WO2016043071A1

WO2016043071A1 - Vehicle hydraulic control device

Info

Publication number: WO2016043071A1
Application number: PCT/JP2015/075241
Authority: WO
Inventors: 行宣犬田; 秀策片倉; 清水　豊
Original assignee: 日産自動車株式会社; ジヤトコ株式会社
Priority date: 2014-09-17
Filing date: 2015-09-04
Publication date: 2016-03-24
Also published as: JPWO2016043071A1; JP6265273B2

Abstract

The purpose of the present invention is to provide a vehicle hydraulic control device designed to achieve both oil pressure supply to the gear change mechanism and cooling of the gear change mechanism when the mechanical oil pump is stopped while being able to improve ease of installation on a vehicle and cost reduction. The vehicle hydraulic control device is provided with: a first oil pressure supply oil path (102) for supplying oil discharged from a mechanical oil pump (O/P), which is operated by a motor/generator (MG), to a line pressure control valve (101); a second oil pressure supply oil path (103) for supplying oil discharged from an electric oil pump (M/O/P), which is operated by a submotor (S/M), to the line pressure control valve (101); a cooling system oil path (104) for supplying oil discharged from the electric oil pump (M/O/P) to a cooling/lubrication system (Lub) of a gear change mechanism; and a switching valve (106) for connecting an electric oil pump discharge oil path (105) to either the second oil pressure supply oil path (103) or the cooling system oil path (104).

Description

Hydraulic control device for vehicle

The present invention relates to a vehicle hydraulic control device including a mechanical oil pump operated by a traveling drive source and an electric oil pump operated by an electric motor.

Conventionally, in order to avoid stopping the supply of hydraulic pressure to the hydraulic system for the speed change mechanism by stopping the mechanical oil pump operated by the travel drive source along with the stop of the travel drive source, 2. Description of the Related Art A vehicle hydraulic control device that includes an electric oil pump that is operated by an electric motor different from a travel drive source is known (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 10-324177

By the way, in the conventional vehicle hydraulic control device, the hydraulic oil discharged from the electric oil pump is supplied to the transmission mechanism hydraulic system. That is, the hydraulic oil discharged from the electric oil pump does not flow directly to the cooling / lubricating system of the transmission mechanism.
For this reason, in order to perform clutch cooling in a scene where the clutch of the transmission mechanism generates heat, such as starting uphill or advancing the accelerator, for example, the transmission mechanism is separate from the electric oil pump that supplies hydraulic pressure instead of the mechanical oil pump. It is conceivable to provide a second electric oil pump that directly supplies hydraulic pressure to the cooling / lubricating system.
However, in this case, two electric oil pumps for supplying hydraulic pressure and cooling / lubricating are provided, which causes problems that the on-vehicle performance of the electric oil pump is reduced and the cost is increased.

The present invention has been made paying attention to the above-mentioned problem, and it is possible to improve the on-board performance and reduce the cost while ensuring both the oil pressure of the transmission mechanism and the cooling function of the transmission mechanism when the mechanical oil pump is stopped. An object of the present invention is to provide a vehicular hydraulic control device.

To achieve the above object, a vehicle hydraulic control apparatus according to the present invention includes a mechanical oil pump, an electric oil pump, a line pressure control valve, a first hydraulic supply oil path, a second hydraulic supply oil path, A cooling system oil passage and a switching valve are provided.
The mechanical oil pump is an oil pump operated by a traveling drive source.
The electric oil pump is an oil pump that is operated by an electric motor different from the travel drive source.
The line pressure control valve regulates the line pressure supplied to the transmission mechanism hydraulic system.
The first hydraulic supply oil passage supplies hydraulic oil discharged from a mechanical oil pump to an input port of a line pressure control valve.
The second hydraulic supply oil passage supplies hydraulic oil discharged from the electric oil pump to an input port of the line pressure control valve.
The cooling system oil passage supplies hydraulic oil discharged from the electric oil pump to the cooling / lubricating system of the transmission mechanism.
The switching valve is provided in a discharge oil passage of the electric oil pump, and connects the discharge oil passage to one of the second hydraulic supply oil passage and the cooling system oil passage.

Therefore, in the vehicle hydraulic control apparatus of the present invention, the discharge oil path of the electric oil pump operated by an electric motor different from the travel drive source is used to supply the hydraulic oil discharged from the electric oil pump using the switching valve. Connected to either the second hydraulic supply oil passage that supplies to the input port of the line pressure control valve or the cooling oil passage that supplies hydraulic oil discharged from the electric oil pump to the cooling / lubricating system of the transmission mechanism can do.
Therefore, when the hydraulic oil supply request to the transmission hydraulic system is generated because the mechanical oil pump is stopped along with the stop of the travel drive source, the switching oil is supplied to the discharge oil passage of the electric oil pump by the switching valve. Connect to the oil passage. As a result, the hydraulic oil discharged from the electric oil pump is regulated to the line pressure by the line pressure control valve and then supplied to the transmission mechanism hydraulic system, thereby ensuring the necessary hydraulic pressure of the transmission mechanism hydraulic system. it can.
On the other hand, when a cooling request for the transmission mechanism is generated, the discharge oil passage of the electric oil pump is connected to the cooling system oil passage by the switching valve. As a result, the hydraulic oil discharged from the electric oil pump is directly supplied to the cooling / lubricating system of the transmission mechanism, and the flow rate (oil amount) of the hydraulic oil flowing through the cooling / lubricating system of the transmission mechanism is increased. Cooling can be performed quickly.
That is, the oil pressure securing of the speed change mechanism and the cooling function of the speed change mechanism when the mechanical oil pump is stopped can be achieved by one electric oil pump and the switching valve. As a result, it is possible to improve the onboard performance and reduce the cost while ensuring both the oil pressure of the transmission mechanism when the mechanical oil pump is stopped and the cooling function of the transmission mechanism.

1 is an overall system diagram illustrating a hybrid vehicle to which a hydraulic control device according to a first embodiment is applied. FIG. 2 is a hydraulic circuit diagram illustrating a hydraulic control circuit included in the hybrid vehicle according to the first embodiment. 6 is a flowchart illustrating a flow of a switching valve hydraulic pressure supply → cooling / lubrication switching process executed in the first embodiment. It is explanatory drawing which shows the structure of a line pressure control valve. It is a map which shows the deviation | shift amount of a target line pressure and an actual line pressure with respect to the supply oil amount change speed to a line pressure control valve. 6 is a flowchart showing a flow of a switching valve cooling / lubrication → hydraulic supply switching process executed in the first embodiment. It is explanatory drawing which shows the operation | movement of a switching valve when the switching valve is switched to the hydraulic pressure supply side, and the flow of hydraulic fluid. It is explanatory drawing which shows the operation | movement of a switching valve when the switching valve is switched to the cooling side, and the flow of hydraulic fluid. In the hydraulic control apparatus according to the first embodiment, a time chart showing the characteristics of the accelerator opening, the vehicle speed, the CL2 temperature (second clutch temperature), the cooling flag, and the hydraulic pressure supply flag when the switching valve is switched from the hydraulic pressure supply side to the cooling side. It is. In the hydraulic control apparatus according to the first embodiment, the mechanical oil pump rotational speed, the hydraulic system supply oil amount for the transmission mechanism, the electric oil pump discharge oil amount, and the mechanical oil pump discharge when the switching valve is switched from the hydraulic supply side to the cooling side. It is a time chart which shows each characteristic of an oil quantity and a switching valve state. In the hydraulic control apparatus according to the first embodiment, the time chart showing the characteristics of the accelerator opening, the vehicle speed, the CL2 temperature (second clutch temperature), the cooling flag, and the hydraulic pressure supply flag when the switching valve is switched from the cooling side to the hydraulic pressure supply side. It is. In the hydraulic control apparatus according to the first embodiment, the mechanical oil pump rotational speed, the hydraulic system supply oil amount for the transmission mechanism, the electric oil pump discharge oil amount, and the mechanical oil pump discharge when the switching valve is switched from the cooling side to the hydraulic supply side It is a time chart which shows each characteristic of an oil quantity and a switching valve state.

Hereinafter, a mode for carrying out the vehicle hydraulic control apparatus of the present invention will be described based on Example 1 shown in the drawings.

(Example 1)
First, the configuration of the vehicle hydraulic control apparatus according to the first embodiment is described as “overall system configuration of hybrid vehicle”, “detailed configuration of hydraulic control circuit”, “hydraulic supply → cooling / lubrication switching processing configuration”, “cooling / lubrication → The description will be divided into “hydraulic supply switching processing configuration”.

[Overall system configuration of hybrid vehicle]
FIG. 1 is an overall system diagram illustrating a hybrid vehicle (an example of a vehicle) to which the control device according to the first embodiment is applied. Hereinafter, the overall system configuration of the hybrid vehicle according to the first embodiment will be described with reference to FIG.

The vehicle hydraulic control apparatus according to the first embodiment is applied to the hybrid vehicle shown in FIG. The drive system of this hybrid vehicle includes an engine Eng, a first clutch CL1, a motor / generator MG, a second clutch CL2, a continuously variable transmission CVT, a final gear FG, a left drive wheel LT, and a right drive. And a wheel RT.

The engine Eng is a lean burnable internal combustion engine, and the engine torque matches the command value by controlling the intake air amount by the throttle actuator, controlling the fuel injection amount by the injector, and controlling the ignition timing by the spark plug. To be controlled.

The first clutch CL1 is a frictional engagement element interposed at a position between the engine Eng and the motor / generator MG. The first clutch CL1 is operated by a hydraulic actuator that is operated by the hydraulic pressure of the hydraulic oil. For example, a dry clutch that is in a released state (normally open) when no hydraulic pressure is applied by a biasing force of a diaphragm spring is used.
The first clutch CL1 controls between the engine Eng and the motor / generator MG to be in a fully engaged / slip engaged / released state depending on the hydraulic pressure applied to the hydraulic actuator. The first clutch CL1 transmits motor torque and engine torque to the second clutch CL2 when fully engaged, and transmits only motor torque to the second clutch CL2 when released.
The complete engagement / slip engagement / release control of the first clutch CL1 is performed by stroke control for the hydraulic actuator.

The motor / generator MG is a three-phase AC permanent magnet synchronous motor that serves as a driving source. The motor / generator MG performs drive torque control and rotation speed control when starting and running. The motor / generator MG performs regenerative braking control during braking or deceleration, and recovers vehicle kinetic energy to the battery BAT.

The second clutch CL2 is a frictional engagement element interposed between the motor / generator MG and the left and right drive wheels LT, RT. Here, the second clutch CL2 is composed of a wet multi-plate friction clutch operated by hydraulic oil pressure (second clutch hydraulic pressure), and complete engagement / slip engagement / release is controlled by the magnitude of the second clutch hydraulic pressure. The
The second clutch CL2 of the first embodiment uses the forward clutch FC and the reverse brake RB provided in the forward / reverse switching mechanism of the continuously variable transmission CVT using planetary gears. That is, during forward travel, the forward clutch FC is the second clutch CL2, and during reverse travel, the reverse brake RB is the second clutch CL2.

The continuously variable transmission CVT is a belt type continuously variable transmission having a primary pulley Pri, a secondary pulley Sec, and a pulley belt V stretched between the primary pulley Pri and the secondary pulley Sec. The primary pulley Pri and the secondary pulley Sec each change the pulley width by supplying hydraulic pressure, and change the diameter of the surface sandwiching the pulley belt V to freely control the gear ratio (pulley ratio).

Furthermore, the input gear of the mechanical oil pump O / P is connected to the motor output shaft MGout of the motor / generator MG via the chain CH. The mechanical oil pump O / P is an oil pump that is operated by the rotational driving force of the motor / generator MG. For example, a gear pump or a vane pump is used. The mechanical oil pump O / P can discharge oil regardless of the rotation direction of the motor / generator MG. Further, here, as the oil pump, an electric oil pump M / O / P that is operated by the rotational driving force of the sub motor S / M is provided. The sub motor S / M is an electric motor provided separately from the motor / generator MG.

The mechanical oil pump O / P and the electric oil pump M / O / P are used to supply hydraulic pressure (control pressure) to be supplied to the first and second clutches CL1 and CL2 and the continuously variable transmission CVT. It is OIL. In this hydraulic supply source OIL, when the amount of oil discharged from the mechanical oil pump O / P is sufficient, the sub motor S / M is stopped and the electric oil pump M / O / P is stopped. Also, when the discharge oil amount of the mechanical oil pump O / P decreases, the sub motor S / M is driven to operate the electric oil pump M / O / P, and this electric oil pump M / O / P also operates. Let the oil discharge.
A three-phase AC permanent magnet synchronous motor capable of controlling the motor speed is used as the sub motor S / M.

In this hybrid vehicle, the first clutch CL1, the motor / generator MG, and the second clutch CL2 constitute a one-motor / two-clutch hybrid drive system. The main drive modes of this system are “EV mode” and “HEV”. Mode ".
The “EV mode” is an electric vehicle mode in which the first clutch CL1 is released, the second clutch CL2 is engaged, and only the motor / generator MG is used as a drive source.
The “HEV mode” is a hybrid vehicle mode in which the first and second clutches CL1 and CL2 are engaged and the engine Eng and the motor / generator MG are used as drive sources.

As shown in FIG. 1, the control system of the hybrid vehicle of the first embodiment includes an inverter INV, a battery BAT, an integrated controller 10, a transmission controller 11, a clutch controller 12, an engine controller 13, and a motor controller 14. And a battery controller 15.

The inverter INV converts a direct current supplied from the battery BAT into a three-phase alternating current supplied to the motor / generator MG, and generates a drive current for the motor / generator MG. Further, the output rotation of the motor / generator MG is reversed by reversing the phase of the generated drive current. Further, when the motor / generator MG is regenerated, the three-phase alternating current is converted into direct current.

The battery BAT is a chargeable / dischargeable secondary battery, and supplies power to the motor / generator MG and charges power regenerated by the motor / generator MG.

The integrated controller 10 includes a battery state (here, input from the battery controller 15), an accelerator opening (here, detected by the accelerator opening sensor 21), and a vehicle speed (here, a value synchronized with the transmission output speed). , Detected by the transmission output speed sensor 22). Based on the result, command values for the actuators (motor / generator MG, engine Eng, first clutch CL1, second clutch CL2, continuously variable transmission CVT) are calculated and transmitted to the controllers 11-15. .
The integrated controller 10 controls the discharge oil amount of the mechanical oil pump O / P, the discharge oil amount of the electric oil pump M / O / P, the line pressure control valve 101, and the switching valve 106 described later. The circuit control means to perform. That is, in this integrated controller 10, when the sub-motor S / M is driven to operate the electric oil pump M / O / P, the amount of oil discharged from the mechanical oil pump O / P (from the detection value of the motor rotation speed sensor 23). The rotational speed of the electric oil pump M / O / P is controlled according to the calculation. Further, the switching control of the switching valve 106 is performed according to the temperature of the second clutch CL2 (detected by the clutch temperature sensor 24) and the amount of oil discharged from the mechanical oil pump O / P.

The transmission controller 11 performs shift control so as to achieve a shift command from the integrated controller 10. This shift control is performed by controlling the hydraulic pressure supplied to the primary pulley Pri of the continuously variable transmission CVT and the hydraulic pressure supplied to the secondary pulley Sec using the line pressure supplied via the hydraulic control circuit 100 as a source pressure. Done.
The surplus pressure generated when the hydraulic pressure supplied from the line pressure to the primary pulley Pri and the hydraulic pressure supplied to the secondary pulley Sec is generated is used for cooling and lubrication of the first clutch CL1 and the second clutch CL2.

The clutch controller 12 includes a second clutch input rotational speed (detected by the motor rotational speed sensor 23), a second clutch output rotational speed (detected by the second clutch output rotational speed sensor 25), a clutch oil temperature (operating oil temperature sensor 26). Detected by). Further, the clutch controller 12 performs first clutch control and second clutch control so as to achieve the first clutch control command and the second clutch control command from the integrated controller 10. The first clutch control is performed by controlling the hydraulic pressure supplied to the first clutch CL1 using the line pressure supplied via the hydraulic control circuit 100 as a source pressure. The second clutch control is performed by controlling the hydraulic pressure supplied to the second clutch CL2 using the line pressure supplied via the hydraulic control circuit 100 as a source pressure.
The excess pressure generated when the hydraulic pressure supplied from the line pressure to the first clutch CL1 and the hydraulic pressure supplied to the second clutch CL2 is generated is used for cooling and lubrication of the first clutch CL1 and the second clutch CL2. Turned.

A circuit for supplying a control hydraulic pressure using the line pressure PL as a source pressure to the primary pulley Pri, the secondary pulley Sec, and the second clutch CL2 of the continuously variable transmission CVT is referred to herein as a “transmission mechanism hydraulic system Sup”. . A circuit for cooling and lubricating the second clutch CL2 is referred to herein as a “transmission mechanism cooling / lubricating system Lub”.

The engine controller 13 inputs the engine speed (detected by the engine speed sensor 27) and performs engine torque control so as to achieve an engine torque command value corresponding to the target engine torque from the integrated controller 10.

The motor controller 14 controls the motor / generator MG so as to achieve a motor torque command value and a motor rotation speed command value corresponding to the target motor torque from the integrated controller 10.

The battery controller 15 manages the state of charge of the battery BAT and transmits the information to the integrated controller 10. Note that the state of charge of the battery BAT is calculated based on the power supply voltage detected by the battery voltage sensor 15a and the battery temperature detected by the battery temperature sensor 15b.

[Detailed configuration of hydraulic control circuit]
FIG. 2 is a hydraulic circuit diagram illustrating a hydraulic control circuit included in the hybrid vehicle according to the first embodiment. The detailed configuration of the hydraulic control circuit according to the first embodiment will be described below with reference to FIG.

The hydraulic control circuit 100 regulates the discharge pressure of a hydraulic pressure supply source OIL composed of a mechanical oil pump O / P and an electric oil pump M / O / P to a line pressure PL, and supplies the line pressure PL to a hydraulic system Sup for a transmission mechanism. Further, in the hydraulic control circuit 100, surplus pressure generated when hydraulic fluid is supplied to the transmission mechanism hydraulic system Sup is supplied to the cooling / lubricating system Lub of the transmission mechanism. Further, in the hydraulic control circuit 100, by switching the switching valve 106, the hydraulic oil discharged from the electric oil pump M / O / P is directly supplied to the cooling / lubricating system Lub of the transmission mechanism.
That is, as shown in FIG. 2, the hydraulic control circuit 100 according to the first embodiment includes a mechanical oil pump O / P, an electric oil pump M / O / P, a line pressure control valve 101, and a first hydraulic supply oil. A passage 102, a second hydraulic supply oil passage 103, a cooling system oil passage 104, an electric oil pump discharge oil passage 105, and a switching valve 106 are provided.

In the mechanical oil pump O / P, the first hydraulic supply oil passage 102 is connected to the discharge port 110a, and the suction circuit 108 is connected to the suction port 110b. The tip of the suction circuit 108 is inserted into the strainer 107. The mechanical oil pump O / P operates when the motor / generator MG is driven to rotate, sucks the hydraulic oil stored in the strainer 107 via the suction circuit 108, and enters the first hydraulic supply oil passage 102. Discharge hydraulic fluid. The discharge pressure at this time depends on the rotation speed of the motor / generator MG.

The electric oil pump M / O / P has an electric oil pump discharge oil passage 105 connected to the discharge port 111a and a suction circuit 108 connected to the suction port 111b. The tip of the suction circuit 108 is inserted into the strainer 107. The electric oil pump M / O / P operates when the sub motor S / M rotates, sucks in the hydraulic oil stored in the strainer 107 via the suction circuit 108, and supplies the electric oil pump discharge oil path 105. And discharge hydraulic oil. The discharge pressure at this time depends on the rotation speed of the sub motor S / M.

The line pressure control valve 101 uses the discharge pressure of the hydraulic supply source OIL (the discharge pressure of the mechanical oil pump O / P and / or the discharge pressure of the electric oil pump M / O / P) as a source pressure for the transmission mechanism. This is a pressure regulating valve that regulates the line pressure PL supplied to the hydraulic system Sup.
That is, the line pressure control valve 101 has a line pressure circuit connected to the input port 101a to the first hydraulic supply oil passage 102 and the second hydraulic supply oil passage 103, and to the output port 101b to the transmission mechanism hydraulic system Sup. 101c is connected. In the line pressure control valve 101, the spool is moved in accordance with an instruction value from the integrated controller 10, and hydraulic fluid supplied from the first hydraulic supply oil passage 102 and / or the second hydraulic supply oil passage 103 is drained (not shown). Line pressure PL is regulated by letting it escape to the circuit.
The line pressure circuit 101c is provided with a pressure regulating valve 101d so that the excess pressure obtained by subtracting the hydraulic pressure required for the transmission hydraulic system Sup from the line pressure PL is released to the cooling / lubricating system Lub of the transmission mechanism. It has become.

The first hydraulic supply oil passage 102 has one end connected to the discharge port 110a of the mechanical oil pump O / P and the other end connected to the input port 101a of the line pressure control valve 101. The first hydraulic supply oil passage 102 supplies the hydraulic oil discharged from the mechanical oil pump O / P to the input port 101 a of the line pressure control valve 101. A first check valve 102 a is provided at an intermediate portion of the first hydraulic supply oil passage 102. The first check valve 102a is a valve that prevents hydraulic fluid from flowing from the line pressure control valve 101 side to the mechanical oil pump O / P side.

The second hydraulic pressure supply oil passage 103 has one end connected to the hydraulic pressure supply side port 106 a of the switching valve 106 and the other end connected to the input port 101 a of the line pressure control valve 101. The second hydraulic supply oil passage 103 supplies the hydraulic oil discharged from the electric oil pump M / O / P to the input port 101 a of the line pressure control valve 101. A second check valve 103 a is provided at an intermediate portion of the second hydraulic supply oil passage 103. The second check valve 103a is a valve that prevents hydraulic fluid from flowing from the line pressure control valve 101 side to the electric oil pump M / O / P side.

One end of the cooling system oil passage 104 is connected to the cooling side port 106b of the switching valve 106, and the other end is connected to the cooling / lubricating system Lub of the transmission mechanism. The cooling system oil passage 104 supplies hydraulic oil discharged from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism.
The hydraulic fluid used in the cooling / lubricating system Lub of the transmission mechanism is collected by the strainer 107 via the drain circuit 109.

The electric oil pump discharge oil passage 105 has one end connected to the discharge port 110 a of the electric oil pump M / O / P and the other end connected to the input port 106 c of the switching valve 106. The electric oil pump discharge oil passage 105 supplies the hydraulic oil discharged from the electric oil pump M / O / P to the second hydraulic supply oil passage 103 or the cooling system oil passage 104 via the switching valve 106.
The electric oil pump discharge oil passage 105 is provided with a pressure sensor 28 for detecting the discharge pressure of the electric oil pump M / O / P and a pressure leak valve 105a. When the discharge pressure of the electric oil pump M / O / P monitored by the pressure sensor 28 reaches a predetermined upper limit pressure, the pressure leak valve 105a is opened so that the pressure in the electric oil pump discharge oil passage 105 is released. It has become.

The switching valve 106 is provided in the electric oil pump discharge oil passage 105, and the electric oil pump discharge oil passage 105 is connected to the second hydraulic supply oil passage 103 and the cooling system oil passage 104 based on a switching command from the integrated controller 10. And connect to either one.
In other words, the switching valve 106 is a switching valve in which the communication destination of the input port 106c is switched by an on / off solenoid. The path 105 is connected to the second hydraulic supply oil path 103. Further, when the input port 106 c of the switching valve 106 is communicated with the cooling side port 106 b, the electric oil pump discharge oil passage 105 is connected to the cooling system oil passage 104.

The transmission mechanism hydraulic system Sup includes a transmission pressure regulating valve 112a provided in the line pressure circuit 101c and a second clutch pressure regulating valve 112b provided in the line pressure circuit 101c. The transmission pressure regulating valve 112a regulates the hydraulic pressure supplied to the primary pulley Pri and the secondary pulley Sec using the line pressure PL as the original pressure, and supplies the hydraulic pressure to the primary pulley Pri and the secondary pulley Sec. . Further, the hydraulic pressure supplied to the forward clutch FC and the reverse brake RB is adjusted by the second clutch pressure adjusting valve 112b with the line pressure PL as the original pressure, and the hydraulic pressure is supplied to the forward clutch FC and the reverse brake RB. The

[Hydraulic supply → Cooling / lubrication switching processing configuration]
FIG. 3 is a flowchart showing a flow of the switching valve hydraulic pressure supply → cooling / lubrication switching process executed in the first embodiment. Hereinafter, the hydraulic pressure supply → cooling / lubrication switching processing configuration of the first embodiment will be described with reference to FIG.

In step S1, the electric oil pump M / O / P is activated, and whether or not the electric oil pump discharge oil passage 105 is connected to the second hydraulic supply oil passage 103 by the switching valve 106, that is, the electric oil pump M It is determined whether or not hydraulic pressure is supplied from / O / P to the transmission mechanism hydraulic system Sup. If YES (electric oil pump ON, switching valve = hydraulic supply side), the process proceeds to step S2. In the case of NO (electric oil pump NO or switching valve = cooling side), since hydraulic pressure is not supplied from the electric oil pump M / O / P to the transmission mechanism hydraulic system Sup, hydraulic pressure supply → cooling / lubrication switching Since it is not necessary to perform processing, the process proceeds to the end.

In step S2, following the determination that the electric oil pump is ON and the switching valve = hydraulic supply side in step S1, it is determined whether or not the temperature of the second clutch CL2 exceeds a predetermined cooling threshold. If YES (CL2 temperature ≧ cooling threshold), the process proceeds to step S3. In the case of NO (CL2 temperature <cooling threshold), cooling of the second clutch CL2 is not necessary, and it is possible to continue supplying hydraulic pressure from the electric oil pump M / O / P to the transmission mechanism hydraulic system Sup. Return to step S1.
Here, the “cooling threshold” is an upper limit temperature at which the second clutch CL2 does not break or malfunction. If the temperature of the second clutch CL2 exceeds the cooling threshold, the second clutch CL2 may be damaged, etc., so that the flow rate of the hydraulic oil flowing through the cooling / lubricating system Lub of the transmission mechanism is increased. Occurs. The temperature of the second clutch CL2 is detected by the clutch temperature sensor 24.

In step S3, following the determination that CL2 temperature ≧ cooling threshold value in step S2, it is necessary to increase the flow rate of the hydraulic oil flowing through the cooling / lubricating system Lub of the transmission mechanism due to the occurrence of the “cooling request”. The second clutch CL2 is slip-engaged and discharged from the mechanical oil pump O / P on the assumption that a command for switching the switching valve 106 to the cooling side and supplying hydraulic pressure to the cooling / lubricating system Lub of the transmission mechanism is output. The flow rate of the hydraulic oil (the amount of oil discharged from the mechanical oil pump O / P) is increased, and the process proceeds to step S4.
Here, in order to slip the second clutch CL2, the hydraulic pressure supplied to the second clutch CL2 (the forward clutch FC or the reverse brake RB) is reduced by the transmission pressure regulating valve 112a. In addition, “increasing the amount of oil discharged from the mechanical oil pump O / P” means that the rotational speed of the motor / generator MG exceeds the rotational speed determined according to the required driving force calculated from the accelerator opening and the vehicle speed. Increase the rotational speed of the mechanical oil pump O / P. That is, in this step S3, the flow rate of the hydraulic oil discharged from the mechanical oil pump O / P is increased at a speed equal to or higher than the increasing speed determined according to the required driving force. Note that since the second clutch CL2 is slip-engaged, even if the rotational speed of the motor / generator MG is increased beyond the rotational speed determined according to the required driving force, the left and right drive wheels LT, RT are not affected.

In step S4, following the CL2 = slip engagement and mechanical oil pump O / P = oil amount increase in step S3, the discharge amount of the mechanical oil pump O / P and the discharge amount of the electric oil pump M / O / P It is determined whether or not the total oil amount has reached an oil amount (= switchable oil amount) that can secure a necessary oil amount in the transmission system hydraulic system Sup. If YES (total oil amount ≧ switchable oil amount), the process proceeds to step S5. If NO (total oil amount <switchable oil amount), the required oil amount in the transmission mechanism hydraulic system Sup is not secured, and the process returns to step S3.
Here, the “switchable oil amount” is an oil amount that can prevent deterioration of power consumption due to a wasteful oil amount while ensuring the line pressure PL.

In step S5, following the determination that total oil amount ≧ switchable oil amount in step S4, assuming that the switchable oil amount is secured by the total oil amount, the operating oil discharged from the electric oil pump M / O / P The flow rate (the amount of oil discharged from the electric oil pump M / O / P) is reduced, and the process proceeds to step S6.
Here, in order to reduce the discharge oil amount of the electric oil pump M / O / P, the rotation speed of the sub-motor S / M is decreased and the rotation speed of the electric oil pump M / O / P is decreased. At this time, the speed is equal to or higher than the reduction speed determined according to the required driving force, and the total oil amount of the discharge amount of the mechanical oil pump O / P and the discharge oil amount of the electric oil pump M / O / P is Reduce the discharge oil amount of the electric oil pump M / O / P at a speed that does not fall below the oil amount necessary to secure the line pressure PL.

In step S6, following the electric oil pump M / O / P = oil amount decrease in step S5, it is determined whether or not the discharge oil amount of the electric oil pump M / O / P is equal to or less than a predetermined first threshold value. . If YES (electric oil pump discharge oil amount ≦ first threshold), the process proceeds to step S7. If NO (electric oil pump discharge oil amount> first threshold value), the process returns to step S4.
Here, the “first threshold value” is a “pressure adjustable oil amount” that can be adjusted by the line pressure control valve 101. That is, the “first threshold value” determines the rate of change in the amount of hydraulic oil supplied to the line pressure control valve 101 immediately after switching the switching valve 106 from the hydraulic pressure supply side to the cooling side, and the switching valve 106 is switched. The undershoot amount (hydraulic pressure decrease amount) of the hydraulic pressure (line pressure PL) supplied to the transmission mechanism hydraulic system Sup is determined accordingly.

That is, the line pressure control valve 101 has an input port 101a, an output port 101b, and a drain port 101e as shown in FIG. 4A. Then, the discharge pressure of the hydraulic pressure supply source OIL is supplied to the input port 101a, and the line pressure PL is adjusted by reducing the discharge pressure of the hydraulic pressure supply source OIL using the feedback pressure from the spring 101f and the line pressure circuit 101c. Press. At this time, an orifice 101h is provided at a midway position of the feedback circuit 101g branched from the line pressure circuit 101c to alleviate the change in the feedback pressure. For this reason, when the amount of hydraulic oil supplied to the line pressure control valve 101, that is, the amount of oil discharged from the hydraulic pressure supply source OIL changes suddenly, the feedback pressure and line pressure circuit 101c is effectively reduced by the feedback pressure fluctuation mitigating action by the orifice 101h. There may be a difference between the pressure and the pressure by the line pressure control valve 101.
That is, as shown in FIG. 4B, when the oil amount change speed (supply oil amount change speed) of the hydraulic oil supplied to the line pressure control valve 101 exceeds a predetermined value α, the difference between the target line pressure and the actual line pressure. Deviation occurs. Moreover, the amount of deviation increases as the supply oil amount change rate increases. When the amount of hydraulic oil supplied to the line pressure control valve 101 decreases rapidly, the actual line pressure rapidly decreases with respect to the target line pressure, the undershoot amount increases, and the pulley belt V does not slip. It is possible that the stage transmission CVT is damaged.

On the other hand, when the switching valve 106 is switched from the hydraulic pressure supply side to the cooling side, the discharge oil of the electric oil pump M / O / P does not flow through the second hydraulic pressure supply oil passage 103 and the hydraulic oil supplied to the line pressure control valve 101. The amount of oil is reduced. Here, if the discharge oil amount of the electric oil pump M / O / P is reduced in advance before switching the switching valve 106 from the hydraulic pressure supply side to the cooling side, the line pressure control valve when the switching valve 106 is switched. The change in the amount of hydraulic oil supplied to 101 can be suppressed. That is, the “first threshold value (= pressure adjustable oil amount)” is a predetermined value representing the rate of change in the amount of oil supplied to the line pressure control valve 101 that occurs when the switching valve 106 is switched from the hydraulic pressure supply side to the cooling side. The line pressure PL is maintained at a hydraulic pressure that can prevent the slippage of the pulley belt V of the continuously variable transmission CVT by suppressing the undershoot of the line pressure PL by enabling proper pressure regulation with the line pressure control valve 101. The value to be

In step S 7, following the determination that the electric oil pump discharge oil amount ≦ the first threshold value in step S 6, the line pressure control valve 101 does not change even if the discharge oil amount of the electric oil pump M / O / P switches the switching valve 106. The control valve 106 is switched from the hydraulic pressure supply side to the cooling side, and the electric oil pump discharge oil passage 105 is cooled, assuming that the pressure is reduced below the value that suppresses the undershoot of the line pressure PL. Connect to the system oil passage 104 and proceed to Step S8. As a result, the hydraulic oil discharged from the electric oil pump M / O / P is supplied to the cooling / lubricating system Lub of the transmission mechanism.

In step S8, following the switching control with the switching valve = cooling side in step S7, the discharge oil amount of the electric oil pump M / O / P is increased, and the process proceeds to step S9.
Here, in order to increase the discharge oil amount of the electric oil pump M / O / P, the rotation speed of the sub motor S / M is increased and the rotation speed of the electric oil pump M / O / P is increased.

In step S9, following the electric oil pump M / O / P = oil amount increase in step S8, the amount of oil discharged from the electric oil pump M / O / P is the amount of oil required in the cooling / lubricating system Lub of the transmission mechanism ( == Required cooling oil amount) is determined. If YES (electric oil pump discharge oil amount ≧ cooling required oil amount), the flow proceeds to the end assuming that the oil amount necessary for cooling the second clutch CL2 and the like is secured by the electric oil pump discharge oil amount. If NO (electric oil pump discharge oil amount <cooling required oil amount), the flow returns to step S8 because the electric oil pump discharge oil amount is not sufficient for cooling the second clutch CL2 and the like.

[Cooling / lubrication → Hydraulic supply switching processing configuration]
FIG. 5 is a flowchart showing the flow of the switching valve cooling / lubrication → hydraulic pressure supply switching process executed in the first embodiment. Hereinafter, the cooling / lubrication → hydraulic supply switching processing configuration of the first embodiment will be described with reference to FIG.

In step S11, the electric oil pump M / O / P is activated, and whether or not the electric oil pump discharge oil passage 105 is connected to the cooling system oil passage 104 by the switching valve 106, that is, the electric oil pump M / O. It is determined whether or not hydraulic pressure is supplied from the / P to the cooling / lubricating system Lub of the transmission mechanism. If YES (electric oil pump ON, switching valve = cooling side), the process proceeds to step S12. In the case of NO (electric oil pump NO or switching valve = hydraulic pressure supply side), the hydraulic oil is not supplied from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism, so cooling / lubrication → Since it is not necessary to perform the hydraulic pressure supply switching process, the process proceeds to the end.

In step S12, following the determination that the electric oil pump is ON and the switching valve is on the cooling side in step S11, it is determined whether or not the temperature of the second clutch CL2 is below a predetermined cooling threshold. If YES (CL2 temperature <cooling threshold), it is determined that cooling of the second clutch CL2 is not necessary, and the process proceeds to step S13. When NO (CL2 temperature ≥ cooling threshold), cooling of the second clutch CL2 is necessary, and it is necessary to continue supplying hydraulic pressure from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism. If there is, return to step S1.

In step S13, following the determination of CL2 temperature <cooling threshold in step S12, it is assumed that there is no “cooling request” that increases the flow rate of hydraulic oil flowing through the cooling / lubricating system Lub of the transmission mechanism. The flow rate of hydraulic oil discharged from M / O / P (the amount of oil discharged from the electric oil pump M / O / P) is reduced, and the process proceeds to step S14.

In step S14, following the electric oil pump M / O / P = oil amount reduction in step S13, a hydraulic pressure supply request is made to supply hydraulic pressure from the electric oil pump M / O / P to the transmission mechanism hydraulic system Sup. Determine whether it occurred. If YES (hydraulic supply requested), the process proceeds to step S15. If NO (no hydraulic supply request), the process proceeds to step S19.
Here, whether or not there is a hydraulic supply request is that the flow rate of the hydraulic oil discharged from the mechanical oil pump O / P cannot secure the required amount of oil in the hydraulic system Sup for the transmission mechanism only by the amount of oil discharged from the mechanical oil pump. It is determined based on whether or not the oil amount determined (= hydraulic supply required oil amount) has been reached. If the discharge oil amount of the mechanical oil pump O / P> the hydraulic oil supply requirement oil amount, the hydraulic oil supply request is not generated and “no hydraulic oil supply request” is set. If the discharge oil amount of the mechanical oil pump O / P is equal to or less than the oil supply requirement oil amount, the oil supply request is generated and “hydraulic supply request is present”.

In step S15, following the determination that there is a hydraulic pressure supply request in step S14, it is determined whether or not the amount of oil discharged from the electric oil pump M / O / P is equal to or less than a predetermined second threshold value. If YES (electric oil pump discharge oil amount ≦ second threshold value), the process proceeds to step S16. If NO (electric oil pump discharge oil amount> second threshold value), the process returns to step S13.
Here, the “second threshold value” is a “pressure adjustable oil amount” that can be adjusted by the line pressure control valve 101. That is, the “second threshold value” determines the rate of change in the amount of hydraulic oil supplied to the line pressure control valve 101 immediately after the switching valve 106 is switched from the cooling side to the hydraulic pressure supply side, and the switching valve 106 is switched. The overshoot amount (hydraulic pressure increase amount) of the hydraulic pressure (line pressure PL) supplied to the transmission mechanism hydraulic system Sup is determined accordingly.

That is, when the switching valve 106 is switched from the cooling side to the hydraulic pressure supply side, the discharge oil of the electric oil pump M / O / P flows into the second hydraulic pressure supply oil passage 103 and the hydraulic oil supplied to the line pressure control valve 101 Increases oil volume. Here, if the discharge oil amount of the electric oil pump M / O / P is reduced in advance before switching the switching valve 106 from the cooling side to the hydraulic pressure supply side, the line pressure control valve when the switching valve 106 is switched. The change in the amount of hydraulic oil supplied to 101 can be suppressed. That is, the “second threshold value (= pressure adjustable oil amount)” is a predetermined value α representing a change in the amount of oil supplied to the line pressure control valve 101 that occurs when the switching valve 106 is switched from the cooling side to the hydraulic pressure supply side. The following is a value that allows the line pressure control valve 101 to perform proper pressure regulation, suppresses overshoot of the line pressure PL, and maintains the line pressure PL at a hydraulic pressure that can avoid a shock of the continuously variable transmission CVT.

In step S16, following the determination that the electric oil pump discharge oil amount ≦ the second threshold value in step S15, the line pressure control valve 101 does not change even if the discharge oil amount of the electric oil pump M / O / P switches the switching valve 106. Therefore, the control valve 106 is switched from the cooling side to the hydraulic pressure supply side, and the electric oil pump discharge oil passage 105 is changed to the first level. 2. Connect to the hydraulic pressure supply oil passage 103 and proceed to Step S17. As a result, the hydraulic oil discharged from the electric oil pump M / O / P is supplied to the transmission mechanism hydraulic system Sup.

In step S17, following the switching control with the switching valve = hydraulic supply side in step S16, the discharge oil amount of the electric oil pump M / O / P is increased, and the process proceeds to step S18.

In step S18, following the electric oil pump M / O / P = oil amount increase in step S17, the discharge oil amount of the electric oil pump M / O / P is the oil amount (line pressure) required for the transmission mechanism hydraulic system Sup. Judgment is made as to whether or not the amount of oil capable of securing PL = the amount of oil required for hydraulic supply has been reached. If YES (electric oil pump discharge oil amount ≧ hydraulic supply oil amount), the flow proceeds to the end assuming that the oil amount necessary to maintain the line pressure PL is secured by the electric oil pump discharge oil amount. In the case of NO (electric oil pump discharge oil amount <hydraulic supply required oil amount), the flow returns to step S17 because the electric oil pump discharge oil amount is not sufficient to maintain the line pressure PL.

In step S19, following the determination that there is no hydraulic pressure supply request in step S14, it is determined whether or not the electric oil pump M / O / P has stopped. If YES (electric oil pump = stop), go to end. If NO (electric oil pump ≠ stop), the process returns to step S13.
Here, the stop of the electric oil pump M / O / P is determined when the number of rotations of the sub motor S / M is equal to or less than a predetermined value at which it can be determined that the motor has stopped.

Next, the actions in the vehicle hydraulic control apparatus of the first embodiment are divided into “electric oil pump flow path switching action”, “hydraulic supply → cooling / lubrication switching action”, and “cooling / lubrication → hydraulic supply switching action”. explain.

[Electric oil pump flow path switching action]
FIG. 6A is an explanatory diagram showing the operation of the switching valve and the flow of hydraulic oil when the switching valve is switched to the hydraulic pressure supply side, and FIG. 6B is a diagram when the switching valve is switched to the cooling side. It is explanatory drawing which shows the operation | movement of a switching valve, and the flow of hydraulic oil. Hereinafter, based on FIG. 6A and FIG. 6B, the electric oil pump flow path switching effect | action of Example 1 is demonstrated.

The hydraulic control circuit 100 according to the first embodiment includes a mechanical oil pump O / P operated by a motor / generator MG and an electric oil pump M / O / operated by a sub motor S / M different from the motor / generator MG. P and. The electric oil pump discharge oil passage 105 connected to the discharge port 111a of the electric oil pump M / O / P is connected to the second hydraulic supply oil passage connected to the input port 101a of the line pressure control valve 101 by the switching valve 106. 103 and a cooling system oil passage 104 connected to the cooling / lubricating system Lub of the speed change mechanism.

That is, as shown in FIG. 6A, when the switching valve 106 is controlled so as to connect the electric oil pump discharge oil passage 105 to the second hydraulic supply oil passage 103, the discharge from the electric oil pump M / O / P is performed. The hydraulic oil thus discharged is supplied to the transmission mechanism hydraulic system Sup through the electric oil pump discharge oil passage 105 → the switching valve 106 → the second hydraulic supply oil passage 103 → the line pressure control valve 101 → the line pressure circuit 101c in this order. .
As a result, when the hydraulic pressure supplied from the mechanical oil pump O / P is less than the hydraulic pressure required for the transmission mechanism hydraulic system Sup, the electric oil pump M / O / P operates from the transmission mechanism hydraulic system Sup. Oil can be supplied. For this reason, it is possible to prevent the line pressure PL from being lowered and to secure the necessary hydraulic pressure in the transmission mechanism hydraulic system Sup.

In contrast, as shown in FIG. 6B, when the switching valve 106 is controlled so as to connect the electric oil pump discharge oil passage 105 to the cooling system oil passage 104, the electric oil pump M / O / P discharges. The hydraulic fluid thus supplied is supplied to the cooling / lubricating system Lub of the transmission mechanism through the electric oil pump discharge oil passage 105 → the switching valve 106 → the cooling system oil passage 104 in order.
Thus, when the temperature of the second clutch CL2 rises and quick clutch cooling is required, the hydraulic oil can be directly supplied from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism. For this reason, the cooling of the transmission mechanism / the lubrication system Lub can be quickly performed.

Thus, since the hydraulic control circuit 100 has the switching valve 106, the connection destination of the electric oil pump discharge oil passage 105 can be switched, and the transmission mechanism hydraulic pressure when the mechanical oil pump O / P is stopped. The hydraulic pressure supply to the system Sup and the cooling function of the second clutch CL2 can be achieved by one electric oil pump M / O / P. As a result, it is possible to improve the in-vehicle performance and reduce the cost while achieving both the hydraulic pressure supply to the transmission mechanism when the mechanical oil pump O / P is stopped and the cooling function of the transmission mechanism.

[Hydraulic supply → Cooling / lubrication switching action]
FIG. 7A shows the characteristics of accelerator opening, vehicle speed, CL2 temperature (second clutch temperature), cooling flag, and hydraulic pressure supply flag when the switching valve is switched from the hydraulic pressure supply side to the cooling side in the control device of the first embodiment. It is a time chart which shows. FIG. 7B shows the mechanical oil pump rotation speed, the hydraulic system supply oil amount for the transmission mechanism, the electric oil pump discharge oil amount, the mechanical type when the switching valve is switched from the hydraulic pressure supply side to the cooling side in the control device of the first embodiment. It is a time chart which shows each characteristic of an oil pump discharge oil amount and a switching valve state. Hereinafter, the hydraulic pressure supply → cooling / lubrication switching operation of the first embodiment will be described with reference to FIGS. 7A and 7B.

Figure 7A, at time t ₀ shown in FIG. 7B, the accelerator depression operation is performed from the vehicle stoppage state. At this time, since the time t ₀ before power transmission from the motor / generator MG to has not been performed, the second clutch temperature is below the cooling threshold. Therefore, a cooling request for supplying hydraulic pressure directly from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism does not occur, and the cooling flag is turned off. On the other hand, since the rotational speed of the motor / generator MG is low, the rotational speed of the mechanical oil pump O / P is a value that can secure the required oil amount (= required oil amount for hydraulic supply) in the transmission mechanism hydraulic system Sup (= The number of revolutions required for hydraulic pressure supply) or less. In other words, the amount of oil discharged from the mechanical oil pump O / P is less than the amount of oil required to supply hydraulic pressure, and a hydraulic supply request to supply hydraulic pressure from the electric oil pump M / O / P to the hydraulic system Sup for the transmission mechanism is generated. The hydraulic supply flag is turned on.

As a result, the sub-motor S / M is driven to operate the electric oil pump M / O / P, and the switching valve 106 is switched to the hydraulic pressure supply side so that the electric oil pump discharge oil passage 105 is set to the second hydraulic supply oil. Connect to path 103. For this reason, the hydraulic oil discharged from the electric oil pump M / O / P flows into the second hydraulic pressure supply oil passage 103 and is supplied to the line pressure control valve 101 to ensure the line pressure PL.

Thereafter, as the rotational speed of the motor / generator MG increases as the vehicle speed increases, the rotational speed of the mechanical oil pump O / P also increases. For this reason, the amount of oil discharged from the mechanical oil pump O / P increases in proportion to the increase in vehicle speed.
On the other hand, the discharge oil amount of the electric oil pump M / O / P is decreased as the discharge oil amount of the mechanical oil pump O / P increases, and the discharge oil amount of the mechanical oil pump O / P Control is performed so that the amount of oil supplied to the hydraulic system Sup for the speed change mechanism, which is the total amount of oil discharged from the electric oil pump M / O / P, maintains the amount of oil required for hydraulic supply.

Then, the temperature gradually of the second clutch CL2 in accordance with the transmitting power from the motor / generator MG is increased, at time t ₁ the time, after the second clutch temperature reaches the cooling threshold, the electric oil pump M / O A cooling request to supply hydraulic pressure directly from the / P to the cooling / lubricating system Lub of the transmission mechanism is generated, and the cooling flag is turned ON. Accordingly, in the flowchart shown in FIG. 3, the process proceeds from step S1 to step S2 to step S3, the second clutch CL2 is slip-engaged, and the flow rate of the hydraulic oil discharged from the mechanical oil pump O / P is requested to drive. Raise at a speed higher than the speed determined by the force.
Therefore, the amount of oil discharged from the mechanical oil pump O / P increases rapidly. In contrast, the amount of oil discharged from the electric oil pump M / O / P is reduced at a speed that assumes that the amount of oil discharged from the mechanical oil pump is increasing at an increasing speed determined according to the required driving force. . Therefore, the amount of oil supplied to the transmission mechanism hydraulic system Sup is greater than the amount of oil required for hydraulic supply.

At time t ₂ when a discharge oil amount of the mechanical oil pump O / P, supplied oil amount to the electric oil pump M / O / P total oil amount of discharge oil amount is speed change mechanism hydraulic system Sup of, When the switchable oil amount is reached, the process proceeds from step S4 to step S5, and the flow rate of the hydraulic oil discharged from the electric oil pump M / O / P is higher than the decrease speed determined according to the required driving force. Thus, the total oil amount is reduced at a speed that is equal to or less than the switchable oil amount and does not fall below the oil pressure required oil amount. Here, the discharge oil amount of the electric oil pump M / O / P is reduced at a speed at which the total oil amount maintains the switchable oil amount.

Then, at time t ₃ time, when the rotational speed of the mechanical oil pump O / P reaches the hydraulic supply required rotational speed, to stop the rotation speed increase of the mechanical oil pump O / P, the mechanical oil pump O / Maintain the discharge oil amount of P. Moreover, at this timing (time t ₃ time points), to completely engaging the second clutch CL2. On the other hand, the discharge oil amount of the electric oil pump M / O / P continues to decrease.
Note that in this time t ₃ point, that the rotational speed of the mechanical oil pump O / P reaches the oil pressure supply required rotational speed, the hydraulic pressure supplied from the electric oil pump M / O / P to the hydraulic system Sup gear shifting mechanism As unnecessary, the hydraulic supply stop permission is generated and the hydraulic supply flag is turned OFF. However, at time t ₁ time, the cooling required by the second clutch temperature exceeds the cooling threshold occurs, this time t ₁ time, already ON / OFF state of the oil pressure supply flag, i.e. hydraulic supply request and the hydraulic pressure supply A command to switch the switching valve 106 to the cooling side is output regardless of whether or not the stop is permitted. That is, the hydraulic pressure supply to the cooling / lubricating system Lub of the transmission mechanism is prioritized over the hydraulic pressure supply to the transmission mechanism hydraulic pressure gauge Sup.

At time t ₄ the time, when the discharge oil amount of the electric oil pump M / O / P reaches the first threshold value, the process proceeds to step S6 → step S7, the switching valve 106 and the switching control on the cooling side, the electric oil pump The discharge oil passage 105 is connected to the cooling system oil passage 104.
As a result, the hydraulic oil discharged from the electric oil pump M / O / P is directly supplied to the cooling / lubricating system Lub of the transmission mechanism via the cooling system oil passage 104, and is supplied to the cooling / lubricating system Lub of the transmission mechanism. The amount of flowing lubricating oil can be increased, and the second clutch CL2 can be quickly cooled.

The flow rate of the hydraulic oil supplied to the transmission mechanism hydraulic system Sup via the line pressure control valve 101 is such that the amount of oil discharged from the mechanical oil pump O / P and the electric oil are changed by the switching valve 106 being switched. From the total amount of oil discharged from the pump M / O / P, only the amount discharged from the mechanical oil pump O / P is used.
At this time, since the discharge oil amount of the electric oil pump M / O / P has been reduced to the first threshold value before switching the switching valve 106, it is supplied to the line pressure control valve 101 as the switching valve 106 is switched. Even if the hydraulic oil is reduced, the oil amount changing speed at this time can be suppressed to a predetermined value α or less. Therefore, the feedback delay of the orifice 101h in the line pressure control valve 101 does not occur, and proper pressure regulation in the line pressure control valve 101 can be achieved. Thereby, undershoot of the line pressure PL that leads to breakage of the continuously variable transmission CVT can be prevented.

Then, by increasing the discharge oil amount of the electric oil pump M / O / P proceeds to step S8, at time t ₅ the time, when the electric oil pump discharge oil amount reaches the cooling oil required amount, to step S9 → End Then, the discharge oil amount of the electric oil pump M / O / P is maintained at an amount necessary for cooling, and the hydraulic pressure supply → cooling / lubrication switching process is ended.

As described above, when a cooling request is generated because the second clutch temperature is equal to or higher than the cooling threshold, the discharge oil amount of the mechanical oil pump O / P and the discharge oil amount of the electric oil pump M / O / P When the total oil amount reaches the switchable oil amount, the discharge oil amount of the electric oil pump M / O / P is reduced to the first threshold value that is the adjustable oil amount that can be adjusted by the line pressure control valve 101. Then, the switching valve 106 is switched to the cooling side.
That is, when switching control is performed by the switching valve 106 to switch the connection destination of the electric oil pump discharge oil passage 105 to the cooling system oil passage 104, the required oil supply amount is ensured by the total oil amount and the electric oil pump discharge is performed. The oil amount is decreased until the oil amount becomes the first threshold value or less.

As a result, even if the flow rate of the hydraulic oil supplied to the line pressure control valve 101 is reduced when the switching valve 106 is switched to the hydraulic pressure supply side, the change rate of the supplied oil amount to the line pressure control valve 101 at this time Can be suppressed below a predetermined value α that can be regulated by the line pressure control valve 101, and an undershoot of the line pressure PL leading to breakage of the continuously variable transmission CVT can be prevented.

Also, when decreasing the discharge oil amount of the electric oil pump M / O / P, while increasing the discharge oil amount of the mechanical oil pump O / P, the discharge oil amount of the mechanical oil pump O / P and the electric oil Control is performed so that the total amount of oil discharged from the pump M / O / P is equal to or less than the switchable amount of oil, and does not fall below the amount of oil required for hydraulic supply. Therefore, it is possible to secure the line pressure PL and prevent the pulley belt V from slipping, suppress excessive driving of the sub motor S / M due to wasteful flow of hydraulic oil, and prevent power consumption deterioration.

Moreover, in the first embodiment, the amount of oil discharged from the electric oil pump M / O / P is reduced while the amount of oil discharged from the mechanical oil pump O / P is reduced as the switching valve 106 is switched to the cooling side. By raising the second clutch CL2, the second clutch CL2 is slip-engaged while the required amount of hydraulic pressure supply is secured by the total oil amount.
That is, in the first embodiment, in order to reduce the amount of oil discharged from the electric oil pump while securing the required oil supply amount by the total oil amount, the rotational speed of the motor / generator MG is equal to or higher than the rotational speed determined according to the required driving force Need to be raised. However, at this time, the second clutch CL2 is slip-engaged so that the left and right drive wheels LT and RT are not affected, and the driver does not feel a shock or discomfort.

When the second clutch temperature exceeds the cooling threshold, a cooling request for directly supplying hydraulic pressure from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism is generated, and a command to switch the switching valve 106 to the cooling side is issued. Is output. That is, the requirement for outputting a command to switch the switching valve 106 to the cooling side does not depend on whether or not there is a hydraulic pressure supply request or a hydraulic pressure supply stop permission. Therefore, when the temperature of the second clutch CL2 exceeds the cooling threshold, the electric oil pump discharge oil passage 105 is forcibly connected to the cooling system oil passage 104 by the switching valve 106.
As a result, the hydraulic pressure supply to the cooling / lubricating system Lub can be prioritized over the hydraulic pressure supply to the transmission hydraulic system Sup, and the second clutch CL2 can be prevented from being damaged due to high temperature. it can.

[Cooling / lubrication → hydraulic supply switching]
FIG. 8A shows the characteristics of accelerator opening, vehicle speed, CL2 temperature (second clutch temperature), cooling flag, and hydraulic pressure supply flag when the switching valve is switched from the cooling side to the hydraulic pressure supply side in the control device of the first embodiment. It is a time chart which shows. FIG. 8B shows the mechanical oil pump rotation speed, the hydraulic system supply oil amount for the transmission mechanism, the electric oil pump discharge oil amount, the mechanical type when the switching valve is switched from the cooling side to the hydraulic pressure supply side in the control device of the first embodiment. It is a time chart which shows each characteristic of an oil pump discharge oil amount and a switching valve state. Hereinafter, based on FIG. 8A and FIG. 8B, the cooling / lubrication → hydraulic pressure supply switching operation of the first embodiment will be described.

When decelerating by depressing the brake, when the motor / generator MG is regenerating, the temperature of the second clutch CL2 is higher than the cooling threshold and a cooling request is generated, and from the mechanical oil pump O / P Consider a case where the amount of discharged oil is sufficient and no hydraulic pressure supply request has occurred.
In such a case, the cooling flag is turned on and the hydraulic pressure supply flag is turned off. For this reason, the electric oil pump M / O / P is actuated, and the electric oil pump discharge oil passage 105 is connected to the cooling system oil passage 104 by the switching valve 106 so that the electric oil pump M / O / P can change the speed change mechanism. Hydraulic pressure is supplied directly to the cooling / lubrication system Lub. The amount of oil discharged from the electric oil pump at this time is controlled according to the amount of oil required for cooling. On the other hand, the hydraulic pressure supply to the transmission mechanism hydraulic system Sup is provided only by the amount of oil discharged from the mechanical oil pump O / P.

When such a state, the temperature of the second clutch CL2 is decreased, with Figure 8A, at time t ₁₁ shown in FIG. 8B, When the second clutch temperature falls below the cooling threshold, the electric oil pump M / O / P Therefore, it is not necessary to actively supply hydraulic pressure to the cooling / lubricating system Lub of the transmission mechanism, and the cooling flag is turned off. Thus, in the flowchart shown in FIG. 5, the process proceeds from step S11 to step S12 to step S13 to step S14, and after the flow rate of the hydraulic oil discharged from the electric oil pump M / O / P is reduced, the electric oil pump M It is determined whether or not a hydraulic pressure supply request for supplying hydraulic pressure from / O / P to the transmission mechanism hydraulic system Sup has occurred.

This time t ₁₁ time, the rotational speed of the mechanical oil pump O / P is relatively high, as can be ensured this mechanical oil pump O / P line pressure PL only by discharge oil amount of the hydraulic supply request is generated Not. Therefore, the process proceeds from step S14 to step S19, and it is determined whether or not the electric oil pump M / O / P is stopped. Then, at the time t ₁₁ time, since the electric oil pump M / O / P is operating, the process returns to step S13, while reducing the amount of oil discharged electric oil pump M / O / P, the cooling of the transmission mechanism / Hydraulic supply to lubrication system Lub is continued.

Then, at time t ₁₂ the time, when the supply amount of oil to the speed change mechanism hydraulic system Sup had financed only by discharge oil amount of the mechanical oil pump O / P is less than the hydraulic pressure supply request oil amount, that is, the electric oil pump When a hydraulic pressure supply request for supplying hydraulic pressure from the M / O / P to the transmission mechanism hydraulic system Sup is generated, the hydraulic pressure supply flag is turned ON. Thus, the process proceeds from step S14 to step S15, and it is determined whether or not the amount of oil discharged from the electric oil pump M / O / P has fallen below a predetermined second threshold value.
This time t ₁₂ time, since the discharge oil amount of the electric oil pump M / O / P is above the second threshold value, while continuing the lowering of the electric oil pump discharge oil amount, the cooling / lubricating system of the transmission mechanism Lub The hydraulic pressure supply to is continued.

At time t ₁₃ the time, when the flow rate of hydraulic oil discharged from the electric oil pump M / O / P reaches the second threshold value, the process proceeds to step S15 → step S16, the switching control by the switching valve 106 to the hydraulic supply side Then, the electric oil pump discharge oil passage 105 is connected to the second hydraulic supply oil passage 103.
As a result, the hydraulic oil discharged from the electric oil pump M / O / P flows through the second hydraulic pressure supply oil passage 103 and is supplied to the line pressure control valve 101, and for the speed change mechanism via the line pressure control valve 101. The amount of oil supplied to the hydraulic system Sup increases, and the line pressure PL can be secured.

Further, the flow rate of the hydraulic oil supplied to the transmission mechanism hydraulic system Sup via the line pressure control valve 101 is only the discharge oil amount of the mechanical oil pump O / P because the switching valve 106 is switched. This is the total amount of oil discharged from the mechanical oil pump O / P and the amount discharged from the electric oil pump M / O / P.
At this time, before the switching valve 106 is switched, the discharge oil amount of the electric oil pump M / O / P is reduced to the second threshold value in advance, so that it is supplied to the line pressure control valve 101 as the switching valve 106 is switched. Even if the amount of the hydraulic oil being increased increases, the oil amount changing speed at this time can be suppressed to a predetermined value α or less. Therefore, the feedback delay of the orifice 101h in the line pressure control valve 101 does not occur, and proper pressure regulation in the line pressure control valve 101 can be achieved. As a result, it is possible to prevent overshoot of the line pressure PL that causes a shock due to a change in the ratio of the continuously variable transmission CVT.

After then, increased discharge oil amount of the electric oil pump M / O / P proceeds to step S17, at time t ₁₄ the time, the electric oil pump discharge oil amount reaches the hydraulic supply oil required amount, step S18 → Proceeding to the end, the discharge oil amount of the electric oil pump M / O / P is maintained at an amount necessary to secure the line pressure PL, and the cooling / lubrication → hydraulic supply switching process is terminated.

In this way, when the second clutch temperature is below the predetermined cooling threshold and the hydraulic oil supply request is generated when the discharge oil amount at the mechanical oil pump O / P falls below the hydraulic oil supply request oil amount, After switching the discharge oil amount of the electric oil pump M / O / P to the second threshold value, which is the adjustable oil amount that can be adjusted by the line pressure control valve 101, the switching valve 106 is switched to the hydraulic pressure supply side. .
That is, when the switching control is performed by the switching valve 106 to switch the connection destination of the electric oil pump discharge oil passage 105 to the second hydraulic supply oil passage 103, the electric oil pump discharge oil amount is decreased until it becomes equal to or less than the second threshold value. .

As a result, even if the flow rate of hydraulic oil supplied to the line pressure control valve 101 increases when the switching valve 106 is switched to the cooling side, the rate of change in the amount of oil supplied to the line pressure control valve 101 at this time is increased. The line pressure control valve 101 can control the pressure to be less than a predetermined value α, and can prevent an overshoot of the line pressure PL that causes the ratio of the continuously variable transmission CVT to fluctuate and generate a shock. Can be suppressed.

Further, in the first embodiment, as shown in the flowchart shown in FIG. 5, while the second clutch temperature exceeds the cooling threshold, it is not determined whether or not the hydraulic pressure supply request is generated. That is, in order to switch the switching valve 106 from the cooling side to the hydraulic pressure supply side, the second clutch CL2 needs to be at a temperature equal to or lower than the cooling threshold. Therefore, the electric oil pump discharge oil passage 105 is connected to the second hydraulic supply oil passage 103 when a hydraulic supply request occurs and a cooling request does not occur.
As a result, the hydraulic pressure supply to the cooling / lubricating system Lub of the transmission mechanism can surely be given priority over the hydraulic supply to the transmission mechanism hydraulic system Sup, and the second clutch CL2 becomes hot and breaks. Can be prevented.

In the case where the second clutch temperature is equal to or lower than the cooling threshold and no hydraulic pressure supply request is generated, the process proceeds from step S11 to step S12 to step S13 to step S14 to step S19 in the flowchart shown in FIG. Oil pump M / O / P is stopped.
Thereby, unnecessary driving of the sub motor S / M is suppressed, and deterioration of power consumption can be prevented.

Next, the effect will be described.
In the vehicle hydraulic control apparatus according to the first embodiment, the effects listed below can be obtained.

(1) a mechanical oil pump O / P operated by a travel drive source (motor / generator MG);
An electric oil pump M / O / P operated by an electric motor (sub motor S / M) different from the travel drive source (motor / generator MG);
A line pressure control valve 101 for regulating the line pressure PL to be supplied to the transmission system hydraulic system Sup;
A first hydraulic supply oil passage 102 for supplying hydraulic oil discharged from the mechanical oil pump O / P to the input port 101a of the line pressure control valve 101;
A second hydraulic supply oil passage 103 for supplying hydraulic oil discharged from the electric oil pump M / O / P to the input port 101a of the line pressure control valve 101;
A cooling system oil passage 104 for supplying the hydraulic oil discharged from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism;
A discharge oil passage (electric oil pump discharge oil passage 105) of the electric oil pump M / O / P is provided, and the discharge oil passage (electric oil pump discharge oil passage 105) is connected to the second hydraulic supply oil passage 103. A switching valve 106 connected to one of the cooling system oil passages 104;
It was set as the structure provided with.
As a result, it is possible to improve the onboard performance and reduce the cost while achieving both the hydraulic pressure supply to the transmission mechanism when the mechanical oil pump is stopped and the cooling function of the transmission mechanism.

(2) circuit control means (integrated controller 10) for controlling the discharge oil amount of the mechanical oil pump O / P, the discharge oil amount of the electric oil pump M / O / P, and the switching valve 106; Prepared,
The circuit control means (integrated controller 10) connects the connection destination of the discharge oil passage (electric oil pump discharge oil passage 105) from the second hydraulic supply oil passage 103 to the cooling system oil passage 104 by the switching valve 106. At the time of switching, the required oil amount in the hydraulic system Sup for the transmission mechanism is calculated based on the total oil amount of the discharge oil amount of the mechanical oil pump O / P and the discharge oil amount of the electric oil pump M / O / P (= The required oil amount for hydraulic supply) is secured, and the discharge oil amount of the electric oil pump M / O / P is reduced below the adjustable oil amount (first threshold) that can be adjusted by the line pressure control valve 101. The configuration.
Thereby, in addition to the effect of (1), undershoot of the line pressure PL that leads to breakage of the continuously variable transmission CVT can be prevented at the time of switching from hydraulic pressure supply to cooling / lubrication.

(3) A friction engagement element (second clutch CL2) capable of slip engagement is disposed between the travel drive source (motor / generator MG) and the drive wheels (left and right drive wheels LT, RT),
The circuit control means (integrated controller 10) secures a required oil amount in the transmission mechanism hydraulic system Sup based on the total oil amount when switching the connection destination of the discharge oil passage (electric oil pump discharge oil passage 105). During this time, the frictional engagement element (second clutch CL2) is slip-engaged.
As a result, in addition to the effect of (2), the required oil supply amount is ensured by the total amount of oil discharged from the mechanical oil pump O / P and the amount discharged from the electric oil pump M / O / P. When the amount of oil discharged from the electric oil pump is reduced, it is possible to prevent the driver from feeling shocked or uncomfortable.

(4) circuit control means (integrated controller 10) for controlling the discharge oil amount of the mechanical oil pump O / P, the discharge oil amount of the electric oil pump M / O / P, and the switching valve 106; Prepared,
The circuit control means (integrated controller 10) connects the connection destination of the discharge oil passage (electric oil pump discharge oil passage 105) from the cooling system oil passage 104 to the second hydraulic supply oil passage 103 by the switching valve 106. When switching, the discharge oil amount of the electric oil pump M / O / P is reduced to a pressure adjustable oil amount (second threshold value) that can be adjusted by the line pressure control valve 101.
As a result, in addition to any of the effects (1) to (3), it is possible to prevent overshoot of the line pressure PL that causes the ratio of the continuously variable transmission CVT to fluctuate when switching between cooling / lubrication and hydraulic pressure supply. it can.

(5) circuit control means (integrated controller 10) for controlling the discharge oil amount of the mechanical oil pump O / P, the discharge oil amount of the electric oil pump M / O / P, and the switching valve 106; Prepared,
The circuit control means (integrated controller 10) causes the switching valve 106 to discharge the discharged oil when a cooling request for supplying hydraulic pressure from the electric oil pump M / O / P to the cooling / lubricating system Lub of the transmission mechanism occurs. The passage (electric oil pump discharge oil passage 105) is connected to the cooling system oil passage 104.
As a result, in addition to any of the effects (1) to (4), the hydraulic supply to the cooling / lubricating system Lub of the transmission mechanism can be given priority over the hydraulic supply to the hydraulic system Sup for the transmission mechanism. It is possible to prevent the occurrence of a malfunction of the transmission mechanism due to heat.

(6) The circuit control means (integrated controller 10) generates a hydraulic pressure supply request for supplying hydraulic pressure from the electric oil pump M / O / P to the transmission mechanism hydraulic system Sup, and the cooling request is generated. If not, the switching valve 106 connects the discharge circuit (electric oil pump discharge oil passage 105) to the second hydraulic supply oil passage 103.
As a result, in addition to the effect of (5), it is possible to reliably give priority to the hydraulic supply to the cooling / lubricating system Lub of the transmission mechanism over the hydraulic supply to the hydraulic system Sup for the transmission mechanism. Can be prevented from occurring.

As mentioned above, although the vehicle hydraulic control apparatus of the present invention has been described based on the first embodiment, the specific configuration is not limited to the first embodiment, and the invention according to each claim of the claims is not limited thereto. Design changes and additions are allowed without departing from the gist.

In the first embodiment, the vehicle hydraulic control apparatus of the present invention is applied to a hybrid vehicle having an engine Eng and a motor / generator MG. However, the present invention is not limited to this. The present invention can also be applied to an electric vehicle equipped only with a motor / generator MG, an engine vehicle equipped only with an engine Eng that stops idling, a plug-in hybrid vehicle, a fuel cell vehicle, and the like.

In the first embodiment, the travel drive source is the motor / generator MG, and the frictional engagement element disposed between the travel drive source and the drive wheels is the second clutch CL2. However, the present invention is not limited to this. For example, the travel drive source for operating the mechanical oil pump may be the engine Eng, and the frictional engagement element disposed between the travel drive source and the drive wheels may be the first clutch CL1.

Further, in the first embodiment, a circuit for supplying the control mechanism hydraulic pressure Sup to the primary pulley Pri, the secondary pulley Sec, and the second clutch CL2 of the continuously variable transmission CVT by using the transmission mechanism hydraulic system Sup as a source pressure. However, for example, a circuit for supplying control hydraulic pressure to the first clutch CL1 may be included. That is, the “transmission mechanism hydraulic system” is a circuit in which hydraulic pressure is supplied via a control valve unit provided in the transmission.
Further, the speed change mechanism is not limited to the continuously variable transmission CVT, and may include a stepped automatic transmission.

Cross-reference of related applications

This application claims priority based on Japanese Patent Application No. 2014-189158 filed with the Japan Patent Office on September 17, 2014, the entire disclosure of which is fully incorporated herein by reference.

Claims

A mechanical oil pump operated by a traveling drive source;
An electric oil pump operated by an electric motor different from the travel drive source;
A line pressure control valve that regulates the line pressure supplied to the hydraulic system for the transmission mechanism;
A first hydraulic supply oil passage for supplying hydraulic oil discharged from the mechanical oil pump to an input port of the line pressure control valve;
A second hydraulic supply oil passage for supplying hydraulic oil discharged from the electric oil pump to an input port of the line pressure control valve;
A cooling system oil passage for supplying hydraulic oil discharged from the electric oil pump to a cooling / lubricating system of the transmission mechanism;
A switching valve provided in a discharge oil passage of the electric oil pump, and connecting the discharge oil passage to either the second hydraulic supply oil passage or the cooling system oil passage;
A vehicle hydraulic control apparatus comprising:
In the vehicle hydraulic control device according to claim 1,
Circuit control means for controlling the discharge oil amount of the mechanical oil pump, the discharge oil amount of the electric oil pump, and the switching valve;
The circuit control means uses the switching valve to switch the connection destination of the discharge oil passage from the second hydraulic supply oil passage to the cooling system oil passage and the discharge oil amount of the mechanical oil pump and the electric oil pump. The required oil amount in the hydraulic system for the transmission mechanism is ensured by the total oil amount with the amount of discharged oil, and the discharge oil amount of the electric oil pump can be regulated by the line pressure control valve. A hydraulic control device for a vehicle, wherein the hydraulic pressure control device drops below an oil amount.
In the vehicle hydraulic control device according to claim 2,
Between the traveling drive source and the drive wheel, a friction fastening element capable of slip fastening is disposed,
When the circuit control means switches the connection destination of the discharge oil path, the circuit control means slip-fastens the friction engagement element while securing the required oil amount in the transmission mechanism hydraulic system by the total oil amount. A vehicle hydraulic control device.
In the vehicle hydraulic control device according to any one of claims 1 to 3,
Circuit control means for controlling the discharge oil amount of the mechanical oil pump, the discharge oil amount of the electric oil pump, and the switching valve;
The circuit control means uses the switching valve to switch the discharge oil amount of the electric oil pump when the connection destination of the discharge oil passage is switched from the cooling system oil passage to the second hydraulic supply oil passage. A hydraulic control apparatus for a vehicle, characterized in that the oil pressure drops below an adjustable oil amount that can be adjusted by a valve.
In the vehicle hydraulic control device according to any one of claims 1 to 4,
Circuit control means for controlling the discharge oil amount of the mechanical oil pump, the discharge oil amount of the electric oil pump, and the switching valve;
The circuit control means connects the discharge oil passage to the cooling system oil passage by the switching valve when a cooling request for supplying hydraulic pressure from the electric oil pump to the cooling / lubrication system of the transmission mechanism is generated. A vehicle hydraulic control device.
In the vehicle hydraulic control device according to claim 5,
When a hydraulic pressure supply request for supplying hydraulic pressure from the electric oil pump to the hydraulic mechanism for the transmission mechanism is generated and the cooling request is not generated, the circuit control means causes the switching valve to switch the discharge circuit to the first circuit. 2. A hydraulic control device for a vehicle, wherein the hydraulic control device is connected to a hydraulic pressure oil passage.