JP2003139230A - Oil pump control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a controller for oil pump which controls the supply condition of oil supplied to an apparatus requiring oil from an oil pump when a system for controlling the oil pump is normal. SOLUTION: This controller for oil pump, equipped with the apparatus requiring oil for controlling power transmitted by a power transmission apparatus and the oil pump for supplying oil to the apparatus requiring oil, includes an oil supply condition control means 8 (step S1 to step S3) which controls the supply condition of the oil supplied to the apparatus requiring oil from the oil pump.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control device for an oil pump that supplies oil to an oil-requiring device of a power transmission device.

[0002]

2. Description of the Related Art Generally, in a power transmission device for a vehicle, it is known that the power transmission state between one rotating member and the other rotating member is controlled by hydraulic pressure. One example is described in JP-A-5-33857. In this publication, the engine power is configured to be sequentially transmitted to a torque converter device, a forward / reverse switching device, a continuously variable transmission, and a differential device. The continuously variable transmission has a primary shaft and a secondary shaft, the primary shaft is provided with a primary pulley, and the secondary shaft is provided with a secondary pulley. Further, a hydraulic cylinder corresponding to the primary pulley and a hydraulic cylinder corresponding to the secondary pulley are provided. Further, the drive belt is wound around the primary pulley and the secondary pulley.

By controlling the hydraulic pressure acting on the hydraulic cylinder of the primary pulley, the ratio of the winding radius of the drive belt to the primary pulley and the winding radius of the drive belt to the secondary pulley, that is, the gear ratio is controlled. To be done. Further, by controlling the hydraulic pressure acting on the hydraulic cylinder of the secondary pulley, the tension of the drive belt is controlled and the capacity of the torque transmitted between the primary pulley and the secondary pulley is controlled.

On the other hand, an oil pump having a function of supplying oil to the hydraulic cylinder of the primary pulley and the hydraulic cylinder of the secondary pulley is provided.
This oil pump is driven by the power of the engine. This oil pump is a roller vane type, is a variable displacement type having a plurality of discharge ports, and has a main pump and a sub pump. Further, various solenoid valves are provided in an oil passage for supplying the oil discharged from the oil pump to the hydraulic cylinder. Furthermore, a control unit for controlling this solenoid valve is provided.

Then, the pump flow rate of the oil pump and the oil usage amount are compared and judged, and the solenoid valve is controlled based on the signal output from the control unit. By such control, the amount of oil supplied to each hydraulic cylinder, in other words, the hydraulic pressure is controlled. By the way, in this publication, when the signal circuit of the solenoid valve is broken, the pump load is reduced by driving only the main pump to reduce the pump flow rate.

[0006]

However, the above publication describes the control of the oil pump when the solenoid valve has a disconnection failure. However, in the above publication, the oil pump when the system is normal is disclosed. The control of the pump was not recognized, and there was still room for improvement in this respect.

The present invention has been made in view of the above circumstances, and when the system for controlling the oil pump is normal, it is possible to control the supply state of the oil supplied from the oil pump to the oil required device. It is an object of the present invention to provide a control device for an oil pump that can be used.

[0008]

In order to achieve the above-mentioned object, the invention of claim 1 provides an oil-requiring device for controlling the power transmitted by a power transmission device, and an oil-requiring device for this oil-requiring device. An oil pump control device including an oil pump for supplying oil, and an oil supply for controlling a supply state of oil supplied from the oil pump to the oil required device based on power transmitted by the power transmission device. It is characterized in that it is provided with a state control means.

According to the first aspect of the invention, the supply state of the oil supplied from the oil pump to the oil required device is controlled based on the power transmitted by the power transmission device. Therefore, the supply state of the oil supplied from the oil pump to the oil required device becomes a state according to the power transmitted by the power transmission device.

According to a second aspect of the present invention, in addition to the structure of the first aspect, the oil supply state control means determines whether or not the power transmitted by the power transmission device is equal to or less than a predetermined value. It is characterized by having a function of changing the supply amount of oil supplied from the oil pump driven by the device to the oil required device.

According to the invention of claim 2, in addition to the same effect as that of the invention of claim 1, the power for driving the oil pump is determined depending on whether or not the power transmitted by the power transmission device is below a predetermined value. The load on the device changes.

According to a third aspect of the present invention, there is provided an oil pump control device comprising an oil-requiring device for controlling the power transmitted by the power transmission device and an oil pump for supplying oil to the oil-requiring device. An oil supply state for controlling the supply state of the oil supplied from the oil pump to the oil required device based on the actual supply state of the oil supplied from the pump to the oil required device and the target supply state of the oil. It is characterized by including a control means.

According to the third aspect of the invention, the actual supply state of the oil supplied from the oil pump to the oil required device is brought close to the target supply state of the oil.

According to a fourth aspect of the present invention, there is provided an oil pump controller including an oil-requiring device for controlling the power transmitted by the power transmission device, and an oil pump for supplying oil to the oil-requiring device. An oil supply state control means is provided for controlling the supply state of the oil supplied from the oil pump to the oil required device based on a request for controlling the speed of the moving body that is moved by the power transmitted by the transmission device. It is characterized by that.

According to the fourth aspect of the present invention, the supply state of the oil supplied from the oil pump to the oil required device is controlled according to the speed of the moving body that is moved by the power transmitted by the power transmission device.

According to a fifth aspect of the present invention, there is provided an oil pump controller including an oil-requiring device for controlling the power transmitted by the power transmission device, and an oil pump for supplying oil to the oil-requiring device. An oil supply state for controlling the supply state of the oil supplied from the oil pump to the oil required device based on a request for controlling the rotation speed ratio between one rotating member and the other rotating member of the transmission device. It is characterized by including a control means.

According to the fifth aspect of the invention, the supply of the oil supplied from the oil pump to the oil-requiring device is performed based on the request for controlling the ratio of the rotational speeds between the one rotary member and the other rotary member. The state is controlled.

According to a sixth aspect of the present invention, in addition to the configuration of the fifth aspect, the oil supply state control means actually changes the rotational speed between the one rotating member and the other rotating member. Based on the progress status and the target progress status,
It further comprises a function of controlling a supply state of oil supplied from the oil pump to the oil required device.

According to the invention of claim 6, in addition to the same effect as that of the invention of claim 5, the actual progress state of the process of changing the rotation speed between one rotating member and the other rotating member. And the target progress state, the supply state of the oil supplied from the oil pump to the oil required device is controlled.

According to a seventh aspect of the present invention, there is provided an oil pump control device including an oil-requiring device for controlling the power transmitted by the power transmission device, and an oil pump for supplying oil to the oil-requiring device. The supply state of the oil supplied from the pump to the oil required device,
An oil supply state control unit for controlling the temperature of the oil is provided.

According to the invention of claim 7, the supply state of the oil supplied from the oil pump to the oil-requiring device can be adapted to the temperature characteristic of the oil.

According to an eighth aspect of the present invention, there is provided an oil pump control device comprising an oil-requiring device for controlling a rotation direction of an output member of a power transmission device and an oil pump for supplying oil to the oil-requiring device. An oil supply state control means for controlling the supply state of the oil supplied from the oil pump to the oil required device based on a request for controlling the rotation direction of the output member is provided.

According to the invention of claim 8, the supply state of the oil supplied from the oil pump to the oil-requiring device is controlled on the basis of the request for controlling the rotation direction of the output member.

In the invention of each claim, the power transmitted by the power transmission device means "the power transmitted between one rotating member and the other rotating member".

[0025]

Next, the basic principle of the present invention will be described with reference to FIG. In the vehicle Ve shown in FIG. 13, a power transmission device 102 is provided in the power transmission path between the driving force source 100 and the wheels 101. As the driving force source 100, at least one of an engine and an electric motor can be used. An engine is a power unit of a type that burns fuel to output power.
As this engine, an internal combustion engine such as a gasoline engine, an LPG engine, a diesel engine, a methanol engine, or a hydrogen engine can be used. An electric motor is a power unit that outputs power by supplying electric power, and the engine and the electric motor have different power generation principles. As the electric motor, one having a power running function of converting electric energy into kinetic energy or a regenerative function of converting kinetic energy into electric energy, for example, a three-phase AC motor generator can be used.

As the power transmission device 102, at least one of a fluid type power transmission device and a transmission can be used. The fluid type power transmission device transmits power by kinetic energy of fluid between a driving side rotating member (one rotating member) and a driven side rotating member (the other rotating member). The member is connected to the driving force source side, and the driven side rotating member is connected to the transmission or the wheel 101 side. The fluid power transmission may be either a torque converter or a fluid coupling. The torque converter is a fluid type power transmission device having a function of amplifying the torque transmitted between the driving side rotation member and the driven side rotation member, and the fluid coupling is the driving side rotation member and the driven side rotation member. It is a fluid type power transmission device that does not have the function of amplifying the torque transmitted between and.

As the transmission, a transmission having at least one of a manual shift function and an automatic shift function can be used. A transmission equipped with a manual gear shifting function is a ratio of the rotational speed of the input rotary member to the rotational speed of the output rotary member, that is, the gear ratio, which is manually operated based on the operating state of the gear ratio selecting device by the driver. Means a transmission that can be changed by. On the other hand, a transmission having an automatic transmission function means a ratio of the rotation speed of the input rotary member and the rotation speed of the output rotary member,
That is, it means a transmission capable of automatically controlling the gear ratio based on conditions other than the operating state of the gear ratio selecting device.

As the transmission, either a continuously variable transmission or a stepped transmission may be used. What is a continuously variable transmission?
It means a transmission capable of controlling the speed ratio continuously or continuously. For this continuously variable transmission,
Examples thereof include a belt type continuously variable transmission and a toroidal type continuously variable transmission.

The belt type continuously variable transmission has a driving side pulley and a driven side pulley, and a belt wound around the groove of the driving side pulley and the groove of the driven side pulley. The driving pulley is connected to the input rotating member (one rotating member), and the driven pulley is connected to the output rotating member (the other rotating member). Then, by adjusting the groove width of the driving pulley, by controlling the winding radius of the belt on the driving pulley and the winding radius of the belt on the driven pulley,
The gear ratio of the belt type continuously variable transmission is controlled. Further, the tension of the belt is controlled by adjusting the groove width of the driven pulley. By adjusting the tension of the belt, the contact pressure between each pulley and the belt, in other words, the capacity of the torque transmitted between the driving pulley and the driven pulley is controlled.

A hydraulic servo mechanism and a hydraulic control device are provided to control the groove width of the driving pulley and the groove width of the driven pulley, respectively. The hydraulic servo mechanism is provided separately for the drive side pulley and the driven side pulley, and each hydraulic servo mechanism has a piston for adjusting the groove width of each pulley separately and a hydraulic chamber for operating each piston. have. The hydraulic control device has a hydraulic circuit communicating with the hydraulic chamber and various solenoid valves provided in the hydraulic circuit. The "belt" of the belt type continuously variable transmission includes a chain.

The toroidal type continuously variable transmission is a transmission having an input disk and an output disk having a toroidal surface, and a power roller in contact with each disk. The input disk is connected to the input rotating member (one rotating member), and the output disk is connected to the output rotating member (the other rotating member). Lubricating oil is present on the contact surface between each disk and the power roller. Then, the power roller is linearly moved in a plane orthogonal to the axis of each disc to adjust the contact radius between the power roller and each disc, thereby changing the speed of transmission between the input rotary member and the output rotary member. The ratio is controlled. Further, by adjusting the contact surface pressure between each disk and the power roller, the capacity of the torque transmitted between the input rotary member and the output rotary member is controlled.

That is, when the contact surface pressure between each disk and the power roller is increased to a high pressure, the lubricating oil becomes glassy, and the power is transmitted between the input rotary member and the output rotary member by so-called traction transmission. . As described above, the hydraulic servo mechanism for adjusting the contact surface pressure between each disk and the power roller is provided. The hydraulic servo mechanism has a piston and a hydraulic chamber that operates each piston. Further, a hydraulic servo mechanism for linearly moving the power roller in a plane orthogonal to the axis of each disk is provided. This hydraulic servo mechanism has a hydraulic chamber.

On the other hand, in the stepped transmission, the gear ratio between the input rotary member (one rotary member) and the output rotary member (the other rotary member) can be controlled discontinuously or stepwise. It means a transmission. Examples of the stepped transmission include a selection gear type transmission and a planetary gear type transmission.
In the selective gear type transmission, the gear ratio between the input rotary member and the output rotary member can be controlled by the operation of the synchronous meshing mechanism. In a planetary gear type transmission, a friction engagement device such as a clutch or a brake is provided, and engagement / disengagement / slip of the friction engagement device is controlled to control the gear ratio between the input rotary member and the output rotary member. Alternatively, at least one of the capacities of the torque transmitted between the input rotary member and the output rotary member can be controlled. In such a stepped transmission,
A hydraulic control device is provided for controlling the synchronous meshing mechanism or the friction engagement device. The hydraulic control device is a hydraulic chamber,
It has a piston, hydraulic circuit, and various solenoid valves.

When the stepped transmission is provided with a manual gear shift function, the driver can switch the gear ratio, that is, the gear stage, by operating the gear ratio selecting device. In this case, the operation state of the gear ratio selection device is called a "shift position". On the other hand, when the continuously variable transmission or the stepped transmission has an automatic speed change function, the driver can switch the control range of the speed ratio by operating the speed ratio selection device. In this case, the operation state of the gear ratio selection device is referred to as "shift range" or "shift position".

As the fluid type power transmission device, one having a lockup clutch can be used. The lock-up clutch is for transmitting power by frictional force between the driving side rotating member and the driven side rotating member. Engagement / release of lockup clutch
A hydraulic control device is provided for controlling slip, that is, engagement pressure, in other words, torque capacity. The hydraulic control device has a hydraulic circuit, various solenoid valves, and the like.

As described above, when the transmission is used as the power transmission device 102, the gear ratio or the torque capacity between the input rotating member and the output rotating member of the transmission is hydraulically controlled. When a fluid type power transmission device having a lockup clutch is used as the power transmission device 102, the torque capacity of the lockup clutch is controlled by hydraulic pressure. When both the fluid type power transmission device and the transmission are used as the power transmission device 102, the drive side rotating member of the fluid type power transmission device is connected to the driving force source 100 side and the driven type of the fluid power transmission device is driven. The side rotating member
The input rotation member of the transmission is connected, and the output rotation member of the transmission is connected to the wheel 101 side.

An oil required device 103 for controlling the power of the power transmission device 102 is provided. The mechanism that constitutes the above-described hydraulic control device, that is, the hydraulic chamber, various solenoid valves, hydraulic circuit, and the like correspond to the oil required device 103.

An oil pump 104 for supplying oil to the oil-requiring device 103 is provided. The oil pump 104A is a kind of positive displacement fluid machine, and a rotary pump or a reciprocating pump can be used as the oil pump 104A. A gear pump, a vane pump, a screw pump, or the like can be used as the rotary pump. The gear pump may be either an external type or an internal type. The vane pump can be either balanced or unbalanced. The screw pump may be either a biaxial type or a triaxial type. An axial piston pump, a radial piston pump, a reciprocating piston pump, or the like can be used as the reciprocating pump. The oil pump 104A may be either a single oil pump or a plurality of oil pumps.

Further, a power unit 105A for driving the oil pump 104A is provided. The driving force source 100 may be shared with the power unit 105A, or may be provided separately from the driving force source 100. When the driving force source 100 is shared as the power unit 105A, an engine or an electric motor can be used as the power unit 105A. In addition to the driving force source, the power unit 105
Even when A is provided, an electric motor can be used as the power unit 105A. When the oil pump 104A is a rotary pump, the oil pump 104A is driven to rotate by the rotation of the output shaft of the power unit 105A, so that the oil in the oil pan 106A is removed.
The oil sucked from the suction port 107A of A and discharged from the discharge port 108A of the oil pump 104A is supplied to the oil required device 103.

When the oil pump 104A is a reciprocating pump, the rotation of the output shaft of the power unit 105A is converted into a reciprocating motion, and the operating member of the oil pump 104A is reciprocated so that the oil in the oil pan 106A becomes oil. The oil is sucked from the suction port 107A of the pump 104A, and the discharge port 108A of the oil pump 104A.
The oil discharged from is supplied to the oil-requiring device 103.

On the other hand, an actuator 109A for controlling the amount of oil supplied from the oil pump 104A to the oil required device 103 is provided. In this actuator 109A, the oil pump 104A is the power unit 105A.
Oil pump 1 when driven by A
This is for controlling the amount of oil supplied from 04A to the oil required device 103. In other words, it controls the discharge amount of the oil pump 104A.

An electronic control unit 110A for controlling the driving force source 100, the actuator 109A, and the oil-requiring unit 103 is also provided. Electronic control unit 1
A signal from a detection device 111A including various sensors and switches is input to 10A, and based on the input signal and previously stored data, the driving force source 100, the actuator 109A, and the oil required device. 103 is controlled. Power transmission device 102
When a transmission is used, the gear ratio between the input rotating member and the output rotating member of the transmission and the capacity of torque transmitted between the input rotating member and the output rotating member of the transmission are Controlled. When a hydraulic power transmission device having a lockup clutch is used as the power transmission device 102, the torque capacity of the lockup clutch is controlled.

Here, the gear ratio between the input rotary member and the output rotary member of the transmission, the capacity of the torque transmitted between the input rotary member and the output rotary member of the transmission, and the torque capacity of the lockup clutch. Since the power transmission state such as is controlled by the hydraulic pressure in the hydraulic chamber, depending on the target hydraulic pressure in the hydraulic chamber,
The amount of oil supplied to the oil requirement device 103 is controlled. That is, the amount of oil supplied from the oil pump 108 to the oil required device 103, that is, the target supply amount is calculated according to the target transmission ratio of the transmission and the target torque capacity of the transmission and the lockup clutch, and the oil required amount is calculated. The actual amount of oil supplied to the device 103 is
Actuator 109A so as to approach the target supply amount
To control.

Further, the present invention can be applied to any vehicle including a front-wheel drive vehicle, a rear-wheel drive vehicle, or a four-wheel drive vehicle in a vehicle having front wheels and rear wheels.

[0045]

Embodiment An embodiment of the present invention will be described below with reference to FIG. FIG. 2 is a skeleton diagram showing a power train of a vehicle Ve to which the invention is applied. This vehicle Ve
Is an FF vehicle (front engine / front drive; front-mounted front wheel drive vehicle), and the engine 1 is used as a driving force source of the vehicle Ve. This engine 1
Is a power unit that outputs power by burning fuel,
In this embodiment, a case where a gasoline engine is used as the engine 1 will be described.

A transaxle 3 is provided on the output side of the engine 1. The transaxle 3 has an inner hollow casing 4, and inside the casing 4, a torque converter 5, a forward / reverse switching mechanism 6, a belt type continuously variable transmission (CVT) 7 and a final reduction gear 8 are provided. ing. First, the configuration of the torque converter 5 will be described. Inside the casing 4, an input shaft 9 rotatable about the same axis (not shown) as the crankshaft 2 is provided, and a turbine runner 10 is provided at an end of the input shaft 9 on the engine 1 side. It is installed.

On the other hand, a front cover 12 is connected to the rear end of the crankshaft 2 via a drive plate 11, and the pump impeller 13 is connected to the front cover 12.
Are connected. The turbine runner 10 and the pump impeller 13 are arranged so as to face each other.
A stator 14 is provided inside the pump impeller 13. A lockup clutch 15 is provided at an end of the input shaft 9 on the front cover 12 side via a damper mechanism 16. A casing (not shown) formed by the front cover 12 and the pump impeller 13 configured as described above.
Oil as a working fluid is supplied therein.

With the above structure, the power of the engine 1 is transmitted from the crankshaft 2 to the front cover 12.
At this time, when the lockup clutch 15 is released, the power of the pump impeller 13 is transmitted to the turbine runner 10 by the kinetic energy of the fluid and then to the input shaft 9. In addition, pump impeller 1
The torque transmitted from the turbine runner 3 to the turbine runner 10 may be amplified by the stator 14. On the other hand, when the lockup clutch 15 is engaged, the power of the front cover 12 is transmitted to the input shaft 9 by the frictional force of the lockup clutch 15.

An oil pump 17 is provided between the torque converter 5 and the forward / reverse switching mechanism 6 inside the casing 4. A rotor (not shown) of the oil pump 17 and the pump impeller 13 are connected by a cylindrical hub 19. A body (not shown) of the oil pump 17 is fixed to the casing 4 side. With this configuration, the power of the engine 1 is transmitted to the rotor of the oil pump 17 via the pump impeller 13, and the oil pump 17 can be driven.

The forward / reverse switching mechanism 6 is provided in the power transmission path between the input shaft 9 and the belt type continuously variable transmission 7. The forward / reverse switching mechanism 6 has a double pinion type planetary gear mechanism 32. The planetary gear mechanism 32 includes a sun gear 33 provided at the end of the input shaft 9 on the belt type continuously variable transmission 7 side, and a ring gear 34 arranged on the outer peripheral side of the sun gear 33 concentrically with the sun gear 33. The pinion gear 35 meshed with the sun gear 33, the pinion gear 36 meshed with the pinion gear 35 and the ring gear 34, the pinion gear 35 and the pinion gear 36
Carrier 3 that holds the surroundings of the robot in an integrally revolvable state
7 and 7. Then, the carrier 37 and the primary shaft 21 are connected. Further, a clutch CR that connects or disconnects the power transmission path between the carrier 37 and the input shaft 9 is provided. Further, a brake BR that controls rotation and fixing of the ring gear 34 is provided on the casing 4 side.

The belt type continuously variable transmission 7 includes a primary shaft 2 arranged concentrically with the input shaft 9.
1 and a secondary shaft 22 arranged in parallel with the primary shaft 21. A primary pulley 23 is provided on the primary shaft 21, and a secondary pulley 24 is provided on the secondary shaft 22 side. The primary pulley 23 includes a fixed sheave 25 fixed to the primary shaft 21,
It has a movable sheave 26 configured to be movable in the axial direction of the primary shaft 21. Further, holding surfaces 54 and 55 that are inclined in the direction of forming the V-shaped groove M1 are formed on the opposing surfaces of the fixed sheave 25 and the movable sheave 26 by mutual combination.

Further, a hydraulic servo mechanism 27 is provided for moving the movable sheave 26 in the axial direction of the primary shaft 21 to move the movable sheave 26 and the fixed sheave 25 closer to and away from each other. This hydraulic servo mechanism 2
7 includes a hydraulic chamber described later and a piston (not shown) that operates in the axial direction of the primary shaft 21 according to the hydraulic pressure of the hydraulic chamber and that is connected to the movable sheave 26.

On the other hand, the secondary pulley 24 has a fixed sheave 28 fixed to the secondary shaft 22 and a movable sheave 29 configured to be movable in the axial direction of the secondary shaft 22. Further, holding surfaces 56 and 57 that are inclined in the direction of forming the V-shaped groove M2 are formed on the opposing surfaces of the fixed sheave 28 and the movable sheave 29 by mutual combination.

Further, a hydraulic servo mechanism 30 is provided which moves the movable sheave 29 in the axial direction of the secondary shaft 22 to move the movable sheave 29 and the fixed sheave 28 closer to and away from each other. This hydraulic servo mechanism 3
0 is provided with a hydraulic chamber described later, and a piston (not shown) that operates in the axial direction of the secondary shaft 22 by the hydraulic pressure of the hydraulic chamber and is connected to the movable sheave 29. The belt 31 is wound around the groove M1 of the primary pulley 23 and the groove M2 of the secondary pulley 24 configured as described above.

Belt type continuously variable transmission 7 and final reduction gear 8
An intermediate shaft 39 that is parallel to the secondary shaft 22 is provided in the power transmission path between and. The intermediate shaft 39 has a counter driven gear 40 and a final drive gear 41.
And are formed. A counter drive gear 42 is formed on the secondary shaft 22, and the counter drive gear 42 and the counter driven gear 40 are meshed with each other.

On the other hand, the final reduction gear 8 has a ring gear 43.
Having a final drive gear 41 and a ring gear 43.
And are meshed. The ring gear 43 is formed on the outer periphery of a differential case (not shown), and a plurality of pinion gears (not shown) are attached inside the differential case. Two side gears (not shown) are meshed with this pinion gear. The front drive shaft 44 is separately connected to the two side gears,
Each front drive shaft 44 has wheels (front wheels) 4
5 is connected.

FIG. 3 is a block diagram showing a control system of the vehicle Ve shown in FIG. An electronic control unit 104 that controls the entire vehicle Ve is provided.
Reference numeral 04 is composed of an arithmetic processing unit (CPU or MPU), a storage device (RAM and ROM), and a microcomputer mainly including an input / output interface.

To the electronic control unit 104, a signal from the ignition switch 105A, a signal from the engine speed sensor 105, a signal from the accelerator opening sensor 106,
A signal from the throttle opening sensor 107, a signal from the brake switch 108 that detects the operating state of the brake pedal, a signal from the shift position sensor 109 that detects the operating state of the shift lever 114, and an input rotational speed that detects the rotational speed of the primary pulley 23. Output rotation speed sensor 111 for detecting the signal of the sensor 110 and the rotation speed of the secondary pulley 24
Signal of the acceleration sensor 62, the signal of the turbine rotation speed sensor 63 that detects the rotation speed of the input shaft 9, the signal of the air conditioner switch 63A, the temperature of the oil flowing inside the casing 4 and the hydraulic circuit of the hydraulic control device 64. The signal from the oil temperature sensor 80, the signal from the wheel rotation speed sensor 81, the signal from the steering angle sensor 82 that detects the steering state of the steering wheel, the signal from the cooling water temperature sensor 83 that detects the cooling water temperature of the engine 1, and the vehicle Ve are A signal from the gradient detection sensor 84 for detecting the gradient of the road on which it is located, a signal from the hydraulic pressure sensor 85, and the like are input.

Based on the signal from the brake switch 108, whether or not the brake pedal is depressed, the amount of depression of the brake pedal, the depression speed of the brake pedal, etc. are detected. The shift position sensor 1
Based on the signal of 09, it is detected whether the drive position or the non-drive position is selected by operating the shift lever 114. Here, the drive position is a state in which a drive train from the engine 1 to the wheels 45, specifically, a state between the input shaft 9 and the primary shaft 21 is controlled to a state in which power transmission can be performed. It means the position to make. On the other hand, the non-driving position refers to the state between the input shaft 9 and the primary shaft 21.
It means the position that controls the power transmission to an impossible state. In this embodiment, drive positions are D (drive) position and B (brake) position.
The position or R (reverse) position can be selected.

In this embodiment, N (neutral) position and P (parking) are set as non-driving positions.
The position can be selected. Of the drive positions, the D position and the B position are forward positions, and the R position is a reverse position. The forward position means a position where a driving force in a direction for moving the vehicle Ve forward is generated when the power of the engine 1 is transmitted to the wheels 45. The reverse position means that when the power of the engine 1 is transmitted to the wheels 45, the vehicle Ve
It means the position where the driving force in the direction of moving backward is generated.

Further, the gear ratio of the belt type continuously variable transmission 7 can be calculated based on the signal of the input speed sensor 110 and the signal of the output speed sensor 111, and based on the signal of the output speed sensor 111. The vehicle speed can be calculated. Further, the braking device 116 includes a brake pedal (not shown), a master cylinder (not shown), a wheel cylinder (not shown) provided on all wheels, and an electromagnetic valve for controlling the hydraulic pressure of each wheel cylinder. Valve (not shown)
And an electronic control unit (not shown) for controlling the solenoid valve.

Various signals input from the electronic control unit 104 to the electronic control unit 104 and the electronic control unit 1 are also provided.
04, a signal for controlling the fuel injection control device 112, a signal for controlling the ignition timing control device 113, a signal for controlling the hydraulic control device 64, a signal for controlling the electronic throttle valve 115, and a braking operation based on the data stored in 04. Device 11
A signal for controlling 6 is output. This fuel injection amount control,
The engine output is controlled by performing at least one of ignition timing control and intake air amount control. Also,
In the braking device 116, the slip ratio of each wheel can be controlled by controlling the hydraulic pressure of each wheel cylinder based on the operation state of the brake pedal and the condition other than the operation state of the brake pedal. A system for controlling the slip ratio of each wheel in this way is called an antilock brake system (ABS).

Next, the hydraulic control device 64 will be described in detail. The hydraulic control device 64 controls engagement / release / slip of the lockup clutch 12, the belt type continuously variable transmission 7, and the forward / reverse switching mechanism 6. The relationship between the electronic control unit 104 and a part of the configuration of the hydraulic control unit 64 will be described based on FIG.

In this embodiment, the oil pump 17 shown in FIG. 4 is composed of a first oil pump 17A and a second oil pump 17B. First, the first
The oil pump 17A has a suction port 123 and a discharge port 1
Has 30. In addition, the second oil pump 17B
Has a suction port 124 and a discharge port 132. Then, the suction ports 123, 1 are connected to the suction oil passage 122 formed from the oil pan 120 via the strainer 121.
24 are connected in parallel.

Further, the primary regulator valve 12
5 is provided, the primary regulator valve 1
25 is a signal pressure input port 126 and an input port 12
7 and an escape port 128. The relief port 128 is connected to the lubricating oil passage 128A. Then, the electronic control unit 104 controls a linear solenoid (not shown) or a duty solenoid (not shown) to control the signal pressure input to the input port 126.

Oil passage 129 connected to input port 127
The discharge port 130 of the first oil pump 17A is connected to the. A hydraulic chamber 131C for the clutch CR and a hydraulic chamber 131B for the brake BR are provided.
Between the hydraulic chambers 131C and 131B and the oil passage 129,
A manual valve 114A that operates based on the operation of the shift lever 114 is provided. The manual valve 114A has an input port 180 connected to the oil passage 129.
And output ports 181, 182. The output port 181 is connected to the hydraulic chamber 131C, and the output port 182 is connected to the hydraulic chamber 131B. Further, in the oil passage 129, the hydraulic chamber 131D of the hydraulic servo mechanism 27 is provided.
And the hydraulic chamber 131E of the hydraulic servo mechanism 30 are connected.

On the other hand, a direction control valve 133 is arranged between the discharge port 132 of the second oil pump 17B and the oil passage 129. The directional control valve 133 is provided on the spool 13
4, a signal pressure chamber 135 arranged to face one end of the spool 134, and a spring 136 for urging the spool 134 toward the signal pressure chamber 135. Spool 134
The two lands 137 and 138 are formed in the input port 139 by the operation of the spool 134.
And the output port 140 or the drain port 141 are selectively connected or disconnected. Furthermore, the electronic control unit 10
4 is provided, and the signal pressure output from the output port 143 of the solenoid valve 142 is input to the signal pressure chamber 135.

The solenoid valve 142 is turned on.
Either an off solenoid valve or a linear solenoid valve may be used. The on / off solenoid valve is a valve for switching the signal pressure output from the output port 143 between high pressure and low pressure by switching between energization (on) and de-energization (off) of the solenoid. It means a solenoid valve that can. The linear solenoid valve is capable of switching between energization (ON) and non-energization (OFF) of the solenoid, and is output from the output port 143 by arbitrarily setting the ratio of on time (duty ratio). It means a solenoid valve that can linearly control the signal pressure.

2 and 3 and the corresponding relationship with the present invention, the forward / reverse switching mechanism 6 and the belt type continuously variable transmission 7 correspond to the power transmission device of the present invention. , The hydraulic chamber 131, the primary regulator valve 125, the input port 127, and the oil passage 129 correspond to the oil required device of the present invention, the engine 1 corresponds to the power unit of the present invention, and the vehicle Ve corresponds to the moving body of the present invention. Regarding the forward / reverse switching mechanism 6, the crankshaft 2 and the input shaft 9 correspond to one rotating member of the present invention, and the primary shaft 21 corresponds to the other rotating member of the present invention. Further, in the belt type continuously variable transmission 7, the primary shaft 21 corresponds to one rotating member of the present invention, and the secondary shaft 2 corresponds to the other rotating member of the present invention. Further, the primary shaft 21 corresponds to the output member of the present invention.

Then, the electronic control unit 104 is controlled by the engine 1 and the lockup clutch 1 based on various signals.
5, various data is stored in advance in order to control the forward / reverse switching mechanism 6, the belt type continuously variable transmission 7, the braking device 116, and the like. For example, the shift position sensor 1
The forward / reverse switching mechanism 6 is controlled based on the signal of 09. First, when the D position or B position is selected, the clutch CR is engaged, the brake BR is released, and the input shaft 9 and the primary shaft 21 are directly connected. In this state, when the torque of engine 1 is transmitted to input shaft 9 via torque converter 5, input shaft 9, carrier 37 and primary shaft 21 rotate integrally. The torque of the primary shaft 21 passes through the primary pulley 23, the belt 31, and the secondary pulley 24, and
2 is transmitted to the final speed reducer 8 via the intermediate shaft 39, and then the torque is further transmitted to the wheels 45.
A driving force for advancing e is generated.

On the other hand, when the R position is selected,
The clutch CR is released and the brake BR is engaged to fix the ring gear 34. Then, as the input shaft 9 rotates, the pinion gears 35, 3
6 revolves around their own axis while rotating, and the carrier 37 rotates in the direction opposite to the rotation direction of the input shaft 9. As a result, the primary shaft 21, the secondary shaft 22, and the intermediate shaft 39 are
The vehicle rotates in the opposite direction to the case of the position or the B position, and a driving force for retracting the vehicle Ve is generated.

By the way, the engagement pressure of the clutch CR when the N position or the P position is selected is
It is controlled to be lower than the engagement pressure of the clutch CR when the D position or the B position is selected. Thus, when the N position or the P position is selected, the input shaft 9 and the primary shaft 2
A state where it is impossible to transmit power to and from 1,
This is the so-called neutral state.

Further, in this embodiment, even when the D position is selected, the so-called "so-called" control for controlling the transmission of power between the input shaft 9 and the primary shaft 21 is impossible. Neutral control "can be performed. The neutral control is executed when the precondition for performing the neutral control is satisfied. This precondition is, for example,
It is established when all the matters that the D position is selected, the accelerator pedal is not depressed, the brake pedal is depressed, and the vehicle speed is zero are detected. When this precondition is satisfied, the engagement pressure of the clutch CR is D position or B position.
It is controlled to be lower than the engagement pressure of the clutch CR when the position is selected and the precondition is not satisfied.

In this way, when the N position or the P position is selected, or "neutral control" is performed.
When performing the above, there are two types of modes for controlling the clutch CR. Specifically, there are a control mode in which the clutch CR is completely released, and a control mode in which the clutch CR is engaged with an engagement pressure at which power cannot be transmitted.

Further, the operating state of the engine 1 is set to the optimum state based on the acceleration request of the vehicle Ve judged from the conditions such as the vehicle speed and the accelerator opening degree, the data stored in the electronic control unit 104, and the like. Then, the gear ratio of the belt type continuously variable transmission 7 is controlled. The gear ratio of the belt type continuously variable transmission 7 is the same as that of the belt 3 in the primary pulley 23.
It changes based on the ratio of the winding radius of 1 and the winding radius of the belt 31 on the secondary pulley 24. The winding radius of the belt 31 on the primary pulley 23 is adjusted by changing the groove width M1, and the winding radius of the belt 31 on the secondary pulley 24 is adjusted by changing the groove width M2. The groove width M1 means the distance between the holding surface 54 and the holding surface 55 in the axial direction of the primary shaft 21. The groove width M2 means the distance between the holding surface 56 and the holding surface 57 in the axial direction of the secondary shaft 22.

Further, the electronic control unit 104 stores a lockup clutch control map having the accelerator opening and the vehicle speed as parameters, and the lockup clutch 15 is engaged / released based on this lockup clutch control map.・ Slip conditions are controlled.

Next, a specific control example in this embodiment will be described with reference to the flowchart of FIG. Figure 1
Corresponds to the invention of claim 1 and claim 2. When the control of FIG. 1 is started, it is determined whether either the N position is selected or the neutral control is being executed (step S1). When a negative determination is made in step S1, the control routine is ended via step S2. In step S2, the following control is performed. For example, when the D position is selected, “the torque transmitted from the input shaft 9 to the primary shaft 21” is calculated. Then, the target hydraulic pressure of the hydraulic chamber 131 is calculated based on the calculated torque. Further, the hydraulic pressure of the oil passage 129 is adjusted based on this target hydraulic pressure. Here, the “torque transmitted from the input shaft 9 to the primary shaft 21” is calculated based on the engine output, the speed ratio of the torque converter 5, and the like.

When controlling the hydraulic pressure of the oil passage 129, the electronic control unit 104 performs various input signal determination processes, and the primary regulator valve 125 and the solenoid valve 142 are controlled based on the determination results. . First, the primary regulator valve 125
By controlling the signal pressure input to the signal pressure input port 126 of the
The amount of oil leaked to 28 is adjusted.

On the other hand, the power of the engine 1 drives the first oil pump 17A and the second oil pump 17B, and the oil discharged from the first oil pump 17A passes through the oil passage 129. It is supplied to the input port 127. By the way, in a system using an on / off solenoid valve as the solenoid valve 142, when the process proceeds to step S2, the signal pressure of the signal pressure chamber 135 of the directional control valve 133 is reduced to a low pressure from the output port 143 of the solenoid valve 142. Controlled. Then, the spool 134 is biased toward the signal pressure chamber 135 by the biasing force of the spring 136. As a result, as shown in the left half of FIG. 4, the input port 139 and the output port 140 are connected and the input port 139 and the drain port 141 are cut off.

Therefore, the oil discharged from the second oil pump 17B is supplied to the input port 127 via the input port 139 and the output port 140 of the directional control valve 133 and the oil passage 129. Thus, the oil discharged from the first oil pump 17A and the oil discharged from the second oil pump 17B are both input port 1
The hydraulic pressure in the oil passage 129 and the hydraulic pressure in the hydraulic chamber 131 are controlled based on the amount of oil that is supplied to the input port 127 and is leaked from the input port 127 to the escape port 128.

On the other hand, in a system using an on / off solenoid valve as the solenoid valve 142, if a positive determination is made in step S1, it is input to the signal pressure chamber 135 of the directional control valve 133. The signal pressure is controlled to be higher than that when the determination is negative in step S1 (step S3), and this control routine ends. By the control in step S3, as shown in the right half of the directional control valve 133 in FIG.
Operates to compress the spring 136 to connect the input port 139 and the drain port 141, and disconnect the input port 139 and the output port 140.

Then, the oil discharged from the second oil pump 17B is transferred to the input port 13 of the directional control valve 133.
Oil pan 1 via 9 and drain port 141
Returned to 20. That is, the oil discharged from the second oil pump 17B is not supplied to the primary regulator valve 125, and only the oil discharged from the first oil pump 17A is supplied to the primary regulator valve 125. Therefore, when the process proceeds to step S3, the amount of oil supplied from the second oil pump 17B to the primary regulator valve 125 is
If the process proceeds to step S2, the second oil pump 17
The amount of oil supplied from B to the primary regulator valve 125 becomes smaller. As the solenoid valve 142, a linear solenoid valve may be used instead of the on / off solenoid valve.

When the determination in step S1 is affirmative, the signal pressure input to the signal pressure port 126 of the primary regulator valve 125 is also negative in step S1. Is different from the signal pressure input to the signal pressure port 126 of. That is, when the determination in step S1 is negative, the amount of oil leaked from the input port 127 to the escape port 128 is larger than the amount of oil leaked from the input port 127.
The amount of oil leaked into the tank is smaller.

As described above, in the control example of FIG.
In both step S2 and step S3, the power of the engine 1 drives the first oil pump 17A and the second oil pump 17B. However, the amount of oil supplied from the second oil pump 17B to the oil passage 129 side in step S3 is smaller than the amount of oil supplied from the second oil pump 17B to the oil passage 129 side in step S2. Few. That is, the oil discharge flow rate of the entire oil pump 17 is controlled to be optimal with respect to the oil flow rate required on the oil passage 129 side.

That is, the load for driving the second oil pump 17B in step S3 is smaller than that for driving the second oil pump 17B in step S2. And in this embodiment,
The second oil pump 17B is driven by the torque of the engine 1.
Since the engine torque is driven, the engine torque required in step S3 is lower than the engine torque required in step S2. Therefore, the fuel efficiency of the engine 1 can be improved in step S3 as compared with step S2.

Here, the correspondence between the functional means shown in FIG. 1 and the configuration of the present invention will be described. Steps S1 to S3 correspond to the oil supply state control means of the present invention. The power transmitted from the input shaft 9 to the primary shaft 21 corresponds to the "power transmitted by the power transmission device" of the present invention, and the amount of oil supplied from the oil pump 17 to the oil passage 129 side, or The oil discharge pressure corresponds to the "supply state of oil supplied from the oil pump to the oil required device" of the present invention.

Next, another control example will be described with reference to FIG. The control example of FIG. 5 corresponds to the invention of claim 3, and specifically, when controlling the gear ratio of the belt type continuously variable transmission 7, the oil is supplied from the oil pump 17 to the oil passage 129 side. This is done when adjusting the amount of oil to be used. That is, the gear ratio of the belt type continuously variable transmission 7 is determined by the electronic control unit 1
This is performed based on the shift map stored in 04. This shift map serves as a reference for selecting the ratio of the rotation speeds of the primary shaft 21 and the secondary shaft 22, that is, the gear ratio, using the vehicle speed and the accelerator opening as parameters, for example. Then, the winding radius of the belt 31 around the primary pulley 23 and the winding radius of the belt 31 around the secondary pulley 24 are adjusted so that the actual gear ratio approaches the selected gear ratio, that is, the target gear ratio. It

Therefore, when the control of FIG. 5 is started, it is determined whether the hydraulic pressure in the hydraulic chamber 131E is less than the target pressure (step S11). Here, the target pressure is the control hydraulic pressure of the secondary pulley 24, and the primary shaft 21
It is set according to the torque and the gear ratio input to.

If the determination in step S11 is affirmative, the oil passage 129 from the second oil pump 17B is changed.
The control for setting a large amount of oil supplied to the side is performed (step S12), and this control routine is ended. The control performed in step S12 is the same as step S1 in FIG.
This is similar to the control of 2. On the other hand, step S11
If the determination is negative, the control routine ends.

As described above, according to the control example of FIG. 5, the oil pump 1 is operated according to the operating conditions of the belt type continuously variable transmission 7.
7, the target oil amount to be supplied to the oil passage 129 side is judged, and the actual oil amount supplied from the oil pump 17 to the oil passage 129 side is controlled based on the judgment result. That is, the discharge amount of the oil pump 17 can be controlled according to the amount of oil required on the oil passage 129 side. Therefore, the engine torque required to drive the oil pump 17 can be adjusted according to the amount of oil required on the oil passage 129 side, which can contribute to the improvement of fuel economy of the engine 1.

Here, the correspondence relationship between the functional means shown in FIG. 5 and the configuration of the present invention will be described. Steps S11 to S12 correspond to the oil supply state control means of the present invention. In addition, the hydraulic chamber 131E in step S11
The hydraulic pressure of corresponds to the "actual supply state of oil" of the present invention, and the target pressure shown in step S11 corresponds to the "target supply state of oil" of the present invention. In the above embodiment, the control oil pressure of the secondary pulley 24 is illustrated as the target pressure, but the oil pressure of the clutch or the brake may be used as the target oil pressure.

FIG. 6 is a flowchart showing another control example. The control example of FIG. 6 is the invention of claim 4 and claim 5
It corresponds to the invention of. In the control example of FIG. 6, the amount of oil supplied from the oil pump 17 to the oil passage 129 is controlled based on a request for controlling the speed of the vehicle Ve. When the control of FIG. 6 is started, whether or not there is a request to rapidly decelerate the vehicle Ve, or the driver operates the shift lever 14 to change the gear ratio of the belt-type continuously variable transmission 7. It is determined whether or not (manual shift operation) has been performed.

The above items and items will be described in detail. First of all, the item of anti-lock brake
The determination can be made based on information such as the system state, the deceleration of the vehicle Ve, the throttle opening and its changing speed, the state of the braking device 116, and the shift position. That is, the anti-lock brake system is operating, the deceleration of the vehicle Ve is equal to or greater than a predetermined value, the throttle opening is less than or equal to a predetermined value, and the throttle opening reduction speed is equal to or less than a predetermined value. At least one of the following information: the value is equal to or more than a value, the increase speed of the operation stroke of the brake pedal is equal to or more than a predetermined value, and the duration of the state in which the brake pedal is depressed is a predetermined time or more. When the information is detected, the item is positively judged.

Next, the following items will be explained.
At least one of the information that the position has been changed to the D position, the N position has been changed to the R position, the D position has been changed to the B position, and the B position has been changed to the D position. When one piece of information is detected, the item is positively determined.

Then, in step S21, when both the items 1 and 2 are negatively determined, this control routine is ended.

On the other hand, in step S21,
If the item (1) or at least one of the items (2) is affirmatively determined, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is controlled to be larger than the oil supply amount in step S21 (step S2).
2) The control routine ends. The specific control in step S22 is the same as the control in step S2 in FIG.

For example, the positive determination of item (1) means that the state of the vehicle Ve is "a vehicle state in which the vehicle speed once decreases or the vehicle speed becomes" zero ", and then the vehicle may be accelerated again. It is in. The case is mentioned.
In such a case, before the vehicle Ve is accelerated again, the speed change control of the belt type continuously variable transmission 7 is changed to a speed change ratio larger than the speed change ratio before the acceleration, and the belt 31 is controlled. It is desirable to quickly perform the control for changing the tension of No. 2 to the tension according to the torque transmitted based on the gear ratio at the time of reacceleration.

Therefore, in step S22, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is controlled to be larger than that before step S21.
By performing such control, the vehicle Ve is once decelerated or stopped, and the vehicle Ve is re-accelerated or restarted while the speed ratio of the belt type continuously variable transmission 7 is set to the maximum speed reduction ratio. In this case, the torque capacity of the belt 31 can be quickly increased. Therefore, the shift responsiveness of the belt-type continuously variable transmission 7 is improved, and the deterioration of the acceleration performance of the vehicle Ve or the restart performance after the stop can be suppressed, and the drivability is improved.

Next, a case where the item (1) is positively determined will be described. First, when the shift position is the N position, the engagement pressure of the clutch CR and the engagement pressure of the brake BR are controlled to be equal to or lower than a predetermined value. Then, when the N position is switched to the D position, the engagement pressure of the clutch CR needs to be changed to a higher engagement pressure than when the N position is selected. Further, when the N position is switched to the R position, the piston corresponding to the brake BR makes a stroke, so that it is necessary to increase the oil flow rate by that stroke.

Therefore, in step S22, control is performed to increase the oil pressure in the hydraulic chamber 131C of the clutch CR or the hydraulic chamber 131B of the brake BR by increasing the amount of oil supplied from the oil pump 17 to the oil passage 129 side. ing. By performing such control,
Control for changing the engagement pressure of the clutch CR or the brake BR to the engagement pressure according to the shift position can be quickly performed. Therefore, it is possible to improve fuel efficiency without deteriorating the generation / cancellation timing of the output torque due to the shift position switching.

Next, of the above items, the case where the D position is changed to the B position will be described. D
The position and the B position are common in that they are both drive positions and forward positions, but the shift map selected at the D position and the shift map selected at the B position are different. This shift map uses vehicle speed and accelerator opening as parameters.
It is a map for setting the gear ratio of the belt type continuously variable transmission 7. Specifically, if the vehicle speed and the accelerator opening are the same, the gear ratio set based on the B position shift map is set to be larger than the gear ratio set based on the D position shift map. The two shift maps are different in that a larger gear ratio is more easily selected.

Whether the D position is switched to the B position or the B position is switched to the D position, the process proceeds to step S22 and the hydraulic chamber 131D or 131E is operated.
By increasing the amount of oil supplied to the engine, it is possible to obtain the effect of improving the speed change response.

Here, the correspondence between the functional means shown in FIG. 6 and the configuration of the present invention will be described. Step S2
1 and step S22 correspond to the oil supply state control means of the present invention. Further, the vehicle speed corresponds to the “speed of the moving body” of the present invention, and the items and items shown in step S21 correspond to the “request for controlling the speed of the moving body” in the present invention, and the control is performed in step S22. The amount of oil to be generated corresponds to the "oil supply state" in the present invention. Further, among the items used in step S21, "changed from the B position to the D position or changed from the D position to the B position" is a "request for controlling the rotation speed ratio". Equivalent to.

Next, another control example will be described with reference to the flowchart of FIG. The control example of FIG. 7 corresponds to the invention of claim 6, and the control example of FIG. 7 is based on the progress state of the shift control of the belt type continuously variable transmission 7 from the oil pump 17 to the oil passage 129. It controls the amount of oil supplied to the side. When the control of FIG. 7 is started, when changing the gear ratio of the belt type continuously variable transmission 7, the “difference a” between the absolute value of the actual shift speed drreal and the absolute value of the target shift speed drtarget is It is determined whether it is larger than "zero" (step S31).

Here, the "gear speed" means the degree of change of the gear ratio, in other words, the rate of change of the gear ratio.
Then, the target shift speed can be obtained based on conditions such as the vehicle speed, the change state of the accelerator opening degree, the torque transmitted to the primary shaft 21, and the like.

When the determination in step S31 is affirmative, the amount of oil supplied from the oil pump 17 to the oil passage 129 is controlled to be larger than the amount of oil at the time of determination in step S31 (step S32). .
Subsequent to step S32, "control for changing the threshold value b used for controlling the solenoid valve 142 when adjusting the amount of oil supplied from the oil pump 17 to the oil passage 129" is performed (step S33), This control routine ends.

That is, after step S33, "If the conditions for determining the target speed change speed are the same as the conditions at the time of determination in step S31,
By controlling the solenoid valve 142 using the threshold value changed in S34, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is adjusted.

On the other hand, if the determination in step S31 is negative, it is determined whether or not the absolute value of the shift speed drreal is greater than the threshold value b (step S3).
4). When a negative determination is made in step S34, it is determined that the amount of oil supplied from the oil pump 17 to the oil passage 129 is appropriate, and this control routine ends. For example, when the actual speed change speed and the target speed change speed are equal, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is controlled to the same amount as at the determination time of step S31.

On the other hand, when the affirmative determination is made in step S34, the threshold value b is changed and the flow rate of the oil supplied from the oil pump 17 to the oil passage 129 is changed to
The control is performed to make the amount less than the determination time of step S31 (step S36), and this control routine is ended.

As described above, in the control example of FIG. 7, when the process proceeds to step S36, the amount of oil supplied from the oil pump 17 to the oil passage 129 is smaller than when the process proceeds to step S32. Step S3 in the embodiment of
You can obtain the same effect as when you proceed to. Also,
If the process proceeds to step S32, the belt type continuously variable transmission 7
It is possible to improve the speed change response of the.

Here, the correspondence relationship between the functional means shown in FIG. 7 and the configuration of the present invention will be described. Step S31
The step S34 corresponds to the oil supply state control means of the present invention. Also, from the oil pump 17 to the oil passage 1
The amount of oil supplied to the 29 side corresponds to the “oil supply state” of the present invention, the “actual shift speed” corresponds to the “actual progress state” of the present invention, and the “target shift speed” is This corresponds to the "target progress state" of the present invention.

Further, another control example will be described with reference to the flowchart of FIG. The control example of FIG. 8 corresponds to the invention of claim 7, and the control example of FIG. 8 adjusts the amount of oil supplied from the oil pump 17 to the oil passage 129 side based on the temperature of the oil. It is a thing. When the control of FIG. 8 is started, it is determined whether the actual oil temperature obtained from the signal of the oil temperature sensor 80 exceeds a predetermined value of the oil temperature stored in the electronic control unit 104 ( Step S
41).

If the determination in step S41 is negative, the amount of oil supplied from the oil pump 17 to the oil passage 129 is controlled to the required amount (step S42), and this control routine ends. The required amount of oil is determined based on the shift position, the gear ratio of the belt type continuously variable transmission 7, the engine torque, the speed ratio of the torque converter 5, and the like. By performing the control in step S42, it is possible to prevent the amount of oil supplied to the lubricating oil passage 129A via the relief port 128, that is, the amount of lubricating oil, from increasing more than necessary. Therefore, an increase in drag resistance of the friction engagement device provided in the transaxle case 4 can be suppressed, or an increase in stirring resistance due to rotation of the rotating member can be suppressed. The loss can be suppressed and the fuel efficiency of the engine 1 can be improved.

On the other hand, when the affirmative determination is made in step S41, the oil amount larger than the oil amount supplied in step S42 is supplied from the oil pump 17 to the oil passage 1.
It is supplied to the 29 side (step S43), and this control routine is ended. That is, oil has a characteristic that its viscosity changes according to temperature changes. Therefore, when the temperature of the oil is equal to or higher than the predetermined temperature, the viscosity of the oil decreases. As a result, the amount of oil leaking from the valve body that constitutes the hydraulic control device 64 or the gap between the components such as the oil pump 17 increases.

That is, even when the amount of oil supplied from the oil pump 17 to the oil passage 129 side is adjusted based on the target oil amount required on the oil passage 129 side, the oil pump 17 actually moves from the oil passage 17 side to the oil passage 129 side. The amount of oil supplied to is smaller than the target amount of oil. Therefore, when an oil leak is predicted to occur in the oil supply path, by increasing the amount of oil supplied from the oil pump 17 to the oil passage 129 side as in step S43, the oil pump 17 to the oil passage 129 side is increased. The amount of oil actually supplied to can be brought close to the target amount of oil.

In step S42, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is
In step S43, the oil path from the oil pump 17 to the oil passage 1
The specific control for increasing the amount of oil supplied to the 29 side is the same as the control of step S3 and step S2 of FIG. Further, since the amount of oil supplied from the oil pump 17 to the oil passage 129 side in step S42 is smaller than the amount of oil supplied from the oil pump 17 to the oil passage 129 side in step S43, the control of step S42 is performed. When it is performed, the same effect as that of the control example of FIG. 1 can be obtained.

FIG. 9 is a diagram showing another embodiment of the hydraulic control device 64. In the embodiment of FIG. 9, the oil pump 17 has a first oil pump 17A, a second oil pump 17B, and a third oil pump 17C. The third oil pump 17C has a suction port 150 and a discharge port 151. Then, the suction oil passage 12 formed from the oil pan 120 via the strainer 121
Two suction ports 123, 124, and 150 are connected in parallel with each other.

On the other hand, a direction control valve 152 is arranged between the discharge port 151 of the third oil pump 17C and the oil passage 129. The directional control valve 152 is provided on the spool 15
3, a signal pressure chamber 154 disposed to face one end of the spool 153, and a spring 155 that biases the spool 153 toward the signal pressure chamber 154. Spool 153
Two lands 156 and 157 are formed on the output port 157, and the input port 158 and the output port 159 or the drain port 160 are selectively connected or disconnected by the operation of the spool 153.

Further, a solenoid valve 161 controlled by the electronic control unit 104 is provided, and the signal pressure output from the output port 162 of the solenoid valve 161 is input to the signal pressure chamber 154. As the solenoid valve 161, either an on / off solenoid valve or a linear solenoid valve may be used. The meanings of the on / off solenoid valve and the linear solenoid valve are the same as those described in the description of FIG. Note that the other configurations in FIG. 9 are the same as the configurations in FIG. 4, so the same reference numerals as those in FIG.

Also in the embodiment of FIG. 9, the same operation as that of the embodiment of FIG. 4 occurs with respect to the same components as those of the embodiment of FIG. Further, in the embodiment of FIG. 9, the amount of oil supplied from the third oil pump 17C to the oil passage 129 is adjusted based on the signal pressure input from the solenoid valve 161 to the signal pressure chamber 154. Specifically, when the signal pressure chamber 154 is controlled to a low pressure, the input port 158 and the output port 159 communicate with each other and the drain port 160 is closed, as shown in the left half of FIG.

On the other hand, when the signal pressure chamber 154 is controlled to a high pressure, the input port 158 and the drain port 160 communicate with each other and the output port 159 is closed, as shown in the right half of FIG. In this way, by controlling the pressure of the signal pressure chamber 154, the third oil pump 17C
The amount of oil supplied from the oil passage 129 is adjusted. That is, in the embodiment of FIG. 9, the solenoid valve 14
By controlling 2 and the solenoid valve 161 separately, the amount of oil supplied from the oil pump 17 to the oil passage 129 can be controlled in three stages. In the vehicle having the hydraulic control device 64 of FIG. 9, the control of FIG.
It is also possible to perform the control shown in FIG.

FIG. 10 is a diagram showing another embodiment of the hydraulic control device 64. 10, components similar to those in FIG. 4 are designated by the same reference numerals as those in FIG. 4 and their description is omitted. In the embodiment of FIG. 10, a third oil pump 17D is provided in parallel with the second oil pump 17B. That is, the third oil pump 17D has a suction port 163 and a discharge port 164. And
The suction port 163 is connected to the oil pan 120 side, and the discharge port 164 is connected to the input port 139 of the directional control valve 133.

In the embodiment of FIG. 10, the oil is supplied from the second oil pump 17B and the third oil pump 17D to the oil passage 129 side based on the signal pressure input from the solenoid valve 142 to the signal pressure chamber 135. The amount of oil to be adjusted is adjusted. That is, from the oil pump 17 to the oil passage 1
The amount of oil supplied to the 29 side is adjusted. And
In a vehicle having the hydraulic control device 64 of FIG.
The control shown in FIG. 5 and the control shown in FIGS. 5 to 8 can also be performed.

FIG. 11 is a diagram showing another embodiment of the hydraulic control device 64. In the embodiment of FIG. 11, the oil passage 12
A directional control valve 165 is provided between the valve 9 and the discharge port 132 of the second oil pump 17B. That is, FIG.
The embodiment shown in FIG. 1 is an example in which a directional control valve 165 is provided instead of the directional control valve 133 shown in FIG. The directional control valve 165 includes a spool 166, lands 167, 168, 169 formed on the spool 166, and the input port 1.
70 and output port 171 and drain port 1
72 and. Further, a signal pressure chamber 173 facing one end side of the spool 166 is formed, and a spring 174 for urging the spool 166 toward the signal pressure chamber 173 side is provided. The output port 179 of the solenoid valve 178 is connected to the signal pressure chamber 173.

Further, the directional control valve 165 is provided with a line pressure input port 175. The line pressure input port 175 communicates with the output port 182 of the manual valve 114A. The directional control valve 165 is connected to the output port 17 that communicates with the hydraulic chamber 131B of the brake BR.
6 and the drain port 17 communicating with the oil pan 120
7 and 7. Other configurations in FIG. 11 are similar to those in FIG.

11 instead of the directional control valve 133 of FIG.
An example of control that can be applied to the hydraulic control device 64 using the directional control valve 165 will be described based on the flowchart of FIG. The control example of FIG. 12 corresponds to the invention of claim 8. When the control of FIG. 12 is started, "R
Whether or not a position has been selected "is determined (step S51). If the determination in step S51 is negative, this control routine ends.

If the determination in step S51 is affirmative, it is determined "whether the actual vehicle speed V exceeds the predetermined vehicle speed Vr" (step S52). This step S
If the determination in step 52 is affirmative, in order to prevent the torque according to the R position of the belt type continuously variable transmission 7 from exceeding a predetermined value, the oil pump 17 is connected to the oil passage 129.
The amount of oil supplied to the side is controlled to a small amount (step S5
2) The control routine ends.

The control in step S52 will be specifically described. When the solenoid valve 178 is an on / off solenoid valve, the signal pressure input to the signal pressure chamber 173 is controlled to be high. Then, the output port 171 of the directional control valve 165 is closed and the input port 170 is closed.
And the drain port 172 are communicated with each other. Therefore, the amount of oil supplied from the second oil pump 17B to the oil passage 129 side is reduced. That is, the total amount of oil supplied from the oil pump 17 to the oil passage 129 side decreases. On the other hand, when a negative determination is made in step S52, the belt type continuously variable transmission 7 outputs a torque equal to or more than a predetermined value in accordance with the R position, that is, the oil pump 17 supplies the oil passage. The total amount of oil supplied to the 129 side increases.

That is, in the control example of FIG. 12, when the R position is selected while the vehicle Ve is traveling, it is avoided that the engagement pressure of the brake BR is increased to a predetermined value or more. Further, in step S53, the amount of oil supplied from the oil pump 17 to the oil passage 129 side is determined by the oil pump 17 from the oil passage 129 in step S54.
Less than the amount of oil supplied to the side. Therefore, when the control of step S53 is performed, the number of parts is reduced because the directional control valve 165 also has a function of prohibiting the R position.

The correspondence between the functional means shown in FIG. 12 and the configuration of the present invention will be described. Steps S51 to S54 correspond to the oil supply state control means of the present invention. Further, the determination content of step S51 corresponds to the "request for controlling the rotation direction of the output member" of the present invention, and the amount of oil supplied from the oil pump 17 to the oil passage 129 and the hydraulic chamber 131B of the brake BR is This corresponds to the "oil supply state" of the present invention. The rotation direction of the output member can also be referred to as the “vehicle traveling direction”.

As described above, FIG. 4, FIG. 9, FIG.
As shown in FIG. 3, the oil pump 17 including a plurality of oil pumps is an oil pump capable of changing the amount of oil supplied to the oil passage 129 side, in other words, the discharge amount, that is, a variable displacement type oil pump. Can be said to be Further, in each of the embodiments of the hydraulic control device 64 described above, when the ON / OFF solenoid is used as the solenoid valves 142, 161, 178, the case where the signal pressure chamber of the directional control valve becomes high pressure by the ON control will be described. However, the signal pressure chamber of the directional control valve can be configured to have a high pressure by the off control. That is, the solenoid valve may be configured such that the correspondence relationship between the current value supplied to the solenoid valve and the flow rate of the oil supplied from the oil pump 17 to the oil passage 129 is reversed. Further, when using on / off solenoids as the solenoid valves 142, 161, 178, either a two-way valve or a three-way valve may be used.

The above control examples are performed on the assumption that the system shown in FIG. 3 functions normally. Specifically, it is assumed that the system that determines the amount of oil required by the oil required device and the system that adjusts the amount of oil supplied from the oil pump to the oil required device are normal. Each of the above control examples can be executed independently, or a plurality of control examples can be combined.

Further, various configurations described with reference to FIG. 2, various configurations described with reference to FIG. 3, various configurations described with reference to FIG. 4, various configurations described with reference to FIG. Of the configurations described in FIG. 10, various configurations described based on FIG. 10, and various configurations described based on FIG. 11, a single configuration or a plurality of configurations is defined in each of the claims. Can be added to at least one of the inventions of. The plurality of configurations may be the configurations described based on a single drawing or the configurations described based on a plurality of drawings.

[0134]

As described above, according to the invention of claim 1, when the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal,
The supply state of the oil supplied from the oil pump to the oil required device can be controlled to a state according to the power transmitted by the power transmission device. Therefore, the power transmitted by the power transmission device can be brought close to a desired state,
It is possible to suppress a decrease in power transmission performance.

According to the invention of claim 2, in addition to the same operation as the invention of claim 1, if the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal, the power transmission device is provided. The load of the power unit necessary for driving the oil pump can be changed depending on whether or not the power transmitted in step S1 is less than or equal to a predetermined value.

According to the third aspect of the present invention, when the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal, the actual supply of oil supplied from the oil pump to the oil required device is performed. The state can be brought closer to the target supply state of oil. Therefore, the power transmitted by the power transmission device can be brought close to the target state.

According to the fourth aspect of the present invention, when the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal, the speed of the moving body moved by the power transmitted by the power transmission device. According to the above, the supply state of the oil supplied from the oil pump to the oil required device is controlled. Therefore, the speed of the moving body can be brought close to the desired state, and the deterioration of the speed control performance of the moving body can be suppressed.

According to the fifth aspect of the invention, when the system for adjusting the amount of oil supplied from the oil pump to the oil-requiring device is normal, the rotation speed between one rotating member and the other rotating member is increased. Based on the request to control the ratio of the oil, the supply state of the oil supplied from the oil pump to the oil required device is controlled. Therefore, the ratio of the rotational speeds of the one rotary member and the other rotary member can be brought close to the desired state, and the performance of the power transmission device can be prevented from being degraded.

According to the invention of claim 6, in addition to the same operation as that of the invention of claim 5, the actual progress state of the process of changing the rotation speed between one rotating member and the other rotating member. And the target progress state, the supply state of the oil supplied from the oil pump to the oil required device is controlled. Therefore, the changed state of the rotation speed between the one rotating member and the other rotating member can be brought close to the desired state, and the performance of the power transmission device can be prevented from being degraded.

According to the seventh aspect of the invention, when the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal, the supply state of the oil supplied from the oil pump to the oil required device is changed. , Can be adapted to the temperature characteristics of the oil. That is, at low temperatures, oil leakage is small and volumetric efficiency is high. Therefore, even if the discharge amount of the oil pump is small, it is possible to prevent the performance of the power transmission device from deteriorating due to insufficient oil amount.

According to the eighth aspect of the invention, when the system for adjusting the amount of oil supplied from the oil pump to the oil required device is normal, the supply state of the oil supplied from the oil pump to the oil required device is , Is controlled based on a request to control the rotation direction of the output member. Therefore, it is possible to suppress deterioration of the performance of the power transmission device.

[Brief description of drawings]

FIG. 1 is a flowchart showing a control example of the present invention.

FIG. 2 is a skeleton diagram showing an example of a power train to which the present invention can be applied.

3 is a block diagram showing a control circuit of the vehicle shown in FIG.

FIG. 4 is a diagram showing an example of the hydraulic control device of FIG.

FIG. 5 is a flowchart showing another control example of the present invention.

FIG. 6 is a flowchart showing another control example of the present invention.

FIG. 7 is a flowchart showing another control example of the present invention.

FIG. 8 is a flowchart showing another control example of the present invention.

9 is a diagram showing another example of the hydraulic control device of FIG.

FIG. 10 is a diagram showing another example of the hydraulic control device of FIG.

FIG. 11 is a diagram showing another example of the hydraulic control device of FIG.

FIG. 12 is a flowchart showing a control example applied to the hydraulic control device of FIG.

FIG. 13 is a diagram showing the basic principle of the present invention.

[Explanation of symbols]

1 ... Engine, 6 ... Forward / reverse switching mechanism, 7 ... Belt type continuously variable transmission, 9 ... Input shaft, 17,
108 ... Oil pump, 21 ... Primary shaft,
22 ... Secondary shaft, 102 ... Power transmission device, 103 ... Oil required device, 105 ... Power device,
125 ... Primary regulator valve, 127 ...
Input port, 129 ... Oil passage, 131B, 131C,
131D, 131E ... Hydraulic chamber.

Claims (8)

[Claims] 1. An oil pump control device comprising an oil-requiring device for controlling the power transmitted by a power transmission device and an oil pump for supplying oil to the oil-requiring device, wherein the power transmission device transmits the power. An oil pump control device, comprising: an oil supply state control means for controlling a supply state of oil supplied from the oil pump to the oil required device based on the power. 2. The oil supply state control means supplies the oil required device from an oil pump driven by a power device based on whether the power transmitted by the power transmission device is a predetermined value or less. The control device for an oil pump according to claim 1, further comprising a function of changing an amount of supplied oil. 3. An oil pump control device comprising an oil-requiring device for controlling power transmitted by a power transmission device, and an oil pump for supplying oil to the oil-requiring device. An oil supply state control means for controlling the supply state of the oil supplied from the oil pump to the oil required device based on the actual supply state of the oil supplied to the device and the target supply state of the oil. A control device for an oil pump, which is characterized in that 4. An oil pump control device comprising an oil-requiring device for controlling the power transmitted by the power transmission device, and an oil pump for supplying oil to the oil-requiring device. And an oil supply state control means for controlling the supply state of the oil supplied from the oil pump to the oil required device based on a request for controlling the speed of the moving body that is moved by the motive power. Control device for oil pump. 5. A control device for an oil pump, comprising: an oil-requiring device for controlling power transmitted by a power transmission device; and an oil pump for supplying oil to the oil-requiring device. Based on the requirement to control the ratio of rotational speeds between the rotating member and the other rotating member,
An oil pump control device comprising: an oil supply state control means for controlling a supply state of oil supplied from the oil pump to the oil required device. 6. The oil supply state control means, based on an actual progress state of a process of changing a rotation speed between the one rotary member and the other rotary member, and a target progress state, the oil. The control device for an oil pump according to claim 5, further comprising a function of controlling a supply state of oil supplied from the pump to the oil required device. 7. An oil pump control device comprising an oil-requiring device for controlling power transmitted by a power transmission device and an oil pump for supplying oil to the oil-requiring device. An oil pump control device comprising: an oil supply state control means for controlling the supply state of oil supplied to the device based on the temperature of the oil. 8. An oil pump control device comprising an oil-requiring device for controlling a rotation direction of an output member of a power transmission device, and an oil pump for supplying oil to the oil-requiring device. A control device for an oil pump, comprising: an oil supply state control means for controlling a supply state of oil supplied from the oil pump to the oil required device based on a request to control the oil pump.