, and the calculated value corresponded to the target slip stone11
5r z Actual slip (yl is still far from the target slip, and the P I D calculation continues for that bale based on the slip error between the two, and the calculated value changes the target slip 91 to -H6・A 攬For example, to explain the case of transitioning from the converter state to the slip state, as shown in FIG. , once the duty ratio z corresponding to the target slip jjJ is greatly exceeded, it finally reaches the target value. Therefore, the actual slip 111 changes as shown by yl in the figure.
After exceeding the target slip 1 bar by -U, this lfl +r! The value will be reached, where Nll 1
It is inevitable that the overshoot Δy' of lill mt+ will become large.

This overshoot causes a slip as shown in Figure 12 (11)
If it becomes too much on the side of insufficient slip, the torque converter will lose its torque fluctuation absorbing mechanism due to insufficient slip.
This is undesirable as it causes movement, and on the other hand, the slit j1. →Sting σ
) (, 1ill), the torque converter deteriorates the power transmission efficiency due to the slip 3, and also increases the fuel consumption and noise of the driving force.

In addition, when transitioning to the slip control -1 state, the actual slip force) is large (if it deviates from the Talislip fan (if the slip error is large), the PID calculation value at the time of slip control σ + 1 + start also corresponds to the target slip G. It takes a long time for the calculated value to become a value corresponding to the target slip boat, and as a result, the slip fiiU (a
It makes the responsiveness of t sad. In this case, during the transition period of slip control, the torque converter is in an insufficient or excessive slip state for a longer period of time, and this poor responsiveness also causes the same problem as described above.

The present invention eliminates two types of threshold values for PID calculation, and
Under such a small slip error that the calculated value becomes the value of these threshold values, the PI'D calculated value is used as is to determine the slip M? (l) If there is a large slip error such that the PID calculation value is outside the range of both threshold values, the threshold value closest to this is used instead of the PID calculation value. The purpose is to solve the above-mentioned overshoot problem by performing fffll ff1tl.

For this purpose, the present invention provides a driving force @a as shown in FIG.
Target slip amount of a torque converter that has both a transmission path that transmits the power from the output shaft 0 to the output shaft 0 via the torque converter b, and a transmission path that transmits the power to the output shaft C via the lock-up clutch d that is connected as appropriate. It has a calculation means e that performs a PID calculation based on the error in the actual slip amount, and the slip Ft that applies a coupling force tulJm to the lock-up clutch d so that the error is eliminated based on the result of the calculation.
In a torque converter slip control device N equipped with a H means f, a threshold setting means g sets two types of threshold values for the PID calculation, and a threshold value setting means g for setting two types of threshold values for the PID calculation, and a threshold value setting means g for setting two types of threshold values for the PID calculation, and a threshold value setting means g for setting two types of threshold values for the PID calculation, and a 1 which is closer to when the threshold value becomes the PID calculation value.

Hereinafter, the present invention will be explained in detail with reference to an embodiment shown in FIG.

FIG. 2 shows the slip control device according to the present invention;
In this embodiment, 1 is an engine as a prime mover,
2 is the crankshaft, 8 is the flywheel, 4 is the IJ-controlled torque converter/verter, and 5 is the tooth [(
(The transmission mechanisms are shown respectively. A pump impeller (input element) that is connected to the crankshaft 2 via a wheel 3 and driven by the engine is scratched a, and a turbine runner (output element) 4b that faces it. The turbine runner 4b is drivingly connected to the output shaft (input shaft of the southeast transmission mechanism 5) 7 of the torque converter 4, and the stator 4c drives the one-way clutch 8. The torque comparator lower part 4 supplies working fluid to its internal converter chamber 1o in the direction of the arrow α, and discharges this working fluid in the direction of the arrow β. The pressure (converter pressure) P below the value formed in the converter chamber lo by the pressure holding valve (not shown)
Keep it at o. Thus, as described above, the engine-driven pump impeller stirs the internal working fluid, causes it to collide with the turbine runner 4b, and then flows through the stator 4c.
C1 Under the reaction force of the stator 40, the turbine runner 4. Rotate b while increasing the torque. Therefore, the power from the engine 1 is transferred to the torque converter 4, the input shaft 9, and the transmission mechanism 5.
The signal is transmitted to the drive wheels via the motor, allowing the heavy vehicle to travel.

Further, the torque converter 4 has a slip r' that can limit the slip (relative rotation between the long sword element 4a and the output element 4b).
jlJ In order to achieve this, a lock-up clutch 11 is provided, which is drive-coupled onto the output shaft 7 via a torsional damper 12, and which is movable in the axial direction on the output shaft and locked separately from the converter chamber 1o. An amplifier chamber 18 is set inside the torque converter 4. The lock amplifier clutch 11 controls the converter pressure P in the converter 5B10. In response to the difference between the lock-up pressure "L/u" in the lock-up chamber 13 and the lock-up pressure "L/u", the torque converter 6 moves to the left in the diagram, and drives and connects the protruding blade elements aa and 4b with a force corresponding to the differential pressure. Slip can be limited.

The lock-up pressure PL/u is adjusted by the slip control valve 14, but this valve is controlled by the valve passed through the lock amplifier chamber 18).
1! a, and the converter pressure P. Boat being guided by 1
4b, a drain port 14°, and a spool 14d.
When is in the neutral position shown in the figure, 14a is both baud) 14
b, 140 is shut off, and when spool 1.4d moves to the right in the figure, 14a is baud) 14b, and when spool L4d moves to the left in the figure, 14a is baud) I
It shall be communicated to J and O respectively. The spool 14d receives lock-up pressure P acting on the right end surface in the figure through the orifice 15, and NIJ acting on the left end surface in the figure.
In response to the differential pressure with the sin pressure P8L/u, the control pressure Ps is created as follows.

That is, from one end 16'a of the opening/opening pressure generation circuit 16, the reference [f (line F in the case of a self-weight transmission) that controls the speed change of the transmission mechanism 5
F,) PL is supplied, and this line EE is connected to the ice 1
7. Drain from the other end 10t of the circuit 16 via 18, and the solenoid valve 1 whose drain period is duty-controlled.
9, a control pressure P8 can be created between the orifices 17 and 18.

In normal state, the solenoid valve 19 is closed to the plunger 19 by the spring 19a.
b is moved to the left in the figure, thereby blocking the drain opening end 16b of the circuit 16, and each time the solenoid 190 is energized, the plunger 19b is moved to the rightward position as shown in the figure to open the drain opening end 16b, and the above-mentioned Drainage shall be allowed. The solenoid 190 is energized by the slip control computer 20 in FIGS. 3(a) and 8('b).
) The duty control is performed so that the operation is performed during the pulse width (on time) of the pulse signal as shown in (). Figure 3G
As shown in FIG. 4, when the duty (%) is small, the time during which the solenoid valve 19 opens the drain opening end 16b is short, and therefore, 1;IJ m1JIC:, Ps is equal to the line pressure PL as shown in FIG. Also, the duty (%) is shown in Figure 3 (
As the pressure increases as shown in b), the solenoid valve [9 opens the drain opening g11'' 16b for a long time, so the 1ill fill pressure P8 gradually decreases as shown in Fig. 4, and finally the orifice 17.18 It is a constant value determined by the opening bond difference.

In FIG. 2, as the control pressure PS increases, this control 6i1! The pressure is spool 14. d to the right as shown in Fig. 5(a), the bow) 14a is gradually increased and communicated with the bow ht4b, and the lock-up pressure PL/u is set to PL/u="Ps".
(However, k is a constant) as shown in Figure 6.
i'ldi increases, and finally becomes constant (+ri) corresponding to the converter pressure PC.Then, as the control pressure Ps decreases,
At the same time, the lock-up pressure PL/u on the end face of the spool 14d on the opposite side of the action causes the spool 14d to move to the left as shown in FIG.
4IC, and the lock-up pressure PL/u is gradually decreased in the same relationship as above, and finally reaches zero. and,
Slip FIi+I (The all valve 141 returns the spool 14d to the neutral position shown in FIG. 2 when the lock amplifier pressure PL/u reaches a value corresponding to the control pressure P8.)
By keeping L/u at this value, this lock amplifier pressure can be made bulletproof by controlling the control pressure PS.

By the way, the control pressure P with respect to the duty (%)
The change characteristics of P8 are as shown in FIG. 4, and from this and the control pressure (P8)-lockup pressure (PL/u) characteristics shown in FIG.
The change characteristics of /u are as shown in FIG.

The slip control computer 20 is operated by the engine, and receives the gear position signal S9 from the gear position sensor 6 regarding the selected gear position of the transmission mechanism 5, and the engine rotation speed (rotation of 1 ha by human power) from the engine rotation speed sensor 21. Number) Signal 5ir1 Speed change fsFfl from output shaft rotation sensor 22
:1δ S regarding the output rotation speed of 15. r and the engine throttle opening from the throttle opening sensor 23 [word STH], and based on these calculation results, the solenoid valve 1
9 duty FfrlJσn+ is performed.

For this purpose, the computer 2o includes, for example, a microprocessor unit (MPU) 24, a random access memory (RA, M) 25, as shown in FIG.
It consists of a microcomputer consisting of a read-only memory (ROM) 26 and an input/output interface m (Ilo) 27.

The IllP U 24 reads the signals from the sensors 6.21 to 23 through the circuit 1027, and outputs the arithmetic results to the red (C drive) circuit 28. (self IF (duty for 6 valve J9) 廿IJυ
However, since the signals Slr and SOr are pulse signals, a counter is needed to count the number of these pulses, and the signal STH is an analog signal, so a counter is needed to convert it into a digital signal. Since the 1iIF calculation result is a binary value, it is assumed that the device has a built-in A/D converter and a counter for converting the 1iif calculation result into a pulse signal for controlling the tutee.

The MPU 24 executes the control programs shown in FIGS. 9 and 10 stored in the ROM 26 to set the solenoid valve 19 to the duty N'd? 1R, adjust the lock-up pressure PL/u according to the duty as shown in FIG. 7, and actuate the lock amplifier clamp.

JOBL shown in FIG. 9 is a timekeeping routine, and it is a poem that executes the JOB20 system subroutine shown in FIG.

It is only for measuring the predetermined time to be used. The routine shown in FIG. 9 is executed repeatedly at regular intervals of, for example, 65 ms, and at each repetition, first, in step 80G, the register named tie Y is incremented by one stage. The registers are cleared in the control routine of Figure 10 as described below.In the next step 3L,
It is determined whether the difference between the contents of the register and the predetermined value stored in the ROM 26 is greater than or equal to zero or less than zero, that is, whether a certain period of time (65 ms x predetermined value) has elapsed after the register was cleared or cleared. . If the content of the register F5 is equal to or greater than the predetermined value and the predetermined time period has elapsed, the control proceeds to step 23, where the content of the register is maintained at the predetermined value, and the flag F2 is reset to 0 in the next step. If the contents of the register are below the predetermined value and within the above-mentioned fixed time, step 8
1 selects step 84, where flag F2 is set to 1.

Thus, if F2=0, a certain period of time has passed since the register was cleared, and if F2ζl, it means that a certain period of time has passed since the register was cleared.

The NIH II routine shown in FIG. 10 is also executed at regular intervals of, for example, 100 ms, and first, in step 4o, the number of revolutions NE of the engine 1 (the number of revolutions of the pump impeller 4a) is calculated. In this calculation, the MPU 24 uses the engine rotation speed @Sir from the sensor 21, but since this signal is a pulse signal, Ilo
The count value of the counter 27 is held in a register, and the engine rotation period is calculated by calculating the difference between the HI values to calculate the engine rotation speed N9.

In the next step 41, the output rotation speed M of the tooth gear transmission mechanism 5 is determined.

Calculate. In this calculation, the MPU 24
Gear shift from 2 @ structure output 1a7 rotation speed signal S. r is used, but since this signal is also a pulse signal, it is processed in the same way as the engine rotational speed NE to obtain the output rotational speed N of the gear shift @ purchase 5. Calculate.

In the next step 4.2, the MPU 24 reads the selected gear position of the two-way transmission 11 based on the signal Sg from the sensor 6, and determines the gear ratio of the tooth gear transmission (145) from this gear position. 8, the gear ratio and step 41
The rotational speed of the torque converter output shaft 7 (the rotational speed of the turbine runner 4b) NT is calculated from the gearshift power rotational speed determined in step 1, and in the next step 4I4, the rotational speed of the torque converter output shaft 7 (the rotational speed of the turbine runner 4b) NT is
The engine throttle opening signal STH from 8 is converted into a digital signal by the A/D converter in l1027, and the throttle opening 19 TH is read.

Next, the control proceeds to step 45, where the torque corresponding to FIG. 1 stored in the ROM 26 is
(Based on the 3t 'Jυ- diagram, engine EO1 turn i N
EM (JXo7)) & IjFJeT
From H, it is determined in which operating mode the engine 1 is shifting the torque converter 4. In FIG. 11, the A/T is) converter area M, L/u where the converter area 4 should be in the non-slip converter state.
/L = lock amplifier region where torque converter 4 should not slip, 5LiP is a slip region where torque converter 4 should be controlled to slip, and in 5LiP region, slip h1 of torque converter 4 is constant ( (for target slip). 'If engine 1 is operating in the 5LiP region, i1r
+J av proceeds from step 45 to step 46,
Here, the % of engine rotation @ (rotation speed of pump impeller 4a) NF and torque converter output shaft rotation speed (rotation speed of turbine runner 4b) NT is NE-NT. The amount of error between this slip amount and the target slip amount is calculated. Next, the control proceeds to step flaw 7, where a calculation is performed from P based on the above-mentioned slip error, and the calculated value is compared with the first threshold value in the next step 4B. As shown in FIG. 12, the first threshold value is set to eliminate the above-mentioned overshoot problem, and is preferably set close to the value for obtaining the output duty 2 corresponding to the target slip amount. When the calculated value of P is smaller than the first threshold, ¥1IJitl proceeds to step 419, where the PID calculated value is now compared with the second threshold. As shown in FIG. 12, the second threshold value is set to V in order to eliminate the above-mentioned problem of responsiveness, and is preferably set at a certain distance from the first threshold value. If the PID calculation value is greater than the second threshold, control proceeds to step 50 where flag F1 is reset to zero. In other words, if the slip error is small and the PID calculation value is within both threshold values, the flag Fl is reset, and in the next step 51 the PI
Write the D operation value as is to the output register. In the next step 52, the binary data of the output register is converted to l102'.
Convert Pabas 1 to weight by η1° number R + j in 7,
By supplying this pulse from l1027 to the solenoid valve 19 via the drive circuit 28, the solenoid valve is normally duty-controlled.

By the way, the output duty of the torque converter 4 is
If the slip exceeds the target slip m, the solenoid valve 1 is increased based on the above calculation result and is controlled thereby.
9 is a lock-up pressure; I'L7u is lowered as is clear from FIG. 7, the coupling force of the lock-up clutch 11 is strengthened, and the slip f44 of the torque converter 41 is sequentially reduced to the i' mark slit tail each time the control program is executed. can be approached. On the other hand, when the torque converter 4 is in the non-slip state h4 with respect to the target slip amount, the output duty is reduced by the above-mentioned operation T>result, and the solenoid valve 19 increases the lock-up pressure P as shown in FIG. ,
/u, the coupling force of the lock-up clutch 11 is weakened, and the slip m of the torque converter can be controlled so that the torque converter G can be sequentially brought to the target slip each time the θ1j program is executed.

By the way, if the calculated value of P is larger than the first threshold value, step 4.8 selects step 53, and here it is determined whether the flag F[ is 1 or 0. Normal slip as mentioned above last time! l; IJυ11 is executed and if the flag F1 is reset to O in step 50, step 53 selects step 541, where the timer (register) described above with reference to FIG. Start measuring time using the program shown in Figure 9. Control then proceeds to step 55 and sets the flag F[ to l+
Furthermore, in step 564, the threshold value of KS1 is written into the output register instead of the calculated value from P.

Thereafter, the control proceeds to step 52, where the m-magnetic valve 19 is operated at a duty of 1 in the same manner as described above. However, since the PID calculation value has reached a ceiling by the first threshold value, the output duty is set to the 12th threshold. It changes as shown by X in the figure, and does not greatly exceed the value 2 corresponding to the target slip h1.
The slip amount changes as shown by y in the figure, and it is possible to prevent a large overshoot from the target slip.

Thereafter, in step 58, flag F is set in step 55.
1 is set to 1, so step 57 is ii!
t4i1, and here it is determined whether the flag F2 is 0 or 1. Until the predetermined time described above with reference to FIG.
6 is selected, and slip opening and opening is repeatedly performed using the PID calculation value as the first threshold. Therefore, if the PID calculation value is still larger than the first threshold value even after a predetermined period of time has passed and the path of step 41B, 53.57 is selected, the first threshold value (1 is the working fluid temperature) is selected. This means that the value of eosinophilic acid is no longer 1 due to changes in the slip 11i111 device installation error and changes in action characteristics over time. Step 5 selected
8, the first threshold value is corrected. For this correction,
Since the first threshold value is too lower than the preferred value, a predetermined value r is added thereto to update the first threshold value. At this time, in order to prevent the opening width of the first threshold value and the second threshold value from becoming wider than the set width, in step 5 (j the second threshold value is also added a predetermined value γ). and update the same (child.

Next, the control proceeds to step 59, where flag F1 is counted to 0, and in the next step 56, the updated first threshold value is written to the output register. 1 Even with this, if the PII calculation value still exceeds the first threshold within the predetermined time, the threshold value is again corrected in the same manner.

In addition, if it is determined in step 419 that the PID calculation value is smaller than the threshold of 2, N1(J 16+
1 proceeds to step 60, where flag F[ is 0.
Determine whether If the normal slip control as described above is executed and the flag Fl is reset to 0 in step 5o, step 60 is the same as step 6.
1, the timer (register) described above with reference to FIG. 9 is reset, and from this point on, time measurement using the program shown in FIG. 9 is started.

Control then proceeds to step 62, where flag Fl is set to 1, and further, step 63, where a second threshold value is written to the output register in place of the PID calculation value. Thereafter, the control proceeds to step 52, where the solenoid valve 19 is duty-controlled in the same manner as described above, but since the PID calculation value has been raised to the second threshold, the output duty is set to the point X in Fig. 12. As shown by y in the figure, it is possible to prevent an eruption where the slip control starts to change more and the responsiveness of the slip control is poor, as shown by y in the figure.

Thereafter, in step 60, flag F is set in step 62.
1 is set to 1, step 64 is selected, and it is determined here whether the flag F2 is O or I. The flag F2 remains at 1 until the predetermined time described above with reference to FIG.
Therefore, step 64 selects step 68 and P
Slip collateral is repeatedly performed using the ID calculation value as the second threshold. However, even after a predetermined period of time has passed, the PI
If the D calculation value is still smaller than the second threshold, step 49;
If the path 60.64 is selected, it means that the second threshold value is no longer a suitable value due to changes in the working fluid temperature, manufacturing errors of the slip control device f, changes in the operating characteristics over time, etc. After a predetermined time, the flag F2 is reset to 0, so that the second threshold value is corrected in step 65, which is selected in step 64. If this correction G fails, the second threshold value is longer than the good gun value, so a predetermined value γ is subtracted from it to update the second σ) threshold value. At this time, in order to prevent the first threshold (σ) value and the width of the second threshold space (σ) from becoming larger than a predetermined width, in step 65, the first (σ) threshold←1 value is also subtracted by a predetermined value γ. Update the same. Next, the control proceeds to step 66, where the flag Fl is reset to 0, and in the next step 68, the updated second threshold value is written to the output register, which also allows the predetermined time to be set. P inside
When the ID calculation value becomes less than or equal to the second threshold value, the threshold value is again corrected in the same manner.

By the way, in step 45, Al1 and &ma L/
If it is determined that it is the u area, control proceeds to step 67, where it is determined whether it is the A/'I' area or the L/u area. A/
- If it is a T area, in step 68 the PI is set in the output register.
Lower limit of D operation (write M, step 6 if L/u area
In step 9, the upper limit value of the PID calculation is written to the output register. Next, the control proceeds from step 68 or 69 to step 52, where the binary data in the output register is converted into a pulse signal by the counter in unit 1027, and this pulse signal is converted into a pulse signal by l10.
It is supplied from 2'7 to the solenoid valve 19 via the drive circuit 28.

By the way, the lower limit value and upper limit value of the PID calculation make the duty 0% and 100%, respectively.

The lock-up pressure PL/u is A/'I as shown in FIG.
Converter pressure P in the 'region. It is set to the same value as , and is set to the lowest value in the L/u region. Therefore, the torque converter 4 is in the humbverter state in which the lock-up clutch [1] is released in the A/T region, and is in the lock-up state in which the lock-up clutch 11 is fully engaged in the ~L/u region.

Thus, the slip control device of the present invention, as described above, has P I
I) Set two types of threshold values for iui calculation, and set the threshold value that is closer to the calculated value than P or outside the range of these thresholds as the PID calculated value +i! ? As explained above, even if the slip error is large, the overshoot of the slip opening and opening can be prevented from becoming large and the responsiveness is poor, and the slip can be reduced by 1 lil.
Gat' □ During the transition period, it is possible to shorten the time during which the torque converter 4 generates vibration due to insufficient slip, or the fuel consumption and noise of the prime mover (engine 1) become stratified due to excessive slip.

In addition, if the configuration is such that both threshold values are always corrected to appropriate values as shown in the illustrated example, the effects described in ``-'' can always be achieved properly even when the temperature of the working fluid changes or the operating characteristics change over time. , it becomes perfect.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram of the slip control υV device Ki of the present invention, Fig. 2 is a system diagram showing an embodiment of the mounting of the present invention, and Figs. The slip 1tiU is a time chart showing the duty change situation outputted by the opening computer. Figure 4 is a characteristic diagram of the feeding control pressure with respect to the duty. Figures 5(a) and 5(b) are the slip i[ lJff
Figure 6 shows the change in lock-up pressure with respect to the control pressure 1
Figure 7 is a diagram showing the variation characteristics of lock-up pressure with respect to duty, Figure 8 is a block diagram of the computer for slip side chain 1, Figures 9 and 10 are the program for slip control computer 11, respectively. FIG. 11 is a control area diagram of the torque converter depending on the engine operating state G. FIG. 12 is a comparison of the slip AI characteristics of the device of the present invention with the slip warm characteristics of a conventional device. FIG. ■... Engine (prime mover a) 4... Torque converter (b) 5... Pawl transmission mechanism 6... Gear position sensor 7...
・Torque converter output shaft (0) 10...Converter chamber [l...Lock-up clutch (d) 18...Lock-up chamber 14...Slip fllJ 1illl
Valve 16... Control pressure generation circuit 19... Solenoid valve 20
,,, Slimb control computer 21...Engine rotation speed sensor 22...Ryoichi transmission mechanism output rotation speed sensor 23...Engine throttle opening sensor 24...Microprocessor unit (MPU) 25... Random access memory (RAM) 26...Read-only memory (ROt,
i) 27...I/O interface circuit CIlo
) 28... Drive circuit e... From P, calculation means f.
...Slip control sub-means Ri...Threshold value d9'' determining means b...Calculated value changing means. Patent applicant Nissan Motor Co., Ltd. Figure 4 Figure 5 (a) (b) Figure 6 Figure 7 figure

Claims (1)

[Scope of Claims] 1. A transmission path that transmits power from the prime mover to the output shaft via a torque converter, and a transmission path that directly transmits the power to the output shaft via a lock amplifier clutch that is appropriately coupled. slip auxiliary leg means having a calculating means for calculating Pl and D based on an error of 1 m of actual slip with respect to a target slip amount of the torque converter, and controlling a coupling force of the lock amplifier clutch so that the error is eliminated based on the result of the calculation; In the torque converter slip control device equipped with the above two threshold values for the PID calculation (
111. A slip control device for a torque converter, characterized in that it is provided with a change means. 2. The threshold value setting means corrects the surface threshold value when the result of the calculation is out of the range for a predetermined time or more. Converter slip control device.