JP6594150B2 - Control device for automatic transmission and control method for automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission control device and an automatic transmission control method.

  A technique for temporarily rotating the electric oil pump at a high speed when the electric oil pump is activated is disclosed in Patent Document 1 (see, for example, paragraph 0010).

JP 2001-90828 A

  When the rotation of the electric oil pump suddenly starts up, such as when the electric oil pump is started, the flow rate of oil discharged from the electric oil pump increases rapidly, which may cause a hydraulic surge. In addition, if the sudden rise of the rotation of the electric oil pump overlaps with an increase in the hydraulic pressure command pressure in the automatic transmission, a hydraulic surge may easily occur or worsen.

  It can be said that the hydraulic surge can be suppressed by slowly starting up the rotation of the electric oil pump or by preventing the rising of the rotation of the electric oil pump from overlapping with the increase in the indicated hydraulic pressure. However, in this case, instead of suppressing the hydraulic surge, the rise of the hydraulic pressure in the automatic transmission is delayed.

  The present invention has been made in view of such problems, and provides an automatic transmission control device and an automatic transmission control method capable of achieving both suppression of hydraulic surge and suppression of delay in rising of hydraulic pressure. For the purpose.

A control device for an automatic transmission according to an aspect of the present invention is a control device for an automatic transmission including an electric oil pump, and the actual pressure of the hydraulic pressure is increased after an instruction to increase the indicated pressure of the hydraulic pressure in the automatic transmission. After the rotational speed of the electric oil pump is increased to a value higher than a set value before reaching the command pressure, the difference between the actual pressure and the command pressure becomes less than a predetermined value. a control unit, a rotational speed that started down toward the set value of the electric oil pump.

According to another aspect of the present invention, there is provided a method for controlling an automatic transmission including an electric oil pump, wherein an actual pressure of the hydraulic pressure is changed to the indicated pressure after an instruction to increase the indicated pressure of the hydraulic pressure in the automatic transmission. Increasing the rotational speed of the electric oil pump to a value higher than a set value before reaching, and increasing the rotational speed of the electric oil pump to a value higher than the set value, then the actual pressure and the magnitude of the difference between the command pressure control method for an automatic transmission including a Rukoto started lowered toward the rotational speed of the electric oil pump to the set value at the timing becomes less than a predetermined value is provided.

  According to these aspects, the rotational speed increase rate can be increased by increasing the rotational speed of the electric oil pump to a value higher than the set value before the actual hydraulic pressure reaches the command pressure. For this reason, it is possible to suppress a delay in rising of the hydraulic pressure. Further, at this time, since the actual hydraulic pressure reaches the command pressure, even if a hydraulic surge occurs due to such control of the rotational speed, the actual pressure can be suppressed lower than the command pressure. it can.

  Furthermore, according to these aspects, after the rotational speed of the electric oil pump is increased to a value higher than the set value, the rotational speed of the electric oil pump is decreased to the set value, so that the peak value of the hydraulic surge is suppressed. You can also. Therefore, according to these aspects, it is possible to achieve both suppression of the hydraulic surge and suppression of the delay in rising of the hydraulic pressure.

It is a schematic block diagram of the vehicle of this embodiment. It is a figure which shows the principal part of a hydraulic control circuit. It is explanatory drawing of the hydraulic surge which generate | occur | produces according to the raise instruction | indication of a line command pressure. It is a figure which shows an example of the control of this embodiment with a flowchart. It is a figure which shows an example of the timing chart corresponding to control of this embodiment. It is a figure which shows the comparative example of FIG. 5A.

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

  FIG. 1 is a schematic configuration diagram of a vehicle. The vehicle includes an engine 1, a torque converter 2, a variator 3, a final reduction mechanism 4, a drive wheel 5, a first oil pump 10, a second oil pump 11, a hydraulic control circuit 12, a controller 13, , Sensor switch group 14. In the vehicle, the automatic transmission 15 includes the variator 3, the torque converter 2, the first oil pump 10, the second oil pump 11, the hydraulic control circuit 12, the controller 13, and the sensor / switch group 14. Configured.

  The engine 1 constitutes a drive source for the vehicle. The output of the engine 1 is transmitted to the drive wheels 5 via the torque converter 2, the variator 3, and the final reduction mechanism 4. In other words, the torque converter 2, the variator 3, and the final reduction mechanism 4 are provided in a power transmission path that transmits power from the engine 1 to the drive wheels 5.

  The torque converter 2 transmits power through the fluid. In the torque converter 2, the power transmission efficiency can be increased by fastening the lockup clutch 2a.

  The variator 3 includes a primary pulley 31, a secondary pulley 32, and a belt 33 wound around the primary pulley 31 and the secondary pulley 32. Hereinafter, the primary is also referred to as PRI and the secondary is also referred to as SEC. The variator 3 constitutes a belt-type continuously variable transmission mechanism that changes speed by changing the winding diameter of the belt 33 by changing the groove widths of the PRI pulley 31 and the SEC pulley 32, respectively.

  The PRI pulley 31 includes a fixed pulley 31a, a movable pulley 31b, and a PRI chamber 31c. In the PRI pulley 31, by controlling the primary pressure supplied to the PRI chamber 31c, the movable pulley 31b is operated and the groove width of the PRI pulley 31 is changed.

  The SEC pulley 32 includes a fixed pulley 32a, a movable pulley 32b, and an SEC chamber 32c. In the SEC pulley 32, the movable pulley 32b operates by controlling the secondary pressure supplied to the SEC chamber 32c, and the groove width of the SEC pulley 32 is changed.

  The belt 33 has a V-shaped sheave surface formed by the fixed pulley 31a and the movable pulley 31b of the PRI pulley 31 and a V-shape formed by the fixed pulley 32a and the movable pulley 32b of the SEC pulley 32. Wound around the sheave surface.

  The final reduction mechanism 4 has a plurality of gear trains and differential gears. The final reduction mechanism 4 rotates the drive wheel 5 via the axle.

  The first oil pump 10 is an electric oil pump, and the second oil pump 11 is a mechanical oil pump. Both the first oil pump 10 and the second oil pump 11 discharge oil supplied to the hydraulic control circuit 12. The variator 3 is supplied with hydraulic pressure using the first oil pump 10 and the second oil pump 11 as hydraulic pressure sources. The second oil pump 11 is driven by the power of the engine 1.

  The hydraulic control circuit 12 adjusts the pressure of the oil discharged from the first oil pump 10 and the second oil pump 11, that is, the hydraulic pressure, and transmits it to each part of the variator 3. In the hydraulic control circuit 12, the line pressure PL, the PRI pressure, and the SEC pressure are adjusted. The line pressure PL is an example of the hydraulic pressure in the automatic transmission 15 and constitutes the original pressure of the hydraulic pressure in the automatic transmission 15. The hydraulic control circuit 12 also supplies hydraulic pressure to the torque converter 2.

  The controller 13 is an electronic control unit, and a signal from the sensor / switch group 14 is input to the controller 13.

  The sensor switch group 14 includes, for example, an accelerator opening sensor that detects the accelerator opening APO, a brake sensor that detects a brake depression force based on the depression amount BRP of the brake pedal, a vehicle speed sensor that detects the vehicle speed Vsp, and a rotational speed Ne. An engine speed sensor that detects the operating position of the shift lever, an oil temperature sensor that detects the oil temperature OLT of the automatic transmission 15, and an ignition switch IGSW for starting and stopping the engine 1 And a pump rotation speed sensor that detects the rotation speed Nep of the first oil pump 10. A signal from the sensor switch group 14 may be input to the controller 13 via another controller, for example.

  The sensor switch group 14 further includes, for example, a line pressure sensor for detecting the line pressure PL, a PRI pressure sensor for detecting the PRI pressure, a SEC pressure sensor for detecting the SEC pressure, and the input side rotational speed of the PRI pulley 31. A PRI rotation speed sensor that detects the rotation speed Npri and a SEC rotation speed sensor that detects the rotation speed Nsec that is the output-side rotation speed of the SEC pulley 32 are included.

  The controller 13 controls the hydraulic control circuit 12 based on a signal from the sensor / switch group 14. The transmission ratio of the variator 3 is changed by controlling the oil discharged from the first oil pump 10 and the second oil pump 11 by the hydraulic control circuit 12 and the controller 13. The controller 13 also controls the discharge amount of the first oil pump 10. Specifically, the controller 13 controls the discharge amount of the first oil pump 10 by controlling the first oil pump 10 so that the rotation speed Nep becomes the target rotation speed Nept.

  FIG. 2 is a diagram showing a main part of the hydraulic control circuit 12. FIG. 2 also shows the first oil pump 10, the PRI chamber 31c, and the SEC chamber 32c. The hydraulic control circuit 12 includes a line pressure control valve 121, a PRI pressure control valve 122, a SEC pressure control valve 123, a line pressure oil passage 124, and a check valve 125.

  The line pressure control valve 121 controls the line pressure PL. The line pressure control valve 121 includes a main body 121a, a spool 121b, and a spring 121c. The line pressure control valve 121 has a port 121d to a port 121g. The line pressure control valve 121 is provided in the line pressure oil passage 124.

  The main body 121a houses a spool 121b and a spring 121c. The spring 121c biases the spool 121b toward the port 121f. The port 121d to the port 121g communicate with the inside and outside of the main body 121a.

  The port 121 d is an inlet port and is connected to the line pressure oil passage 124. The port 121e is an outlet port and is connected to a circulation system or the like. The port 121f is a feedback port, and the actual pressure of the line pressure PL is input to the port 121f as a feedback pressure through an orifice or the like. The port 121g is a pilot port, and a control pressure Ps corresponding to the indicated pressure of the line pressure PL is input to the port 121g by a solenoid valve (not shown).

  In the line pressure control valve 121, the spool 121b moves to a position where the force acting on the spool 121b, specifically, the acting force according to the feedback pressure, the urging force of the spring 121c, and the acting force according to the control pressure Ps are balanced. Thus, the line pressure PL is controlled so that the actual pressure becomes the command pressure. Hereinafter, the actual pressure of the line pressure PL is referred to as a line actual pressure PLr, and the command pressure of the line pressure PL is referred to as a line command pressure PLi.

  The PRI pressure control valve 122 controls the PRI pressure, and the SEC pressure control valve 123 controls the SEC pressure. The PRI pressure control valve 122 and the SEC pressure control valve 123 are provided in the downstream portion of the line pressure control valve 121 in the line pressure oil passage 124. Like the line pressure control valve 121, a control valve having a feedback port or the like can be applied to the PRI pressure control valve 122 and the SEC pressure control valve 123.

  The first oil pump 10 supplies oil to the line pressure oil passage 124 via the check valve 125. The first oil pump 10 further supplies oil to the PRI chamber 31 c via the PRI pressure control valve 122 and supplies oil to the SEC chamber 32 c via the SEC pressure control valve 123. Although not shown, the second oil pump 11 is connected to the line pressure oil passage 124 in parallel with the first oil pump 10.

By the way, when the line command pressure PLi is rapidly increased, the increase of the feedback pressure is delayed with respect to the increase of the control pressure Ps. For this reason, the spool 121b moves to the port 121f side and enters an overstroke state in which the port 121e is closed rather than the equilibrium state. As a result, even if the feedback pressure reaches the line command pressure PLi, oil cannot be drained from the outlet port 121e immediately, and a hydraulic surge may occur.

FIG. 3 is an explanatory diagram of a hydraulic surge that occurs in response to an instruction to increase the line command pressure PLi.
FIG. 3 shows a case where there is an instruction to increase the line instruction pressure PLi but there is no rise in the rotation of the first oil pump 10. In FIG. 3, the pump flow rate indicates the total flow rate of the supply flow rates of the first oil pump 10 and the second oil pump 11.

In this example, the instruction to increase the line command pressure PLi is performed in a state where all the pump flow rate Q1 is supplied by the second oil pump 11, and thus there is no rise in the rotation of the first oil pump 10. When a hydraulic surge occurs in response to this, the hydraulic surge causes an overshoot of the line pressure PL where the actual line pressure PLr exceeds the line command pressure PLi.

Further, the hydraulic surge may occur when the rotation of the first oil pump 10 suddenly starts up. This is because when the rotation of the first oil pump 10 suddenly rises, the flow rate of oil discharged from the first oil pump 10 increases rapidly. When the sudden rise of the rotation of the first oil pump 10 and the increase instruction of the line instruction pressure PLi overlap, there is a possibility that a hydraulic surge is likely to be generated or worsened.

  For this reason, in this embodiment, the controller 13 performs control as described below.

  FIG. 4 is a flowchart illustrating an example of the control performed by the controller 13. The controller 13 repeatedly executes the processing of this flowchart, for example, every minute time.

  In step S <b> 1, the controller 13 determines whether there is an instruction to increase the rotational speed Nep of the first oil pump 10. The instruction to raise the first oil pump 10 includes that the target rotational speed Nept of the first oil pump 10 has been significantly changed. The fact that the first oil pump 10 has been instructed can further include a state during which the rotational speed Nep is increasing thereafter.

  An instruction to raise the first oil pump 10 can be detected based on the state of the vehicle including the state of the automatic transmission 15, for example. The vehicle state includes, for example, a target value such as a target rotational speed Nept and a line command pressure PLi calculated based on the output of the sensor / switch group 14 in addition to a state detected based on the output of the sensor / switch group 14.

  In step S <b> 1, the controller 13 specifically determines whether or not there has been an instruction to rapidly increase the rotational speed Nep of the first oil pump 10. The fact that the first oil pump 10 has been instructed to rise rapidly may be, for example, that the difference between the reached value and the initial value of the target rotational speed Nept of the first oil pump 10 is larger than a predetermined value.

  This is because, for example, a request to achieve the change of the rotational speed Nep to the reached value within a predetermined time tends to increase the rotational speed increase rate of the first oil pump 10 as the difference increases. Because.

  Regarding the above-mentioned instruction for sudden increase of the rotational speed Nep, the predetermined value is a value for defining that the rise of the rotation of the first oil pump 10 is steep enough to cause an overshoot of the line pressure PL. Can be set in advance. Further, the difference can be a value obtained by subtracting the initial value from the reached value. If a negative determination is made in step S1, this flowchart is temporarily terminated. If the determination is affirmative in step S1, the process proceeds to step S2.

In step S2, the controller 13 determines whether or not there has been an instruction to increase the line command pressure PLi. The instruction to increase the line command pressure PLi includes that the line command pressure PLi has been significantly changed. The instruction to increase the line command pressure PLi can further include a state until the actual line pressure PLr reaches the line command pressure PLi. An instruction to increase the line command pressure PLi can be detected based on the state of the vehicle, for example.

Specifically, in step S2, the controller 13 determines whether or not there has been a rapid increase instruction for the line command pressure PLi. When the line command pressure PLi is instructed in a stepwise manner, for example, when the line command pressure PLi is commanded stepwise, for example, the difference between the reached value and the initial value of the line command pressure PLi is larger than a predetermined value. It can be said that. Line command pressure PLi
For example, it may be determined that the line instruction pressure increase rate is higher than a predetermined increase rate. When the line instruction pressure PLi is instructed to increase stepwise, the initial value of the line instruction pressure PLi is specifically the line instruction pressure PLi immediately before the increase instruction.

With respect to the above-described rapid increase instruction of the line command pressure PLi, the predetermined value is a value for defining that the increase of the line command pressure PLi based on the increase command is steep enough to cause an overshoot of the line pressure PL. It can be set in advance by experiments or the like. The same applies to the predetermined rate of increase. The difference can be a value obtained by subtracting the initial value from the reached value.

If the determination is affirmative in step S2, the process proceeds to step S3. In step S3, the controller 13 sets the target rotational speed Nept of the first oil pump 10 to the second target rotational speed Nep2. The second target rotation speed Nep2 is a rotation speed that is set when the determination conditions of step S1 and step S2 are satisfied, that is, when the increase instruction of the rotation speed Nep and the line instruction pressure PLi overlap, and will be described later. It is set higher than the target rotational speed Nep1.

Specifically, the second target rotational speed Nep2 increases to a value higher than the first target rotational speed Nep1 before the line actual pressure PLr reaches the line command pressure PLi. Is set as follows. The second target rotation speed Nep2 can be set in advance according to the state of the vehicle and the set time Ts, for example. The second target rotation speed Nep2 may be a constant value.

In step S4, the controller 13 determines whether or not the difference ΔPL between the line actual pressure PLr and the line command pressure PLi is less than a predetermined value α. Specifically, the difference ΔPL can be a value obtained by subtracting the line actual pressure PLr from the line command pressure PLi.

The predetermined value α is a value regarding the timing at which the line actual pressure PLr reaches the line command pressure PLi, and can be set in advance by experiments or the like. With the predetermined value α, it is possible to detect the timing before the line actual pressure PLr becomes the line command pressure PLi in consideration of control responsiveness and the like. For this reason, the predetermined value α can be set to a value larger than zero, for example. The predetermined value α may be zero.

In step S4, the controller 13 may determine whether or not the set time Ts has elapsed since the instruction to increase the line command pressure PLi. The set time Ts is set as a time during which the magnitude of the difference ΔPL is less than the predetermined value α after an instruction to increase the line command pressure PLi. The set time Ts can be set in advance by experiments or the like. The set time Ts may be measured and set for each workpiece on the production line, for example.

The controller 13 may store the time during which the magnitude of the difference ΔPL is less than the predetermined value α after giving an instruction to increase the line command pressure PLi, and may set the set time Ts based on the stored time. That is, the controller 13 may learn the set time Ts. The set time Ts can be set to, for example, the latest value, minimum value, or calculated value of the stored time. The initial value of the set time Ts may be set in advance.

When learning the set time Ts, the controller 13 determines the rotational speed Ne, which is the operating state of the engine 1, the oil temperature OLT of the automatic transmission 15, the initial value of the line command pressure PLi at the time of an increase command, and the line at the time of a command to increase. Time can be stored in accordance with at least one of the reached values of the command pressure PLi. This is because, when these change, the time can also change. If a negative determination is made in step S4, the process returns to step S3.

Thus, until the magnitude of the difference ΔPL becomes less than the predetermined value α, as a result of the negative determination in step S4, the rotation speed Nep is controlled to be the second target rotation speed Nep2. As a result, before the line actual pressure PLr reaches the line command pressure PLi, the rotation speed Nep is controlled to rise to a value higher than the first target rotation speed Nep1.

  If the magnitude of the difference ΔPL is less than the predetermined value α, an affirmative determination is made in step S4, and the process proceeds to step S5. In step S5, the controller 13 sets the target rotational speed Nept of the first oil pump 10 to the first target rotational speed Nep1. The first target rotational speed Nep1 is a set value, specifically, the following rotational speed.

  That is, the required flow rate of the first oil pump 10 is obtained by subtracting the flow rate of the second oil pump 11 from the required flow rate of the entire hydraulic control circuit 12, and the required discharge amount of the first oil pump 10 depends on the required flow rate. Determined. Therefore, the first target rotation speed Nep1 is specifically a rotation speed according to the required discharge amount.

  Following the affirmative determination in step S4, when the process proceeds to step S5, the rotational speed Nep is lowered to the first target rotational speed Nep1. In addition, also when it is negative determination by step S2, a process progresses to step S5. After step S5, the process of this flowchart is once ended.

  The controller 13 is a control device for the automatic transmission 15 including the first oil pump 10, and performs the process of step S3 following the affirmative determination of step S2 and the negative determination of step S4, and the step following the affirmative determination of step S4. By performing the process of S5, it functions as a control unit. The controller 13 has a control unit by functioning as a control unit. It may be understood that the control device for the automatic transmission 15 further includes the hydraulic control circuit 12 and the sensor / switch group 14.

  Next, main effects of the controller 13 will be described.

  FIG. 5A is a diagram illustrating an example of a timing chart corresponding to the control performed by the controller 13. FIG. 5B is a diagram illustrating a comparative example of FIG. 5A, and illustrates a case where an instruction to increase the rotational speed Nep to the first target rotational speed Nep1 is continued.

  5A and 5B show the supply flow rate of the first oil pump 10 as the pump flow rate. Regarding the pump flow rate, the solid line indicates the actual pump flow rate Qep corresponding to the rotation speed Nep, and the broken line indicates the target pump flow rate Qept corresponding to the target rotation speed Nept. The pump flow rate Qep1 is a target pump flow rate corresponding to the first target rotation speed Nep1, and the pump flow rate Qep2 is a target pump flow rate corresponding to the second target rotation speed Nep2.

5A and 5B, as can be seen from the change in the target pump flow rate Qept, the rotation of the first oil pump 10 starts to rise at the timing T1. The line command pressure PLi is also commanded to increase at timing T1. Such an increase instruction of the line instruction pressure PLi may be performed in the following cases, for example.

That is, the amount of oil supplied to the first oil pump 10 is increased, for example, when the accelerator pedal is depressed or when the engine 1 is started. In these cases, in order to respond to an increase in engine torque or to start shifting, an instruction to increase the line command pressure PLi may be given.

5A and 5B, the difference ΔPL between the line actual pressure PLr and the line command pressure PLi.
Is less than the predetermined value α at timing T2. Therefore, the time between the timing T1 and the timing T2 corresponds to the set time Ts.

In the comparative example shown in FIG. 5B, as can be seen from the change in the target pump flow rate Qept, the target rotational speed Nept is kept at the first target rotational speed Nep1 from the timing T1. As a result, when a hydraulic surge occurs due to the rise of the rotation of the first oil pump 10 and an instruction to increase the line command pressure PLi, an overshoot of the line pressure PL is greatly generated. In addition, since the target rotation speed Nept remains at the first target rotation speed Nep1, the gradient of change in the actual pump flow rate Qep continues to be positive after the timing T2.

In the case of the present embodiment shown in FIG. 5A, the controller 13 determines the actual line pressure P, as can be seen from the timing T1 ′ after the instruction to increase the line instruction pressure PLi at the timing T1.
Before Lr reaches the line command pressure PLi, the rotation speed Nep is changed to the first target rotation speed Nep1.
To a higher value. Further, the controller 13 thereafter decreases the rotational speed Nep to the first target rotational speed Nep1 as can be seen from the change in the actual pump flow rate Qep after the timing T2.

According to the controller 13 having such a configuration, the line actual pressure PLr is changed to the line command pressure PLi.
By increasing the rotational speed Nep to a value higher than the first target rotational speed Nep1 before reaching, the rotational speed increase rate can be increased. For this reason, a delay in the rise of the line pressure PL can be suppressed. At this time, since the line actual pressure PLr does not reach the line command pressure PLi, the line actual pressure P is temporarily caused by the control of the rotational speed Nep.
Even if a hydraulic surge that causes a convex S portion in the change in Lr occurs, the line actual pressure PLr can be suppressed to be lower than the line command pressure PLi.

  Furthermore, according to the controller 13 having such a configuration, the rotational speed Nep is then lowered to the first target rotational speed Nep1, so that the gradient of the change in the actual pump flow rate Qep can be made negative. Therefore, the supply flow rate of the first oil pump 10 can be reduced. As a result, as can be seen from the following equation 1, the peak value of the hydraulic surge can be suppressed.

[Formula 1]
dP / dt = K (Qin−Qout) / V
In Equation 1, “P” is the actual line pressure PLr, “t” is the time, “K” is the bulk modulus, “Qin” is the oil supply flow rate to the line pressure oil passage 124, and “Qout”. Indicates the flow rate of oil outflow from the line pressure oil passage 124, and “V” indicates the volume of the line pressure oil passage 124.

  When the rotational speed Nep is lowered to the first target rotational speed Nep1, the supply flow rate Qin is reduced according to the equation 1, so the line pressure change rate dP / dt is reduced. For this reason, by lowering the rotational speed Nep to the first target rotational speed Nep1, the increase in the actual line pressure PLr can be suppressed, so that the peak value of the hydraulic surge can be suppressed.

  Therefore, according to the controller 13 having such a configuration, it is possible to achieve both suppression of hydraulic surge and suppression of delay in rising of the line pressure PL. Specifically, the controller 13 can improve the durability of the parts and the shift shock by suppressing the hydraulic surge (effect corresponding to claims 1 and 6).

  When the magnitude of the difference ΔPL becomes less than the predetermined value α at the timing T2, the controller 13 decreases the rotation speed Nep to the first target rotation speed Nep1.

  According to the controller 13 having such a configuration, the rotational speed Nep can be reduced at an appropriate timing in order to achieve both suppression of the hydraulic surge and suppression of the delay in the rise of the line pressure PL (the effect corresponding to claim 2). ).

The controller 13 can be configured to reduce the rotational speed Nep to the first target rotational speed Nep1 after the set time Ts has elapsed since the instruction to increase the line command pressure PLi.

According to the controller 13 having such a configuration, the rotational speed Nep can be controlled without detecting in real time that the magnitude of the difference ΔPL has become less than the predetermined value α. For this reason, it is possible to prevent a situation in which the control of the rotational speed Nep is not in time for the hydraulic surge generated in an extremely short time in response to the start of rotation of the first oil pump 10 or the increase instruction of the line instruction pressure PLi. (Effect corresponding to claim 3).

The controller 13 may be configured to store a time during which the magnitude of the difference ΔPL is less than the predetermined value α after giving an instruction to increase the line command pressure PLi, and to set the set time Ts based on the stored time. it can.

  According to the controller 13 having such a configuration, the set time Ts can be appropriately set even if the automatic transmission 15 varies in individual differences. Therefore, even if there is a variation in individual differences in the automatic transmission 15, the rotational speed Nep can be appropriately controlled (effect corresponding to claim 4).

The controller 13 determines the time according to the rotation speed Ne, the oil temperature OLT of the automatic transmission 15, the initial value when the line command pressure PLi is instructed to increase, or the reached value when the line command pressure PLi is instructed to increase. It can be set as the structure which memorize | stores.

  According to the controller 13 having such a configuration, even if the set time Ts varies due to these factors, the rotation speed Nep can be appropriately controlled by appropriately setting the set time Ts ( Effect corresponding to claim 5).

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  In the embodiment described above, the case where the hydraulic pressure in the automatic transmission 15 is the line pressure PL has been described. However, the hydraulic pressure in the automatic transmission 15 may be PRI pressure or SEC pressure, for example.

  In the embodiment described above, the case where the automatic transmission 15 includes the variator 3 has been described. However, the automatic transmission 15 may be configured to include, for example, a stepped automatic transmission mechanism, that is, a so-called automatic transmission. The variator 3 may be, for example, a toroidal continuously variable transmission mechanism.

  In the above-described embodiment, the case where the engine 1 is a drive source has been described. However, the drive source may be, for example, the motor, the engine 1, and the motor.

  In the embodiment described above, the case where the controller 13 has a control unit has been described. However, the control unit may be configured by a plurality of controllers, for example.

1 Engine (drive source)
3 Variator 10 1st oil pump (electric oil pump)
11 Second oil pump 12 Hydraulic control circuit 13 Controller (control unit)
15 Automatic transmission

Claims (6)

A control device for an automatic transmission comprising an electric oil pump,
Wherein after up indication hydraulic indicated pressure in the automatic transmission, after the actual pressure of the hydraulic pressure is raised to a value higher than the set value the speed of the electric oil pump before reaching the command pressure, the controller magnitude of the difference between the actual pressure and the command pressure is that started down toward the set point rotational speed of the electric oil pump at the timing becomes less than a predetermined value,
A control device for an automatic transmission, comprising: The automatic transmission control device according to claim 1,
Wherein the control unit determines that the magnitude of the difference between the actual pressure and the command pressure is by detecting that less than the predetermined value, becomes the timing,
A control device for an automatic transmission. The automatic transmission control device according to claim 1 ,
The control unit determines that the timing has been reached by detecting that a set time has elapsed since the instruction to increase the command pressure.
A control device for an automatic transmission. A control device for an automatic transmission according to claim 3,
The control unit stores a time during which the magnitude of the difference between the actual pressure and the command pressure is less than the predetermined value after giving an instruction to increase the command pressure, and sets the set time based on the stored time. Set
A control device for an automatic transmission. The automatic transmission control device according to claim 4,
The control unit is configured such that an operating state of a drive source of a vehicle including the automatic transmission, an oil temperature of the automatic transmission, an initial value when the instruction pressure is instructed to increase, or an instruction to increase the instruction pressure. The time is stored according to the reached value of
A control device for an automatic transmission. A method for controlling an automatic transmission including an electric oil pump,
After the instruction to increase the command pressure of the hydraulic pressure in the automatic transmission, the rotational speed of the electric oil pump is increased to a value higher than a set value before the actual pressure of the hydraulic pressure reaches the command pressure;
After increasing the rotational speed of the electric oil pump to a value higher than the set value, the rotational speed of the electric oil pump at a timing when the magnitude of the difference between the actual pressure and the command pressure becomes less than a predetermined value. the lowered toward the set value, including Rukoto,
A control method for an automatic transmission, comprising:

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