JP2023077582A - Hydraulic pressure control device - Google Patents

Abstract

To accurately determine an adhesion state of an application valve while reducing costs of a hydraulic control device and improving efficiency by selectively supplying hydraulic pressure to two hydraulic engagement elements via the application valve from one pressure regulation valve.SOLUTION: When a signal pressure is not supplied from a signal pressure output valve, a selector valve of a hydraulic pressure control device permits supply of a hydraulic pressure to a second hydraulic engagement element side from a common pressure regulation valve. When a signal pressure is supplied from the signal pressure output valve, the selector valve permits supply of a hydraulic pressure to a first hydraulic engagement element side from the common pressure regulation valve and flowout of oil which has been separately supplied from the signal pressure output valve. When oil from the signal pressure output valve is not supplied via the selector valve, an application valve permits supply of a hydraulic pressure from the common pressure regulation valve to the second hydraulic pressure engagement element. When oil from the signal pressure output valve is supplied via the selector valve, the application valve permits supply of a hydraulic pressure from the common pressure regulation valve to the first hydraulic pressure engagement element.SELECTED DRAWING: Figure 4

Description

The present disclosure relates to a hydraulic control device for a transmission that selectively engages at least two of a plurality of hydraulic engagement elements to form a plurality of forward gears and reverse gears.

Conventionally, there is a first hydraulic engagement element (B2) that is engaged when the first forward speed and reverse gear are established, and a second hydraulic engagement element (B2) that is engaged when the first forward speed is established and is released when the reverse gear is established. Five hydraulic engagement elements including a hydraulic engagement element (C1) and a third hydraulic engagement element (C3) which is released when the first forward speed is established and is engaged when the third forward speed and reverse speed are established. An automatic transmission having a coupling element is known (see, for example, Patent Document 1). This automatic transmission forms a first forward speed, a sixth forward speed and a reverse speed by engaging any two of the five hydraulic engagement elements, and the first hydraulic engagement element (B2) and the engagement of the second hydraulic engagement element (C1) establishes the first forward speed. The hydraulic control device for supplying hydraulic pressure to the five hydraulic engagement elements includes a first solenoid valve capable of outputting a first signal hydraulic pressure, a second solenoid valve capable of outputting a second signal hydraulic pressure, and a first switching valve. , a second switching valve, and five linear solenoid valves each adjusting the source pressure (line pressure) to generate the engagement pressure for the corresponding hydraulic engagement element. The first switching valve selectively forms a state in which the source pressure is output as the forward range pressure and a state in which the source pressure is output as the non-forward range pressure by supplying and discharging the first signal hydraulic pressure. In addition, the second switching valve is in a first state in which the forward range pressure supplied to the first input port is output from the first output port by supply and discharge of the second signal hydraulic pressure, and in a non-operating state in which the forward range pressure supplied to the first input port is output from the first output port. and selectively forming a second state in which the forward range pressure is output from the first output port. Further, the five linear solenoid valves are composed of a first linear solenoid valve that adjusts the source pressure to generate a first engagement pressure to the first hydraulic engagement element, and a second hydraulic engagement that adjusts the forward range pressure. A second linear solenoid valve that generates a second engagement pressure to the element and a third engagement pressure to the third hydraulic engagement element by adjusting the hydraulic pressure output from the first output port of the second switching valve. and a generating third linear solenoid valve.

In such a hydraulic control device, two of the first switching valve, the first linear solenoid valve and the second linear solenoid valve fail to engage at least one of the second engaging element and the first engaging element. However, by controlling the remaining one valve, it is possible to avoid unintentional formation of the shift stage. Further, the second switching valve cuts off the supply of the forward range pressure or the non-forward range pressure to the third hydraulic engagement element and the supply of the forward range pressure or the non-forward range pressure to the third hydraulic engagement element. selectively form a state. Further, the second switching valve is configured such that when the gear is switched from the reverse speed to the first forward speed, the second switching valve switches the second switching valve from the second solenoid valve until the second engaging element changes from the disengaged state to at least the engaged state. It is maintained in the second state by two-signal oil pressure. As a result, even if an open failure occurs in the third linear solenoid valve, the supply of the forward range pressure to the third linear solenoid valve can be cut off by the second switching valve. 1 hydraulic engagement element can suppress the occurrence of a shock caused by maintaining the engagement.

JP 2019-065963 A

In the conventional hydraulic control system described above, a linear solenoid valve is provided for each of the plurality of hydraulic engagement elements of the automatic transmission. In order to reduce costs and improve efficiency, it is preferable to reduce the number of linear solenoid valves in the hydraulic control device. Further, in the above-described conventional hydraulic control device, it is not possible to accurately determine the sticking state of the second switching valve that selectively supplies the forward range pressure or the non-forward range pressure to the third hydraulic engagement element.

Therefore, the present disclosure selectively supplies hydraulic pressure from one pressure regulating valve to two hydraulic engagement elements via an apply valve to reduce the cost and improve the efficiency of the hydraulic control device, and to reduce the cost of the apply valve. The main purpose is to make it possible to accurately determine the sticking state.

The hydraulic control device of the present disclosure includes a first hydraulic engagement element (C2), a second hydraulic engagement element (B2) that is not simultaneously engaged with said first hydraulic engagement element (C2), and a residual hydraulic engagement. In a hydraulic control system (60) for a transmission (25) selectively engaging at least any two of the elements (C1, C3, C4, B1) to form a plurality of forward and reverse gears, a dual-purpose pressure regulating valve (SL2) that adjusts the source pressure (PL) to generate hydraulic pressure (Psl2) to the first hydraulic engagement element (C1) and the second hydraulic engagement element (B2); at least one dedicated pressure regulating valve (SL1, SL3, SL4, SL5) for regulating the pressure (PL) to generate hydraulic pressure to the corresponding said remaining hydraulic engagement elements (C1, C3, C4, B1); a plurality of pressure regulating valves including, a signal pressure output valve (SC2) that outputs the signal pressure (Psc2), and when the signal pressure (Psc2) is not supplied from the signal pressure output valve (SC2), While allowing the supply of the hydraulic pressure (Psl2) from the dual-purpose pressure regulating valve (SL2) to the second hydraulic engagement element (B2) side, the dual-purpose pressure regulating valve (SL2) to the first hydraulic engagement element A first communication state is formed to regulate the supply of the hydraulic pressure (Psl2) to the (C2) side and the outflow of oil separately supplied from the signal pressure output valve (SC2), and the signal pressure output valve (SC2) supply of the hydraulic pressure (Psl2) from the dual-purpose pressure regulating valve (SL2) to the first hydraulic engagement element (C2) side and the signal pressure output A second hydraulic pressure regulator valve (SC2) that allows outflow of oil separately supplied from the valve (SC2) and regulates the supply of the hydraulic pressure (Psl2) from the dual-purpose pressure regulating valve (SL2) to the second hydraulic engagement element (B2) side. a switching valve (200) forming a communication state; ) to the first hydraulic engagement element (C2) from the dual-use pressure regulating valve (SL2), and the switching valve (200) to the second hydraulic engagement element ( A first supply state is formed to allow the supply of the hydraulic pressure (Psl2) from the dual-purpose pressure regulating valve (SL2) to B2), and the signal pressure output valve (SC2) is supplied via the switching valve (200). of the hydraulic pressure (Psl2) from the dual-use pressure regulating valve (SL2) to the first hydraulic engagement element (C2) from the switching valve (200) when the oil (Psc2) of the A second supply state is formed in which the supply is permitted and the supply of the hydraulic pressure (Psl2) from the dual-use pressure regulating valve (SL2) to the second hydraulic engagement element (B2) from the switching valve (200) is restricted. and an apply valve (300).

In the hydraulic control device of the present disclosure, the dual-use pressure regulating valve generates (adjusts) the first hydraulic engagement element and the second hydraulic engagement element that is not simultaneously engaged with the first hydraulic engagement element. Hydraulic pressure can be selectively supplied from the apply valve. As a result, it is possible to reduce the number of pressure regulating valves in the hydraulic control device, thereby reducing costs by reducing the number of pressure regulating valves and improving efficiency by reducing leakage oil. Further, when the signal pressure from the signal pressure output valve is not supplied to the switching valve, the switching valve that establishes the first communication state allows hydraulic pressure to be supplied from the dual-purpose pressure regulating valve to the side of the second hydraulic engagement element. At the same time, the supply of oil from the signal pressure output valve to the apply valve is regulated, and the apply valve does not receive the supply of oil (signal pressure) from the signal pressure output valve via the switching valve, thereby entering the first supply state. Form. As a result, the supply of hydraulic pressure from the dual-purpose pressure regulating valve to the first hydraulic engagement element is regulated by the apply valve, and the hydraulic pressure from the dual-purpose pressure regulating valve is supplied to the second hydraulic engagement element via the apply valve. be done. Further, when the signal pressure from the signal pressure output valve is supplied to the switching valve, the switching valve forming the second communication state allows the supply of hydraulic pressure from the dual-purpose pressure regulating valve to the side of the first hydraulic engagement element. At the same time, the supply of oil from the signal pressure output valve to the apply valve is permitted, and the apply valve that receives the supply of oil (signal pressure) from the signal pressure output valve via the switching valve forms the second supply state. As a result, the supply of hydraulic pressure from the dual-purpose pressure regulating valve to the second hydraulic engagement element is regulated by the apply valve, and the hydraulic pressure from the dual-purpose pressure regulating valve is supplied to the first hydraulic engagement element via the apply valve. be done. Therefore, when the apply valve is stuck in the first supply state, the signal pressure from the signal pressure output valve is supplied to the switching valve, and the switching valve causes the dual-purpose pressure regulating valve to move toward the first hydraulic engagement element. Even if the supply of hydraulic pressure to and the outflow of oil separately supplied from the signal pressure output valve are permitted, the first hydraulic engagement element cannot be engaged, and the transmission enters the neutral state. On the other hand, when the apply valve is fixed while forming the second supply state, the signal pressure from the signal pressure output valve is not supplied to the switching valve, and the switching valve causes the dual-purpose pressure regulating valve to output the second hydraulic pressure. Even if hydraulic pressure is allowed to be supplied to the engaging element, the second hydraulic engaging element cannot be engaged, and the transmission is put into a neutral state. As a result, in the hydraulic control device of the present disclosure, it is possible to accurately determine the sticking state of the apply valve from the presence or absence of signal pressure output from the signal pressure output valve and the formation state of the gear stage of the transmission. .

1 is a schematic configuration diagram of a vehicle equipped with a power transmission device including a hydraulic control device of the present disclosure; FIG. 2 is a schematic configuration diagram showing a power transmission device mounted on the vehicle of FIG. 1; FIG. FIG. 3 is an operation table showing the relationship between each speed stage of the transmission included in the power transmission device of FIG. 2 and the operating state of hydraulic engagement elements; FIG. 1 is a system diagram showing a main part of a hydraulic control device of the present disclosure; FIG. 4 is an operation table showing energized states of solenoid valves included in the hydraulic control device of the present disclosure; 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a system diagram for explaining the operation of the hydraulic control device of the present disclosure; FIG. 4 is a flow chart for explaining the operation of the hydraulic control device of the present disclosure;

Next, embodiments 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 60 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. Further, 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 "EG ECU") that controls an electronically controlled hydraulic brake unit (not shown). , “brake ECU”) 16 and a transmission electronic control unit (hereinafter referred to as “TM ECU”) 21 for controlling the power transmission device 20 .

The EG ECU 14 is a microcomputer including a CPU (not shown), etc. The EG ECU 14 includes 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 depression amount (operation amount) of the accelerator pedal 91. , signals from various sensors such as the vehicle speed sensor 99, signals from the brake ECU 16 and the TM ECU 21, and the like. Based on these signals, the EG ECU 14 controls electronically controlled throttle valves, fuel injection valves, spark plugs and the like, all of which are not shown. The brake ECU 16 is also a microcomputer including a CPU (not shown). Input signals, etc. The brake ECU 16 controls a brake actuator (hydraulic actuator) and the like (not shown) based on these signals.

The TMECU 21 is also a microcomputer including a CPU (not shown), and includes a shift position sensor 96 that detects the shift position, which is the operation position of the shift lever 95, an accelerator pedal position sensor 92, an input rotation speed of the automatic transmission 25 (turbine runner 23b or An input rotation speed sensor 97 that detects the rotation speed of the input shaft 26 of the automatic transmission 25, and an output rotation speed sensor that detects the output rotation speed of the automatic transmission 25 (the rotation speed of the ring gear 37 of the second planetary gear mechanism 35). Signals from various sensors such as 98 and vehicle speed sensor 99 and signals from EG ECU 14 and brake ECU 16 are input. The TM ECU 21 controls the power transmission device 20 based on these signals. Further, in the present embodiment, the shift positions of the shift lever 95 include a parking position (P) selected when parking, a reverse position (R) for backward running, and a neutral position for cutting off transmission of power by the automatic transmission 25. In addition to the position (N) and the drive position (D) for normal forward travel, there is a sports position (S) that allows the driver to select any gear stage.

As shown in FIG. 2, the power transmission device 20 includes a transmission case 22, a starting device (fluid transmission device) 23 accommodated in the transmission case 22, and a mechanical oil pump 24 driven by power from the engine 12. , an automatic transmission 25, a gear mechanism (gear train) 40, a differential gear (differential mechanism) 50, a hydraulic control device 60, and the like.

The transmission case 22 includes a housing 22a, a transaxle case 22b fastened (fixed) to the housing 22a, and fastened (fastened) to the transaxle case 22b so as to be positioned between the housing 22a and the transaxle case 22b. It includes a front support 22c that is fixed) and a center support 22d that is fastened (fixed) to the transaxle case 22b. In this embodiment, the housing 22a, the transaxle case 22b, and the center support 22d are made of aluminum alloy, for example, and the front support 22c is made of steel (iron alloy) or aluminum alloy.

The starting device 23 includes a front cover connected to the crankshaft of the engine 12 via a drive plate (not shown) or the like, an input-side pump impeller 23p having a pump shell tightly fixed to the front cover, an automatic transmission 25, and an automatic transmission 25. a turbine runner 23t on the output side connected to the input shaft 26 of the pump impeller 23p; It includes a one-way clutch 23o and the like which are supported by the shaft and limit the rotating direction of the stator 23s to one direction. Pump impeller 23p, turbine runner 23t and stator 23s form a torque converter having a torque amplifying action.

Further, the starting device 23 includes a lock-up clutch 23c for connecting and disconnecting the front cover and the input shaft 26 of the automatic transmission 25, and a lockup clutch 23c between the front cover and the input shaft 26 of the automatic transmission 25. and a damper device 23d for damping vibrations. In this embodiment, the lockup clutch 23c is configured as a multi-plate friction 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 hydraulic clutch. Also, the starting device 23 may include a fluid coupling that does not have 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 via a winding transmission mechanism 240, and an internal gear (outer rotor) meshing with the external gear 241. 242, an external gear 241 and an internal gear 242. The gear pump has a pump body and a pump cover (both not shown) defining a gear chamber (not shown) for accommodating the external gear 241 and the internal gear 242. The input shaft 26 of the automatic transmission 25 is placed on a separate axis. The mechanical oil pump 24 is driven by power from the engine 12 via a winding transmission mechanism 240, and pumps hydraulic oil (not shown) stored in a hydraulic oil reservoir (not shown) provided at the bottom of the transaxle case 22b. ATF) is sucked and pumped to the hydraulic control device 60 . The winding transmission mechanism 240 is wound around the drive sprocket rotating integrally with the pump impeller 23p of the starting device 23, the driven sprocket rotating integrally with the external gear 241 of the mechanical oil pump 24, the drive sprocket, and the driven sprocket. Including chains, etc.

The automatic transmission 25 is configured as an eight-speed transmission, and as shown in FIG. It includes four clutches C1, C2, C3 and C4 as hydraulic engagement elements for changing the power transmission path from the side to the output side, two brakes B1 and B2.

The first planetary gear mechanism 30 includes a sun gear (fixed element) 31 which is an external gear, and a ring gear 32 which is an internal gear arranged concentrically with the sun gear 31, and meshes with each other. A planetary carrier 34 holds a plurality of sets of two pinion gears 33a and 33b, the other of which meshes with the ring gear 32, so as to rotate freely (rotatably) and revolve. As illustrated, 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 22c, and the planetary carrier 34 of the first planetary gear mechanism 30 is , is connected to the input shaft 26 so as to be integrally rotatable. Further, 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 the reduced power 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 arranged concentrically with the first and second sun gears 36a and 36b, and a second sun gear 36b. A plurality of short pinion gears 38a meshing with the first 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 . 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 drive wheels of the

The clutch C1 connects and disconnects 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. The clutch C2 connects and disconnects the input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 to each other. The clutch C3 connects and disconnects 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. The clutch C4 connects and disconnects 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. In this embodiment, as the clutches C1, C2, C3 and C4, a piston, a plurality of friction engagement plates (friction plates and separator plates), and an engagement hydraulic pressure (hydraulic oil) from the hydraulic control device 60 are supplied. A multi-disc friction hydraulic clutch is employed that includes an oil chamber, a centrifugal hydraulic pressure cancellation chamber to which hydraulic oil is supplied from the hydraulic control device 60 in order to cancel the centrifugal hydraulic pressure generated in the engagement oil chamber, and the like.

The brake B<b>1 fixes (connects) the second sun gear 36 b of the second planetary gear mechanism 35 to the transmission case 22 so as not to rotate, and releases the fixation of the second sun gear 36 b to the transmission case 22 . The brake B<b>2 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 planetary carrier 39 from the transmission case 22 . In this embodiment, as the brakes B1 and B2, multi-disc friction hydraulic brakes 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 are employed. .

These clutches C 1 -C 4 and brakes B 1 and B 2 are supplied and discharged with hydraulic fluid by the hydraulic control device 60 to operate. FIG. 3 shows an operation table showing the relationship between each shift stage of the automatic transmission 25 and the operation states of the clutches C1-C4 and the brakes B1 and B2. The automatic transmission 25 has the clutches C1-C4 and the brakes B1 and B2 in the states shown in the operation table of FIG. Provide steps. That is, each gear stage of automatic transmission 25 is formed by engagement of any two of clutches C1-C4 and brakes B1 and B2. At least one of the clutches C1-C4 and the brakes B1 and B2 may be a mesh engagement element such as a dog clutch.

Gear mechanism 40 includes a counter drive gear 41 , a counter shaft 42 , a counter driven gear 43 , a drive pinion gear 44 and a differential ring gear 45 . The counter drive gear 41 is connected to the ring gear 37 of the second planetary gear mechanism 35 of the automatic transmission 25 , and the counter shaft 42 extends parallel to the input shaft 26 of the automatic transmission 25 . The counter driven gear 43 is fixed to the counter shaft 42 and meshes with the counter drive gear 41 . The drive pinion gear 44 is formed (or fixed) on the countershaft 42 , and the differential ring gear 45 meshes with the drive pinion gear 44 and is connected to the differential gear 50 .

FIG. 4 is a system diagram showing the essential parts of the hydraulic control device 60 of the present disclosure. The hydraulic control device 60 is connected to the above-described mechanical oil pump 24 capable of sucking and discharging hydraulic oil from the hydraulic oil reservoir of the transaxle case 22b through a strainer. The hydraulic control device 60 is controlled by the TM ECU 21, generates the hydraulic pressure required by the starting device 23 and the automatic transmission 25, and supplies low-pressure oil such as lubrication objects such as various bearings and centrifugal hydraulic pressure cancellation chambers of the clutches C1-C4. Hydraulic oil is supplied to the part (part to be lubricated). As shown, the hydraulic control device 60 includes a valve body 600B in which a plurality of oil passages are formed, primary regulator valves, secondary regulator valves and modulator valves (none of which are shown), linear solenoid valves SL1, SL2, SL3, SL4, SL5, a first signal pressure output valve SC1, a second signal pressure output valve SC2, a third signal pressure output valve SC3, a first switching valve 100, a second switching valve (switching valve) 200, and a third switching valve (apply valve) 300 . In this embodiment, the hydraulic control device 60 does not have a manual valve that interlocks with the shift lever 95, and constitutes a shift-by-wire device together with the TM ECU 21. That is, the TM ECU 21 controls the hydraulic control device 60 so that the automatic transmission 25 is in a state corresponding to the shift position of the shift lever 95 set by the driver.

The valve body 600 is attached to a side portion of a transaxle case 22b that constitutes the transmission case 22, for example. A primary regulator valve (not shown) of the hydraulic control device 60 converts the pressure of hydraulic oil supplied from the mechanical oil pump 24 to the oil passage L21 of the valve body 600, that is, the line pressure PL, into the signal pressure supplied from the linear solenoid valve (not shown). Adjust accordingly. The linear solenoid valve that outputs the signal pressure adjusts the pressure of hydraulic oil from the mechanical oil pump 24 side (for example, a modulator valve) and outputs pressure corresponding to the accelerator opening or throttle valve opening of the vehicle 10. It is controlled by the TM ECU 21 so as to do so. Also, the secondary regulator valve adjusts the pressure of hydraulic fluid drained from the primary regulator valve according to the signal pressure from the linear solenoid valve, and generates a secondary pressure (circulation pressure) lower than the line pressure PL. Further, the modulator valve reduces (regulates) the line pressure PL from the oil passage L1 to generate a substantially constant modulator pressure Pmod.

The linear solenoid valves SL1-SL5 have a common configuration, and include an electromagnetic portion controlled by the TM ECU 21, a spool axially movably arranged in a sleeve held by the valve body 600, and a spring that biases the spool toward the electromagnetic portion; an input port that communicates with the oil passage L1 of the valve body 600 via the oil passage L2 or the oil passage L3; an output port; a feedback port that communicates with the output port; Including drain port. In the present embodiment, the linear solenoid valves SL1-SL5 are normally closed valves that open when current is supplied to the electromagnetic section, and are supplied to the input ports according to the current applied to the electromagnetic section. The line pressure PL is adjusted and output from the output port. That is, in the linear solenoid valves SL1-SL5, the thrust generated by power supply to the electromagnetic part (coil), the biasing force of the spring, and the hydraulic pressure supplied from the output port to the feedback port act on the spool to the electromagnetic part side. By balancing the thrust, the pressure of hydraulic fluid supplied to the input port (line pressure PL) is adjusted to a desired pressure.

Further, in this embodiment, the linear solenoid valve SL1 adjusts the line pressure PL to generate hydraulic pressure to the clutch C1, and the linear solenoid valve SL2 adjusts the line pressure PL to generate hydraulic pressure to the clutch C2 and the brake B2. Generate Psl2. Furthermore, the linear solenoid valve SL3 adjusts the line pressure PL to generate hydraulic pressure to the clutch C3, the linear solenoid valve SL4 adjusts the line pressure PL to generate hydraulic pressure to the clutch C4, and the linear solenoid valve SL5 adjusts the line pressure PL to generate hydraulic pressure to the brake B1. That is, in the hydraulic control device 60, the linear solenoid valves SL1, SL3-SL5 are dedicated pressure regulating valves that generate hydraulic pressure to the corresponding clutches C1, C3, C4 or brake B1, and the linear solenoid valve SL2 is the clutch It is a dual-purpose pressure regulating valve corresponding to both C2 and brake B2. In this embodiment, the input ports of the linear solenoid valves SL1, SL4 and SL5 corresponding to the clutches C1 and C4 or the brake B1 that are engaged only when the first forward speed to the eighth speed (forward speed) are established are It communicates with the oil passage L21 via the first switching valve 100 and the oil passage L22. Further, the input port of the linear solenoid valve SL2 communicates with the oil passage L21 through the oil passage L23, and the input port of the linear solenoid valve SL3 communicates with the oil passage L21 through the oil passage L24.

The first signal pressure output valve SC1 is, for example, a normally closed ON/OFF solenoid valve that is energized and controlled by the TM ECU 21, and the input port of the first signal pressure output valve SC1 is an oil passage L21 formed in the valve body 600 or a modulator valve. communicates with the output port of The first signal pressure output valve SC1 causes the line pressure PL or the modulator pressure Pmod as the original pressure supplied to the input port to flow out from the output port as the first signal pressure Psc1 when current is supplied to the electromagnetic section.

The second signal pressure output valve SC2 is also, for example, a normally closed ON/OFF solenoid valve that is energized and controlled by the TM ECU 21. The input port of the second signal pressure output valve SC2 is an oil passage L1 formed in the valve body 600 or a modulator valve. communicates with the output port of The second signal pressure output valve SC2 outputs the source pressure (line pressure PL or modulator pressure Pmod) common to the first signal pressure output valve SC1 supplied to the input port when current is supplied to the electromagnetic section, as a second signal. It flows out from the output port as pressure Psc2.

The third signal pressure output valve SC3 is also, for example, a normally closed ON/OFF solenoid valve energized and controlled by the TM ECU 21, and the input port of the third signal pressure output valve SC3 is connected to an oil passage L1 formed in the valve body 600 or a modulator valve communicates with the output port of The third signal pressure output valve SC3 has a common source pressure (line pressure PL or modulator pressure Pmod ) flows out from the output port as the third signal pressure Psc3.

The first switching valve 100 includes a first spool S1 having a plurality of lands and arranged to be axially movable within the valve body 600, and a first spring that biases the first spool S1 upward in FIG. SP1 and SP1. Further, the first switching valve 100 includes a source pressure input port 101, a source pressure output port 102, a first signal pressure input port 105, a holding pressure input port 106, an inflow port 111, an outflow port 112, and a parking and port 117 .

The source pressure input port 101 of the first switching valve 100 communicates with the oil passage L21 of the valve body 600 , and the source pressure output port 102 communicates with the oil passage L22 formed in the valve body 600 . The first signal pressure input port 105 is arranged on the opposite side of the spring chamber in which the first spring SP1 is arranged, and the output of the first signal pressure output valve SC1 is transmitted through the oil passage L25 formed in the valve body 600. communicate with the port. Further, the holding pressure input port 106 communicates with a spring chamber in which the first spring SP1 is arranged and communicates with an oil passage L26 formed in the valve body 600. As shown in FIG. The inflow port 111 communicates with the output port of the second signal pressure output valve SC2 through an oil passage L27 formed in the valve body 600, and the outflow port 112 communicates with an oil passage L28 formed in the valve body 600. communicate. The oil passage L26, which communicates with the holding pressure input port 106, is branched from the oil passage L28. As a result, the holding pressure input port 106 communicates with the outflow port 112 through parts of the oil passages L26 and L28. Furthermore, the parking port 117 communicates with the hydraulic inlet of the shift-by-wire parking lock mechanism 70 via an oil passage formed in the valve body 600 .

In this embodiment, the mounting state of the first switching valve 100 is such that the first signal pressure input port 105 and the holding pressure input port 106 receive the first or second signal pressure from the first or second signal pressure output valves SC1, SC2. This is the first state (left half state in FIG. 4) in which the first spool S1 is urged upward in FIG. 4 by the first spring SP1 without supplying Psc1 and Psc2. In the first state (attached state) of the first switching valve 100, the first spool S1 communicates the source pressure input port 101 and the source pressure output port 102, and communicates the inflow port 111 and the outflow port 112 with each other.

Further, when the first switching valve 100 is in the first state, if current is supplied to the electromagnetic portion of the second signal pressure output valve SC2, hydraulic oil (second The 2-signal pressure Psc2) flows into the inflow port 111 through the oil passage L27 and flows out through the outflow port 112 into the oil passage L28. Furthermore, part of the hydraulic fluid from the second signal pressure output valve SC2 flows into the holding pressure input port 106 via the oil passages L28 and L26. As a result, the second signal pressure Psc2 from the second signal pressure output valve SC2 acts on the pressure receiving surface of the first spool S1 on the side of the first spring SP1, and the first switching valve 100 forms the first state. Furthermore, in this embodiment, the pressure receiving surface of the first spool S1 on the first signal pressure input port 105 side and the pressure receiving surface on the holding pressure input port 106 (first spring SP1) side have the same area. Therefore, when the first switching valve 100 is in the first state and the second signal pressure output valve SC2 is outputting the second signal pressure Psc2, the first signal pressure output from the first signal pressure output valve SC1 Even if Psc1 is supplied to the first signal pressure input port 105, the first switching valve 100 continues to form the first state.

On the other hand, the second signal pressure Psc2 from the second signal pressure output valve SC2 is not supplied to the holding pressure input port 106, and the first signal pressure Psc1 from the first signal pressure output valve SC1 is supplied to the first signal pressure input port 105. When supplied, the first spool S1 moves downward in FIG. 4 against the biasing force of the first spring SP1 by the thrust acting on the first spool S1 due to the first signal pressure Psc1, and the first switching valve 100 forms the second state (right half state in FIG. 4). In the second state of the first switching valve 100, the first spool S1 blocks communication between the source pressure input port 101 and the source pressure output port 102 and blocks communication between the inflow port 111 and the outflow port 112. Furthermore, in the second state, the first spool S1 allows the inflow port 111 and the parking port 117 to communicate with each other.

The second switching valve 200 includes a second spool S2 that has a plurality of lands and is arranged axially movably within the valve body 600, and a second spring that biases the second spool S2 upward in FIG. SP2 and SP2. Furthermore, the second switching valve 200 has an input port 201, a first output port 203, a second output port 204, a second signal pressure input port 205, a first inflow port 211, and a second inflow port 212. , and the signal pressure outlet port 215 .

An input port 201 of the second switching valve 200 communicates with an output port of the linear solenoid valve SL2 via an oil passage L31 formed in the valve body 600, and a first output port 203 is formed in the valve body 600. The second output port 204 communicates with an oil passage L34 formed in the valve body 600 . Further, the second signal pressure input port 205 is arranged on the opposite side of the spring chamber in which the second spring SP2 is arranged, and the outflow of the first switching valve 100 through oil passages L30 and L28 formed in the valve body 600. Communicates with port 112 . Also, the first inflow port 211 communicates with the outflow port 112 of the first switching valve 100 via an oil passage L28 formed in the valve body 600 . Further, the second inflow port 212 communicates with output ports of linear solenoid valves SL3, SL4 and SL5 as dedicated pressure regulating valves through an oil passage L32 formed in the valve body 600 and the like. Also, the signal pressure outflow port 215 communicates with an oil passage L35 formed in the valve body 600 .

In this embodiment, when the second switching valve 200 is mounted, the second signal pressure is output to the second signal pressure input port 205 through the inflow port 111, the outflow port 112, and the oil passages L28 and L30 of the first switching valve 100. A first communication state in which hydraulic oil (second signal pressure Psc2) is not supplied from the valve SC2 and the second spool S2 is urged upward in FIG. 4 by the second spring SP2 (left half state in FIG. 4). is. In the first communication state (mounted state) of the second switching valve 200, the second spool S2 communicates the input port 201 and the second output port 204, and connects the second inflow port 212 and the signal pressure outflow port 215. communicate. Furthermore, in the first communication state, the second spool S2 blocks communication between the input port 201 and the first output port 203 and communication between the first inflow port 211 and the signal pressure outflow port 215 .

On the other hand, when the second signal pressure input port 205 is supplied with the hydraulic oil from the second signal pressure output valve SC2, that is, the second signal pressure Psc2, the second spool S2 is driven by the second signal pressure Psc2. 4 against the biasing force of the second spring SP2, and the second switching valve 200 forms the second communication state (right half state in FIG. 4). In the second communication state of the second switching valve 200, the second spool S2 allows communication between the input port 201 and the first output port 203, and communication between the first inflow port 211 and the signal pressure outflow port 215. Furthermore, in the second communication state, the second spool S2 blocks communication between the input port 201 and the second output port 204 and communication between the second inflow port 212 and the signal pressure outflow port 215 .

The third switching valve 300 includes a third spool S3 that has a plurality of lands and is arranged to be axially movable within the valve body 600, and a third spring that biases the third spool S3 upward in FIG. SP3 and SP3. Further, the third switching valve 300 includes a first input port 311, a second input port 312, a first supply port 313, a second supply port 314, a third signal pressure input port 315, and a switching port 316. , a holding pressure inlet port 317 , a holding pressure outlet port 318 , and a holding pressure inlet port 319 .

A first input port 311 of the third switching valve 300 communicates with a first output port 203 of the second switching valve 200 via an oil passage L33 formed in the valve body 600, and a second input port 312 communicates with the valve body. It communicates with the second output port 204 of the second switching valve 200 via an oil passage L34 formed at 600 . The first supply port 313 communicates with the engagement oil chamber of the clutch C2 through an oil passage formed in the valve body 600, and the second supply port 314 communicates with an oil passage formed in the valve body 600. to the engaging oil chamber of the brake B2. Furthermore, the third signal pressure input port 305 is arranged on the opposite side of the spring chamber in which the third spring SP3 is arranged, and the signal pressure outflow port 215 of the second switching valve 200 is supplied through the oil passage L35 of the valve body 600. communicate with. Also, the switching port 316 communicates with a spring chamber in which the first spring SP1 is arranged, and also communicates with the output port of the third signal pressure output valve SC3 via an oil passage formed in the valve body 600 . Further, the holding pressure inflow port 317 is supplied with a substantially constant modulator pressure Pmod generated by the modulator valve described above. Also, the holding pressure outflow port 318 communicates with an oil passage L36 formed in the valve body 600 . The holding pressure introduction port 319 faces the holding pressure receiving surface S3p formed on the third spool S3 and communicates with the holding pressure outflow port 318 via the oil passage L36. Note that the line pressure PL may be supplied to the holding pressure inflow port 317 instead of the modulator pressure Pmod.

In this embodiment, the mounting state of the third switching valve 300 is such that hydraulic oil (second The third spool S3 is urged upward in FIG. 4 by the third spring SP3 without being supplied with the two-signal pressure Psc2) or hydraulic oil (hydraulic pressure) from any one of the linear solenoid valves SL3, SL4 and SL5. This is the first supply state (left half state in FIG. 4). In the first supply state (attached state) of the third switching valve 300, the third spool S3 blocks the communication between the first input port 311 and the first supply port 313, and disconnects the second input port 312 and the second supply port. Communicate with port 314 .

On the other hand, hydraulic oil (second signal pressure Psc2) from the second signal pressure output valve SC2 or linear solenoid valves SL3, SL4 and SL5 is supplied to the third signal pressure input port 315 via the second switching valve 200 and the oil passage L35. When the hydraulic oil (hydraulic pressure) is supplied from any one, the third spool S3 resists the biasing force of the third spring SP3 by the thrust acting on the third spool S3 due to the second signal pressure Psc2. Moving downwards in FIG. 4, the third switching valve 300 forms the second supply state (right half state in FIG. 4). In the second supply state of the third switching valve 300, the third spool S3 allows communication between the first input port 311 and the first supply port 313 and communication between the second input port 312 and the second supply port 314. Cut off.

Further, in the hydraulic control device 60, when the third switching valve 300 forms the second supply state, the hydraulic oil supplied from the modulator valve to the holding pressure inflow port 317, that is, the modulator pressure Pmod is held through the holding pressure outflow port 318. It is supplied to the pressure introduction port 319 and acts on the holding pressure receiving surface S3p of the third spool S3. Furthermore, the pressure receiving area of the holding pressure receiving surface S3p is determined so that the thrust generated by the modulator pressure Pmod acting on the holding pressure receiving surface S3p is balanced with the biasing force generated by the third spring SP3 in the second supply state. It is As a result, once the third switching valve 300 enters the second supply state by supplying hydraulic fluid (hydraulic pressure) to the third signal pressure input port 315, hydraulic fluid (hydraulic pressure) is supplied to the third signal pressure input port 315. Even if the supply is cut off, the third switching valve 300 continues to form (hold) the second supply state. On the other hand, when the switching port 316 (spring chamber) is supplied with the third signal pressure from the third signal pressure output valve SC3, the third switching valve 300 causes the hydraulic fluid to flow into the third signal pressure input port 315. The first supply state is established regardless of whether (hydraulic pressure) is supplied or not.

Next, operation of the hydraulic control device 60 will be described with reference to FIGS. 5 to 11. FIG.

When the ignition switch (start switch) of the vehicle 10 is turned on with the shift lever 95 set to the parking position, the TM ECU 21 outputs first and second signal pressures Psc1 and Psc2 as shown in FIG. A current is supplied to the electromagnetic portions of the first and second signal pressure output valves SC1 and SC2 so as to. As a result, as shown in FIG. 6, the first switching valve 100 forms the second state, and the communication between the source pressure input port 101 and the source pressure output port 102 and the communication between the inflow port 111 and the outflow port 112 are interrupted. The inflow port 111 and the parking port 117 communicate with each other while being blocked. Therefore, when the shift lever 95 is set to the parking position, as shown in FIG. 6, the second signal pressure Psc2 from the second signal pressure output valve SC2 is applied to the first switching valve 100 (inflow port 111 and parking port 117). ) to the parking lock mechanism 70 to form the parking lock state.

In addition, the communication between the inflow port 111 and the outflow port 112 of the first switching valve 100 is blocked, so that the second signal pressure Psc2 from the second signal pressure output valve SC2 becomes the second signal pressure of the second switching valve 200. It is not supplied to the input port 205 (and the first inflow port 211), and the second switching valve 200 forms the first communication state. As a result, the input port 201 and the second output port 204 communicate with each other, and the second inflow port 212 and the signal pressure outflow port 215 communicate with each other. Furthermore, the communication between the first inflow port 211 and the signal pressure outflow port 215 of the second switching valve 200 is blocked, so that the second signal pressure Psc2 from the second signal pressure output valve SC2 is Even if the modulator pressure Pmod is supplied to the holding pressure inflow port 317 without being supplied to the third signal pressure input port 315, the third switching valve 300 forms the first supply state. Thereby, the communication between the second input port 312 and the second supply port 314 is established, and the communication between the first input port 311 and the first supply port 313 is blocked. Further, the TM ECU 21 supplies current to the electromagnetic portion of the first signal pressure output valve SC1 so that the first signal pressure Psc1 is output as shown in FIG. 5 when the shift lever 95 is set to the neutral position. At the same time, the energization of the second and third signal pressure output valves SC2 and SC3 is released. As a result, the supply of the second signal pressure Psc2 from the second signal pressure output valve SC2 to the parking lock mechanism 70 is stopped, and the parking lock state can be released.

On the other hand, when the driver sets the shift lever 95 to the reverse position, the TM ECU 21 outputs the first and third signal pressures Psc1 and Psc3 as shown in FIG. Current is supplied to the electromagnetic parts of the output valves SC1 and SC3. Furthermore, the TM ECU 21 controls the linear solenoid valves SL2 and SL3 according to a predetermined procedure. Thereby, as shown in FIG. 7, the first switching valve 100 forms the second state, and the second switching valve 200 forms the first communication state. In addition, by supplying the third signal pressure from the third signal pressure output valve SC3 to the switching port 316 (spring chamber), the third switching valve 300 supplies hydraulic fluid (hydraulic pressure) to the third signal pressure input port 315. ) is supplied, the first supply state is established. Hydraulic oil (line pressure PL) from the primary regulator valve side is supplied to the input port of the linear solenoid valve SL3 through the oil passages L21 and L24, and the hydraulic oil pressure-regulated by the linear solenoid valve SL3 is supplied to the clutch C3. is supplied to the engagement oil chamber of Hydraulic oil (line pressure PL) from the primary regulator valve side is supplied to the input port of the linear solenoid valve SL2 through the oil passage L23, and the hydraulic oil (oil pressure Psl2) pressure-regulated by the linear solenoid valve SL2 is supplied to the input port of the linear solenoid valve SL2. The oil is supplied to the engagement oil chamber of the brake B2 through the input port 201 and the second output port 204 of the second switching valve 200 and the second input port 312 and the second supply port 314 of the third switching valve 300 .

As a result, the clutch C3 and the brake B2 can be engaged to establish the reverse first speed. When the shift lever 95 is set to the reverse position, the TM ECU 21 supplies the third signal pressure Psc3 from the third signal pressure output valve SC3 to the switching port 316 of the third switching valve 300, and then the linear solenoid valve Start controlling SL2 and SL3. As a result, even if hydraulic fluid (hydraulic pressure) from the linear solenoid valve SL3 is supplied to the third signal pressure input port 315 via the second inflow port 212 and the signal pressure outflow port 215 of the second switching valve 200, the third The switching valve 300 can be held in the first supply state.

When the driver sets the shift lever 95 to the drive position or the sport position (forward running position), the TM ECU 21, as shown in FIG. In order to stop all the outputs of the first, second and third signal pressure output valves SC1, SC2 and SC3, the energization of the electromagnetic parts is released. As a result, as shown in FIG. 8, the first switching valve 100 forms the first state, the original pressure input port 101 and the original pressure output port 102 are communicated, and the inflow port 111 and the outflow port 112 are connected. communicate. Further, since the second signal pressure Psc2 is not output from the second signal pressure output valve SC2, even if the inflow port 111 and the outflow port 112 of the first switching valve 100 are in communication, the second switching valve 200 can 1 supply state is formed, the input port 201 and the second output port 204 communicate, and the second inflow port 212 and the signal pressure outflow port 215 communicate. Furthermore, even if the second inflow port 212 and the signal pressure outflow port 215 of the second switching valve 200 are in communication, if hydraulic pressure is not output from any of the linear solenoid valves SL3, SL4 and SL5, the third switching valve 300 forms a first supply state in which a second input port 312 and a second supply port 314 are in communication.

When the shift lever 95 is set to a forward travel position such as the drive position, the hydraulic oil (line pressure PL) from the primary regulator valve side flows from the oil passage L21 of the valve body 600 to the original pressure of the first switching valve 100. Supplied to the input ports of linear solenoid valves SL1, SL4 and SL5 corresponding to clutches C1 and C4 and brake B1 which are engaged only when the forward stage is formed via input port 101, source pressure output port 102, oil passage L22, etc. be done. An input port of the linear solenoid valve SL2 communicates with the oil passage L1 via an oil passage L23. Therefore, by controlling the linear solenoid valves SL1 and SL2 by the TMECU 21, hydraulic oil whose pressure is regulated by the linear solenoid valve SL1 is supplied to the engaging oil chamber of the clutch C1, and the pressure is regulated by the linear solenoid valve SL2. Oil (oil pressure Psl2) flows through oil passage L31, input port 201 and second output port 204 of second switching valve 200, oil passage L34, second input port 312 and second supply port 314 of third switching valve 300. is supplied to the engagement oil chamber of the brake B2. As a result, the clutch C1 and the brake B2 can be engaged to establish the first forward speed.

Further, when the upshift condition for upshifting to the second forward speed or the like is satisfied while the first forward speed is established, the TM ECU 21 outputs the first and third signals as shown in FIG. Current is supplied to the electromagnetic portion of the second signal pressure output valve SC2 while the electromagnetic portions of the pressure output valves SC1 and SC3 are de-energized. As a result, as shown in FIG. 9, the first switching valve 100 forms the first state, the original pressure input port 101 and the original pressure output port 102 are communicated, and the inflow port 111 and the outflow port 112 are connected. communicate. Also, the second signal pressure Psc2 from the second signal pressure output valve SC2 is supplied to the second signal pressure input port 205 through the inflow port 111 and the outflow port 112 of the first switching valve 100 and the oil passage L28. , the second switching valve 200 forms the second communication state. This allows the input port 201 and the first output port 203 to communicate with each other. Furthermore, when the second switching valve 200 forms the second communication state, the first inflow port 211 and the signal pressure outflow port 215 are communicated with each other, so that the second signal pressure input port 205 and the oil passage L28 separate from the second signal pressure input port 205 Outflow of hydraulic fluid (second signal pressure Psc2) supplied to the first inflow port 211 from the second signal pressure output valve SC2 is allowed. Hydraulic fluid from the second signal pressure output valve SC2 supplied to the first inflow port 211 passes through the signal pressure outflow port 215 of the second switching valve 200 and the oil passage L35 to the third switching valve 300. It is supplied to the signal pressure input port 315 . As a result, the third switching valve 300 forms the second supply state, and the first input port 311 and the first supply port 313 communicate with each other.

Hydraulic oil (line pressure PL) from the primary regulator valve side flows from the oil passage L21 of the valve body 600 through the original pressure input port 101 and the original pressure output port 102 of the first switching valve 100, the oil passage L22, and the like. It is supplied to input ports of linear solenoid valves SL1, SL4 and SL5 corresponding to clutches C1, C4 and brake B1 which are engaged only when the forward speed is established. Further, the input port of the linear solenoid valve SL2 communicates with the oil passage L1 through the oil passage L23, and the input port of the linear solenoid valve SL3 communicates with the oil passage L1 through the oil passage L24. Therefore, according to the vehicle speed and the degree of accelerator opening of the vehicle 10, hydraulic pressure from two of the linear solenoid valves SL1 to SL5 engages any two of the clutches C1 to C4 and the brake B1 to move forward. A desired shift stage of 2nd speed-forward 8th speed can be formed.

Here, when an abnormality such as sticking of the second spool S2 occurs in the second switching valve 200 of the hydraulic control device 60, the second signal pressure Psc2 from the second signal pressure output valve SC2 is applied to the second signal pressure input port 205. 10, the second switching valve 200 allows the supply of the hydraulic pressure Psl2 from the linear solenoid valve SL2 to the brake B2 (second hydraulic engagement element) side, as shown in FIG. A communication state may be formed. Further, the fifth forward speed to the eighth forward speed of the automatic transmission 25 are formed by engaging the clutch C2 (first engagement element) with any one of the clutches C1, C3, C4 and the brake B1. However, the second switching valve 200, which should normally be in the second communication state when any one of the fifth forward speed to the eighth forward speed is to be established, establishes the first communication state and the linear solenoid valve SL2 is closed. If the hydraulic pressure Psl2 from is supplied to the brake B2, a shift stage other than the fifth forward speed to the eighth forward speed will be established.

That is, when the fifth forward speed is established, the second switching valve 200 establishes the first communication state and the hydraulic pressure Psl2 from the linear solenoid valve SL2 is supplied to the brake B2, as can be seen from FIG. , the first forward speed is established and the vehicle 10 may suddenly decelerate. Further, when the sixth forward speed is established, the second switching valve 200 establishes the first communication state and the hydraulic pressure Psl2 from the linear solenoid valve SL2 is supplied to the brake B2, as can be seen from FIG. , the reverse 2nd speed is formed. Further, when the seventh forward speed is established, the second switching valve 200 establishes the first communication state and the hydraulic pressure Psl2 from the linear solenoid valve SL2 is supplied to the brake B2, as can be seen from FIG. , reverse 1st speed is formed.

Based on these, the second switching valve 200 of the hydraulic control device 60, when forming the first communication state, communicates the second inflow port 212 and the signal pressure outflow port 215 to function as a linear valve as a dedicated pressure regulating valve. Hydraulic oil (hydraulic pressure) from any one of the solenoid valves SL3, SL4 and SL5 is configured to be supplied to the third signal pressure input port 315 of the third switching valve 300. FIG. Further, once the second supply state is established by supplying the hydraulic oil (hydraulic pressure) to the third signal pressure input port 315, the third switching valve 300 of the hydraulic control device 60 switches to the third signal pressure input port 315. The second supply state is continuously formed (held) even if the supply of hydraulic oil (hydraulic pressure) is cut off. As a result, even if the second switching valve 200 is stuck in the first supply state, any one of the second forward speed, third speed, fourth speed, sixth speed, seventh speed and eighth forward speed can be selected. is supplied to the third signal pressure input port 305 of the third switching valve 300 from any one of the linear solenoid valves SL3, SL4 and SL5, and the third switching valve 300 is switched to the second It is possible to maintain the second supply state in which communication between the input port 312 and the second supply port 314 is cut off. As a result, even if the second switching valve 200 is stuck in the first supply state, the hydraulic pressure Psl2 from the linear solenoid valve SL2 is reduced when any one of the fifth forward speed to the eighth forward speed should be established. It is possible to bring the automatic transmission 25 into the neutral state by not supplying the brake B2. Therefore, according to the hydraulic control device 60, it is possible to satisfactorily suppress sudden deceleration of the vehicle 10 due to the downshift from the fifth forward speed to the first forward speed.

On the other hand, when the second signal pressure Psc2 is no longer output from the second signal pressure output valve SC2 due to the occurrence of some abnormality when any one of the fifth forward speed to the eighth forward speed is to be established, FIG. As shown, the second switching valve 200 forms a first communication state in which the input port 201 and the second output port 204 are communicated with each other by the biasing force of the second spring SP2. In this case also, the third switching valve 300 is switched between the second input port 312 and the second switching valve 300 depending on which one of the second, third, fourth, sixth, seventh and eighth forward speeds is established. Since the second supply state in which the communication with the supply port 314 is cut off can be maintained, the hydraulic pressure Psl2 from the linear solenoid valve SL2 is not supplied to the brake B2 to bring the automatic transmission 25 into the neutral state. becomes possible. Therefore, in this case as well, it is possible to satisfactorily suppress the sudden deceleration of the vehicle 10 due to the downshift from the fifth forward speed to the first forward speed.

Next, the procedure for determining the sticking state of the third switching valve (apply valve) 300 in the hydraulic control device 60 will be described with reference to FIGS. 12 to 14. FIG.

As shown in FIG. 12, when the gear stage of the automatic transmission 25 is any one of the fifth forward speed to the eighth forward speed, the second switching valve 200 switches the output from the second signal pressure output valve SC2. By supplying the second signal pressure Psc2 to the second signal pressure input port 205 through the first switching valve 100, the input port 201 and the first output port 203 are communicated, and the first inflow port 211 and the signal A second communication state is formed in which communication with the pressure outlet port 215 is established. At this time, if the third spool S3 of the third switching valve 300 is fixed in the state of forming the first supply state, that is, in the state in which the third spring SP3 is expanded, the second input port 312 and the second supply port 314 , and communication between the first input port 311 and the first supply port 313 is blocked. Therefore, if the third switching valve 300 is stuck in the first supply state when any one of the fifth forward speed to the eighth forward speed is established, the linear solenoid valve as a dual-purpose pressure regulating valve Even if the second switching valve 200 allows the supply of the hydraulic pressure Psl2 from SL2 to the clutch C2 and the outflow of hydraulic oil (second signal pressure Psc2) from the second signal pressure output valve SC2, the clutch C2 is not engaged. As a result, the automatic transmission 25 is put into a neutral state.

Further, as shown in FIG. 13, when the gear stage of the automatic transmission 25 is the first reverse speed or the first forward speed, the second switching valve 200 outputs the second signal from the second signal pressure output valve SC2. Since the pressure Psc2 is not supplied to the second signal pressure input port 205 through the first switching valve 100, the input port 201 and the second output port 204 are communicated, and the second inflow port 212 and the signal pressure outflow port 215 are communicated. A first communication state is formed to communicate with. At this time, when the third spool S3 of the third switching valve 300 is fixed in the state of forming the second supply state, that is, when the third spring SP3 is contracted, the first input port 311 and the first supply port 313 are fixed. , and communication between the second input port 312 and the second supply port 314 is blocked. Therefore, if the third switching valve 300 is stuck in the state of forming the second supply state when the first reverse speed or the first forward speed is established, the linear solenoid valve SL2 as the dual-purpose pressure regulating valve will shift from the brake B2 to the brake B2. and the outflow of hydraulic oil (hydraulic pressure) from the linear solenoid valve SL3 as a dedicated pressure regulating valve are permitted by the second switching valve 200, the brake B2 cannot be engaged. , the automatic transmission 25 is brought into the neutral state.

Based on these characteristics of the hydraulic control device 60, the vehicle 10 executes a routine shown in FIG. The TM ECU 21 serving as a discriminating unit repeatedly executes this process at predetermined time intervals (minute time intervals). At the start of the routine of FIG. 14, the TMECU 21 sets the target shift stage of the automatic transmission 25 set based on the accelerator opening and the vehicle speed, the input rotation speed of the automatic transmission 25 detected by the input rotation speed sensor 97, Information necessary for determining the stuck state of the third switching valve 300, such as the output rotation speed of the automatic transmission 25 detected by the output rotation speed sensor 98, is obtained (step S100). Next, the TM ECU 21 calculates the actual gear ratio set by the automatic transmission 25 based on the input rotation speed and the output rotation speed obtained in step S100 (step S110). Furthermore, the TM ECU 21 determines whether or not the calculated actual gear ratio is outside a relatively narrow predetermined range including the gear ratio of the target gear stage acquired in step S100 (step S120).

When it is determined that the actual gear ratio calculated in step S110 is within the predetermined range (step S120: NO), the TMECU 21 determines that the actual gear ratio substantially matches the gear ratio of the target gear stage, and the third It is assumed that the automatic transmission 25 is not in the neutral state due to the sticking of the switching valve 300, and the routine of FIG. 14 is once terminated. On the other hand, when it is determined that the actual gear ratio calculated in step S110 is outside the predetermined range (step S120: YES), the TMECU 21 determines that the actual gear ratio substantially matches the gear ratio of the target gear stage. It is assumed that the automatic transmission 25 is in the neutral state due to the sticking of the third switching valve 300, and it is determined whether or not the target shift speed is the reverse first speed (step S130).

When the automatic transmission 25 is in the neutral state and the target shift stage is the first reverse speed, the third spool S3 of the third switching valve 300 forms the second supply state as shown in FIG. Since the third spring SP3 is fixed in a contracted state, the hydraulic pressure Psl2 from the linear solenoid valve SL2 is not supplied to the brake B2. Therefore, when it is determined in step S130 that the target gear stage is the first reverse speed (step S130: YES), the TM ECU 21 sets the third switching valve 300 to the second supply state (the third spring SP3 The contraction-side fixation flag Fs is turned on (step S140) to indicate that it is fixation in the contracted state), and the routine of FIG. 14 is terminated. When the contraction-side fixation flag Fs is turned on in step S140, the fail-safe process is executed in consideration of the fixation in the state where the third switching valve 300 is in the second supply state.

Further, when it is determined in step S130 that the target gear stage is not the first reverse speed (step S130: NO), the TM ECU 21 determines whether or not the target gear stage is the first forward speed (step S150). . After an affirmative determination is made in step S120, even if it is determined in step S150 that the target shift speed is the first forward speed, as shown in FIG. It is fixed in the state of forming the second supply state (the state in which the third spring SP3 is contracted). Therefore, when it is determined in step S150 that the target gear stage is the first forward speed (step S150: YES), the TM ECU 21 turns on the compression side fixation flag Fs (step S140), and ends the routine of FIG. Let

Further, when it is determined in step S150 that the target gear stage is not the first forward speed (step S150: NO), the TMECU 21 determines that the target gear stage is the fifth, sixth, seventh, and eighth forward speeds. (step S160). When the TM ECU 21 determines that the target shift stage is not one of the fifth forward speed to the eighth forward speed (step S160: NO), the routine of FIG. 14 is terminated at that time. On the other hand, after an affirmative determination is made in step S120, if it is determined in step S160 that the target gear stage is any one of the fifth forward speed to the eighth forward speed, as shown in FIG. The third spool S3 of the valve 300 is fixed in the state of forming the first supply state, that is, the state in which the third spring SP3 is expanded, so that the hydraulic pressure Psl2 from the linear solenoid valve SL2 is not supplied to the clutch C2. become. Therefore, when it is determined in step S160 that the target gear stage is one of the fifth forward speed to the eighth forward speed (step S160: YES), the TMECU 21 causes the third switching valve 300 to form the first supply state. The extension-side fixation flag Fe is turned on (step S170) to indicate that it is fixed in the extended state (the state in which the third spring SP3 is expanded), and the routine of FIG. 14 is terminated. When the elongation-side fixation flag Fs is turned on in step S170, the fail-safe process is executed in consideration of the fixation in the state where the third switching valve 300 is in the first supply state.

As described above, in the hydraulic control device 60 of the present disclosure, the clutch C2 (first hydraulic engagement element) and the brake B2 (second hydraulic engagement element), which is not simultaneously engaged with the clutch C2, are: The hydraulic pressure Psl2 generated (adjusted) by the linear solenoid valve SL2 (combined pressure regulating valve) can be selectively supplied from the third switching valve 300 as an apply valve. As a result, it is possible to reduce the number of linear solenoid valves (pressure regulating valves) in the hydraulic control device 60, so that cost can be reduced by reducing the number of linear solenoid valves and efficiency can be improved by reducing oil leakage.

Further, when the second signal pressure Psc2 from the second signal pressure output valve SC2 is not supplied to the second signal pressure input port 205 of the second switching valve 200, the second switching valve 200 that forms the first communication state Hydraulic oil from the second signal pressure output valve SC2 to the third switching valve 300 is allowed to be supplied from the linear solenoid valve SL2 as the dual-purpose pressure regulating valve to the brake B2 side as the second hydraulic engagement element. (second signal pressure Psc2) and the supply of hydraulic fluid (second signal pressure Psc2) from the second signal pressure output valve SC2 to the third switching valve 300 are regulated, and the third switching valve 300 The first supply state is formed by not receiving the supply of hydraulic fluid (second signal pressure Psc2) from the second signal pressure output valve SC2 via the valve 200. FIG. As a result, the third switching valve 300 regulates the supply of the hydraulic pressure Psl2 from the linear solenoid valve SL2 to the clutch C2 as the first hydraulic engagement element, and the pressure from the linear solenoid valve SL2 via the third switching valve 300 is supplied to the brake B2. Furthermore, when the second signal pressure Psc2 from the second signal pressure output valve SC2 is supplied to the second switching valve 200, the second switching valve 200, which forms the second communication state, transfers the pressure from the linear solenoid valve SL2 to the clutch C2. is allowed to be supplied with the hydraulic pressure Psl2, and the supply of hydraulic fluid (second signal pressure Psc2) from the second signal pressure output valve SC2 to the third switching valve 300 is allowed, and the third switching valve 300 is allowed to operate in the second switching Hydraulic fluid (second signal pressure Psc2) is supplied from the second signal pressure output valve SC2 via the valve 200 to form the second supply state. As a result, the supply of the hydraulic pressure Psl2 from the linear solenoid valve SL2 to the brake B2 is restricted by the third switching valve 300, and the hydraulic pressure Psl2 from the linear solenoid valve SL2 is supplied to the clutch C2 via the third switching valve 300. be done.

Therefore, when the third switching valve 300 is stuck in the first supply state, the second switching valve 200 is supplied with the second signal pressure Psc2 from the second signal pressure output valve SC2, and the second switching valve 200 is supplied with the second signal pressure Psc2. Even if the valve 200 allows the supply of the hydraulic pressure Psl2 from the linear solenoid valve SL2 to the clutch C2 side and the outflow of hydraulic oil (the second signal pressure Psc2) separately supplied from the second signal pressure output valve SC2, the clutch C2 can no longer be engaged, and the automatic transmission 25 is brought into a neutral state. On the other hand, when the third switching valve 300 is stuck in the second supply state, the second signal pressure Psc2 from the second signal pressure output valve SC2 is no longer supplied to the second switching valve 200. Even if the second switching valve 200 allows the hydraulic pressure Psl2 to be supplied from the linear solenoid valve SL2 to the brake B2 side, the brake B2 cannot be engaged and the automatic transmission 25 is put into the neutral state. As a result, in the hydraulic control device 60, depending on whether or not the second signal pressure output valve SC2 is outputting the second signal pressure Psc2 according to the gear stage of the automatic transmission 25 and the formation state of the gear stage of the automatic transmission 25, , the stuck state of the third switching valve 300 can be accurately determined.

Further, in the automatic transmission 25, the clutch C2 is engaged when a plurality of forward low speed stages including the starting stage, that is, the first forward speed, the fifth forward speed, and the eighth forward speed, which are on the higher speed side than the first forward speed and the fourth forward speed, are formed. The brake B2 is engaged when the first reverse speed and the second reverse speed are established, and when the first forward speed, which is the starting gear, is established. Further, the second signal pressure output valve SC2 outputs the second signal pressure Psc2 when the second forward speed to the eighth forward speed (forward low speed and high forward speed other than the first forward speed which is the starting speed) is established. Further, when the automatic transmission 25 is in the neutral state and the target gear stage of the automatic transmission 25 is any of the forward fifth gear to the eighth gear (forward high speed stage), the TM ECU 21 as a determination unit It is determined that the third switching valve 300 is fixed in the state of forming the first supply state (the state in which the third spring SP3 is expanded). Further, the TMECU 21 causes the third switching valve 300 to form the second supply state when the automatic transmission 25 is in the neutral state and the target speed is the first reverse speed or the first forward speed which is the start speed. It is determined that the third spring SP3 is fixed in a state where the third spring SP3 is contracted. As a result, it is possible to accurately determine the sticking state of the third switching valve 300 during operation of the automatic transmission 25 .

Further, the second switching valve 200 of the hydraulic control device 60 includes a second spool S2, a second spring SP2 that biases the second spool S2, and an input port 201 to which the hydraulic pressure Psl2 from the linear solenoid valve SL2 is supplied. , a first inflow port 211 supplied with hydraulic fluid (second signal pressure Psc2) from the second signal pressure output valve SC2, a first output port 203, a second output port 204, and a signal pressure outflow port 215. and a second signal pressure input port 205 to which the second signal pressure Psc2 from the second signal pressure output valve SC2 is supplied. Further, the second switching valve 200 allows the input port 201 and the second output port 204 to communicate and communicates with the first inflow port 211 when the second signal pressure Psc2 is not supplied to the second signal pressure input port 205. When the second signal pressure Psc2 is supplied to the second signal pressure input port 205, the input port 201 and the first output port 203 are connected to each other. are communicated with each other, and a second communication state is formed in which the first inflow port 211 and the signal pressure outflow port 215 are communicated with each other. Further, the third switching valve 300 of the hydraulic control device 60 includes a third spool S3, a third spring SP3 that biases the third spool S3, and a first switching valve 200 that communicates with the first output port 203 of the second switching valve 200. 1 input port 311, a second input port 312 communicating with the second output port 204 of the second switching valve 200, a first supply port 313 communicating with the oil chamber of the clutch C2, and the oil chamber of the brake B2. It has a second supply port 314 and a third signal pressure input port 315 communicating with the signal pressure output port 215 of the second switching valve 200 . Further, the third switching valve 300 operates when hydraulic oil (second signal pressure Psc2) is not supplied to the third signal pressure input port 315 from the signal pressure outflow port 215 of the second switching valve 200. 312 and the second supply port 314 are in communication with each other, and hydraulic fluid (second signal pressure Psc2) is supplied to the third signal pressure input port 315 from the signal pressure outflow port 215 of the second switching valve 200. When connected, a second supply state is formed that communicates the first input port 311 and the first supply port 313 . As a result, while the hydraulic pressure Psl2 is selectively supplied to the clutch C2 and the brake B2 from the single linear solenoid valve SL2 via the third switching valve 300, the stuck state of the third switching valve 300 is prevented during the operation of the automatic transmission 25. can be accurately determined. The hydraulic control device 60 may be applied to a transmission that selectively engages three or more hydraulic engagement elements to provide a plurality of gear stages.

It goes without saying that the invention of the present disclosure is not limited to the above-described embodiments, and various modifications can be made within the scope of the present disclosure. Furthermore, the above-described embodiment is merely one specific form of the invention described in the Summary of the Invention column, and does not limit the elements of the invention described in the Summary of the Invention column.

INDUSTRIAL APPLICABILITY The invention of the present disclosure can be used in industries such as the manufacturing industry of hydraulic control devices.

10 vehicle, 12 engine, 20 power transmission device, 21 transmission electronic control unit (TMECU), 24 mechanical oil pump, 25 automatic transmission, 60 hydraulic control device, 600 valve body, 100 first switching valve, 101 source pressure input port, 102 source pressure output port, 105 first signal pressure input port, 106 holding pressure input port, 111 inflow port, 112 outflow port, 117 parking port, 200 second switching valve, 201 input port, 203 first output port, 204 second output port, 205 second signal pressure input port, 211 first inflow port, 212 second inflow port, 215 signal pressure outflow port, 300 third switching valve, 311 first input port, 312 second input port, 313 first supply port 314 second supply port 315 third signal pressure input port 316 switching port 317 holding pressure inflow port 318 holding pressure outflow port 319 holding pressure introduction port B1, B2 brakes C1, C2 , C3, C4 clutch, S1 first spool, S2 second spool, S3 third spool, SC1 first signal pressure output valve, SC2 second signal pressure output valve, SC3 third signal pressure output valve, SL1, SL2, SL3 , SL4, SL5 linear solenoid valve, SP1 first spring, SP2 second spring, SP3 third spring.

Claims (3)

selectively engaging at least any two of a first hydraulic engagement element, a second hydraulic engagement element that is not engaged simultaneously with the first hydraulic engagement element, and the remaining hydraulic engagement elements In a hydraulic control device for a transmission that forms a plurality of forward gears and reverse gears,
A dual-purpose pressure regulating valve that adjusts the source pressure to generate hydraulic pressure to the first hydraulic engagement element and the second hydraulic engagement element, and adjusts the source pressure to the corresponding remaining hydraulic engagement elements. a plurality of pressure regulating valves including at least one dedicated pressure regulating valve that produces a hydraulic pressure of
a signal pressure output valve that outputs signal pressure;
When the signal pressure is not supplied from the signal pressure output valve, the hydraulic pressure is allowed to be supplied from the dual-purpose pressure regulating valve to the second hydraulic engagement element side, and from the dual-purpose pressure regulating valve A first communication state is formed to restrict the supply of the hydraulic pressure to the first hydraulic engagement element side and the outflow of the oil separately supplied from the signal pressure output valve, and the signal pressure from the signal pressure output valve is controlled. While being supplied, the dual-purpose pressure regulating valve allows the hydraulic pressure to be supplied from the dual-purpose pressure regulating valve to the first hydraulic engagement element side and allows the oil separately supplied from the signal pressure output valve to flow out. a switching valve that forms a second communication state that regulates the supply of the hydraulic pressure from the valve to the second hydraulic engagement element side;
When the oil is not supplied from the signal pressure output valve via the switching valve, the supply of the hydraulic pressure from the dual-purpose pressure regulating valve to the first hydraulic engagement element from the switching valve is restricted. At the same time, a first supply state is formed in which the hydraulic pressure from the dual-use pressure regulating valve is allowed to be supplied from the switching valve to the second hydraulic engagement element, and the hydraulic pressure is supplied from the signal pressure output valve via the switching valve. When receiving the supply of the oil, it allows the supply of the hydraulic pressure from the dual-use pressure regulating valve from the switching valve to the first hydraulic engagement element, and from the switching valve to the second hydraulic engagement element. an apply valve that forms a second supply state that regulates the supply of the hydraulic pressure from the dual-purpose pressure regulating valve to the
Hydraulic controller with In the hydraulic control device according to claim 1,
The first hydraulic engagement element is engaged when a plurality of forward high speed stages on a higher speed side than a plurality of forward low speed stages including a starting stage of the transmission are formed,
the second hydraulic engagement element is engaged when the reverse gear is formed and when the start gear is formed;
The signal pressure output valve outputs the signal pressure when the forward low speed stage and the forward high speed stage other than the starting stage are formed,
It is determined that the apply valve is stuck in the state of forming the first supply state when the transmission is in the neutral state and the target gear stage of the transmission is one of the forward high speed stages. and, when the transmission is in the neutral state and the target shift speed of the transmission is the reverse speed or the start speed, the apply valve is stuck in the state of forming the second supply state. A hydraulic control device further comprising a determination unit that determines that In the hydraulic control device according to claim 1 or 2,
The switching valve includes a spool, a spring that biases the spool, an input port to which the hydraulic pressure is supplied from the dual-purpose pressure regulating valve, and an inflow port to which the oil is supplied from the signal pressure output valve. , a first output port, a second output port, a signal pressure outflow port, and a signal pressure input port to which the signal pressure from the signal pressure output valve is supplied, and the signal pressure input port is supplied with the signal pressure. When pressure is not supplied, the first communication state is formed in which the input port and the second output port are communicated and the communication between the inflow port and the signal pressure outflow port is cut off, and the signal pressure is forming the second communication state in which the input port and the first output port are communicated and the inflow port and the signal pressure outflow port are communicated when the signal pressure is supplied to the input port;
The apply valve includes a spool, a spring that biases the spool, a first input port that communicates with the first output port of the switching valve, and a second input that communicates with the second output port of the switching valve. a port, a first supply port communicating with the oil chamber of the first hydraulic engagement element, a second supply port communicating with the oil chamber of the second hydraulic engagement element, and the signal pressure outflow port of the switching valve. and a signal pressure input port communicating with the second input port and the second supply port when the signal pressure input port is not supplied with the oil from the signal pressure outflow port of the switching valve. and when the oil is supplied to the signal pressure input port from the signal pressure outflow port of the switching valve, the first input port and the first output port Hydraulic control device for establishing said second supply state to communicate with the

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