JP5789839B2 - Control device for lock-up clutch - Google Patents

Description

  The present invention relates to a control device for a lock-up clutch provided in a torque converter, and more particularly to a technique for learning and correcting an output characteristic of a lock-up solenoid valve that changes a lock-up differential pressure of a lock-up clutch in accordance with an instruction differential pressure.

  There are individual differences in the output characteristics of the lock-up solenoid valve, and even if the same command differential pressure (command current) is applied, the output characteristics differ for each lock-up solenoid valve. That is, according to the lockup solenoid valve having a relatively high output characteristic, the lockup differential pressure is increased, and according to the lockup solenoid valve having a relatively low output characteristic, the lockup differential pressure is decreased. For this reason, when changing the lock-up clutch from the engaged state to the released state, the lock-up solenoid valve with high output characteristics is relatively delayed in releasing the lock-up clutch, and the lock-up solenoid valve with low output characteristics is Will be released relatively quickly.

  In order to suppress such a variation in the release timing of the lockup clutch, a method of correcting the command differential pressure of the lockup differential pressure at the start of the release control of the lockup clutch has been conventionally employed. Specifically, the time from the start of the release control of the lockup clutch to the completion of the release (hereinafter also simply referred to as “release time”) is measured, and when the obtained release time is shorter than the reference value, The command differential pressure of the lockup differential pressure at the start of the release control of the lockup clutch is learned and corrected to the high pressure side so that the release time of the lockup clutch becomes longer, while the obtained release time is longer than the reference value In this case, the indicated differential pressure is learned and corrected to the low pressure side so that the release time is shortened.

  When the vehicle decelerates, it becomes easier to stall if the lock-up clutch release timing is delayed. It is also possible to design the lock-up clutch so that the release timing of the lock-up clutch is optimal. In this case, for a lockup solenoid valve having an output characteristic lower than that of the output upper limit product, the command differential pressure of the lockup differential pressure at the start of the lockup clutch release control is corrected to the high pressure side. On the other hand, if the release timing of the lock-up clutch is too early, it is easy for the vehicle to shock due to a sudden change in torque. To decide.

  For example, in the lockup clutch control device disclosed in Patent Document 1, lockup at the start of smooth-off control (at the start of release control of the lockup clutch) in which the engagement hydraulic pressure of the lockup clutch is smoothly lowered and released is performed. The command differential pressure of the differential pressure is corrected according to the release time of the lockup clutch.

  Patent Document 2 discloses a method for calculating the engagement torque capacity of the lockup clutch.

JP 2008-121750 A JP 11-344110 A

  By learning the variation of the output characteristics of the lockup solenoid valve through the release time of the lockup clutch, and correcting the command differential pressure of the lockup differential pressure at the start of the release control of the lockup clutch according to the release time, The release timing of the lockup clutch becomes gradually better.

  However, if torque fluctuation occurs due to load fluctuation of auxiliary equipment, execution of fuel cut, etc. between the start of smooth-off control and the release of the lockup clutch, the release time as the learning value can be obtained appropriately. There may not be. Therefore, in order to minimize the adverse effects due to erroneous learning, the correction amount per operation for the command differential pressure at the start of smooth-off control is limited to a small amount.

  However, since the correction amount per one time is limited to a small amount, it takes a lot of time until the release timing of the lockup clutch becomes good. Repeatedly give you discomfort.

  The present invention was devised in view of the problems described above, and learns the variation in the output characteristics of the lockup solenoid valve through the release time of the lockup clutch, and calculates the command differential pressure at the start of the release control of the lockup clutch. An object of the present invention is to provide a lockup clutch control device that can shorten the learning period until the lockup clutch release timing becomes good in the lockup clutch control device that performs correction according to the release time.

  As means for solving the above-described problems, the lockup clutch control device of the present invention is configured as follows.

That is, the control device for a lockup clutch of the present invention is provided in a torque converter that transmits an output from an engine to an input shaft side of an automatic transmission via a pump impeller and a turbine runner, and the engine side and the automatic transmission are provided. A hydraulic lock-up clutch that can be engaged and disengaged with a solenoid valve that has a solenoid valve that changes the lock-up differential pressure according to the commanded differential pressure, and that controls the engagement and release of the lock-up clutch via this solenoid valve. Assuming that when the lockup clutch shifts from the disengaged state to the engaged state, the differential rotational speed detection means for detecting that the differential rotational speed of the lockup clutch has become less than a predetermined value, and the differential rotational speed detection Lockup for estimating a lockup differential pressure when the means detects that the differential rotational speed is less than a predetermined value A value obtained by subtracting the indicated differential pressure when it is detected that the differential rotational speed is less than a predetermined value from the pressure estimation means and the lockup differential pressure estimated by the lockup differential pressure estimation means Output characteristic selection means for comparing the output characteristics of the solenoid valve by comparing with a preset reference value, and the lockup clutch according to the selection result by the output characteristic selection means during the release control of the lockup clutch Correction means for correcting the indicated differential pressure at the start of release of the lockup clutch, and controls at least the release of the lockup clutch .

  According to the lockup clutch control device having such a configuration, when the differential rotation speed of the lockup clutch is less than a predetermined value, the output characteristics of the solenoid valve can be instantly learned, and therefore, it is adversely affected by torque fluctuations. And an appropriate learning value can be obtained. For this reason, the amount of correction for the command differential pressure at the start of smooth-off control can be increased, and as a result, the learning period from the start of learning until the release timing of the lockup clutch is improved can be significantly shortened. It becomes.

  According to the lockup clutch control device of the present invention, the learning period from the start of learning until the release timing of the lockup clutch becomes good can be significantly shortened.

It is a figure which shows schematic structure of the vehicle carrying the control apparatus which concerns on embodiment of this invention. It is a figure which shows the hydraulic control circuit for operating a lockup clutch. It is a block diagram which shows the structure of control systems, such as ECU. It is a time chart which shows the lockup differential pressure when the lockup clutch is engaged from the released state, the engine speed and the turbine speed. It is a flowchart which shows the procedure of the learning control at the time of lockup ON which a control apparatus performs. It is an example of the map which defined the capacity | capacitance coefficient of the torque converter. It is a flowchart which shows the procedure of the smooth-off control which a control apparatus performs. It is a time chart which shows the indication differential pressure which changes by smooth off control. It is a flowchart which shows the procedure of the learning control at the time of lockup OFF which a control apparatus performs.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. First, prior to description of learning control executed by the lockup clutch control device according to this embodiment, a schematic configuration example of a vehicle equipped with this control device will be described with reference to FIG.

  The vehicle shown in FIG. 1 is an FF (front engine / front drive) type vehicle, and includes an engine 1, a torque converter 2, a forward / reverse switching device 3, a belt-type continuously variable transmission 4, a reduction gear device 5, a differential gear. A device 6, an ECU (Electronic Control Unit) 8, a hydraulic control circuit 20, and the like are mounted.

  A crankshaft 11, which is an output shaft of the engine 1, is connected to the torque converter 2, and the output of the engine 1 is transmitted from the torque converter 2 to the forward / reverse switching device 3, the belt type continuously variable transmission 4, and the reduction gear device 5. To the differential gear device 6 and distributed to the left and right drive wheels (not shown).

<Engine>
The engine 1 is, for example, a multi-cylinder gasoline engine, and the amount of intake air taken into the engine 1 is adjusted by an electronically controlled throttle valve 12. The opening of the throttle valve 12 (throttle opening) is detected by a throttle opening sensor 102. Further, the coolant temperature of the engine 1 is detected by a water temperature sensor 103.

  The throttle opening of the throttle valve 12 is driven and controlled by the ECU 8. Specifically, the optimum intake air amount (target) according to the operating state of the engine 1 such as the engine speed Ne detected by the engine speed sensor 101 and the accelerator pedal depression amount (accelerator opening) Ap of the driver. The throttle opening of the throttle valve 12 is controlled so that the intake amount) is obtained.

<Torque converter>
The torque converter 2 includes a pump impeller 21 on the input shaft side, a turbine runner 22 on the output shaft side, a stator 23 that exhibits a torque amplification function, and a one-way clutch 24, and is provided between the pump impeller 21 and the turbine runner 22. The power is transmitted through the fluid.

  The torque converter 2 is provided with a lockup clutch 25 that directly connects the input side and the output side thereof. The lockup clutch 25 has a differential pressure (lockup differential pressure) ΔP between the hydraulic pressure in the engagement side oil chamber 26 and the hydraulic pressure in the release side oil chamber 27 (ΔP = hydraulic pressure in the engagement side oil chamber 26 minus the release side). A hydraulic friction clutch that is frictionally engaged with the front cover 2a by the hydraulic pressure in the oil chamber 27, and is brought into an engaged state (engaged state) or a released state by controlling the differential pressure ΔP. That is, the lockup clutch 25 is engaged by setting the lockup differential pressure ΔP to a positive value, and the lockup clutch 25 is released by setting the lockup differential pressure ΔP to zero or less. The lockup differential pressure ΔP is controlled by a lockup control valve 82 and the like which will be described later and the ECU 8.

  The torque converter 2 is provided with a mechanical oil pump 7 that is connected to and driven by a pump impeller 21. The hydraulic pressure supplied from the oil pump 7 becomes the original pressure of the hydraulic control circuit 20.

<Forward / backward switching device>
The forward / reverse switching device 3 includes a planetary gear mechanism 30, a reverse clutch C1, and a forward brake B1. When the reverse clutch C1 is released and the forward brake B1 is engaged, the rotation of the turbine shaft 28 is reversed and decelerated and transmitted to the input shaft 40. When the forward brake B1 is released and the reverse clutch C1 is engaged, the turbine shaft 28 and the input shaft 40 are directly connected. Further, when both the reverse clutch C1 and the forward brake B1 are released, the forward / reverse switching device 3 cuts off the power to form a neutral state.

<Belt type continuously variable transmission>
The belt type continuously variable transmission 4 includes an input-side primary pulley 41, an output-side secondary pulley 42, a metal belt 43 wound between the primary pulley 41 and the secondary pulley 42, and the like. . A hydraulic actuator 413 for changing the V groove width between the fixed sheave 411 and the movable sheave 412 is disposed on the movable sheave 412 side of the primary pulley 41. The V groove width is changed by controlling the hydraulic pressure supplied to the hydraulic actuator 413. Similarly, a hydraulic actuator 423 for changing the V groove width between the fixed sheave 421 and the movable sheave 422 is also arranged on the movable sheave 422 side of the secondary pulley 42, and is supplied to the hydraulic actuator 423. The V groove width is changed by controlling the hydraulic pressure.

<Hydraulic control circuit>
Next, the hydraulic control circuit 20 for controlling the hydraulic oil supplied to the torque converter 2 with the lockup clutch 25 will be described with reference to FIG. In FIG. 2, 71 is a primary regulator valve, and SLS is a linear solenoid valve for pressure regulation control of the line pressure PL. A normally open linear solenoid valve is used as the linear solenoid valve SLS, and the signal pressure of the linear solenoid valve SLS is controlled in accordance with an instruction from the ECU 8.

  The primary regulator valve 71 is a valve for regulating the oil supplied from the oil pump 7 to a predetermined line pressure PL. The solenoid pressure Psls output from the linear solenoid valve SLS is input to the signal port 71a of the primary regulator valve 71. The primary regulator valve 71 regulates the line pressure PL to a hydraulic pressure proportional to the solenoid pressure Psls.

  In FIG. 2, 82 is a lock-up control valve, 84 is a solenoid valve (lock-up solenoid valve), and 86 is a secondary regulator valve.

  The lock-up control valve 82 is a valve for controlling the engagement / release operation of the lock-up clutch 25, and surplus oil generated in accordance with the regulated state of the line pressure PL of the primary regulator valve 71 is removed from the lock-up clutch 25. The engagement / release operation of the lock-up clutch 25 is controlled by supplying the hydraulic oil chambers 26 and 27.

  The lockup control valve 82 includes a spring 82a, a spool 82b, a signal port 82c, an input port 82d, a first output port 82g, a second output port 82h, and the like. The spool 82b is biased from one direction by a spring 82a, and the output pressure Ps output from the solenoid valve 84 is input to a signal port 82c provided at a position facing the spring 82a. The original pressure Po is input from the secondary regulator valve 86 to the input port 82d. The first output port 82g is connected to the release-side oil chamber 27 of the lockup clutch 25 via the oil passage 88. The second output port 82h is connected to the engagement side oil chamber 26 of the lockup clutch 25 via the oil passage 90.

  The solenoid valve 84 outputs the output pressure Ps to the signal port 82c of the lockup control valve 82 in accordance with the instruction differential pressure of the ECU 8. When the output pressure Ps decreases, the spool 82b is pushed and moved by the spring 82a to approach the upper position (the left position in FIG. 2), and the original pressure Po is locked via the input port 82d and the first output port 82g. 25 open side oil chambers 27 are supplied. As a result, the lockup differential pressure ΔP of the lockup clutch 25 is reduced, and the lockup clutch 25 is released. On the other hand, when the output pressure Ps increases, the spool 82b approaches the lower position (the right position in FIG. 2) against the spring 82a, and the original pressure Po is locked up via the input port 82d and the second output port 82h. The oil is supplied to the engagement side oil chamber 26 of the clutch 25. As a result, the lockup differential pressure ΔP of the lockup clutch 25 increases, and the lockup clutch 25 enters the engaged state.

  In addition to the configuration described above, the hydraulic pressure control circuit 20 incorporates a solenoid, a control valve, and the like (not shown) for controlling the hydraulic pressure supplied to the belt type continuously variable transmission 4.

<ECU>
As shown in FIG. 3, the ECU 8 is mainly configured by a microcomputer including a CPU 81, a ROM 83, a RAM 85, a backup RAM 87, and the like. The ECU 8 controls the engine 1 and a belt type continuously variable transmission via the hydraulic control circuit 20. And a CVT-ECU that controls the lock-up clutch 25.

  The CPU 81, ROM 83, RAM 85, and backup RAM 87 are connected to each other via a bus 89, and are connected to an input interface 91 and an output interface 93.

  The input interface 91 includes an engine speed sensor 101, a throttle opening sensor 102, a water temperature sensor 103, a turbine speed sensor 104, a primary pulley speed sensor 105, a secondary pulley speed sensor 106, an accelerator position sensor 107, a shift lever. Are connected to a lever position sensor 110, a brake pedal sensor 112, a hydraulic oil temperature sensor 113, a vehicle speed sensor 114, and the like, and output signals from these sensors are supplied to the ECU 8. .

  The output interface 93 is connected to the throttle motor 13, the fuel injection device 14, the ignition device 15, the hydraulic control circuit 20, and the like. The ECU 8 controls the output of the engine 1, the gear ratio control and the belt clamping pressure control of the belt-type continuously variable transmission 4, the engagement / release control of the lockup clutch 25, and the front / rear control based on the output signals of the sensors. Engagement / release control of the reverse clutch C1 and the forward brake B1 is executed.

<Learning control when lock-up is on>
Next, learning control executed by the ECU 8 when the lockup clutch 25 is engaged from the released state (when lockup is on) will be described. In the learning control according to the present embodiment, the lockup differential pressure is estimated when the lockup clutch 25 is engaged (when the differential rotation speed of the lockup clutch 25 becomes less than a predetermined value JDGFIN), and the estimated lockup is performed. Similarly, a value obtained by subtracting the indicated differential pressure ΔPt when the lockup clutch 25 is engaged (when the differential rotation speed of the lockup clutch 25 becomes less than the predetermined value JDGFIN) is subtracted from the differential pressure ΔPs. Compared with the value JDGH or the predetermined low-side reference value JDGL, the output characteristic of the lockup solenoid valve 84 is selected using the learning correction value. The command differential pressure at the start of smooth-off control, which will be described in detail later, is corrected according to the learning correction value that is the selection result.

  FIG. 4 shows an example of a time chart showing a change example of the lockup differential pressure ΔP when the lockup clutch 25 is engaged from the released state, and an example of a time chart of the engine speed Ne1 to Ne3 and the turbine speed Nt. . Reference numerals X <b> 1 and Ne <b> 1 indicate a case where a nominal product is adopted as the lockup solenoid valve 84. Reference numerals X2 and Ne2 indicate cases where a lockup solenoid valve 84 having relatively high output characteristics is employed. Symbols X3 and Ne3 indicate cases where a lockup solenoid valve 84 having a relatively low output characteristic is employed.

  When the lockup solenoid valve 84 having a relatively high output characteristic is adopted, the lockup solenoid valve 84 is obtained by subtracting the command differential pressure ΔPt when the lockup clutch 25 is engaged from the estimated lockup differential pressure ΔPs. The magnitude of the value is represented by the length of the arrow Z2. When a lockup solenoid valve 84 having a relatively low output characteristic is adopted, the command differential pressure ΔPt when the lockup clutch 25 is engaged is subtracted from the estimated lockup differential pressure ΔPs described above. The magnitude of the obtained value is represented by the length of the arrow Z3. It can be said that the longer the lengths of these arrows Z2 and Z3, the greater the variation in output characteristics compared to the nominal product. When this variation (the length of the arrows Z2 and Z3) is greater than a predetermined value (the absolute value of the Hi-side reference value JDGH or the Low-side reference value JDGL), the indicated differential pressure at the start of smooth-off control, which will be described in detail later Is greatly corrected so that early convergence of learning correction is achieved.

  Hereinafter, the control procedure of the learning control at the time of lock-up on executed by the ECU 8 will be described with reference to the flowchart shown in FIG.

  In step ST1, the ECU 8 determines whether or not an execution condition for executing the learning control at the time of lock-up on is satisfied. This execution condition should be set according to the vehicle type. For example, the operating oil temperature of the lockup clutch 25 is a predetermined value (for example, 60 ° C.) or more, and the engine coolant temperature is a predetermined value (for example, 70). It is mentioned that the above-mentioned execution conditions are above. If an affirmative determination is made in step ST1, the process proceeds to step ST2. If a negative determination is made, this routine is exited.

  In step ST2, the ECU 8 determines whether or not the differential rotational speed DN (the difference between the engine rotational speed Ne and the turbine rotational speed Nt) of the lock-up clutch 25 is less than a predetermined value JDGFIN. If an affirmative determination is made in step ST2, the process proceeds to step ST3. If a negative determination is made, this routine is exited. The predetermined value JDGFIN is preferably set to a value (for example, within 50 rpm) that can be considered that the lockup clutch 25 is almost engaged.

In step ST3, the ECU 8 calculates an estimated value ΔPs of the lockup differential pressure when the differential rotation speed DN of the lockup clutch 25 becomes less than a predetermined value JDGFIN. The estimated value ΔPs of the lockup differential pressure can be expressed by the following equation (1).
ΔPs = TC _{L / U} / (S _{L / U} * μ) (1)
Here, TC _{L / U} is the torque capacity of the lock-up clutch 25, S _{L / U} is the effective area of the friction engagement portion of the lock-up clutch 25, and μ is the friction engagement portion of the lock-up clutch 25. It is a coefficient of friction.

Further, the torque capacity TC _{L / U} of the lockup clutch 25 is expressed by the following equation (2).
TC _{L / U} = Te-P _loss -Ie * dωe / dt-C * ωe ² (2)
Here, Te is the engine torque, P _loss is the load of the oil pump 7, Ie is the inertia of the rotating parts from the engine 1 to the pump impeller 21, ωe is the rotational angular velocity of the engine 1, and dωe / dt is The rotational angular acceleration of the engine 1 and C is a capacity coefficient of the torque converter 2 of the lockup clutch 25. As is well known, the engine torque can be obtained from the throttle opening and the engine speed, and the pump load can be obtained from the line pressure PL of the hydraulic control circuit 20.

  Further, the ECU 8 has a map as shown in FIG. 6 in which the capacity coefficient C of the torque converter 2 is determined using the rotational speed ratio between the engine speed and the turbine speed as a parameter. A capacity coefficient C is obtained from the rotational speed ratio detected based on the output value of the turbine rotational speed sensor 104 and the map. In the map shown in FIG. 6, the capacity coefficient C decreases as the rotational speed ratio increases. Such characteristics can be obtained by experiments, simulations, and the like.

  In step ST4, the ECU 8 determines whether or not a value obtained by subtracting the current command differential pressure ΔPt from the estimated value ΔPs of the lockup differential pressure is greater than a predetermined Hi-side reference value JDGH. If an affirmative determination is made here, the process proceeds to step ST5, and if a negative determination is made, the process proceeds to step ST6.

  In step ST5, the ECU 8 sets zero as the learning correction value LC. When zero is set as the learning correction value LC in step ST5, it can be said that the employed lockup solenoid valve 84 has higher output characteristics than the nominal product.

  In step ST6, the ECU 8 determines whether or not a value obtained by subtracting the current command differential pressure ΔPt from the estimated value ΔPs of the lockup differential pressure is smaller than a predetermined value JDGL. If an affirmative determination is made here, the process proceeds to step ST7, and if a negative determination is made, the process proceeds to step ST8.

  In step ST7, the ECU 8 sets HOSEI1 as the learning correction value LC. In this step ST7, when HOSEI1 is set as the learning correction value LC, it can be said that the employed lockup solenoid valve 84 has lower output characteristics than the nominal product.

  In step ST8, the ECU 8 sets HOSEI2 as the learning correction value LC. In this step ST8, when HOSEI2 is set as the learning correction value LC, it can be said that the employed lockup solenoid valve 84 has the same output characteristics as the nominal product. HOSEI1 and HOSEI2 have a relationship of HOSEI1 <HOSEI2 as absolute values.

<Smooth off control>
Next, the smooth-off control of the lockup clutch 25 executed by the ECU 8 will be described with reference to the flowchart shown in FIG. In this smooth-off control, the lockup differential pressure (indicated differential pressure) is suddenly reduced at the start of the control, and then the lockup differential pressure is gradually lowered (as smoothly as possible) to suppress the shock during release. This is lock-up off control for releasing the up clutch 25.

  In step ST11, the ECU 8 determines whether or not a predetermined execution condition for executing the smooth-off control is satisfied. The predetermined execution condition should be set individually according to the vehicle type. Examples of the execution condition include that the accelerator is off and the vehicle is in a deceleration state. If an affirmative determination is made in step ST11, the process proceeds to step ST12. If a negative determination is made, the present routine is exited.

  In step ST12, the ECU 8 determines whether or not smooth off control is started. If a positive determination is made here, the process proceeds to step ST13. If a negative determination is made, the process proceeds to step ST16. Note that it is possible to determine whether or not it is at the start of smooth-off control by various methods. For example, after being set to ON at the start of smooth-off control and reflecting a lock-up off learning value described later, This can be done by referring to a flag to be set OFF.

In step ST13, the ECU 8 determines whether or not the learning correction value LC obtained by the “learning control at the time of lock-up on” is larger than the lock-up off learning value L _off . Here, the lock-up off learning value L _off is a value for correcting the command differential pressure at the start of the smooth off control. When an affirmative determination is made in step ST13, the learning correction value LC obtained by “learning control at lock-up on” is adopted as the lock-up off learning value L _off (step ST14), and the set lock-up off is set. The learning value is reflected (ST15). As shown in FIG. 8, the command differential pressure ΔPt of the lockup clutch 25 at the start of smooth-off control (time A) is obtained when a lockup solenoid valve 84 having an output characteristic comparable to that of the nominal product is used. Is corrected to the high pressure side by HOSEI1, and when the lock-up solenoid valve 84 whose output characteristics are lower than the nominal value is lower than the nominal value, only HOSEI2 is corrected to the high pressure side. If the learning correction value LC = 0, a negative determination is made in step ST13, and the lock-up learning value L _off is not updated.

  In step ST16, the ECU 8 sets a value obtained by subtracting a predetermined value (a minute value) from the command differential pressure at the time of execution of the process of the previous step ST16 as a new command differential pressure (step ST16). As shown in the range of time A to time B in FIG. 8, the command differential pressure ΔPt of the lockup differential pressure gradually decreases every time this step ST16 is executed.

<Learning control during lock-up off>
Next, learning control executed by the ECU 8 when the lockup clutch 25 shifts from the engaged state to the released state (at the time of lockup off) will be described with reference to the flowchart shown in FIG. The learning control at the time of lock-up off is performed according to the time from the start of release control of the lock-up clutch 25 to the completion of release (hereinafter also simply referred to as “release time”). To correct.

  In step ST31, the ECU 8 determines whether or not a prohibition condition for prohibiting learning control at the time of lock-up off is satisfied. This prohibition condition should be set according to the vehicle type. For example, the operating oil temperature of the lockup clutch 25 is lower than a predetermined value (for example, 60 ° C.), and the engine cooling water temperature is a predetermined value (for example, 70). The above execution conditions include that the temperature is less than (° C.) and the accelerator is on. If a negative determination is made in step ST31, the process proceeds to step ST32. If an affirmative determination is made, the routine is exited.

In step ST32, when the ECU 8 determines that the actual release time T of the lockup clutch 25 is longer than the target release time Tt (step ST32: YES), it is obtained by subtracting a predetermined value from the lockup off learning value _Loff. The value is set as a new lockup-off learning value L _off . As a result, the command differential pressure at the start of smooth-off control (time A) is reduced, the release time of the lockup clutch 25 is shortened, and the actual release time T of the lockup clutch 25 is close to the target release time.

In step ST32, when the ECU 8 determines that the actual release time T of the lockup clutch 25 is shorter than the target release time Tt (step ST32: NO), the ECU 8 is obtained by adding a predetermined value from the lockup off learning value _Loff. The value is set as a new lockup-off learning value L _off . As a result, the command differential pressure at the start of smooth-off control (time A) increases, the release time of the lockup clutch 25 becomes longer, and the actual release time T of the lockup clutch 25 approaches the target release time.

  As is apparent from the above description, according to the present embodiment, the output characteristics of the lockup solenoid valve 84 can be reduced when the lockup clutch 25 is engaged (when the differential rotational speed of the lockup clutch 25 is less than a predetermined value). Since learning can be performed instantaneously, an appropriate learning value can be obtained without being adversely affected by torque fluctuation due to execution of fuel cut or the like. For this reason, the correction amount for the command differential pressure at the start of smooth-off control can be increased, and as a result, the release timing of the lock-up clutch is improved from the start of learning as compared with the conventional lock-up clutch control device. It is possible to significantly reduce the time until

  The present invention can be applied to, for example, a control device that learns and corrects the output characteristics of a lockup solenoid valve that changes the lockup differential pressure of the lockup clutch in accordance with the commanded differential pressure.

1 Engine 2 Torque converter 4 Belt type continuously variable transmission (automatic transmission)
8 ECU
21 Pump Impeller 22 Turbine Runner 25 Lockup Clutch 40 (Automatic Transmission) Input Shaft 84 Lockup Solenoid Valve 101 Engine Speed Sensor 104 Turbine Speed Sensor

Claims (1)

Hydraulic lockup that is provided in a torque converter that transmits the output from the engine to the input shaft side of the automatic transmission via the pump impeller and turbine runner, and that allows the engine side and the automatic transmission side to be fastened and released Regarding the clutch,
In a control device that has a solenoid valve that changes a lock-up differential pressure in accordance with an indicated differential pressure, and that controls engagement / release of a lock-up clutch via the solenoid valve.
Differential rotation speed detection means for detecting that the differential rotation speed of the lockup clutch is less than a predetermined value when the lockup clutch shifts from the released state to the engaged state;
A lockup differential pressure estimation means for estimating a lockup differential pressure when the differential rotation speed detection means detects that the differential rotation speed is less than a predetermined value;
A value obtained by subtracting the indicated differential pressure when it is detected that the differential rotational speed is less than a predetermined value from the lockup differential pressure estimated by the lockup differential pressure estimating means is preset. An output characteristic selecting means for selecting the output characteristic of the solenoid valve in comparison with a reference value;
Correction means for correcting the command differential pressure at the start of releasing the lockup clutch according to the selection result by the output characteristic selection means during the release control of the lockup clutch;
And a lockup clutch control device that controls at least release of the lockup clutch.