JP5772413B2 - Hydraulic control device for automatic transmission - Google Patents

Description

  The present invention relates to a hydraulic control device for an automatic transmission.

  The automatic transmission of the vehicle accelerates and decelerates the output rotation of the engine and outputs it to the drive wheels. Examples of the automatic transmission include a planetary gear type stepped transmission, a parallel gear type stepped transmission, a friction type continuously variable transmission, a hydraulic mechanical type continuously variable transmission, and a gear type continuously variable transmission. These automatic transmissions include a speed change mechanism that is operated by an operating force of a hydraulic actuator. The hydraulic actuator operates with the fluid force of the hydraulic oil supplied by the hydraulic control device. The hydraulic control device adjusts the pressure of oil discharged from the oil pump and supplies the oil to the hydraulic actuator.

  Conventionally, a hydraulic control device for an automatic transmission including both a mechanical pump and an electric pump is known. In such a hydraulic control device, when the engine is stopped, the electric pump can pump hydraulic oil to the hydraulic actuator. Therefore, for example, when the engine is stopped by idling stop control or the like, the operation of the hydraulic actuator can be maintained by supplying the hydraulic oil to the hydraulic actuator by the electric pump. Thereby, the speed change mechanism can be operated immediately after the engine is restarted.

  Patent Documents 1 and 2 disclose a technique for preheating oil in an intake oil passage or a discharge oil passage of an electric pump prior to starting of the electric pump. The hydraulic control device disclosed in Patent Document 1 replaces a part of the suction oil passage of the electric pump and the oil of the discharge oil passage with the oil pumped up from the oil pan by the mechanical pump. The hydraulic control device disclosed in Patent Document 2 replaces the oil in the suction oil passage of the electric pump with the oil in the oil pan by driving the electric pump in a reverse rotation.

JP 2009-52638 A JP 2011-000978 A

  However, in the hydraulic control device disclosed in Patent Document 1, only a part of the oil in the suction oil passage is replaced with the oil in the oil pan. As the oil stagnating in the suction oil passage cools, the viscosity of the oil increases and the suction resistance at the start of the electric pump increases. At this time, whether or not the electric pump can discharge oil is determined by the fact that the electric pump has a larger suction resistance than when the discharge resistance becomes higher due to the high viscosity of the oil in the discharge oil passage. The effect of not being able to inhale oil is relatively greater. In order to be able to suck oil when the oil in the suction oil passage is highly viscous, it is necessary to increase the size of the suction port or to select a high-power drive motor. Therefore, there is a problem that the physique of the electric pump becomes large and the power consumption of the drive motor of the electric pump increases. In addition, the hydraulic control device disclosed in Patent Document 1 uses a dedicated electromagnetic switching valve for switching the oil passage, which increases the cost.

In the hydraulic control device disclosed in Patent Document 2, the electric pump is driven to rotate in reverse before the original electric pump is used, so that the drive motor consumes power. Therefore, there is a problem that the power consumption of the drive motor increases. In addition, it is necessary to add a control circuit for reverse rotation driving, and the control circuit becomes complicated and the cost increases.
The present invention has been made in view of the above points, and an object of the present invention is to downsize the drive motor without increasing the size of the suction port of the electric pump, and to provide a dedicated electromagnetic switching valve and drive motor. It is an object of the present invention to provide a hydraulic control device for an automatic transmission that does not require a reverse drive circuit and consumes electric power immediately after starting an electric pump without consuming wasteful power.

The present invention is a hydraulic control device for an automatic transmission capable of supplying hydraulic oil to a hydraulic actuator of an automatic transmission that accelerates or decelerates the output rotation of an engine, and includes a mechanical pump, an electric pump, and a first discharge oil. comprising a road, and a second discharge oil passage, a suction oil passage, and a pressure adjusting means, and subjected the oil supply passage, and an oil passage switching means.
The mechanical pump can be driven by the engine, and the electric pump can be driven electrically regardless of the operating state of the engine. The first discharge oil passage is connected to the discharge port of the mechanical pump, and the second discharge oil passage is connected to the discharge port of the electric pump. The suction oil passage is connected to the suction port of the electric pump. The pressure adjusting means adjusts the hydraulic pressure of the first discharge oil passage by discharging the oil of the first discharge oil passage . Test oil supply passage connects the outlet and the electric pump discharge port of the pressure regulating means.

Oil path switching means activates the second discharge fluid passage first operating position for blocking且one test oil supply passage is communicated, and, in a second operating position to block the second discharge oil passage and communicates the test oil supply passage To do. The oil path switching means can supply oil discharged from the electric pump to the hydraulic actuator when operated to the first operating position. The oil passage switching means, Ru oil and replacement of the suction oil passage is supplied to the suction oil path of the electric pump oil supply oil path and operating in the second operating position.

According to such a hydraulic control device, when the oil passage switching means is moved to the second operation position when the mechanical pump is driven, the mechanical pump sucks from the oil reservoir such as an oil pan and discharges to the first discharge oil passage. some of the oil, the pressure adjusting means is discharged to adjust the pressure, it is supplied to the electric pump and its suction oil passage via the supply oil passage. Therefore, all the oil of the electric pump and its suction oil passage is replaced with warm oil supplied from the supply oil passage. Accordingly, since the electric pump and the oil in the suction oil passage are preheated prior to the start of the electric pump, the suction resistance at the start of the electric pump can be reduced. Therefore, a small drive motor can be used for the electric pump without increasing the size of the suction port, and therefore the electric pump can suck and discharge oil immediately after starting while reducing power consumption. it can.

Preferably, the oil passage switching means is operated by oil discharged from the mechanical pump. In this configuration, power is not consumed when the oil passage switching means is operated. Therefore, power consumption can be reduced.
Further, for the operation of the oil passage switching means, for example, a solenoid valve, an electric circuit, and control for driving them are unnecessary. Therefore, the configuration of the hydraulic control device can be simplified.
Preferably, the oil passage switching means operates to the first operation position when the discharge pressure of the mechanical pump is less than a predetermined pressure, and operates to the second operation position when the discharge pressure of the mechanical pump exceeds the predetermined pressure. . Further , the predetermined pressure is set to a minimum value necessary for operating the hydraulic actuator. In this configuration, it is possible to avoid a situation in which the shift control becomes impossible due to the oil discharged from the mechanical pump being supplied to the electric pump and its suction oil passage.

Preferably, when the operating position of the oil passage switching means is the second operating position, the electric pump is rotated in the direction opposite to the rotational direction in which the pump action is performed by the oil discharged from the mechanical pump. Thereby, the oil in the electric pump and the suction oil passage can be replaced.
Preferably , the second discharge oil passage is connected to the first discharge oil passage. The second discharge oil passage is provided with a check valve that allows only the oil flow from the electric pump to the first discharge oil passage. According to this, when the operating position of the oil passage switching means is the first operating position, the oil in the first discharge oil passage is prevented from flowing out to the oil reservoir via the electric pump and the suction oil passage. can do. Therefore, it is possible to prevent a decrease in line pressure of the hydraulic control device.

Preferably, the flow restriction means is provided in test oil supply passage. Therefore, it is possible to avoid a situation where the oil supplied to the torque converter or the like is insufficient due to the supply of the oil discharged from the pressure adjusting means to the electric pump and the suction oil passage.
Preferably, at least a portion of the oil flowing through the electric pump passes through the drive motor of the electric pump. According to this, since the coil of the drive motor is warmed by the oil, the current required when starting the drive motor is reduced, and the power consumption can be suppressed.

1 is a schematic diagram showing a vehicle drive device including an automatic transmission that uses a hydraulic control device according to a first embodiment of the present invention. FIG. It is a figure which shows the hydraulic control apparatus of FIG. 1, and the friction engagement apparatus of an automatic transmission. It is a figure which shows the relationship between the discharge flow rate of the mechanical pump of FIG. 1, and an engine speed. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 1, Comprising: It is a figure at the time of engine operation and when line pressure is higher than predetermined pressure. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 1, Comprising: It is a figure at the time of engine operation and a line pressure being less than predetermined pressure. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 1, Comprising: It is a figure when the engine is stopped and the electric pump is operating. It is a figure which shows the hydraulic control apparatus by the modification of 1st Embodiment of this invention. It is a figure which shows the hydraulic control apparatus by 2nd Embodiment of this invention, and the friction engagement apparatus of an automatic transmission. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 7, Comprising: It is a figure at the time of engine operation and a line pressure being higher than predetermined pressure. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 7, Comprising: It is a figure at the time of engine operation and a line pressure being less than predetermined pressure. It is a figure which shows the line pressure generation part of the hydraulic control apparatus of FIG. 7, Comprising: It is a figure when the engine is stopped and the electric pump is operating. It is a figure which shows the hydraulic control apparatus by the modification of 2nd Embodiment of this invention.

Hereinafter, hydraulic control devices according to a plurality of embodiments of the present invention will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.
Note that the first embodiment and the modification of the first embodiment correspond to a reference embodiment.
(First embodiment)
An automatic transmission using the hydraulic control apparatus according to the first embodiment of the present invention is shown in FIG. The automatic transmission 90 is used in a drive system having an engine stop function that automatically stops the engine 91 when the vehicle is stopped or coasting. The automatic transmission 90 includes a torque converter 93 coupled to the crankshaft 92 of the engine 91, a planetary gear type transmission mechanism 94, and an automatic transmission hydraulic control device (hereinafter referred to as “hydraulic control device”) 10. It is a stepped transmission provided. The transmission mechanism 94 is a hydraulic pressure that couples a plurality of planetary gear devices (not shown) and the rotating elements (sun gear, carrier, ring gear) of each planetary gear device to the rotating elements and transmission cases of other planetary gear devices so as to transmit torque. Friction engagement devices 95 to 99 of the type. The hydraulic friction engagement devices 95 to 99 include, for example, a wet multi-plate clutch or a wet multi-plate brake. The output shaft 100 of the automatic transmission 90 is connected to the drive wheels 104 via the propeller shaft 101, the differential gear 102 and the drive shaft 103.

The automatic transmission 90 automatically controls the engagement and disengagement of the friction engagement devices 95 to 99 individually, and switches the power transmission path between the turbine shaft 105 and the output shaft 100 of the torque converter 93, thereby Any one of the gear positions is established.
As shown in FIG. 2, the hydraulic control device 10 selectively supplies hydraulic oil to the hydraulic actuators 106 to 110 of the friction engagement devices 95 to 99 and controls the pressure of the hydraulic oil. The hydraulic control device 10 includes a mechanical pump 21, an electric pump 30, a line pressure control valve 40, a manual valve 45, linear solenoid valves 50 to 54, an oil path switching valve 65, and the like.

The mechanical pump 21 is an oil pump driven by the engine 91 (see FIG. 1). The mechanical pump 21 sucks oil stored in the oil pan 111 of the automatic transmission 90 through the first suction oil passage 22. The oil sucked into the mechanical pump 21 is pressurized in the mechanical pump 21 and discharged from the discharge port 25 to the first discharge oil passage 23.
The first discharge oil passage 23 connects the discharge port 25 of the mechanical pump 21 and the introduction port 49 of the manual valve 45. The oil discharged from the mechanical pump 21 to the first discharge oil passage 23 is supplied to the introduction port 49 of the manual valve 45.
The first discharge oil passage 23 is provided with a check valve 24 that allows only oil to flow from the mechanical pump 21 toward the manual valve 45 side.
FIG. 3 is a diagram showing the relationship between the engine speed Ne [rpm] and the discharge flow rate Q [l / min] of the mechanical pump 21. As shown in FIG. 3, when the discharge flow rate Q exceeds a predetermined engine speed Ne1, the discharge flow rate Q increases as the engine speed Ne increases.

Returning to FIG. 2, the electric pump 30 is an oil pump driven by a drive motor 31. The electric pump 30 can be driven regardless of the operating state of the engine. The electric pump 30 sucks oil stored in the oil pan 111 through the second suction oil passage 32. The oil sucked into the electric pump 30 is pressurized in the electric pump 30 and discharged from the discharge port 35 to the second discharge oil passage 33. The second intake oil passage 32 corresponds to an “intake oil passage” in the claims.
The second discharge oil passage 33 connects the discharge port 35 of the electric pump 30 and the manual valve 45 side with respect to the check valve 24 in the first discharge oil passage 23. The oil discharged from the electric pump 30 to the second discharge oil passage 33 is supplied to the introduction port 49 of the manual valve 45 via the first discharge oil passage 23.
The second discharge oil passage 33 is provided with a check valve 34 that allows only the flow from the electric pump 30 to the first discharge oil passage 23. The check valve 34 prevents the oil in the first discharge oil passage 23 from flowing out to the electric pump 30 via the second discharge oil passage 33.

The line pressure control valve 40 as “pressure adjusting means” is a pilot type pressure adjusting valve connected to the manual valve 45 side with respect to the check valve 24 in the first discharge oil passage 23. The line pressure control valve 40 adjusts the pressure of oil supplied to the manual valve 45, that is, the line pressure. For example, the line pressure is adjusted to increase as the engine load increases.
The spool 44 of the line pressure control valve 40 moves due to a balance between the biasing force of the spring 41, the force received from the oil of the first discharge oil passage 23, and the force received from the discharge oil of a solenoid valve (not shown), and the first relief The opening 42 and the second relief opening 43 are opened and closed. The pressure of the discharge oil of the solenoid valve is controlled so as to increase or decrease according to the engine load. Thereby, when the line pressure is higher than the target value, excess oil is discharged from the first relief port 42 and the second relief port 43.

The target value of the line pressure is set to a minimum value necessary for operating the hydraulic actuators 106 to 110, for example. This target value is changed according to the running state of the vehicle. As shown in FIG. 3, the surplus exceeding the discharge flow rate Qn of the mechanical pump 21 necessary for setting the line pressure to the target value becomes the relief flow rate Qr of the line pressure control valve 40. The sum of the relief flow rate Q1 of the first relief port 42 and the relief flow rate Q2 of the second relief port 43 coincides with the relief flow rate Qr.
The oil relief from the first relief port 42 is returned to the oil pan 111. Further, the oil relief from the second relief port 43 is supplied to the torque converter 93 via the torque converter pressure control circuit 112.
Hereinafter, the pressure of the oil on the mechanical pump 21 side with respect to the check valve 24 in the first discharge oil passage 23 is referred to as discharge pressure, and is distinguished from line pressure. The discharge pressure and the line pressure can be equal.

The manual valve 45 is an oil passage switching valve having a spool 44 that is linked to the select lever 113. The select lever 113 is operated to, for example, four operation positions by the driver of the vehicle. The above four operation positions are an operation position for parking (parking position), an operation position for reverse travel (reverse position), an operation position for blocking power transmission (neutral position), and an operation for forward travel Position (drive position). The spool 44 is mechanically or electrically connected to the select lever 113 and operates according to the operation position of the select lever 113.
When the operation position of the select lever 113 is the parking position or the neutral position, the spool 44 is switched to a position where the first discharge oil path 23, the forward oil path 47, and the reverse oil path 48 are blocked.

When the operation position of the select lever 113 is the reverse position, the spool 44 blocks the first discharge oil passage 23 and the forward oil passage 47 and communicates the first discharge oil passage 23 and the reverse oil passage 48. Switch to the position to be made. As a result, the oil in the first discharge oil passage 23 can be supplied to the linear solenoid valve 50 through the reverse oil passage 48.
Further, when the operation position of the select lever 113 is the drive position, the spool 44 blocks the first discharge oil passage 23 and the reverse oil passage 48 and communicates the first discharge oil passage 23 and the forward oil passage 47. Switch to the position to be made. Thereby, the oil in the first discharge oil passage 23 can be supplied to the linear solenoid valves 51 to 54 through the forward oil passage 47.

The linear solenoid valves 50 to 54 are direct acting control valves capable of continuously changing the discharge pressure. The discharge pressure of the linear solenoid valves 50 to 54 is controlled by the electronic control unit 55.
The linear solenoid valve 50 is provided corresponding to the friction engagement device 95 that is involved in the establishment of the reverse gear. The linear solenoid valve 50 can adjust the pressure of oil supplied from the manual valve 45 via the reverse oil passage 48 and can supply the pressure to the hydraulic actuator 106 of the friction engagement device 95. The hydraulic actuator 106 is operated by hydraulic oil supplied from the linear solenoid valve 50.

  The linear solenoid valves 51 to 54 are provided corresponding to the friction engagement devices 96 to 99 involved in the establishment of the forward shift speed. The linear solenoid valves 51 to 54 can adjust the pressure of the oil supplied from the manual valve 45 via the forward oil passage 47 and supply it to the corresponding hydraulic actuator. The hydraulic actuators 107 to 110 are operated by oil supplied from the corresponding linear solenoid valve. Which of the friction engagement devices 96 to 99 is engaged is determined in advance for each of a plurality of forward shift speeds.

Subjected the oil supply passage 60 is connected to the first discharge oil passage 23 side to the check valve 34 of the second discharge passage 33, and a third port 69 of the oil passage switching valve 65 to be described later. A flow restriction means 61 is provided in the supply oil passage 60. The flow restricting means 61 is constituted by, for example, a throttle valve. The supply oil passage 60 can supply oil from the first discharge oil passage 23 to the third port 69 of the oil passage switching valve 65.

The oil passage switching valve 65 as “oil passage switching means” is provided between the check valve 34 and the electric pump 30 in the second discharge oil passage 33. The oil passage switching valve 65 includes a first port 67 connected to the electric pump 30 side of the second discharge oil passage 33, and a second port 68 connected to the first discharge oil passage 23 side of the second discharge oil passage 33. , A spool type three-way valve having a third port 69 connected to the supply oil passage 60.
The oil passage switching valve 65 communicates the second discharge oil passage 33 and disconnects the supply oil passage 60 and the electric pump 30 from each other, and the supply oil passage 60 and the electric pump 30. It operates to the second operating position that allows communication and shuts off the second discharge oil passage 33. When the oil passage switching valve 65 is operated to the second operation position, the oil in the supply oil passage 60 is supplied to the electric pump 30 and the second suction oil passage 32.

A branch oil passage 26 that branches from the first discharge oil passage 23 is connected to the oil passage switching valve 65 between the mechanical pump 21 and the check valve 24. The oil passage switching valve 65 is operated by the fluid force of the oil discharged from the mechanical pump 21 supplied from the branch oil passage 26. That is, the oil passage switching valve 65 operates without consuming electric power. Specifically, the oil passage switching valve 65 operates to the first operating position by the biasing force of the spring 66 when the discharge pressure of the mechanical pump 21 is less than a predetermined pressure. The oil passage switching valve 65 is operated to the second operating position by the acting force of the oil discharged from the mechanical pump 21 when the discharge pressure of the mechanical pump 21 exceeds the predetermined pressure. The predetermined pressure is set to a target value of the line pressure, for example.
The branch oil passage 26 is provided with a flow restriction means 27. The flow restriction means 27 is constituted by a throttle valve, for example.

Next, the operation of the hydraulic control device 10 will be described with reference to FIGS. 1 and 4 to 6. The broken line arrow A in FIGS. 4 to 6 indicates the flow of oil.
(Before engine start)
FIG. 1 shows a state before the engine is started. In this state, since the mechanical pump 21 is stopped and the line pressure is less than the predetermined pressure, the operating position of the oil passage switching valve 65 becomes the first operating position.

(When the engine is running and the line pressure is higher than the specified pressure)
When the engine is started and the mechanical pump 21 is activated from the state of FIG. 1 and the line pressure becomes higher than a predetermined pressure, the oil passage switching valve 65 is activated to the second operation position as shown in FIG. At this time, the supply oil passage 60 and the discharge port 35 of the electric pump 30 communicate with each other. The oil in the oil pan 111 moves back and forth between a hydraulic actuator, a torque converter, and the like, and absorbs heat at various places and warms up. The supply oil passage 60 supplies part of the oil that the mechanical pump 21 sucks from the oil pan 111 and discharges to the first discharge oil passage 23 to the electric pump 30 through the oil passage switching valve 65. The rotor of the electric pump 30 is rotated in the direction opposite to the rotational direction in which the pump action is performed by the oil supplied by the supply oil passage 60.

As a result, all the oil in the electric pump 30 and the second suction oil passage 32 before the oil passage switching valve 65 is moved to the second operation position is pushed out to the oil supplied by the supply oil passage 60. And discharged to the oil pan 111. The electric pump 30 and the second suction oil passage 32 are filled with relatively high temperature oil.
The flow restriction means 61 restricts the flow rate of the oil passing through the supply oil passage 60 to prevent the oil in the first discharge oil passage 23 from flowing out abruptly.

(When the engine is operating and the line pressure is less than the specified pressure)
From the state of FIG. 4, for example, when the oil in the hydraulic control device 10 is hot and the vehicle speed is low and the line pressure is less than a predetermined pressure, the oil passage switching valve 65 operates to the first operating position as shown in FIG. 5. . At this time, the supply oil passage 60 and the discharge port 35 of the electric pump 30 are shut off. Thereby, the supply of oil from the supply oil passage 60 to the electric pump 30 and the second suction oil passage 32 is stopped.

(When the engine is stopped and the electric pump 30 is operating)
From the state of FIG. 5, for example, when the vehicle stops and the engine stops by the idling stop function, or when the vehicle decelerates and the engine stops by the engine stop function, the oil path switching valve 65 is first activated as shown in FIG. 6. Actuating into position, the electric pump 30 is activated. At this time, the supply oil passage 60 and the electric pump 30 are shut off, and the electric pump 30 and the first discharge oil passage 23 communicate with each other through the second discharge oil passage 33. The line pressure is set to such a level that the friction engagement device engaged immediately before the engine is stopped can maintain the engagement. The electric pump 30 is selected to be the minimum that can deliver the pressure.

When the engine is restarted from the state of FIG. 6, the state of FIG. 4 is reached through the state of FIG. 5 as the line pressure increases.
Here, there are cases where the state shown in FIG. 4 is reached and the state shown in FIG. 6 is reached, and where the state shown in FIG.

  As described above, the hydraulic control apparatus 10 according to the first embodiment includes the supply oil passage 60 and the oil passage switching valve 65. The supply oil passage 60 connects the first discharge oil passage 23 and the discharge port 35 of the electric pump 30. The oil passage switching valve 65 communicates the second discharge oil passage 33 and disconnects the supply oil passage 60 and the electric pump 30 from each other, and the supply oil passage 60 and the electric pump 30. It operates to the second operating position that allows communication and shuts off the second discharge oil passage 33. When the oil passage switching valve 65 is operated to the second operation position, the oil in the supply oil passage 60 is supplied to the electric pump 30 and the second suction oil passage 32.

  According to such a hydraulic control device 10, when the oil path switching valve 65 is operated to the second operation position when the mechanical pump 21 is driven, the mechanical pump 21 sucks from the oil pan 111 and enters the first discharge oil path 23. Part of the oil to be discharged is supplied to the electric pump 30 and the second suction oil passage 32 via the supply oil passage 60. All the oil in the electric pump 30 and the second suction oil passage 32 is replaced with warm oil supplied from the supply oil passage 60. Therefore, since the oil in the electric pump 30 and the second suction oil passage 32 is preheated prior to the start of the electric pump 30, the suction resistance at the start of the electric pump 30 can be reduced. Therefore, the small drive motor 31 can be used for the electric pump 30 without increasing the size of the second suction oil passage 32. Therefore, the electric pump 30 immediately after start-up can be surely performed while reducing power consumption. The oil can be sucked and discharged.

Further, in the hydraulic control apparatus 10 according to the first embodiment, the oil passage switching valve 65 is operated by oil discharged from the mechanical pump 21. In this configuration, power is not consumed when the oil passage switching valve 65 is operated. Therefore, power consumption can be reduced.
Further, regarding the operation of the oil passage switching valve 65, for example, an electromagnetic valve, an electric circuit, and control for driving them are unnecessary. Therefore, the configuration of the hydraulic control device 10 can be simplified.

  In the hydraulic control apparatus 10 according to the first embodiment, the oil passage switching valve 65 operates to the first operating position when the discharge pressure of the mechanical pump 21 is less than a predetermined pressure, and the discharge pressure of the mechanical pump 21 is When the predetermined pressure is exceeded, the second operating position is activated. The predetermined pressure is set to a minimum value necessary for operating the hydraulic actuators 106 to 110. With this configuration, it is possible to avoid a situation in which the shift control becomes impossible due to the oil discharged from the mechanical pump 21 being supplied to the electric pump 30 and the second suction oil passage 32.

  Moreover, in the hydraulic control apparatus 10 according to the first embodiment, when the operating position of the oil passage switching valve 65 is the second operating position, the electric pump 30 performs a pumping action with oil discharged from the mechanical pump 21. It is rotated in the direction opposite to the rotation direction. Thereby, the oil in the electric pump 30 and the second suction oil passage 32 can be replaced.

In the hydraulic control apparatus 10 according to the first embodiment, the second discharge oil passage 33 is connected to the first discharge oil passage 23. The second discharge oil passage 33 is provided with a check valve 34 that allows only the flow of oil from the electric pump 30 to the first discharge oil passage 23. According to this, when the operation position of the oil passage switching valve 65 is the first operation position, the oil in the first discharge oil passage 23 passes through the electric pump 30 and the second suction oil passage 32 to the oil pan 111. It is possible to avoid leakage. Therefore, it is possible to prevent a decrease in line pressure.
Further, in the hydraulic control apparatus 10 according to the first embodiment, the flow restriction means 61 is provided in the supply oil passage 60. Therefore, it is possible to avoid a situation in which the line pressure rapidly decreases due to supplying the oil discharged from the mechanical pump 21 to the electric pump 30 and the second suction oil passage 32.

(Modification of the first embodiment)
FIG. 7 is a diagram illustrating a hydraulic control apparatus according to a modification of the first embodiment. As shown by a broken line arrow A in FIG. 7, in the hydraulic control device 70, at least a part of the oil flowing in the electric pump 30 passes through the drive motor 31 that drives the electric pump 30. According to this, since the coil of the drive motor 31 is warmed by oil, the drive current at the start of the drive motor 31 is reduced, and power consumption can be suppressed.

(Second Embodiment)
A hydraulic control apparatus according to a second embodiment of the present invention will be described. As shown in FIGS. 8 to 11, the hydraulic control device 75 according to the second embodiment includes a second relief port 43 of the line pressure control valve 40 as a “pressure adjusting unit” and a third port 69 of the oil passage switching valve 65. comprising a supply oil passage 76 as a "test oil supply passage" that connects and. The broken line arrow A in FIGS. 9 to 11 shows the flow of oil.
(Before engine start)
Before the engine is started, the operating position of the oil passage switching valve 65 is the first operating position as shown in FIG.

(When the engine is running and the line pressure is higher than the specified pressure)
When the engine is started and the mechanical pump 21 is activated from the state of FIG. 1 and the line pressure becomes higher than a predetermined pressure, the oil passage switching valve 65 is activated to the second operation position as shown in FIG. At this time, the supply oil passage 76 and the discharge port 35 of the electric pump 30 communicate with each other. The supply oil passage 76 passes a part of oil discharged from the line pressure control valve 40 from the oil pan 111 via the mechanical pump 21 and the first discharge oil passage 23 to the electric pump 30 through the oil passage switching valve 65. Supply. The rotor of the electric pump 30 is rotated in the direction opposite to the rotational direction in which the pump action is performed by the oil supplied by the supply oil passage 76.

  As a result, all the oil in the electric pump 30 and the second suction oil passage 32 before the oil passage switching valve 65 is moved to the second operation position is pushed out to the oil supplied by the supply oil passage 76. And discharged to the oil pan 111. The electric pump 30 and the second suction oil passage 32 are filled with relatively high temperature oil.

In the second embodiment, as in the first embodiment, when the line pressure exceeds a target value determined according to, for example, the load of the engine, the oil in the first discharge oil passage 23 is the first of the line pressure control valve 40. It is discharged from the relief port 42 and the second relief port 43. As shown in FIG. 2, the surplus exceeding the discharge flow rate Qn of the mechanical pump necessary for setting the line pressure to the target value becomes the relief flow rate Qr of the line pressure control valve. The sum of the relief flow rate Q1 of the first relief port 42 and the relief flow rate Q2 of the second relief port 43 coincides with the relief flow rate Qr.
The flow rate restricting unit 77 secures the flow rate of the oil supplied to the torque converter 93 by limiting the flow rate of the oil passing through the supply oil passage 76.

(When the engine is operating and the line pressure is less than the specified pressure)
From the state of FIG. 9, for example, when the oil in the hydraulic control device 10 is hot and the vehicle speed is low and the line pressure is less than a predetermined pressure, the oil passage switching valve 65 is operated to the first operating position as shown in FIG. 10. . At this time, the supply oil passage 76 and the discharge port 35 of the electric pump 30 are shut off. Thereby, the supply of oil from the supply oil passage 76 to the electric pump 30 and the second suction oil passage 32 is stopped.

(When the engine is stopped and the electric pump 30 is operating)
From the state of FIG. 10, for example, when the vehicle stops and the engine stops by the idling stop function, or when the vehicle decelerates and the engine stops by the engine stop function, the oil path switching valve 65 is first activated as shown in FIG. 11. Actuating into position, the electric pump 30 is activated. At this time, the supply oil passage 76 and the electric pump 30 are shut off, and the electric pump 30 and the first discharge oil passage 23 communicate with each other through the second discharge oil passage 33. The line pressure is set to such a level that the friction engagement device engaged immediately before the engine is stopped can maintain the engagement.

  As described above, the hydraulic control device 75 according to the second embodiment includes the supply oil passage 76 and the oil passage switching valve 65. The supply oil passage 76 connects the second relief port 43 of the line pressure control valve 40 and the electric pump 30. The oil passage switching valve 65 communicates the second discharge oil passage 33 and disconnects the supply oil passage 76 and the electric pump 30 from each other, and the supply oil passage 76 and the electric pump 30. It operates to the second operating position that allows communication and shuts off the second discharge oil passage 33. When the oil path switching valve 65 is operated to the second operating position, the oil relieved from the second relief port 43 is supplied to the electric pump 30 and the second suction oil path 32.

  According to such a hydraulic control device 75, when the oil path switching valve 65 is operated to the second operating position when the mechanical pump 21 is driven, the mechanical pump 21 sucks from the oil pan 111 and enters the first discharge oil path 23. Part of the oil to be discharged is relieved from the second relief port 43 of the line pressure control valve 40 and supplied to the electric pump 30 and the second intake oil passage 32 via the supply oil passage 60. All the oil in the electric pump 30 and the second suction oil passage 32 is replaced with warm oil supplied from the supply oil passage 60. Therefore, since the oil in the electric pump 30 and the second suction oil passage 32 is preheated prior to the start of the electric pump 30, the suction resistance at the start of the electric pump 30 can be reduced. Therefore, the small drive motor 31 can be used for the electric pump 30 without increasing the size of the second suction oil passage 32. Therefore, the electric pump 30 immediately after start-up can be surely performed while reducing power consumption. The oil can be sucked and discharged.

  In the second embodiment, since the flow restriction means 77 is provided in the supply oil passage 76, the oil that is relieved from the second relief port 43 is supplied to the electric pump 30 and the second suction oil passage 32. Thus, a situation where the oil supplied to the torque converter pressure control circuit 112 is insufficient can be avoided.

(Modification of the second embodiment)
FIG. 12 is a diagram illustrating a hydraulic control apparatus according to a modification of the second embodiment. As shown by a broken line arrow A in FIG. 12, in the hydraulic control device 80, at least a part of the oil flowing in the electric pump 30 passes through the drive motor 31 that drives the electric pump 30. According to this, since the coil of the drive motor 31 is warmed by oil, the drive current at the start of the drive motor 31 is reduced, and power consumption can be suppressed.

(Other embodiments)
In another embodiment of the present invention, the automatic transmission is not limited to a planetary gear type stepped transmission, but may be, for example, a parallel gear type stepped transmission, a friction type continuously variable transmission, a hydraulic mechanical type continuously variable transmission, and a gear. You may comprise a type continuously variable transmission.
In another embodiment of the present invention, the hydraulic actuator is not limited to the hydraulic cylinder of the friction engagement device, but may be another type of hydraulic actuator such as a hydraulic cylinder that operates a variable groove width pulley of a belt-type continuously variable transmission. It may be.
In another embodiment of the present invention, the oil passage switching means may comprise an electrically driven valve. In this case, the control device may be configured to control the operation of the oil passage switching means.
In another embodiment of the present invention, the flow restriction means may not be provided in the supply oil passage.

In another embodiment of the present invention, the pressure adjusting means is not limited to a pilot valve, and may be a direct acting valve, for example.
In another embodiment of the present invention, the valve that directly controls the hydraulic oil supplied to the hydraulic actuator is not limited to a direct acting valve such as a linear solenoid valve, and may be a pilot valve. Further, the valve that directly controls the hydraulic oil supplied to the hydraulic actuator is not limited to the one having an electromagnetic drive unit, and may have, for example, an electric drive unit.
In another embodiment of the present invention, the automatic transmission is not limited to the vertical type as shown in FIG. 1 but may be a horizontal type. The automatic transmission may be of a type without a torque converter.

  Thus, the present invention is not limited to the above-described embodiments, and can be applied to various forms without departing from the gist thereof.

10, 70, 75, 80 ... Hydraulic control device for automatic transmission 21 ... Mechanical pump 25 ... Discharge port 23 ... First discharge oil passage 30 ... Electric pump 32 ... Second suction oil passage (suction oil passage)
33 ... Second discharge oil passage 35 ... Discharge port 60 ... Supply oil passage 65 ... Oil passage switching valve (oil passage switching means)
76 ... Supply oil passage 90 ... Automatic transmission 91 ... Engine 106-110 ... Hydraulic actuator

Claims (8)

A hydraulic control device for an automatic transmission capable of supplying hydraulic oil to a hydraulic actuator of an automatic transmission that accelerates or decelerates the output rotation of an engine,
A mechanical pump that can be driven by the engine;
An electric pump that can be electrically driven regardless of the operating state of the engine;
A first discharge oil passage connected to a discharge port of the mechanical pump;
A second discharge oil passage connected to a discharge port of the electric pump;
A suction oil passage connected to a suction port of the electric pump;
Pressure adjusting means for adjusting the hydraulic pressure of the first discharge oil passage by discharging the oil of the first discharge oil passage;
And subjected the oil supply passage to connect with said discharge port of the electric pump and the outlet of the pressure regulating means,
First operating position for blocking and before bellflower oil supply passage communicates with the second discharge passage, and operates the pre bellflower oil supply passage to the second operating position for blocking and communicates the second discharge fluid passage the oil in which the electric pump and first operates the operating position to discharge can be supplied to the hydraulic actuator, the suction of the second actuating the electric pump oil before Campanulaceae supply passage when actuated position an oil and replaced Ru oil passage switching means of the suction oil path is supplied to the oil passage,
A hydraulic control device for an automatic transmission, comprising: 2. The hydraulic control device for an automatic transmission according to claim 1 , wherein the oil passage switching means is operated by oil discharged from the mechanical pump. The oil passage switching means operates to the first operation position when the discharge pressure of the mechanical pump is less than a predetermined pressure, and operates to the second operation position when the discharge pressure of the mechanical pump exceeds the predetermined pressure. The hydraulic control device for an automatic transmission according to claim 1 or 2 , characterized in that: 4. The hydraulic control device for an automatic transmission according to claim 3 , wherein the predetermined pressure is set to a minimum value necessary for operating the hydraulic actuator. When the operation position of the oil passage switching means is the second operation position, the electric pump is rotated in a direction opposite to a rotation direction in which the pump action is performed by oil discharged from the mechanical pump. The hydraulic control device for an automatic transmission according to any one of claims 1 to 4 . The second discharge oil passage is connected to the first discharge oil passage,
The check valve according to any one of claims 1 to 5 , further comprising a check valve provided in the second discharge oil passage and allowing only an oil flow from the electric pump to the first discharge oil passage. The hydraulic control device for an automatic transmission according to the item. Before provided bellflower oil supply passage, the automatic transmission according to any one of claims 1 to 6, further comprising a flow restricting means for restricting the flow rate of the oil flowing through the equivalent 該供 oil supply passage Hydraulic control device. The hydraulic control device for an automatic transmission according to any one of claims 1 to 7 , wherein at least a part of the oil flowing in the electric pump passes through a drive motor of the electric pump. .

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