WO2018168970A1 - Hydraulic control device - Google Patents

Abstract

A hydraulic control device (70B) comprising: a first oil passage (L1) which is connected to a mechanical pump (24), and which comprises a first check valve (77) midway therealong; a second oil passage (L2) which is connected to an electric pump (28), and which is connected with the side of the first oil passage (L1) downstream of the first check valve (77); a third oil passage (L3) which branches from the second oil passage (L2); a regulator valve (71) which is connected to the first oil passage (L1) between the mechanical pump (24) and the first check valve (77); and a switch valve (80) that forms a first state in which the supply of oil, which has been supplied from the electric pump (28) to the third oil passage (L3), to a low-pressure oil supply unit of a transmission is permitted, and a second state in which the supply of oil, which has been supplied from the electric pump (28) to the third oil passage (L3), to the low-pressure oil supply unit is restricted.

Description

Hydraulic control device

The present disclosure relates to a hydraulic control that regulates oil supplied from at least one of a mechanical pump driven by power from a prime mover of a vehicle and an electric pump driven by electric power and supplies the pressure to an engagement element of a transmission. Relates to the device.

2. Description of the Related Art Conventionally, a first hydraulic circuit for supplying hydraulic oil to primary and secondary pulleys and clutches of a continuously variable transmission, and a second hydraulic pressure for supplying hydraulic oil to a torque converter and a lubrication unit (low pressure oil supply unit) A first hydraulic pressure when the engine pump is stopped and the hydraulic pump is supplied with hydraulic oil by stopping the operation of the engine due to idling stop; an engine pump driven by a circuit and an engine; an electric pump driven by a motor; There is known a hydraulic pump device including a stop valve that is closed so as to prohibit the outflow of hydraulic oil from a circuit to a second hydraulic circuit (see, for example, Patent Document 1). In this hydraulic pump device, when the hydraulic oil is supplied by the electric pump, the hydraulic oil from the electric pump is supplied only to the first hydraulic circuit by closing the stop valve. Thereby, the hydraulic oil from the electric pump is supplied with priority over the primary pulley, the secondary pulley, and the clutch.

JP 2010-78088 A

In the invention described in Patent Document 1, priority is given to the supply of hydraulic oil to the primary pulley and the secondary pulley and the clutch when the engine is stopped due to idling stop, thereby suppressing the increase in size and cost of the electric pump. Yes. However, in the invention described in Patent Document 1, when the engine operation is stopped due to idling stop, the stop valve prohibits the flow of hydraulic oil from the first hydraulic circuit to the second hydraulic circuit and operates from the engine pump. Since the oil is not discharged, the hydraulic oil cannot be supplied to the torque converter or the lubrication unit.

Therefore, the invention of the present disclosure suppresses the increase in size and cost of the electric pump, and when the oil is not supplied from the mechanical pump when the engine is stopped, the engagement element of the transmission and the low-pressure oil supply The main purpose is to provide a hydraulic control device capable of ensuring a good supply amount of oil to both of the parts.

The hydraulic control device according to the present disclosure regulates oil from at least one of a mechanical pump driven by power from an engine of a vehicle and an electric pump driven by electric power to perform a plurality of engagements of the transmission. In a hydraulic control device that supplies at least one of the elements,
A first oil passage connected to the mechanical pump and including a first check valve for restricting the inflow of oil to the mechanical pump side, and the first check passage connected to the electric pump and the first check valve A second oil passage connected to the first oil passage on the downstream side of the valve, a third oil passage branched from the second oil passage, and a joining portion of the first oil passage and the second oil passage And a fourth oil passage connecting the at least one engagement element, and the first oil passage between the mechanical pump and the first check valve, and from the mechanical pump A regulator valve that regulates oil to generate an original pressure, a signal pressure output valve that outputs a signal pressure, and a low pressure oil supply unit of the transmission according to an output state of the signal pressure by the signal pressure output valve A first state allowing the supply of oil supplied from the electric pump to the third oil passage; It is intended to include a switching valve forming a second state for restricting the supply of oil supplied to the third oil passage from the electric pump for pressure oil supply.

In the hydraulic control device according to the present disclosure, the first state in which the supply of the oil supplied from the electric pump to the third oil passage to the low-pressure oil supply unit of the transmission is allowed according to the output state of the signal pressure by the signal pressure output valve. The switching valve can be switched to form either one of the second state in which the supply of oil supplied from the electric pump to the low-pressure oil supply unit to the third oil passage is restricted. As a result, when oil is no longer supplied from the mechanical pump when the engine is stopped, the oil from the electric pump is reduced to low pressure via the third oil passage and the switching valve by switching the switching valve to the first state. It becomes possible to supply to the oil supply unit. In addition, by switching the switching valve to the second state while the engine is stopped, the oil from the electric pump is not supplied to the low pressure oil supply unit, and the engine is connected to the engine via the second oil path and the fourth oil path. It can be supplied to an engagement element that is engaged at restart. As a result, the oil for both the engagement element and the low-pressure oil supply unit of the transmission is suppressed when the oil is not supplied from the mechanical pump with the stop of the engine operation while suppressing the increase in size and cost of the electric pump. This makes it possible to ensure a good supply amount.

It is a schematic block diagram of the vehicle carrying the power transmission device containing the hydraulic control apparatus of this indication. It is a schematic block diagram which shows the power transmission device mounted in the vehicle of FIG. FIG. 3 is an operation table showing a relationship between each shift stage of the automatic transmission included in the power transmission device of FIG. 2 and operation states of clutches and brakes. It is a systematic diagram showing a hydraulic control device of this indication. 2 is a time chart for explaining the operation of the hydraulic control device and the like when the engine is started in response to a start request to the vehicle after the operation of the engine is stopped with the stop of the vehicle in FIG. 1. It is a systematic diagram showing other hydraulic control devices of this indication. 2 is a time chart for explaining the operation of the hydraulic control device and the like when the engine is restarted after the operation of the engine is stopped in accordance with the stop of the vehicle or the inertial running of FIG. 1. It is a schematic block diagram which shows the other switching valve applicable to the hydraulic control apparatus shown in FIG.

Next, an embodiment for carrying out the invention of the present disclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram of a vehicle 10 equipped with a power transmission device 20 including a hydraulic control device 70 of the present disclosure. A vehicle 10 shown in the figure is a front-wheel drive vehicle having an engine 12 and a power transmission device 20 that transmits power from the engine 12 to left and right drive wheels (front wheels) DW. When the vehicle is idling, the engine 12 is stopped, and the engine 12 is restarted in response to a start request to the vehicle 10 by the driver. It is possible to perform inertial running that stops the operation of the vehicle. In addition, as shown in FIG. 1, the vehicle 10 includes an engine electronic control unit (hereinafter referred to as “EG ECU”) 14 that controls the engine 12 and a brake electronic control unit (hereinafter referred to as “electronic control hydraulic brake unit”) that is not shown. , “Brake ECU”) 16 and a shift electronic control unit (hereinafter referred to as “TMECU”) 21 for controlling the power transmission device 20.

The EGECU 14 is a microcomputer including a CPU (not shown), a crankshaft position sensor (not shown) that detects the rotational position of the crankshaft of the engine 12, and an accelerator pedal position sensor 92 that detects the amount of depression (operation amount) of the accelerator pedal 91. In addition, signals from various sensors such as the vehicle speed sensor 99, signals from the brake ECU 16 and TMECU 21, and the like are input. Based on these signals, the EGECU 14 controls an electronically controlled throttle valve, fuel injection valve, spark plug, etc. (not shown). The brake ECU 16 is also a microcomputer including a CPU (not shown). Signals from various sensors such as a master cylinder pressure sensor 94 and a vehicle speed sensor 99 for detecting the master cylinder pressure corresponding to the depression amount of the brake pedal 93, and from the EGECU 14 and the like. Input signals. Based on these signals, the brake ECU 16 controls a brake actuator (hydraulic actuator) (not shown) and the like.

The TMECU 21 is also a microcomputer including a CPU (not shown), and includes a shift position sensor 96 for detecting an operation position of the shift lever 95 for selecting a desired shift position from a plurality of shift positions, an accelerator pedal position sensor 92, a vehicle speed. Sensor 99, signals from various sensors such as an input rotation speed sensor for detecting the input rotation speed of the automatic transmission 25 (the rotation speed of the turbine runner 23b or the input shaft 26 of the automatic transmission 25), signals from the EGECU 14 and the brake ECU 16 Enter etc. The TMECU 21 controls the power transmission device 20 based on these signals.

As shown in FIG. 2, the power transmission device 20 includes a transmission case 22, a starting device (fluid transmission device) 23 housed in the transmission case 22, and a mechanical oil pump 24 driven by power from the engine 12. , An electric oil pump 28 driven by electric power from a battery (not shown), an automatic transmission 25, a gear mechanism (gear train) 40, a differential gear (differential mechanism) 50, a hydraulic control device 70, and the like.

In addition to the housing 221 and the transaxle case 222 fastened (fixed) to the housing 221, the transmission case 22 is fastened to the transaxle case 222 so as to be positioned between the housing 221 and the transaxle case 222 ( A front support 223 that is fixed) and a center support 224 that is fastened (fixed) to the transaxle case 222. In the present embodiment, the housing 221, the transaxle case 222, and the center support 224 are formed of, for example, an aluminum alloy, and the front support 223 is formed of a steel material (iron alloy) or an aluminum alloy.

The starting device 23 includes a front cover connected to the crankshaft of the engine 12 via a drive plate (not shown), an input-side pump impeller 23p having a pump shell that is tightly fixed to the front cover, and an automatic transmission 25. An output-side turbine runner 23t coupled to the input shaft 26, a pump impeller 23p, and a stator 23s disposed inside the turbine runner 23t to rectify the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a stator (not shown) A one-way clutch 23o that is supported by the shaft and restricts the rotation direction of the stator 23s to one direction is included. Pump impeller 23p, turbine runner 23t, and stator 23s constitute a torque converter having a torque amplifying action.

Further, the starting device 23 connects the front cover and the input shaft 26 of the automatic transmission 25 to each other and releases the connection between the front cover and the input shaft 26 of the automatic transmission 25. And a damper device 23d for damping the vibration. In the present embodiment, the lock-up clutch 23c is configured as a multi-plate friction type hydraulic clutch having a plurality of friction engagement plates (friction plates and separator plates). However, the lockup clutch 23c may be a single plate friction type hydraulic clutch. The starting device 23 may include a fluid coupling that does not include the stator 23s.

The mechanical oil pump 24 includes an external gear (inner rotor) 241 connected to the pump impeller 23p of the starting device 23 through a winding transmission mechanism 240, and an internal gear (outer rotor) 242 that meshes with the external gear. A gear pump having a pump body and a pump cover (both not shown) that define a gear chamber (not shown) that accommodates the external gear 241 and the internal gear 242, and is separate from the input shaft 26 of the automatic transmission 25. Arranged on the axis. The mechanical oil pump 24 is driven by the power from the engine 12 via the winding transmission mechanism 240 and is stored in a hydraulic oil reservoir (not shown) provided at the bottom of the transaxle case 222 ( ATF) is sucked and pumped to the hydraulic control device 70. The winding transmission mechanism 240 is a drive sprocket that rotates integrally with the pump impeller 23p of the starting device 23, a driven sprocket that rotates integrally with the external gear of the mechanical oil pump 24, a drive sprocket, and a chain that is wound around the driven sprocket. Etc.

The electric oil pump 28 includes an electric motor (not shown) controlled by the TMECU 21 and an impeller rotated by the electric motor, and sucks the hydraulic oil stored in the hydraulic oil storage section of the transaxle case 222. To the hydraulic control device 70. In the present embodiment, an electric oil pump 28 that can change the discharge flow rate and the discharge pressure by controlling the flow rate of the electric motor is employed. However, the electric oil pump 28 may be capable of changing the discharge flow rate and the discharge pressure by the rotational speed control (duty control) of the electric motor.

The automatic transmission 25 is configured as an 8-speed transmission, and, as shown in FIG. 2, a double pinion type first planetary gear mechanism 30, a Ravigneaux type second planetary gear mechanism 35, and an input It includes four clutches C1, C2, C3 and C4 and two brakes B1 and B2 for changing the power transmission path from the side to the output side.

The first planetary gear mechanism 30 is engaged with a sun gear (fixed element) 31 that is an external gear and a ring gear 32 that is an internal gear arranged concentrically with the sun gear 31 and one of the gears is engaged with the sun gear 31. The other has a planetary carrier 34 that holds a plurality of pairs of two pinion gears 33a and 33b meshing with the ring gear 32 so as to be rotatable (rotatable) and revolved. As shown in the figure, the sun gear 31 of the first planetary gear mechanism 30 is non-rotatably connected (fixed) to the transmission case 22 via the front support 223, and the planetary carrier 34 of the first planetary gear mechanism 30 is The input shaft 26 is connected so as to be integrally rotatable. The first planetary gear mechanism 30 is used as a so-called reduction gear, decelerates the power transmitted to the planetary carrier 34 as an input element, and outputs it from the ring gear 32 as an output element.

The second planetary gear mechanism 35 includes a first sun gear 36a and a second sun gear 36b which are external gears, a ring gear 37 which is an internal gear disposed concentrically with the first and second sun gears 36a and 36b, A plurality of short pinion gears 38a meshing with one sun gear 36a, a plurality of long pinion gears 38b meshing with the second sun gear 36b and the plurality of short pinion gears 38a and meshing with the ring gear 37, a plurality of short pinion gears 38a and a plurality of long pinion gears 38b And a planetary carrier 39 that holds the magnet so as to be rotatable (rotatable) and revolved. The ring gear 37 of the second planetary gear mechanism 35 functions as an output member of the automatic transmission 25, and the power transmitted from the input shaft 26 to the ring gear 37 is transmitted to the left and right via the gear mechanism 40, the differential gear 50 and the drive shaft 51. Is transmitted to the driving wheel.

The clutch C1 connects the ring gear 32 of the first planetary gear mechanism 30 and the first sun gear 36a of the second planetary gear mechanism 35 to each other and releases the connection between them. The clutch C2 connects the input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 to each other and releases the connection between them. The clutch C3 connects the ring gear 32 of the first planetary gear mechanism 30 and the second sun gear 36b of the second planetary gear mechanism 35 to each other and releases the connection therebetween. The clutch C4 connects the planetary carrier 34 of the first planetary gear mechanism 30 and the second sun gear 36b of the second planetary gear mechanism 35 to each other and releases the connection therebetween. In this embodiment, the clutches C1, C2, C3, and C4 are engaged with pistons, a plurality of friction engagement plates (friction plates and separator plates), and engagement hydraulic pressure (hydraulic fluid) supplied from the hydraulic control device 70. In order to cancel the centrifugal oil pressure generated in the oil chamber and the engagement oil chamber, a multi-plate friction type hydraulic clutch including a centrifugal oil pressure cancel chamber supplied with hydraulic oil from the hydraulic control device 70 is employed.

The brake B1 fixes (connects) the second sun gear 36b of the second planetary gear mechanism 35 to the transmission case 22 in a non-rotatable manner and releases the second sun gear 36b from the transmission case 22. The brake B2 fixes the planetary carrier 39 of the second planetary gear mechanism 35 to the transmission case 22 so as not to rotate, and releases the fixation of the planetary carrier 39 to the transmission case 22. In the present embodiment, as the brakes B1 and B2, a multi-plate friction type hydraulic brake including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like is employed. .

These clutches C1 to C4 and brakes B1 and B2 operate upon receiving and supplying hydraulic oil from the hydraulic control device 70. FIG. 3 shows an operation table showing the relationship between the respective shift stages of the automatic transmission 25 and the operation states of the clutches C1 to C4 and the brakes B1 and B2. The automatic transmission 25 shifts the forward first speed to the eighth speed and the reverse first speed and the second speed by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. Provide a step. That is, each shift stage of the automatic transmission 25 is formed by engaging any two of the clutches C1 to C4 and the brakes B1 and B2. Further, when the operation of the engine 12 is stopped while the vehicle 10 is traveling due to the execution of idle stop control or inertial traveling, one of the two clutches and brakes corresponding to the gear position corresponding to the vehicle speed or the like is released. At the same time, the other is engaged to form a neutral state, and the clutch to be engaged is changed according to the traveling state of the vehicle 10. Note that at least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch.

The gear mechanism 40 is fixed to a counter drive gear 41 connected to the ring gear 37 of the second planetary gear mechanism 35 of the automatic transmission 25 and a counter shaft 42 extending in parallel with the input shaft 26 of the automatic transmission 25. A counter driven gear 43 that meshes with the counter drive gear 41, a drive pinion gear 44 formed (or fixed) on the counter shaft 42, and a diff ring gear 45 that meshes with the drive pinion gear 44 and is connected to the differential gear 50. As shown in FIG. 2, the counter drive gear 41 of the gear mechanism 40 is fixed to the transaxle case 222 via a plurality of bolts so as to be positioned between the first and second planetary gear mechanisms 30 and 35. The support 224 is rotatably supported through a bearing.

FIG. 4 is a system diagram showing the hydraulic control device 70. The hydraulic control device 70 is connected to the mechanical oil pump 24 and the electric oil pump 28 that can suck and discharge the hydraulic oil from the hydraulic oil reservoir of the transaxle case 222 via the strainer 60. The hydraulic control device 70 generates the hydraulic pressure required by the starting device 23 and the automatic transmission 25, and also provides a low pressure oil supply unit (such as a lubrication target such as various bearings, a centrifugal hydraulic pressure cancellation chamber C1c of the clutches C1 to C4, and the like). Supply hydraulic oil to the lubricated part). As shown in the figure, the hydraulic control device 70 includes a valve body 700 having a plurality of oil passages L1 to L9 and the like, a primary regulator valve 71, a secondary regulator valve 72, a modulator valve 74, an oil cooler 75, and a linear solenoid valve SL1. , SLT, signal pressure output valve SR, switching valve 80 and the like.

The valve body 700 is attached to a side portion of the transaxle case 222 that constitutes the transmission case 22, for example. An oil passage L1 (first oil passage) of the valve body 700 is connected to a discharge port of the mechanical oil pump 24, and a first check valve 77 is installed in the middle thereof. The first check valve 77 allows the hydraulic oil to flow from the mechanical oil pump 24 side to the downstream side when the hydraulic pressure on the upstream side, that is, the mechanical oil pump 24 side is higher than the hydraulic pressure on the downstream side, and upstream. When the hydraulic pressure on the side is equal to or lower than the hydraulic pressure on the downstream side, the flow of hydraulic oil from the mechanical oil pump 24 side to the downstream side is blocked. That is, the first check valve 77 closes in response to a decrease in hydraulic pressure from the mechanical oil pump 24.

The oil passage L2 (second oil passage) of the valve body 700 has one end connected to the discharge port of the electric oil pump 28 and the other end connected to the oil passage L1 downstream of the first check valve 77. The second check valve 78 is installed in the middle. The second check valve 78 allows the hydraulic oil to flow from the electric oil pump 28 side to the downstream side when the oil pressure on the upstream side, that is, the electric oil pump 28 side is higher than that on the downstream side, that is, the oil passage L1. When the hydraulic pressure on the upstream side is equal to or lower than the hydraulic pressure on the downstream side, the flow of hydraulic oil from the electric oil pump 28 side to the downstream side is blocked. Thereby, when the electric oil pump 28 is operated in a state where the mechanical oil pump 24 is stopped along with the operation stop of the engine 12, the hydraulic pressure from the electric oil pump 28 enters the oil passage L1. It is supplied as the line pressure PL. Further, the oil passage L3 (third oil passage) of the valve body 700 is branched from the oil passage L2 between the electric oil pump 28 and the second check valve 78.

The primary regulator valve 71 is connected to the oil passage L1 between the mechanical oil pump 24 and the first check valve 77, and the hydraulic pressure from the linear solenoid valve SLT is used as a signal pressure from the mechanical oil pump 24. The original pressure is generated by regulating the hydraulic oil. Thus, when the mechanical oil pump 24 is driven by the engine 12 while the electric oil pump 28 is stopped, the original pressure regulated by the primary regulator valve 71 is supplied to the oil passage L1 by the line pressure PL. Will be supplied as Further, the secondary regulator valve (second regulator valve) 72 uses the hydraulic pressure from the linear solenoid valve SLT as a signal pressure, and the hydraulic oil drained from the primary regulator valve 71 when the original pressure is generated (drain oil). Is adjusted to generate a secondary pressure (circulation pressure) Psec lower than the original pressure (line pressure PL).

The linear solenoid valve SLT is controlled by the TMECU 21 so as to adjust the hydraulic oil from the mechanical oil pump 24 side (for example, the modulator valve 74) and output a hydraulic pressure corresponding to the accelerator opening of the vehicle 10 or the opening of the throttle valve. Is done. In the present embodiment, the TMECU 21 can control the linear solenoid valve SLT regardless of the accelerator opening degree of the vehicle 10, and the primary regulator valve 71 and the secondary regulator can be controlled by controlling the output pressure of the linear solenoid valve SLT. The amount of drain oil of the valve 72 can be adjusted. Further, the modulator valve 74 has an input port connected to the oil passage L4 branched from the oil passage L1 on the downstream side of the first check valve 77, and supplies hydraulic oil (line pressure PL) from the oil passage L1. The pressure is regulated (decompressed) to output a substantially constant modulator pressure Pmod. Furthermore, the oil cooler 75 cools the hydraulic oil (drain oil) drained from the secondary regulator valve 72 as the secondary pressure Psec is generated.

The linear solenoid valve SL1 (pressure regulating valve) has an input port connected to the oil passage L1, and regulates hydraulic fluid (line pressure PL) from the oil passage L1 to the engagement oil chamber C1e of the clutch C1. A hydraulic pressure (engagement hydraulic pressure) is generated. Further, the linear solenoid valve SL1 (the value of the current applied to the solenoid unit) is controlled by the TMECU 21. Further, the hydraulic control device 70 has a plurality of linear solenoid valves (not shown) corresponding to any one or two of the clutches C2, C3 and C4 and the brakes B1 and B2 of the automatic transmission 25. The linear solenoid valve is also controlled by the TMECU 21. In the present embodiment, the oil passage L1 is connected to an input port of a linear solenoid valve corresponding to, for example, the clutches C2 and C3 and the brake B2 among these linear solenoid valves (not shown). The input port of the linear solenoid valve corresponding to the clutch C4 and the brake B1 is connected to the output port of the primary regulator valve 71 through an oil passage (not shown) formed in the valve body 700.

Signal pressure output valve SR is on-off solenoid valve, for example _{normally closed} type that is controlled energized by TMECU21, the input port of the signal pressure output valve SR is a modulator valve via the oil passage L5, which is formed in the valve body 700 It communicates with 74 output ports. The signal pressure output valve SR outputs the modulator pressure Pmod from the modulator valve 74 as the signal pressure Psr from the output port when energizing the solenoid unit.

The switching valve 80 urges the spool 800, a spool 800 that is movably disposed in the axial direction in the valve body 700, a partition member 801 that is fixed in the valve body 700 so as to be aligned with the spool 800 in the axial direction, and the spool 800. And a ball 805 as a valve body disposed in the partition member 801. Further, the switching valve 80 includes a first input port 80a, a second input port 80b, a first output port 80c, a second output port 80d, a signal pressure input port 80e, and first and second drain ports 80f. , 80 g.

The spool 800 has two lands 800x and 800y formed at intervals in the axial direction and a ball pressing portion 800z, and is arranged in the valve body 700 so that the ball pressing portion 800z is positioned on the partition member 801 side. Is done. The partition member 801 has a ball chamber 801a formed so as to open on the spool 800 side. The spring 802 is disposed between the land 800 y and the partition member 801 so as to surround the ball pressing portion 800 z of the spool 800, and biases the spool 800 upward in FIG. 4 so as to be separated from the partition member 801. The ball 805 is disposed so as to be movable in the axial direction of the spool 800 in a ball chamber 801 a defined in the partition member 801.

The first input port 80a communicates with the space between the two lands 800x and 800y of the spool 800 and also communicates with the drain port of the secondary regulator valve 72 through an oil passage L6 formed in the valve body 700. The hydraulic oil drained from the secondary regulator valve 72 as the secondary pressure Psec is generated is supplied to the first input port 80a via the oil passage L6. The second input port 80 b is connected to the oil passage L 3 formed in the valve body 700 and communicates with the ball chamber 801 a of the partition member 801. The hydraulic oil from the electric oil pump 28 is supplied to the second input port 80b via the oil passage L3 when the electric oil pump 28 is operated.

The first output port 80c has a substantially triangular cross-sectional shape that tapers from the partition member 801 side toward the spool 800 side, and the hydraulic oil of the oil cooler 75 is formed through an oil passage L7 formed in the valve body 700. Connect to the entrance. The second output port 80d is connected to an oil passage L8 formed in the valve body 700 and communicates with the ball chamber 801a of the partition member 801. As shown in FIG. 4, the oil passage L8 has a check valve 79 in the middle, and the end of the oil passage L8 opposite to the second output port 80d is connected to the first output port 80c and the oil. The oil passage L7 communicates with the cooler 75. When the hydraulic pressure on the upstream side, that is, the second output port 80d (electric oil pump 28) side is higher than the hydraulic pressure on the downstream side, that is, the oil passage L7, the check valve 79 moves from the second output port 80d side to the oil passage L7 side. The flow of hydraulic oil is allowed, and the flow of hydraulic oil from the second output port 80d side to the oil path L7 side is blocked when the hydraulic pressure on the second output port 80d side is equal to or lower than the hydraulic pressure on the oil path L7 side.

The signal pressure input port 80e communicates with the output port of the signal pressure output valve SR via an oil passage L9 formed in the valve body 700. The first drain port 80f has a substantially triangular cross-sectional shape that tapers from the spool 800 side toward the partition member 801 side, and can communicate with the space between the two lands 800x and 800y of the spool 800. The second drain port 80g communicates with a spring chamber in which the spring 802 is disposed and can communicate with the ball chamber 801a of the partition member 801. Thereby, the hydraulic oil remaining in the ball chamber 801a can be returned from the second drain port 80g to the hydraulic oil reservoir through an oil passage (not shown) of the valve body 700.

In the present embodiment, the switching valve 80 is attached in such a manner that the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is not supplied to the signal pressure input port 80e, and the spool 800 is moved upward in FIG. It is the 1st state (state of the left half in the figure) urged so that it may separate from division member 801. In the mounted state (first state) of the switching valve 80, the first input port 80a and the first drain port 80f communicate with each other through the space between the two lands 800x and 800y of the spool 800. When the switching valve 80 is attached, the upper end of the first output port 80c in the drawing is slightly communicated with the space between the two lands 800x and 800y of the spool 800. Thereby, when the switching valve 80 forms the first state, the drain oil from the secondary regulator valve 72 supplied to the oil passage L6 basically flows into the first drain port 80f, and the first drain port 80f. To the hydraulic oil reservoir through an oil passage (not shown) of the valve body 700. Further, when the switching valve 80 forms the first state, a small part of the drain oil from the oil passage L6 flows into the oil passage L7 via the first output port 80c. As a result, it is possible to suppress the entry of foreign matter between the land 800y of the spool 800 and the first output port 80c.

Further, when the switching valve 80 forms the first state, the spool 800 is biased so as to be separated from the partition member 801 by the spring 802, so that the ball pressing portion 800 z of the spool 800 is moved to the partition member 801. Located in the vicinity of the opening of the ball chamber 801a, an axial interval is formed between the ball pressing portion 800z and the ball 805 in the ball chamber 801a. Accordingly, when the hydraulic oil is supplied from the electric oil pump 28 to the oil passage L3 when the switching valve 80 forms the first state, the ball is caused by the action of the hydraulic pressure supplied from the oil passage L3 to the second input port 80b. 805 is pressed by the valve seat portion on the upper side (the signal pressure input port 80e side) of the partition member 801 in the figure. As a result, the second input port 80b of the switching valve 80 communicates with the second output port 80d via the ball chamber 801a, and the hydraulic oil from the oil passage L3 flows to the second input port 80b, the ball chamber 801a, and the second output. It becomes possible to flow into the oil passage L7 through the port 80d and the oil passage L8 (check valve 79).

On the other hand, when the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is supplied to the signal pressure input port 80e, the spool 800 moves toward the partition member 801 against the biasing force of the spring 802, The switching valve 80 forms the second state (the state on the right half in FIG. 4). When the switching valve 80 forms the second state, the communication between the first input port 80a and the first drain port 80f is blocked by the land 800x of the spool 800, and the first input port 80a The entire first output port 80c communicates with the space between the two lands 800x and 800y. Thereby, when the switching valve 80 forms the second state, the drain oil from the secondary regulator valve 72 supplied to the oil passage L6 can flow into the oil passage L7 via the first output port 80c.

Further, when the switching valve 80 forms the second state, the spool 800 moves toward the partition member 801, so that the ball pressing portion 800z of the spool 800 contacts the ball 805 in the ball chamber 801a, The ball 805 is pressed against the valve seat portion below the partition member 801 in the drawing (on the second output port 80d side). In the present embodiment, the area of the pressure receiving surface of the spool 800 that receives the signal pressure Psr (modulator pressure Pmod) supplied to the signal pressure input port 80e is a threshold at which the hydraulic pressure (discharge pressure) from the electric oil pump 28 is predetermined. The thrust applied to the spool 800 by the action of the signal pressure Psr when the pressure is less than the thrust applied to the ball 805 by the action of the urging force of the spring 802 and the hydraulic pressure supplied from the oil passage L3 to the second input port 80b. It is determined to overcome the harmony.

Thus, even when the hydraulic oil is supplied from the electric oil pump 28 to the oil passage L3 when the switching valve 80 forms the second state, the ball 805 is basically separated by the ball pressing portion 800z of the spool 800. It remains pressed by the valve seat 801 in the lower part of the figure (the second output port 80d side). As a result, when the switching valve 80 forms the second state in response to the supply of the signal pressure Psr to the signal pressure input port 80e, the ball 805 causes the second input port 80b of the switching valve 80 and the second output. The communication with the port 80d is cut off, and the hydraulic oil from the electric oil pump 28 can be supplied to the oil path L1 side without being supplied to the second output port 80d.

In the present embodiment, the threshold value for the hydraulic pressure (discharge pressure) from the electric oil pump 28 is subjected to experiments and analysis as an upper limit value of the discharge pressure that does not cause the electric oil pump 28 (magnet coupling) to step out. It has been established. Therefore, if the discharge pressure of the electric oil pump 28 increases more than necessary due to some factor and the hydraulic pressure from the electric oil pump 28 exceeds the above threshold, the ball is caused by the action of the hydraulic pressure supplied from the oil passage L3 to the second input port 80b. The sum of the thrust applied to 805 and the biasing force of the spring 802 overcomes the thrust applied to the spool 800 by the action of the signal pressure Psr supplied to the signal pressure input port 80e, and the switching valve 80 forms the first state. Thus, communication between the second input port 80b and the second output port 80d is permitted. Thus, when the discharge pressure of the electric oil pump 28 increases more than necessary, the switching valve 80 can function as a relief valve to suppress the occurrence of step-out of the electric oil pump 28.

Next, referring to FIG. 4 and FIG. 5, the engine 12 is restarted in response to a start request to the vehicle 10 after the operation of the engine 12 is stopped as the vehicle 10 stops due to the execution of the idle stop control. The operation of the hydraulic control device 70 during operation will be described. In the following description, the “operation stop” of the engine 12 means that the engine 12 has been rotated at a lower speed and a sufficient amount of hydraulic oil is not being discharged from the mechanical oil pump 24. Including a state in which the operation is completely stopped.

When the operation of the engine 12 is stopped as the vehicle 10 stops, the TMECU 21 releases the energization of the signal pressure output valve SR (maintains the release state) in response to the operation stop (engine stop command) of the engine 12. Then, the output of the signal pressure Psr is stopped and the electric oil pump 28 is operated. Thereby, the switching valve 80 forms the first state described above, and the hydraulic pressure from the electric oil pump 28 is supplied from the oil passage L2 to the oil passage L1 as the line pressure PL. In addition, since the switching valve 80 forms the first state, a part of the oil from the electric oil pump 28 is oil passage L3, the second input port 80b of the switching valve 80, the ball chamber 801a, and the second output port 80d. Then, the oil flows into the oil passage L7 via the oil passage L8 (check valve 79), and is further supplied to the low-pressure oil supply section including the centrifugal oil pressure cancellation chamber C1c of the clutch C1 via the oil cooler 75. As a result, even if the mechanical oil pump 24 stops with the operation stop of the engine 12 and the drain oil from the primary regulator valve 71 generated with the generation of the original pressure decreases, the centrifugal hydraulic pressure cancellation chamber of the clutch C1 is reduced. It is possible to suppress a shortage of the amount of hydraulic oil supplied to the low-pressure oil supply unit of the automatic transmission 25 including C1c.

While the electric oil pump 28 is operated in such a state that the switching valve 80 forms the first state in this way, the TMECU 21 is engaged when starting the vehicle 10 by restarting the engine 12 from the linear solenoid valve SL1. The hydraulic pressure is such that the engagement oil chamber C1e can be filled with hydraulic oil without giving torque capacity to the clutch C1 (see FIG. 3) (the piston can be moved to eliminate the stroke). The hydraulic pressure command value Psl1 * for the linear solenoid valve SL1 is set so as to be output. Further, during this time, the TMECU 21 controls the electric oil pump 28 so as to generate a hydraulic pressure corresponding to the hydraulic pressure command value Psl1 * for the linear solenoid valve SL1 and the amount of hydraulic oil supplied to the low pressure oil supply unit.

Further, when the vehicle 10 is stopped (after the engine 12 is stopped), when the driver of the vehicle 10 releases the brake pedal 93 and the accelerator pedal 91 is depressed, the vehicle 10 is requested to start. (Time t1 in FIG. 5), in response to the start request, the TMECU 21 energizes the signal pressure output valve SR and outputs the signal pressure Psr while operating the electric oil pump 28. As a result, the switching valve 80 forms the second state described above, so that the communication between the second input port 80b and the second output port 80d is cut off, and the electric oil pump 28 to the low-pressure oil supply unit of the automatic transmission 25 is disconnected. The supply of hydraulic oil is cut off.

Furthermore, when the engine 12 is started in response to a start request for the vehicle 10 and the mechanical oil pump 24 discharges hydraulic oil accordingly, the primary regulator valve 71 regulates the hydraulic oil from the mechanical oil pump 24. The secondary regulator valve 72 generates a secondary pressure Psec lower than the primary pressure by regulating the drain oil of the primary regulator valve 71. At this time, the original pressure generated by the primary regulator valve 71 does not flow downstream of the first check valve 77 until it becomes higher than the hydraulic pressure from the electric oil pump 28. The drain oil of the secondary regulator valve 72 flows into the oil passage L7 from the oil passage L6 via the first input port 80a and the first output port 80c of the switching valve 80 that forms the second state, and further the oil cooler 75. To the low pressure oil supply section including the centrifugal hydraulic pressure cancel chamber C1c of the clutch C1.

As a result, in response to the start request after the operation of the engine 12 is stopped, the hydraulic oil from the electric oil pump 28 is regulated by the linear solenoid valve SL1 and supplied to the engagement oil chamber C1e, and the drain oil of the secondary regulator valve 72 is supplied. Since the centrifugal hydraulic pressure cancellation chamber C1c can be supplied, it is possible to quickly engage the clutch C1 while suppressing the sudden engagement according to the start request. Further, at this time, it is not necessary to increase the discharge flow rate of the electric oil pump 28 in order to cover the supply amount of the hydraulic oil to the low pressure oil supply portion including the centrifugal hydraulic pressure cancel chamber C1c of the clutch C1, so that the electric oil pump 28 Can be reduced in size and cost. As a result, according to the hydraulic control device 70, the amount of hydraulic oil supplied to the low-pressure oil supply unit including the centrifugal hydraulic pressure cancellation chamber C1c of the clutch C1 is insufficient while reducing the size and cost of the electric oil pump 28. It becomes possible to suppress.

Further, in the hydraulic control device 70 including the switching valve 80, the second is applied until the sum of the thrust applied to the ball 805 and the urging force of the spring 802 overcomes the thrust applied to the spool 800 by the action of the signal pressure Psr. The hydraulic oil from the electric oil pump 28 can be supplied to the linear solenoid valve SL1 and the like while the communication between the input port 80b and the second output port 80d is cut off. Therefore, as shown in FIG. 5, by increasing the discharge pressure (line pressure PL) of the electric oil pump 28, the brake B2 (FIG. 5) that is engaged with the clutch C1 when the engine 10 is restarted and the vehicle 10 is started. 3), the hydraulic oil (line pressure) PL from the electric oil pump 28 is regulated and supplied, and the brake B2 can be engaged. At this time, even if the discharge pressure of the electric oil pump 28 increases more than necessary due to some factor, the switching valve 80 can function as a relief valve to suppress the occurrence of step-out of the electric oil pump 28.

Further, according to the switching valve 80, the output of the signal pressure Psr from the signal pressure output valve SR is stopped to form the first state and the signal pressure Psr from the signal pressure output valve SR to the signal pressure input port 80e. It is possible to form the second state by supplying. When the switching valve 80 forms the second state, the ball 805 can more reliably suppress the leakage of hydraulic oil between the second input port 80b and the second output port 80d. It is possible to further reduce the burden on the electric oil pump 28 by supplying the hydraulic oil from the oil pump 28 only to the clutch C1 side.

When the supply of hydraulic oil from the electric oil pump 28 to the low pressure oil supply unit of the automatic transmission 25 is interrupted after the engine 12 is started, the drain of the secondary regulator valve 72 supplied to the low pressure oil supply unit. The linear solenoid valve SLT may be controlled regardless of the accelerator opening or the like so that the oil flow rate is sufficiently secured. Further, when the electric oil pump 28 is stopped after the engine 12 is started, the flow rate of the drain oil of the secondary regulator valve 72 is sufficiently secured, and the hydraulic pressure from the electric oil pump 28 is the original pressure from the mechanical oil pump 24. The discharge pressure of the electric oil pump 28 may be gradually reduced according to the original pressure generated by the primary regulator valve 71 so that it can be quickly replaced.

Furthermore, in the switching valve 80, the first output port 80c slightly communicates with the space between the two lands 800x and 800y of the spool 800 when the first state is formed, but the present invention is not limited to this. That is, the switching valve 80 may be configured such that communication between the first input port 80a and the first output port 80c is blocked by the land 800y of the spool 800 when the first state is formed.

In addition, since the vehicle 10 can perform inertial traveling that stops the operation of the engine 12 during traveling, the hydraulic control device 70 and the TMECU 21 perform the above-described operation during inertial traveling of the vehicle 10. It may be configured as follows. That is, the TMECU 21 cancels the energization of the signal pressure output valve SR (maintains the release state) and stops the output of the signal pressure Psr according to the stop of the engine 12 (engine stop command) accompanying the execution of inertial running. At the same time, the electric oil pump 28 may be operated, and the signal pressure output valve SR may be energized to output the signal pressure Psr while the electric oil pump 28 is operated in response to a request to cancel inertial running.

As a result, even if the mechanical oil pump 24 is stopped along with the stop of the operation of the engine 12 for coasting, and the drain oil of the secondary regulator valve 72 is reduced, the electric oil pump is operated, so that the clutches C1˜ It is possible to suppress a shortage of the amount of hydraulic oil supplied to the low pressure oil supply section of the automatic transmission 25 including the C4 centrifugal hydraulic pressure cancellation chamber C1c and the like. Further, in response to a request to cancel inertial running, the hydraulic oil from the electric oil pump 28 is supplied to at least one of the engagement oil chambers C1e of the clutches C1 to C4 engaged when the engine 12 is restarted, and the secondary. The drain oil of the regulator valve 72 is supplied to the centrifugal oil pressure cancel chamber C1c and the like, and at least one of the clutches C1 to C4 can be quickly engaged while suppressing sudden engagement.

FIG. 6 is a system diagram showing another hydraulic control device 70B of the present disclosure. Note that among the components of the hydraulic control device 70B, the same components as those of the hydraulic control device 70 described above are denoted by the same reference numerals, and redundant description is omitted.

The hydraulic control device 70B is also connected to the mechanical oil pump 24 and the electric oil pump 28, generates the hydraulic pressure required by the starting device 23 and the automatic transmission 25, and lubricates objects such as various bearings and the clutches C1 to C4. The hydraulic oil is supplied to a low-pressure oil supply unit (lubricated part) such as the centrifugal hydraulic pressure cancellation chamber C1c. In the hydraulic control device 70B, an oil passage L1 (first oil passage) of the valve body 700B is connected to a discharge port of the mechanical oil pump 24, and a first check valve 77 is installed in the middle thereof. The oil passage L2 (second oil passage) of the valve body 700B includes a second check valve 78 in the middle thereof. One end of the oil passage L2 is connected to the discharge port of the electric oil pump 28, the other end is connected to the downstream side of the first check valve 77 of the oil passage L1, and the oil passage L3 branches from the oil passage L2. Has been.

Further, the merging section _{J 12} of the oil passage L1 and L2, the oil passage connected to the engaging oil chamber C1e of the clutch C1 with including a linear solenoid valve SL1 (No. 4 oil passage) L40 and the clutch C2-C4, An oil passage communicating with the engagement oil chambers of the brakes B1 and B2 is connected. As illustrated, the branch portion _{J 23} between the oil passage L2 and the oil passage L3 includes an electric oil pump 28 is provided between the merging portion _{J 12} of the oil passage L1 and the oil passage L2, the oil passage L2 between the junction unit _{J 12} and the branch portion _{J 23,} second check valve 78 is installed. The second check valve 78 serves to permit the flow of oil from the electric oil pump 28 side is higher than the hydraulic pressure in the hydraulic pressure merging portion J ₁₂ side to the oil passage L40 side of the diversion unit J _23, branch portion blocking the flow of oil into the oil passage L40 side from the electric oil pump 28 side when the oil pressure in J ₂₃ side is a hydraulic or less in the combined unit J ₁₂ side. Thus, the hydraulic oil from the electric oil pump 28 is supplied to the clutch C1 and the like while preventing the hydraulic oil from the mechanical oil pump 24 from being supplied to the low pressure oil supply unit via the oil passage L3 and the switching valve 80. Is possible.

In addition, the hydraulic control device 70B supplies an oil passage (secondary pressure) from the regulator valve (71) regulated by the secondary regulator valve 72 to the fluid chamber 230 of the starting device (torque converter) ( (Fifth oil passage) L51 and L52, second switching valve 85, check valve (third check valve) 86, for example, modulator pressure Pmod from modulator valve 74 is output as signal pressure when energizing the solenoid portion And an on / off solenoid valve SL output from the port. The second switching valve 85 communicates between the oil passage L51 and the oil passage L52 and communicates between the oil passage L61 and the oil passage L62, the communication between the oil passage L51 and the oil passage L52, and the oil passage L61 and the oil. A shut-off state in which communication with the path L62 is released can be formed, and either a communication state or a shut-off state is formed in the output state of the signal pressure from the on / off solenoid valve SL. The check valve 86 includes a coil spring (not shown), and is installed on the oil passage L62 so as to be positioned between the second switching valve 85 and the oil cooler 75. The check valve 86 restricts the flow of the working oil to the oil cooler 75 side by the biasing force of the coil spring in accordance with the pressure drop of the return oil from the fluid chamber 230. With this configuration, even if the drain oil from the primary regulator valve 71 is not supplied to the fluid chamber 230 due to the operation of the engine 12, that is, the mechanical oil pump 24 is stopped, the hydraulic fluid is put into the fluid chamber 230. Can be secured.

Further, in the hydraulic control device 70B, the hydraulic oil that has flowed out of the drain port of the secondary regulator valve 72 is returned to the hydraulic oil reservoir through the strainer 60. Further, in the hydraulic control device 70B, the hydraulic oil outlet of the oil cooler 75 communicates with the first input port 80a of the switching valve 80 via the oil passage L6, and an oil passage (not shown) formed in the valve body 700B. Through the hydraulic oil inlet of the centrifugal oil pressure cancellation chamber C1c of the clutch C1. Further, in the hydraulic control device 70B, the oil passage L7 connected to the first output port 80c of the switching valve 80 is, as shown in FIG. 6, the hydraulic oil of the low-pressure oil supply section that is the centrifugal hydraulic pressure cancellation chamber C1c of the clutch C1. It communicates with an oil passage that communicates with the inlet.

Next, referring to FIG. 6 and FIG. 7, the engine 12 is restarted in response to the start request and the inertia travel release request after the operation of the engine 12 is stopped in accordance with the execution of the idle stop control and the inertia travel. The operation of the hydraulic control device 70B at this time will be described.

When the driver of the vehicle 10 releases the depression of the accelerator pedal 91 and the brake pedal 93 is depressed, and the operation of the engine 12 is stopped when the vehicle 10 is stopped by the idle stop control, the TMECU 21 In response to the operation stop (engine stop command), the energization to the signal pressure output valve SR is canceled (maintained in the release state) to stop the output of the signal pressure Psr and to operate the electric oil pump 28 (time in FIG. 7). t _a ). Thereby, the switching valve 80 forms the first state described above, and the hydraulic pressure from the electric oil pump 28 is supplied from the oil passage L2 to the oil passage L1 as the line pressure PL. Further, since the switching valve 80 forms the first state, a part of the oil from the electric oil pump 28 is supplied to the oil passages L2 and L3, the second input port 80b of the switching valve 80, the ball chamber 801a, and the second output. The oil flows into the oil passage L7 via the port 80d and the oil passage L8 (check valve 79), and is supplied to the low-pressure oil supply section including the centrifugal oil pressure cancellation chamber C1c of the clutch C1. As a result, even if the hydraulic oil is not supplied from the mechanical oil pump 24 when the operation of the engine 12 is stopped, the hydraulic oil from the electric oil pump 28 is supplied to the low-pressure oil via the oil passages L2 and L3, the switching valve 80 and the like. It becomes possible to supply to a supply part.

After the operation of the electric oil pump 28 starts, for example, when the vehicle speed of the vehicle 10 decreases to the first vehicle speed in response to the depression of the brake pedal 93 by the driver (time t _b in FIG. 7), the TMECU 21 performs the signal pressure output valve SR. And the signal pressure Psr is output, and as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is increased compared to when the switching valve 80 forms the first state. Further, the TMECU 21 is engaged with a brake B1 that is engaged when the second forward speed is formed in order to enable quick start at the second forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve corresponding to the brake B1 is controlled so as to be in a state immediately before the match. As a result, the switching valve 80 forms the second state described above, so that the communication between the second input port 80b and the second output port 80d is cut off, and the hydraulic oil from the electric oil pump 28 is supplied to the automatic transmission 25. The oil is supplied from the oil passage L2 to the engagement oil chamber of the brake B1 without being supplied to the low-pressure oil supply unit.

The TMECU 21 causes the signal pressure output valve SR to output the signal pressure Psr until a predetermined hydraulic pressure supply time has elapsed from the start of control of the linear solenoid valve of the brake B1 (start of supply of hydraulic oil from the electric oil pump 28). At the same time, the discharge flow rate of the electric oil pump 28 is increased. As a result, the hydraulic oil is rapidly filled into the engagement oil chamber of the brake B1. When the hydraulic pressure supply time from the start of control of the linear solenoid valve of the brake B1 has elapsed (time t _c in FIG. _7), TMECU21 stops the output of the signal pressure Psr to release the energization of the signal pressure output valve SR, While fully opening the linear solenoid valve of the brake B1, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state. As a result, the hydraulic oil from the electric oil pump 28 is supplied to the brake B1 so that the hydraulic pressure in the engagement oil chamber is maintained, and the switching valve 80 forms the first state described above, whereby the oil passage It is also supplied to the low-pressure oil supply unit via L2, L3, the switching valve 80, and the like.

Further, when the vehicle speed of the vehicle 10 decreases to the second vehicle speed (<first vehicle speed) according to the depression of the brake pedal 93 by the driver (time t _d in FIG. 7), the TMECU 21 sets the signal pressure output valve SR. Energization is performed to output the signal pressure Psr, and the discharge flow rate of the electric oil pump 28 is increased compared to when the switching valve 80 forms the first state. Furthermore, the TMECU 21 is engaged with a brake B2 that is engaged when the first forward speed is established in order to enable quick start at the first forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve corresponding to the brake B2 is controlled so as to be in a state immediately before the match. As a result, the switching valve 80 forms the second state so that the communication between the second input port 80b and the second output port 80d is cut off, and the hydraulic oil from the electric oil pump 28 is used as the low-pressure oil of the automatic transmission 25. Without being supplied to the supply unit, the oil is supplied from the oil passage L2 to the engagement oil chamber of the brake B2. As hydraulic oil from the electric oil pump 28 is supplied to the brake B2, the hydraulic oil in the engagement oil chamber of the brake B1 is drained.

The TMECU 21 causes the signal pressure output valve SR to output the signal pressure Psr until a predetermined hydraulic pressure supply time has elapsed from the start of control of the linear solenoid valve of the brake B2 (start of supply of hydraulic oil from the electric oil pump 28). At the same time, the discharge flow rate of the electric oil pump 28 is increased. As a result, the hydraulic oil is rapidly filled into the engagement oil chamber of the brake B2. When the hydraulic pressure supply time has elapsed since the start of the control of the linear solenoid valve of the brake B2 (time t _e in FIG. 7), the TMECU 21 stops energization of the signal pressure output valve SR and stops the output of the signal pressure Psr, While fully opening the linear solenoid valve of the brake B2, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state. Thereby, the hydraulic oil from the electric oil pump 28 is supplied to the brake B2 so that the hydraulic pressure in the engagement oil chamber is maintained, and the switching valve 80 forms the above-described first state, whereby the oil passage It is also supplied to the low-pressure oil supply unit via L2, L3, the switching valve 80, and the like.

Further, when the vehicle 10 is stopped in response to depression of the brake pedal 93 by the driver (time in FIG. 7 _t f), TMECU21, together to output the signal pressure Psr by energizing the signal pressure output valve SR, the switching valve 80 Increases the discharge flow rate of the electric oil pump 28 compared to when the first state is formed. Further, the TMECU 21 is engaged with a clutch C1 that is engaged when the first forward speed is formed in order to enable quick start at the first forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve SL1 corresponding to the clutch C1 is controlled so as to be in a state immediately before the combination. As a result, the switching valve 80 forms the second state described above, so that the communication between the second input port 80b and the second output port 80d is cut off, and the hydraulic oil from the electric oil pump 28 is supplied to the automatic transmission 25. The oil is supplied from the oil passage L2 to the engagement oil chamber C1e of the clutch C1 through the oil passage L40 without being supplied to the low-pressure oil supply section.

The TMECU 21 outputs the signal pressure Psr to the signal pressure output valve SR until a predetermined hydraulic pressure supply time elapses from the start of control of the linear solenoid valve SL1 of the clutch C1 (start of supply of hydraulic oil from the electric oil pump 28). And the discharge flow rate of the electric oil pump 28 is increased. As a result, the hydraulic oil is rapidly filled into the engagement oil chamber C1e of the clutch C1. When the hydraulic pressure supply time has elapsed since the start of control of the linear solenoid valve SL1 (time t _g in FIG. _7), TMECU21 stops the output of the signal pressure Psr to release the energization of the signal pressure output valve SR, linear solenoid While fully opening the valve SL1, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state. Thereby, the hydraulic oil from the electric oil pump 28 is supplied to the clutch C1 and the brake B2 so that the hydraulic pressure in the engagement oil chamber C1e and the like is maintained, and the switching valve 80 forms the first state described above. As a result, the oil is supplied also to the low-pressure oil supply unit including the centrifugal oil pressure cancellation chamber C1c via the oil passages L2 and L3, the switching valve 80, and the like.

As described above, according to the hydraulic control device 70B, the switching valve 0 is switched to the first state when hydraulic oil is no longer supplied from the mechanical oil pump 24 when the engine 12 is stopped by the idle stop control. Thus, the hydraulic oil from the electric oil pump 28 can be supplied to the low-pressure oil supply unit such as the centrifugal hydraulic pressure cancel chamber C1c through the switching valve 80. Further, by switching the switching valve 80 to the second state, the hydraulic oil from the electric oil pump 28 is supplied to the clutch C1 and the like that are engaged when the engine 12 is restarted without being supplied to the low pressure oil supply unit. Can do.

As a result, when the hydraulic oil is not supplied from the mechanical oil pump 24 when the operation of the engine 12 is stopped while reducing the size and cost of the electric oil pump 28, the clutch C1 of the automatic transmission 25, etc. It is possible to ensure a good supply amount of hydraulic oil to both of the oil supply units. Then, after the vehicle 10 is stopped, when the driver releases the brake pedal 93 and the accelerator pedal 91 is depressed to make a start request to the vehicle 10 (time t _h in FIG. 7), the mechanical oil The hydraulic oil from the electric oil pump 28 is supplied from the linear solenoid valve SL1 to the engagement oil chamber C1e and supplied to the centrifugal hydraulic pressure cancellation chamber C1c via the switching valve 80 until the hydraulic pressure by the pump 24 increases, thereby requesting a start. Accordingly, the clutch C1 can be quickly engaged while suppressing sudden engagement.

In addition, when the operation of the engine 12 is stopped by the idle stop control, the hydraulic control device 70B starts supplying hydraulic oil from the electric oil pump 28 to the clutch C1 and the brake B1 that are engaged when the engine 12 is restarted. The switching valve 80 forms the second state until the hydraulic pressure supply time has elapsed and the clutch C1 and the like are in a state immediately before engagement. Further, when the switching valve 80 forms the second state while the operation of the engine 12 is stopped by the idle stop control, the discharge flow rate of the electric oil pump 28 is higher than when the switching valve 80 forms the first state. Increased. As a result, while the engine 12 is stopped by the idle stop control, a large amount of oil is quickly supplied to the clutch C1 and the like that are engaged at the time of restart, and the clutch C1 and the like according to the restart of the engine 12 Can be quickly engaged, and the time during which hydraulic oil is not supplied from the electric oil pump 28 to the low-pressure oil supply unit can be further shortened.

On the other hand, when an engine stop command for the engine 12 is issued in accordance with the inertial running of the vehicle 10, the TMECU 21 releases the energization of the signal pressure output valve SR (maintains the released state) and stops the output of the signal pressure Psr. And the electric oil pump 28 is operated (time t _i in FIG. 7). As a result, even if the hydraulic oil is not supplied from the mechanical oil pump 24 when the operation of the engine 12 is stopped, the hydraulic oil from the electric oil pump 28 is supplied to the low pressure oil supply unit via the switching valve 80 or the like. Is possible.

Further, after the operation of the electric oil pump 28 is started, when the vehicle speed of the vehicle 10 decreases to the first coasting speed (time t _j in FIG. 7), the TMECU 21 controls the signal pressure so that the switching valve 80 forms the second state. The output valve SR is energized to output the signal pressure Psr and, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is increased compared to when the switching valve 80 forms the first state. Further, the TMECU 21 is engaged with a clutch C1 that is engaged when the fourth forward speed is established in order to enable quick start at the fourth forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve SL1 is controlled so as to be in a state immediately before the match. As a result, the engagement oil chamber C1e of the clutch C1 is operated from the start of control of the linear solenoid valve SL1 of the clutch C1 (the start of supply of hydraulic oil from the electric oil pump 28) until a predetermined hydraulic pressure supply time elapses. Oil is rapidly filled. When the hydraulic pressure supply time has elapsed from the start of control of the linear solenoid valve SL1 (time t _k in FIG. 7), the TMECU 21 releases the signal pressure output valve SR to stop the output of the signal pressure Psr, and the linear solenoid valve While SL1 is fully opened, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state.

Further, when the vehicle speed of the vehicle 10 decreases to the second coasting speed (<first coasting speed) (time t ₁ in FIG. 7), the TMECU 21 outputs a signal pressure so that the switching valve 80 forms the second state. The valve SR is energized to output the signal pressure Psr, and the discharge flow rate of the electric oil pump 28 is increased compared to when the switching valve 80 forms the first state. Further, the TMECU 21 is engaged with a brake B2 that is engaged when the first forward speed is formed in order to enable quick start at the first forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve corresponding to the brake B2 is controlled so as to be in a state immediately before the match. As a result, the hydraulic oil is supplied to the engagement oil chamber of the brake B2 from the start of control of the linear solenoid valve of the brake B2 (start of supply of hydraulic oil from the electric oil pump 28) until a predetermined hydraulic pressure supply time elapses. Quick filling. When the hydraulic pressure supply time elapses from the start of the control of the linear solenoid valve of the brake B2 (time t _m in FIG. 7), the TMECU 21 stops energizing the signal pressure output valve SR and stops the output of the signal pressure Psr, While fully opening the linear solenoid valve of the brake B2, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state.

When the driver requests the engine 12 to be restarted by depressing the accelerator pedal 91 (time t _n in FIG. 7), the TMECU 21 outputs a signal pressure so that the switching valve 80 forms the second state. The valve SR is energized to output the signal pressure Psr, and as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is increased as compared to when the switching valve 80 forms the first state. Further, the TMECU 21 is engaged with a clutch C1 that is engaged when the first forward speed is established in order to enable quick start at the first forward speed when the accelerator pedal 91 is depressed by the driver. The linear solenoid valve SL1 is controlled so as to be in a state immediately before the match. As a result, the hydraulic oil from the electric oil pump 28 is kept low until a predetermined hydraulic pressure supply time elapses from the start of control of the linear solenoid valve SL1 of the clutch C1 (start of supply of hydraulic oil from the electric oil pump 28). The oil is not supplied to the oil supply section, that is, the centrifugal oil pressure cancel chamber C1c, and the engagement oil chamber C1e of the clutch C1 is rapidly filled with the hydraulic oil. Thus, the hydraulic oil from the electric oil pump 28 can be supplied to the clutch C1 to be engaged in response to the restart of the engine 12 without being supplied to the low-pressure oil supply unit, and the clutch C1 can be engaged. .

When the hydraulic pressure supply time has elapsed from the start of control of the linear solenoid valve SL1 (time t _o in FIG. _7), TMECU21 stops the output of the signal pressure Psr to release the energization of the signal pressure output valve SR, the linear solenoid valve While SL1 is fully opened, as shown in FIG. 7, the discharge flow rate of the electric oil pump 28 is returned to the value when the switching valve 80 forms the first state. When the engine 12 is restarted and the rotational speed of the engine 12 increases to a predetermined rotational speed at which a sufficient amount of hydraulic oil is discharged from the mechanical oil pump 24 (time t _p in FIG. 7), the TMECU 21 The operation of the electric oil pump 28 is stopped.

As described above, according to the hydraulic control device 70B, the switching valve 0 is switched to the first state when hydraulic oil is no longer supplied from the mechanical oil pump 24 when the operation of the engine 12 is stopped due to the inertial running. Thus, the hydraulic oil from the electric oil pump 28 can be supplied to the low pressure oil supply unit such as the centrifugal oil pressure cancel chamber C1c via the switching valve 80. Further, by switching the switching valve 80 to the second state, the hydraulic oil from the electric oil pump 28 is supplied to the clutch C1 and the like that are engaged when the engine 12 is restarted without being supplied to the low pressure oil supply unit. Can do. When the driver depresses the accelerator pedal 91 to request the vehicle 10 to start or accelerate, the hydraulic oil from the electric oil pump 28 is supplied to the linear solenoid valve until the hydraulic pressure by the mechanical oil pump 24 increases. By supplying from SL1 to the engagement oil chamber C1e and to the centrifugal hydraulic pressure cancellation chamber C1c via the switching valve 80, it is possible to quickly engage the clutch C1 while suppressing sudden engagement according to the start request. It becomes possible.

In addition, while the engine 12 is stopped due to the inertia running, the hydraulic control device 70B starts supplying hydraulic oil from the electric oil pump 28 to the clutch C1 and the brake B1 that are engaged when the engine 12 is restarted. The switching valve 80 forms the second state until the hydraulic pressure supply time elapses and the clutch C1 and the like are in a state immediately before engagement. Furthermore, when the switching valve 80 forms the second state while the engine 12 is stopped due to the inertial running, the discharge flow rate of the electric oil pump 28 is larger than when the switching valve 80 forms the first state. Is increased. As a result, while the engine 12 is stopped due to the inertial running, a large amount of oil is quickly supplied to the clutch C1 and the like that are engaged at the time of restart, and the clutch C1 according to the restart of the engine 12 Etc. can be quickly engaged, and the time during which hydraulic oil is not supplied from the electric oil pump 28 to the low-pressure oil supply unit can be further shortened. The processing to be executed from the time t _n in FIG. 7 by TMECU21 to time t _p is the idling stop control is executed when the restart request of the engine 12 after the operation of the engine 12 is stopped it is made Also good.

FIG. 8 is a schematic configuration diagram showing another switching valve 80B applicable to the hydraulic control device 70B in place of the switching valve 80 described above.

8 includes a first valve 81 and a second valve 82. The switching valve 80B shown in FIG. The first valve 81 has two lands 810x and 810y and is disposed in the valve body 700B so as to be movable in the axial direction, a first spring 812 for biasing the first spool 810, 1 input port 81a, 1st output port 81c, signal pressure input port 81e, and 1st and 2nd drain ports 81f and 81g are included. The first input port 81a communicates with the space between the two lands 810x and 810y of the first spool 810 and communicates with the hydraulic oil outlet of the oil cooler 75 via an oil passage L6 formed in the valve body 700B. The first output port 81c has a substantially triangular cross-sectional shape similar to that of the first output port 80c, and communicates with an oil passage L7 formed in the valve body 700B. The signal pressure input port 81e communicates with the output port of the signal pressure output valve SR via an oil passage L9 formed in the valve body 700B. The first drain port 81f has a substantially triangular cross-sectional shape similar to the first drain port 80f, and can communicate with the space between the two lands 810x and 810y of the first spool 810. The second drain port 81g communicates with a spring chamber in which the first spring 812 is disposed. The oil passage L6 connected to the first input port 81a and the oil passage L7 connected to the first output port 81c may be communicated with each other via an oil passage L10 in which an orifice is installed midway. .

The second valve 82 has two lands 820x and 820y and is disposed in the valve body 700B so as to be movable in the axial direction, a second spring 822 for biasing the second spool 820, A two-input port 82b, a second output port 82d, and a signal pressure input port 82e are included. The second input port 82b is connected to an oil passage L3 formed in the valve body 700B. The second input port 82b is connected to the electric oil pump 28 from the electric oil pump 28 via the oil passage L3 when the electric oil pump 28 is operated. Hydraulic oil is supplied. As shown in FIG. 8, a relief valve 88 is connected to the oil passage L3. The relief valve 88 outputs the relief valve 88 when the hydraulic pressure from the mechanical oil pump 24 is below a predetermined value and the first check valve 77 is closed (when the mechanical oil pump 24 is stopped). A part of the flowing hydraulic oil is drained according to the input pressure to the relief valve 88 so that the pressure does not exceed the line pressure PL required when the clutch C1 and the brakes B1 and B2 are engaged. . As a result, when the discharge pressure of the electric oil pump 28 increases more than necessary, sudden engagement of the clutch C1, etc., excessive supply of oil to the low pressure oil supply unit, occurrence of out-of-step of the electric oil pump 28, etc. It becomes possible to suppress. The second output port 82d is connected to the oil passage L8 formed in the valve body 700B, and the signal pressure input port 82e is output from the signal pressure output valve SR via the oil passage L9 formed in the valve body 700B. Communicate with the port.

The mounting state of the first valve 81 is that the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is not supplied to the signal pressure input port 81e, and the first spool 810 is moved upward by the first spring 812 in FIG. It is the 2nd state (state of the left half in a figure) energized. In addition, the second valve 82 is attached in the state shown in FIG. 8 when the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is not supplied to the signal pressure input port 82e and the second spool 820 is moved by the second spring 822. It is the 2nd state (state of the left half in a figure) urged | biased upwards. In the mounted state (second state) of the first valve 81, the first input port 81a and the first drain port 81f communicate with each other via the space between the two lands 810x and 810y of the first spool 810, and the first The upper end of the output port 81c in the drawing slightly communicates with the space between the two lands 810x and 810y of the first spool 810. Further, in the mounted state (second state) of the second valve 82, the communication between the second input port 82b and the second output port 82d is restricted (blocked) by the land 820y of the second spool 820.

On the other hand, when the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is supplied to the signal pressure input port 81 e of the first valve 81, the first spool 810 resists the urging force of the first spring 812. The first valve 81 moves downward in FIG. 8 to form the first state (the right half state in the figure). When the first valve 81 forms the second state, the land 810x of the first spool 810 blocks communication between the first input port 81a and the first drain port 81f, and the first input port 81a The entire first output port 81c communicates with the space between the two lands 810x and 810y of one spool 810. Thereby, when the first valve 81 forms the second state, the hydraulic oil supplied from the oil cooler 75 to the oil passage L6 can flow into the oil passage L7 via the first output port 81c. .

When the signal pressure Psr (modulator pressure Pmod) from the signal pressure output valve SR is supplied to the signal pressure input port 82 e of the second valve 82, the second spool 820 resists the urging force of the second spring 822. 8 moves downward, and the second valve 82 forms the first state (the right half state in the figure). When the second valve 82 forms the second state, the second input port 82b communicates with the second output port 82d through the space between the two lands 820x and 820y of the second spool 820. As a result, when the second valve 82 forms the first state, hydraulic oil from the electric oil pump 28 supplied to the oil passage L3 can flow into the oil passage L8 via the second output port 82d. Become.

When the switching valve 80B as described above is applied to the hydraulic control device 70B, when the hydraulic oil is not supplied from the mechanical oil pump 24 when the operation of the engine 12 is stopped, the first and second valves 81, The hydraulic oil from the electric oil pump 28 is supplied by supplying the signal pressure Psr from the signal pressure output valve SR to the signal pressure input ports 81e and 82e of 82 and switching the first and second valves 81 and 82 to the first state. Can be supplied to the low-pressure oil supply unit via the oil passage L3, the second valve 82, and the like. Further, when the operation of the engine 12 is stopped, the output of the signal pressure Psr from the signal pressure output valve SR is stopped and the first and second valves 81 and 82 are switched to the second state, whereby the operation from the electric oil pump 28 is performed. Without supplying oil to the low pressure oil supply unit, oil can be supplied from the oil passage L2 to the clutch C1 and the like that are engaged when the engine 12 is restarted via the oil passage L40.

As described above, the hydraulic control device according to the present disclosure includes the mechanical pump (24) driven by power from the engine (12) of the vehicle (10) and the electric pump (28) driven by electric power. In a hydraulic control device (70B) that regulates oil from at least one of the oil and supplies it to at least one of a plurality of engagement elements (C1) of the transmission (25), the mechanical pump (24) A first oil passage (L1) including a first check valve (77) that is connected and restricts the inflow of oil to the mechanical pump (24) side, and is connected to the electric pump (28). And a second oil passage (L2) connected to the first oil passage (L1) on the downstream side of the first check valve (77) and a third branch branched from the second oil passage (L2). An oil passage (L3), the first oil passage (L1), and the second oil passage (L2), A fourth oil passage (L40) connecting the merging portion (J ₁₂ ) and at least one of the engagement elements (C1), the mechanical pump (24), and the first check valve (77) And a regulator valve (71) that is connected to the first oil passage (L1) and regulates the oil from the mechanical pump (2) to generate an original pressure, and outputs a signal pressure (Psr) The electric pump (SR) and the electric pump for the low pressure oil supply part (C1c) of the transmission (25) according to the output state of the signal pressure (Psr) by the signal pressure output valve (SR) 28) from the electric pump (28) to the third oil passage (L3) for the first state allowing the supply of oil supplied to the third oil passage (L3) from the low pressure oil supply section (C1c). A second state that regulates the supply of oil supplied to the Those comprising a valve (80,80B).

In the hydraulic control device according to the present disclosure, the first state in which the supply of the oil supplied from the electric pump to the third oil passage to the low-pressure oil supply unit of the transmission is allowed according to the output state of the signal pressure by the signal pressure output valve. The switching valve can be switched to form either one of the second state in which the supply of oil supplied from the electric pump to the low-pressure oil supply unit to the third oil passage is restricted. As a result, when oil is no longer supplied from the mechanical pump when the engine is stopped, the oil from the electric pump is reduced to low pressure via the third oil passage and the switching valve by switching the switching valve to the first state. It becomes possible to supply to the oil supply unit. In addition, by switching the switching valve to the second state while the engine is stopped, the oil from the electric pump is not supplied to the low pressure oil supply unit, and the engine is connected to the engine via the second oil path and the fourth oil path. It can be supplied to an engagement element that is engaged at restart. As a result, the oil for both the engagement element and the low-pressure oil supply unit of the transmission is suppressed when the oil is not supplied from the mechanical pump with the stop of the engine operation while suppressing the increase in size and cost of the electric pump. This makes it possible to ensure a good supply amount.

A branch (J ₂₃ ) between the second oil passage (L2) and the third oil passage (L3) is provided between the electric pump (28) and the junction (J ₁₂ ). the merging portion between the _{(J 12)} and said branch portion _{(J 23),} the hydraulic pressure in the branch portion _{(J 23)} the merging portion also good, the second oil passage _{(L2) (J 12} ) Side oil pressure is allowed to flow from the electric pump (28) side to the fourth oil passage (L4) side when the hydraulic pressure is higher than the oil pressure on the branch portion (J ₂₃ ) side, J ₁₂₎ second check valve for blocking the flow of oil into the fourth oil passage (L4) side from the electric pump (28) side (78) may be placed when it is a hydraulic or less in side. Thereby, it is possible to supply oil from the electric pump to the engagement element while preventing oil from the mechanical pump from being supplied to the low-pressure oil supply unit via the third oil passage and the switching valve.

Further, the hydraulic control device (70B) includes a fifth oil passage (L51, L52) for supplying drain oil from the regulator valve (71) to the fluid chamber (230) of the fluid transmission device, and the fluid chamber. A sixth oil passage (L61, L62) for supplying the return oil from (230) to the low-pressure oil supply section (C1c), and the pressure reduction of the return oil from the fluid chamber (230) A third check valve (91) installed on the sixth oil passage (L62) may be further included so as to regulate the flow of oil to the low pressure oil supply section (C1c) side. As a result, even if the drain oil from the regulator valve is not supplied to the fluid chamber of the fluid transmission device due to the operation of the engine, that is, the mechanical pump is stopped, the oil can be secured in the fluid chamber. Become.

The third oil passage (L3) has an output pressure when the hydraulic pressure from the mechanical pump (24) is less than a predetermined value and the first check valve (77) is closed. A part of the oil flowing in is drained according to the input pressure so as not to exceed the original pressure (PL) required when the at least one engaging element (C1, B1, B2) is engaged. A relief valve (91) may be connected. As a result, when the discharge pressure of the electric pump increases more than necessary, it is possible to suppress sudden engagement of engagement elements, excessive supply of oil to the low-pressure oil supply unit, occurrence of step-out of the electric pump, etc. It becomes possible.

Furthermore, the switching valve (80B) includes a first input port (81a) to which drain oil from the regulator valve is supplied, and a first output port (81c) connected to the low-pressure oil supply unit (C1c). A first signal pressure input port (81e) to which the signal pressure (Psr) is supplied and a first spring (812) when the signal pressure (Psr) is not supplied to the signal pressure input port (81e). When the communication between the first input port (81a) and the first output port (81c) is restricted and the signal pressure (Psr) is supplied to the signal pressure input port (81e). A first spool (810) that allows communication between the first input port (81a) and the first output port (81c) against a biasing force of the first spring (812); Lube (81), a second input port (82b) connected to the third oil passage (L3), a second output port (82d) connected to the low-pressure oil supply section (C1c), The second signal pressure input port (82e) to which the signal pressure (Psr) is supplied, and when the signal pressure (Psr) is not supplied to the signal pressure input port (82e), it is biased by the second spring (822). The communication between the second input port (82b) and the second output port (82d) is restricted, and the second pressure is applied when the signal pressure (Psr) is supplied to the signal pressure input port (82e). A second valve (82) including a second spool (820) that allows communication between the second input port (82b) and the second output port (83d) against the biasing force of the spring (822); Including Good. Thus, the first state is formed by supplying the signal pressure from the signal pressure output valve to the signal pressure input port, and the output of the signal pressure from the signal pressure output valve to the signal pressure input port is stopped. Two states can be formed.

The switching valve (80) includes a first input port (80a) to which the drain oil is supplied, a second input port (80b) connected to the third oil passage (L3), and the low-pressure oil. A first output port (80c) connected to the supply unit (C1c), a second output port (80d) connected to the low-pressure oil supply unit (C1c), and a signal supplied with the signal pressure (Psr) When the signal pressure (Psr) is not supplied to the pressure input port (80e) and the signal pressure input port (80e), the first input port (80a) and the first output are biased by a spring (802). The first input port is restricted against communication with the port (80c) and resists the biasing force of the spring (802) when the signal pressure (Psr) is supplied to the signal pressure input port (80e). (80 ) And the first output port (80c), and the third oil passage (L3) when the signal pressure (Psr) is not supplied to the signal pressure input port (80e). The second input port (80b) and the second output port (80d) are allowed to communicate with each other by the action of the hydraulic pressure supplied to the second input port (80b) and the signal pressure input port (80e). A ball (805) that is pressed by the spool (800) when the signal pressure (Psr) is supplied to the second input port (80b) and blocks the communication between the second output port (80d). May be included.

Further, the hydraulic control device (79) includes a check valve (79) for restricting the backflow of oil flowing out from the second output port (83d, 80d) to the second output port (83d, 80d). May be included.

Further, the electric pump (28) may supply oil to the second oil passage (L2) in response to the stop of the operation of the engine (12) when the vehicle (10) stops, and the signal pressure The output valve (SR) supplies the signal pressure (Psr) to the switching valve (80, 80B) in response to the operation stop of the engine (12) when the vehicle (10) stops, and the engine (12 When the oil from the electric pump (28) is supplied to the engagement elements (C1, B1, B2) that are engaged when the engine (12) is restarted. The supply of the signal pressure to 80, 80B) is stopped, and the supply of the signal pressure (Psr) to the switching valve (80, 80B) is stopped in response to the restart of the engine (12) in response to a start request. It may be. As a result, when oil is no longer supplied from the mechanical pump when the engine is stopped according to the stoppage of the vehicle, the amount of oil supplied to the low-pressure oil supply unit is ensured while the engine is restarted. Oil can be supplied to the engaging elements to be engaged.

In addition, the vehicle (10) may be capable of executing inertial traveling that stops the operation of the engine (12) during traveling, and the electric pump (28) performs inertial traveling of the vehicle (10). Oil may be supplied to the second oil passage (L2) in response to the operation stop of the engine (12) for execution, and the signal pressure output valve (SR) is provided for the engine for inertial running. The signal pressure (Psr) is supplied to the switching valve (80, 80B) in response to the operation stop of (12), and oil from the electric pump (28) is supplied to the engine during the operation stop of the engine (12). (12) When supplying to the engagement elements (C1, B1, B2) engaged at the time of restart, the supply of the signal pressure (Psr) to the switching valve (80, 80B) is stopped, Accompanying the request to cancel inertial running The supply of the signal pressure to the switching valve (80,80B) serial in response to restart of the engine (12) (Psr) may be configured to stop. As a result, when oil is no longer supplied from the mechanical pump due to engine shutdown in response to inertial running, restarting the engine while ensuring good oil supply to the low-pressure oil supply unit It is possible to supply oil to the engaging elements that are sometimes engaged.

And the invention of this indication is not limited to the said embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the above-described embodiment is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column.

The invention of the present disclosure can be used in the manufacturing industry of hydraulic control devices.

Claims (9)

Pressure is adjusted from at least one of a mechanical pump driven by power from a vehicle engine and an electric pump driven by electric power to at least one of a plurality of engagement elements of the transmission. In the hydraulic control device to supply,
A first oil passage that is connected to the mechanical pump and includes a first check valve in the middle thereof that restricts the inflow of oil to the mechanical pump;
A second oil passage connected to the electric pump and connected to the first oil passage on the downstream side of the first check valve;
A third oil passage branched from the second oil passage;
A fourth oil passage connecting the joining portion of the first oil passage and the second oil passage and the at least one engagement element;
A regulator valve that is connected to the first oil passage between the mechanical pump and the first check valve and that regulates oil from the mechanical pump to generate an original pressure;
A signal pressure output valve that outputs a signal pressure; and
A first state that allows the supply of oil supplied from the electric pump to the third oil passage to the low-pressure oil supply part of the transmission according to the output state of the signal pressure by the signal pressure output valve; A switching valve that forms a second state that restricts the supply of oil supplied from the electric pump to the third oil passage to the low-pressure oil supply unit;
A hydraulic control device comprising: The hydraulic control device according to claim 1,
A branch portion between the second oil passage and the third oil passage is provided between the electric pump and the merging portion,
Between the merging portion and the branching portion of the second oil passage, when the oil pressure on the branching portion side is higher than the oil pressure on the merging portion side, the oil from the electric pump side to the fourth oil passage side A second check valve is provided that allows the flow and blocks the flow of oil from the electric pump side to the fourth oil passage side when the hydraulic pressure at the branching portion side is equal to or lower than the hydraulic pressure at the merging portion side. Hydraulic control device. In the hydraulic control device according to claim 1 or 2,
A fifth oil passage for supplying drain oil from the regulator valve to a fluid chamber of a fluid transmission device;
A sixth oil passage for supplying the return oil from the fluid chamber to the low-pressure oil supply unit;
A hydraulic control further comprising: a third check valve installed on the sixth oil passage so as to restrict the flow of oil to the low-pressure oil supply unit in response to a pressure drop of the return oil from the fluid chamber. apparatus. In the hydraulic control device according to any one of claims 1 to 3,
When the hydraulic pressure from the mechanical pump is not more than a predetermined value and the first check valve is closed, the output pressure is applied to the third oil passage at least one of the engagement elements. A hydraulic control device to which a relief valve for draining a part of the inflowed oil according to the input pressure is connected so as not to exceed the original pressure required when combining. In the hydraulic control device according to any one of claims 1 to 4,
The switching valve is
A first input port to which drain oil from the regulator valve is supplied; a first output port connected to the low pressure oil supply unit; a first signal pressure input port to which the signal pressure is supplied; and the signal pressure. When the signal pressure is not supplied to the input port, it is urged by a first spring to restrict the communication between the first input port and the first output port, and the signal pressure is supplied to the signal pressure input port. A first valve that includes a first spool that permits communication between the first input port and the first output port against an urging force of the first spring when
A second input port connected to the third oil passage; a second output port connected to the low pressure oil supply; a second signal pressure input port to which the signal pressure is supplied; and the signal pressure input port. When the signal pressure is not supplied to the first pressure spring, the first spring is biased to restrict the communication between the second input port and the second output port, and the signal pressure is supplied to the signal pressure input port. And a second valve including a second spool that allows communication between the second input port and the second output port against an urging force of the second spring. In the hydraulic control device according to any one of claims 1 to 4,
The switching valve is
A first input port to which the drain oil is supplied;
A second input port connected to the third oil passage;
A first output port connected to the low-pressure oil supply unit;
A second output port connected to the low-pressure oil supply unit;
A signal pressure input port to which the signal pressure is supplied;
When the signal pressure is not supplied to the signal pressure input port, it is biased by a spring to restrict communication between the first input port and the first output port, and the signal pressure is supplied to the signal pressure input port. A spool that allows communication between the first input port and the first output port against the biasing force of the spring when
When the signal pressure is not supplied to the signal pressure input port, the communication between the second input port and the second output port is allowed by the action of the hydraulic pressure supplied from the third oil passage to the second input port. And a ball that is pressed by the spool when the signal pressure is supplied to the signal pressure input port and blocks communication between the second input port and the second output port;
Including hydraulic control device. The hydraulic control device according to claim 5 or 6,
A hydraulic control device including a check valve that restricts the backflow of oil flowing out from the second output port toward the second output port. The hydraulic control device according to claim 5,
The electric pump supplies oil to the second oil passage in response to a stop of operation of the engine when the vehicle stops.
The signal pressure output valve supplies the signal pressure to the switching valve in response to the stoppage of the engine when the vehicle stops, and the oil from the electric pump is supplied to the engine when the engine is stopped. The supply of the signal pressure to the switching valve is stopped when supplying to the engaging element that is engaged at the time of start, and the signal pressure is supplied to the switching valve in response to restart of the engine accompanying a start request Hydraulic control device to stop. In the hydraulic control device according to claim 5 or 7,
The vehicle is capable of performing inertial traveling to stop the operation of the engine during traveling,
The electric pump supplies oil to the second oil passage in response to the operation stop of the engine for performing inertial running of the vehicle,
The signal pressure output valve supplies the signal pressure to the switching valve in response to the operation stop of the engine for the inertia traveling, and the oil from the electric pump is supplied to the engine when the engine is stopped. When supplying to the engaging element that is engaged at the time of starting, the supply of the signal pressure to the switching valve is stopped, and the switching valve according to the restart of the engine in response to the inertial travel release request Hydraulic control device that stops the supply of signal pressure.

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