JP2011214621A - Hydraulic control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic control device capable of engaging a hydraulic frictional engagement element even if hydraulic pressure cannot be supplied from a solenoid valve to the hydraulic frictional engagement element corresponding to the solenoid valve due to the abnormality of the state of supply of hydraulic pressure from the solenoid valve while suppressing an increase in the cost and the size of the hydraulic control device.SOLUTION: When an oil pump 29 is driven by an engine and the state of supply of hydraulic pressure from the C1 linear solenoid valve SLC1 causes abnormality, a selector valve 70 forms a second state in which a line pressure PL (Pd) from a manual valve 53 as a hydraulic pressure which does not depend on the state of generation of the hydraulic pressures of the C1 linear solenoid valve SLC1 and a B1 linear solenoid valve SLB1 can be supplied to a clutch C1 using, as a signal pressure, a B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1.

Description

  The present invention relates to a hydraulic control device for a transmission that can transmit power applied to an input member to an output member by changing a gear ratio to a plurality of stages by engaging and disengaging a plurality of hydraulic friction engagement elements.

  Conventionally, hydraulic control of an automatic transmission provided with a failure-time switching valve that is switched to a failure-time position when the hydraulic pressure supplied to the hydraulic servos of a plurality of friction engagement elements that are not normally engaged simultaneously is input simultaneously. An apparatus is known (see, for example, Patent Document 1). The hydraulic control device includes a solenoid valve that outputs a signal pressure in a predetermined state and an oil passage that supplies hydraulic pressure to a hydraulic servo of one of the plurality of friction engagement elements. A switching valve that communicates the oil passage based on the signal pressure, and the failure switching valve includes an input port that inputs the signal pressure of the solenoid valve, and an output port that communicates with the input port when switched to the failure position. Have The failure switching valve outputs a failure signal pressure based on the signal pressure of the solenoid valve from the output port when the failure switching valve is switched to the failure position in a predetermined state, and the switching valve is based on the failure signal pressure. Shut off the oil passage. Thus, in this hydraulic control device, even when a failure occurs in which a plurality of friction engagement elements are engaged at the same time, the failure switching valve outputs a failure signal pressure to release one friction engagement element. And when the one frictional engagement element is not engaged based on the signal pressure of the solenoid valve, even when a plurality of other frictional engagement elements are engaged. The failure signal pressure can be prevented from being output.

JP 2004-36671 A

  By the way, in the hydraulic control apparatus as described above, it may be impossible to supply hydraulic pressure to any one of a plurality of friction engagement elements due to some abnormality. Therefore, no countermeasure is disclosed when it is impossible to supply hydraulic pressure to one friction engagement element. In such a case, it is conceivable that the oil pressure is switched from the normal hydraulic pressure supply source to the one friction engagement element by using the signal pressure from the solenoid valve dedicated to the failure as described above. However, if the hydraulic control device is equipped with a solenoid valve dedicated to failure, the cost may be increased and the size of the device may be increased accordingly.

  Therefore, the hydraulic control device according to the present invention has a hydraulic friction from the solenoid valve corresponding to an abnormality in the hydraulic pressure supply state from any one of the plurality of solenoid valves while suppressing an increase in cost and an increase in size of the device. The main object is to enable the engagement of the hydraulic frictional engagement element to be maintained even when hydraulic pressure cannot be supplied to the engagement element.

  The hydraulic control apparatus according to the present invention employs the following means in order to achieve the main object.

The hydraulic control device according to the present invention comprises:
In a hydraulic control device for a transmission that can transmit power applied to an input member to an output member by changing a gear ratio to a plurality of stages by engaging and disengaging a plurality of hydraulic friction engagement elements,
A first solenoid valve that generates hydraulic pressure to a first hydraulic friction engagement element of the plurality of hydraulic friction engagement elements;
A second solenoid valve for generating hydraulic pressure to a second hydraulic friction engagement element among the plurality of hydraulic friction engagement elements;
When the supply state of the hydraulic pressure from the first solenoid valve is normal, the first hydraulic friction engagement element forms a first state in which the hydraulic pressure from the first solenoid valve can be supplied, and When an abnormality occurs in the supply state of the hydraulic pressure from one solenoid valve, the first and second solenoids are applied to the first hydraulic friction engagement element by using the hydraulic pressure from the second solenoid valve as a signal pressure. A switching valve that forms a second state that enables supply of hydraulic pressure independent of the generation state of the hydraulic pressure of the valve;
It is characterized by providing.

  In this hydraulic control device, when the supply state of the hydraulic pressure from the first solenoid valve is normal, the first state in which the hydraulic pressure from the first solenoid valve can be supplied to the first hydraulic friction engagement element is the switching valve. It is formed by. In addition, the switching valve uses the oil pressure from the second solenoid valve as a signal pressure when the abnormality occurs in the supply state of the oil pressure from the first solenoid valve. A second state is formed in which the hydraulic pressure independent of the hydraulic pressure generation state of the first and second solenoid valves can be supplied. Accordingly, when an abnormality occurs in the supply state of the hydraulic pressure from the first solenoid valve, the second state is formed by the switching valve, and the hydraulic pressure that does not depend on the generation state of the hydraulic pressures of the first and second solenoid valves is increased. 1 is supplied to the hydraulic friction engagement element, thereby maintaining the engagement of the first hydraulic friction engagement element even if an abnormality occurs in the supply state of the hydraulic pressure from the first solenoid valve. It becomes possible. Then, when there is an abnormality in the supply state of the hydraulic pressure from the first solenoid valve in this way, the hydraulic pressure from the second solenoid valve is used as the signal pressure to switch from the first state to the second state. Therefore, it is not necessary to prepare a dedicated solenoid valve or the like when an abnormality occurs for switching from the first state to the second state, thereby suppressing an increase in cost and an increase in the size of the apparatus. The abnormality in the supply state of the hydraulic pressure from the first solenoid valve includes at least an abnormality in the first solenoid valve itself and an abnormality such as blockage of an oil passage that occurs between the first solenoid valve and the switching valve. .

  Further, the switching valve is in a normal state in which the hydraulic pressure is supplied from the first solenoid valve, and the hydraulic pressure from the second solenoid valve is changed to a signal pressure as the second hydraulic friction engagement element is engaged. May be configured not to execute switching from the first state to the second state. Thereby, when the supply state of the hydraulic pressure from the first solenoid valve is normal, the hydraulic pressure that does not depend on the generation state of the hydraulic pressure of the first and second solenoid valves is generated as the hydraulic pressure is generated by the second solenoid valve. Supplying to the hydraulic friction engagement element can be prevented.

  Furthermore, the hydraulic control device may further include a regulator valve that adjusts the hydraulic pressure from a hydraulic pressure generation source to generate a line pressure, and a modulator valve that adjusts the line pressure to generate a constant modulator pressure. The first solenoid valve adjusts the line pressure to generate a first solenoid valve pressure to the first hydraulic friction engagement element, and the second solenoid valve adjusts the line pressure to adjust the line pressure. The second solenoid valve pressure to the two hydraulic friction engagement elements may be generated, and the hydraulic pressure not depending on the generation state of the first and second solenoid valves may be the line pressure. The switching valve has a spool biased by a spring, and at least the modulator pressure and the second solenoid valve pressure are signal pressures. The hydraulic control device may be configured such that when the supply state of hydraulic pressure from the first solenoid valve is normal, the thrust applied to the spool by the action of the modulator pressure is generated by the spring. The switching valve forms the first state by overcoming the urging force and at least the thrust applied to the spool by the action of the second solenoid valve pressure, and the hydraulic pressure is supplied from the first solenoid valve. When an abnormality has occurred, the second solenoid valve pressure is increased, and the biasing force of the spring and at least the thrust applied to the spool by the action of the second solenoid valve pressure are caused by the action of the modulator pressure. By overcoming the thrust applied to the switching valve, the switching valve It may be configured to form a state. Thus, the first state is formed when the hydraulic pressure supply state from the first solenoid valve is normal regardless of the supply state of the second solenoid valve pressure from the second solenoid valve to the second hydraulic friction engagement element. At the same time, it is possible to form the second state when an abnormality occurs in the supply state of the hydraulic pressure from the first solenoid valve.

  The line pressure may be further supplied as a signal pressure to the switching valve, and the hydraulic pressure control device may be operated by the action of the modulator pressure when the hydraulic pressure supply state from the first solenoid valve is normal. The thrust applied to the spool overcomes the thrust applied by the spring and the thrust applied to the spool by the action of the second solenoid valve pressure and the thrust applied to the spool by the action of the line pressure. When the switching valve forms the first state and an abnormality occurs in the supply state of the hydraulic pressure from the first solenoid valve, at least the second solenoid valve pressure is increased and the urging force by the spring and the line are increased. Pressure and the thrust applied to the spool by the action of the second solenoid valve pressure It may be configured such that the switching valve by overcoming the thrust applied to the spool by the action of the modulator pressure to form the second state. As a result, the second state can be more reliably formed when an abnormality has occurred in the supply state of the hydraulic pressure from the first solenoid valve.

  Further, the switching valve includes a first input port to which the first solenoid valve pressure is supplied, a second input port to which the line pressure is supplied, and a first signal pressure input port to which the modulator pressure is supplied. A second signal pressure input port to which the second solenoid valve pressure is supplied, a third signal pressure input port to which the line pressure is supplied, and an output communicating with the hydraulic inlet of the first hydraulic friction engagement element. A port, and the thrust applied to the spool by the action of the modulator pressure is caused by the thrust applied by the spring and the action of the second solenoid valve pressure and the action of the line pressure. When the thrust applied to the spool is overcome, the first input port communicates with the output port and is biased by the spring. And the thrust applied to the spool by the action of the second solenoid valve pressure and the thrust applied to the spool by the action of the line pressure overcome the thrust applied to the spool by the action of the modulator pressure. The second input port and the output port may be communicated with each other.

  The hydraulic control device may further include a manual valve capable of switching a supply destination of the line pressure from the regulator valve in accordance with a selected shift range, and the second control port and the second input port of the switching valve. The line pressure may be supplied to the third signal pressure input port via the manual valve when the forward travel shift range is selected.

  Further, the first hydraulic friction engagement element may be engaged at least when the first speed and the second speed of the transmission are set, and the second hydraulic friction engagement element may be engaged. The element may be engaged at least when the second speed of the transmission is set. Thus, even if the hydraulic pressure cannot be supplied from the first solenoid valve to the first hydraulic friction engagement element due to an abnormality in the supply state of the hydraulic pressure from the first solenoid valve, the hydraulic pressure from the second solenoid valve is used. By forming the second state, the engagement of the first hydraulic frictional engagement element is maintained and the second hydraulic frictional engagement element is engaged to start and advance the vehicle at the second speed. Can be ensured.

It is a schematic block diagram of the motor vehicle 10 which is a vehicle carrying the power transmission device 20 including the hydraulic control device 50 according to the embodiment of the present invention. 2 is a schematic configuration diagram of a power transmission device 20. FIG. 3 is an operation table showing the relationship between each gear position of the automatic transmission 30 included in the power transmission device 20 and the operation states of clutches and brakes. 3 is a collinear diagram illustrating the relationship between the rotational speeds of rotating elements constituting the automatic transmission 30. FIG. 2 is a system diagram showing a hydraulic control device 50. FIG. 2 is a schematic configuration diagram illustrating an example of an electromagnetic pump 60. FIG. It is a systematic diagram which shows the principal part of the hydraulic control apparatus 50B which concerns on a modification.

  Next, the form for implementing this invention is demonstrated using an Example.

  FIG. 1 is a schematic configuration diagram of an automobile 10 that is a vehicle equipped with a power transmission device 20 including a hydraulic control device 50 according to an embodiment of the present invention, and FIG. 2 is a schematic configuration diagram of the power transmission device 20. . An automobile 10 shown in these drawings includes an engine 12 as a power generation source that is an internal combustion engine that outputs power by an explosion combustion of a mixture of hydrocarbon fuel such as gasoline and light oil and air, and operation control of the engine 12. An engine electronic control unit (hereinafter referred to as “engine ECU”) 14, a brake electronic control unit (hereinafter referred to as “brake ECU”) 15 for controlling an electronically controlled hydraulic brake unit (not shown), and a fluid transmission ( (Starting device) 23, stepped automatic transmission 30, hydraulic control device 50 for supplying and discharging hydraulic oil (working fluid) to and from them, a shift electronic control unit (hereinafter referred to as "shift ECU") 21 for controlling them, and the like And is connected to the crankshaft 16 of the engine 12 and transmits power from the engine 12 as a power generation source to the left and right. And a power transmission device 20 for transmitting to wheels DW.

  As shown in FIG. 1, the engine ECU 14 includes an accelerator opening Acc from an accelerator pedal position sensor 92 that detects a depression amount (operation amount) of an accelerator pedal 91, a vehicle speed V from a vehicle speed sensor 99, and rotation of the crankshaft 16. A signal from various sensors such as a crankshaft position sensor (not shown) for detecting the engine, a signal from the brake ECU 15 and the shift ECU 21 and the like are input, and based on these signals, the engine ECU 14 Controls fuel injection valves, spark plugs, etc. In addition, the engine electronic control unit 14 according to the embodiment stops the operation of the engine 12 when the normal engine 12 is idling as the automobile 10 stops, and responds to a start request to the automobile 10 by depressing the accelerator pedal 91. Accordingly, automatic start / stop control (idle stop control) for restarting the engine 12 is configured to be executable.

  The brake ECU 15 receives the master cylinder pressure detected by the master cylinder pressure sensor 94 when the brake pedal 93 is depressed, the vehicle speed V from the vehicle speed sensor 99, signals from various sensors (not shown), the engine ECU 14 and the transmission ECU 21. The brake ECU 15 controls a brake actuator (hydraulic actuator) (not shown) and the like based on these signals. The transmission ECU 21 of the power transmission device 20 is accommodated in the transmission case 22. The shift ECU 21 includes a shift range SR from a shift range sensor 96 that detects an operation position of a shift lever 95 for selecting a desired shift range from a plurality of shift ranges, a vehicle speed V from a vehicle speed sensor 99, and not shown. Signals from various sensors, signals from the engine ECU 14 and brake ECU 15, and the like are input, and the transmission ECU 21 controls the fluid transmission device 23, the automatic transmission 30, and the like based on these signals. The engine ECU 14, the brake ECU 15 and the transmission ECU 21 are configured as a microprocessor centered on a CPU (not shown). In addition to the CPU, a ROM for storing a processing program, a RAM for temporarily storing data, and an input / output port And a communication port (both not shown). The engine ECU 14, the brake ECU 15 and the transmission ECU 21 are connected to each other via a bus line or the like, and exchange of data necessary for control is executed between these ECUs as needed.

  The power transmission device 20 includes a fluid transmission device 23 housed in the transmission case 22, an oil pump (mechanical pump) 29, an automatic transmission 30, and the like. The fluid transmission device 23 is configured as a fluid torque converter with a lock-up clutch, and as shown in FIG. 2, a pump impeller 24 connected to the crankshaft 16 of the engine 12 via the front cover 18 and a turbine The turbine runner 25 fixed to the input shaft (input member) 31 of the automatic transmission 30 through the hub, the pump impeller 24, and the hydraulic oil (ATF) from the turbine runner 25 to the pump impeller 24 disposed inside the turbine runner 25. ), A one-way clutch 27 that restricts the rotational direction of the stator 26 to one direction, a lock-up clutch 28 having a damper mechanism, and the like. The fluid transmission device 23 functions as a torque amplifier due to the action of the stator 26 when the rotational speed difference between the pump impeller 24 and the turbine runner 25 is large, and functions as a fluid coupling when the rotational speed difference between the two is small. The lock-up clutch 28 is capable of executing lock-up for connecting the pump impeller 24 (front cover 18) and the turbine runner 25 (turbine hub) and releasing the lock-up. When a predetermined lock-up on condition is satisfied after the vehicle 10 is started, the pump impeller 24 and the turbine runner 25 are locked (directly connected) by the lock-up clutch 28, and the power from the engine 12 is mechanically connected to the input shaft 31. And it will be transmitted directly. At this time, the fluctuation of the torque transmitted to the input shaft 31 is absorbed by the damper mechanism.

  The oil pump 29 as a hydraulic pressure generation source is configured as a gear pump including a pump assembly including a pump body and a pump cover, and an external gear connected to the pump impeller 24 of the fluid transmission device 23 via a hub. The hydraulic control device 50 is connected. When the engine 12 is in operation, the external gear is rotated by the power from the engine 12, whereby the hydraulic oil stored in the oil pan (not shown) is sucked by the oil pump 29 through the strainer. And is discharged from the oil pump 29. Therefore, during operation of the engine 12, the oil pump 29 can generate the hydraulic pressure required by the fluid transmission device 23 and the automatic transmission 30, and supply hydraulic oil to lubricated parts such as various bearings. .

  The automatic transmission 30 is configured as a four-stage stepped transmission, and as shown in FIG. 2, a Ravigneaux type planetary gear mechanism 32 and a power transmission path from the input side to the output side are changed. It includes three clutches C1, C2 and C3, two brakes B1 and B3 and a one-way clutch F2. The Ravigneaux type planetary gear mechanism 32 meshes with two sun gears 33a and 33b that are external gears, a ring gear 34 that is an internal gear fixed to an output shaft (output member) 37 of the automatic transmission 30, and the sun gear 33a. A plurality of short pinion gears 35a, a plurality of long pinion gears 35b meshed with the ring gear 34 and meshed with the sun gear 33b and the plurality of short pinion gears 35a, and a plurality of short pinion gears 35a and a plurality of long pinion gears 35b coupled to each other. And a carrier 36 supported by the transmission case 22 via a one-way clutch F2 while being held to revolve freely. The output shaft 37 of the automatic transmission 30 is connected to the drive wheels DW via a gear mechanism 38 and a differential mechanism 39.

  The clutch C1 as the first hydraulic friction engagement element is a hydraulic clutch that can fasten the input shaft 31 and the sun gear 33a of the Ravigneaux planetary gear mechanism 32 and release the fastening of both. The clutch C2 is a hydraulic clutch that can fasten the input shaft 31 and the carrier 36 of the Ravigneaux type planetary gear mechanism 32 and can release the fastening of both. The clutch C3 is a hydraulic clutch that can fasten the input shaft 31 and the sun gear 33b of the Ravigneaux type planetary gear mechanism 32 and release the fastening of both. The brake B1 as the second hydraulic friction engagement element is a hydraulic clutch that can fix the sun gear 33b of the Ravigneaux type planetary gear mechanism 32 to the transmission case 22 and release the fixation of the sun gear 33b to the transmission case 22. The brake B3 is a hydraulic clutch that can fix the carrier 36 of the Ravigneaux type planetary gear mechanism 32 to the transmission case 22 and release the carrier 36 from the transmission case 22. These clutches C <b> 1 to C <b> 3 and brakes B <b> 1 and B <b> 3 operate by receiving and supplying hydraulic oil from the hydraulic control device 50. FIG. 3 shows an operation table showing the relationship between the respective shift stages of the automatic transmission 30 and the operating states of the clutches C1 to C3, the brakes B1 and B3, and the one-way clutch F2. FIG. The collinear diagram which illustrates the relationship of the rotation speed between rotation elements is shown. The automatic transmission 30 provides the first to fourth forward speeds and the first reverse speed by setting the clutches C1 to C3 and the brakes B1 and B3 to the states shown in the operation table of FIG.

  FIG. 5 is a system diagram showing a hydraulic control device 50 that supplies and discharges hydraulic fluid to and from the fluid transmission device 23 and the automatic transmission 30 including the lockup clutch 28 described above. The hydraulic control device 50 is connected to the oil pump 29 that is driven by the power from the engine 12 and sucks and discharges the hydraulic oil from the oil pan. A primary regulator valve 51 that generates a pressure PL, a modulator valve 52 that generates a constant modulator pressure Pmod, a manual valve 53 that switches the supply destination of the line pressure PL from the primary regulator valve 51 according to the operating position of the shift lever 95, The C1 linear solenoid valve SLC1 for adjusting the line pressure PL from the manual valve 53 (primary regulator valve 51) to generate the C1 solenoid valve pressure Pslc1 to the clutch C1, and the pressure from the manual valve 53 (primary regulator valve 51). The C1 linear solenoid valve SLC2 that generates the C2 solenoid valve pressure Pslc2 to the clutch C2 by adjusting the engine pressure PL, and the B1 solenoid valve to the brake B1 by adjusting the line pressure PL from the manual valve 53 (primary regulator valve 51) B1 linear solenoid valve SLB1 that generates pressure Pslb1, an electromagnetic pump (electric pump) 60 that is driven by power from an auxiliary battery (not shown) and sucks and discharges hydraulic oil from an oil pan, and a C1 linear solenoid valve to clutch C1 A switching valve 70 that can form a first state in which the C1 solenoid valve pressure Pslc1 from the SLC1 can be supplied and a second state in which the hydraulic pressure Pemop from the electromagnetic pump 60 can be supplied to the clutch C1 is included. Note that the electronic components such as the linear solenoid valves SLC1, SLC2 and SLB1 and the electromagnetic pump 60 included in the hydraulic control device 50 are controlled by the transmission ECU 21.

  As shown in FIG. 5, the hydraulic control device 50 according to the embodiment is connected to the output ports of the linear solenoid valves SLC1, SLC2, and SLB1, and is connected to the C1 solenoid valve pressure Pslc1, the C2 solenoid valve pressure Pslc2, and the B1 solenoid valve pressure Pslb1. A shuttle valve (maximum pressure selection valve) 54 that outputs the maximum pressure Pmax is included. The primary regulator valve 51 of the embodiment inputs the maximum pressure Pmax from the shuttle valve 54 as a signal pressure, and sets the line pressure PL based on the maximum pressure Pmax. However, the primary regulator valve 51 may be driven by a linear solenoid valve that regulates and outputs hydraulic oil from the oil pump 29 side (for example, the modulator valve 52). Further, the modulator valve 52 of the embodiment is a pressure regulating valve that regulates the line pressure PL from the primary regulator valve 51 by using the biasing force of the spring and the feedback pressure to generate a constant modulator pressure Pmod.

  The manual valve 53 is a spool that can slide in the axial direction in conjunction with the shift lever 95, an input port to which the line pressure PL is supplied, the C1 linear solenoid valve SLC1, the C2 linear solenoid valve SLC2, and the B1 linear solenoid valve SLB1. It has a drive range output port communicating with the input port via the oil passage, a reverse range output port communicating with the hydraulic inlet of the clutch C3 via the oil passage, and the like. When the driver selects a forward drive shift range such as a drive range, a sports range, or a second speed engine brake range, the spool of the manual valve 53 causes the input port to communicate with only the drive range output port. The line pressure PL (Pd) is supplied to the linear solenoid valves SLC1, C2 linear solenoid valve SLC2 and B1 linear solenoid valve SLB1. Further, when the reverse range for reverse running is selected by the driver, the input port is communicated only with the reverse range output port by the spool of the manual valve 53, whereby the line pressure PL (Pr) is supplied to the clutch C3. The clutch C3 is engaged. When a parking range or neutral range is selected by the driver, communication between the input port, the drive range output port, and the reverse range output port is blocked by the spool of the manual valve 53.

  The C1 linear solenoid valve SLC1 is a normally open linear solenoid valve that adjusts the line pressure PL from the manual valve 53 according to a current value applied from an auxiliary battery (not shown) to generate the C1 solenoid valve pressure Pslc1. The C2 linear solenoid valve SLC2 is a normally open linear solenoid valve that adjusts the line pressure PL from the manual valve 53 according to a current value applied from an auxiliary battery (not shown) to generate a C2 solenoid valve pressure Pslc2. In the embodiment, the C2 solenoid valve pressure Pslc2 generated by the C2 linear solenoid valve SLC2 is directly supplied to the hydraulic inlet of the clutch C2 via the oil passage. The B1 linear solenoid valve SLB1 is a normally closed linear solenoid valve that adjusts the line pressure PL from the manual valve 53 according to a current value applied from an auxiliary battery (not shown) to generate the B1 solenoid valve pressure Pslb1. In the embodiment, the B1 solenoid valve pressure Pslb1 generated by the B1 linear solenoid valve SLB1 is directly supplied to the hydraulic pressure inlet of the brake B1 via the oil passage. The hydraulic control device 50 according to the embodiment is configured so that the first runner of the automatic transmission 30 is set when the first-speed engine brake range (L range) is selected by the driver. 12) includes an apply valve 55 that switches a supply source of hydraulic pressure to the brake B3 that is engaged when the friction torque is transmitted from the side to the output shaft 37 (during the first speed engine braking) and during reverse running. The apply valve 55 includes a first input port communicating with the output port of the C2 linear solenoid valve SLC2, a second input port communicating with the reverse range output port of the manual valve 53, and an output port communicating with the hydraulic inlet of the brake B3. The C2 solenoid valve pressure Pslc2 from the C2 linear solenoid valve SLC2 is supplied to the brake B3 during the first-speed engine brake, and the line pressure PL (Pr) from the manual valve 53 is braked during the reverse running. It is made to supply to B3.

  In the embodiment, the linear solenoid valves SLC1, SLC2, and SLB1 having the same size and the same maximum output pressure are employed from the viewpoint of cost and ease of design. Further, in the automatic transmission 30 of the embodiment, the torque sharing ratio of the brake B1 that is engaged when the second speed and the fourth speed are set is the same as that of the clutch C1 and the fourth speed that are simultaneously engaged when the second speed is set. It is smaller than the torque sharing ratio of the clutch C2 that is simultaneously engaged at the time of setting. Accordingly, the output pressure required for the B1 linear solenoid valve SLB1 corresponding to the brake B1 during traveling of the automobile 10 is required for the C1 linear solenoid valve SLC1 corresponding to the clutch C1 and the C2 linear solenoid valve SLC2 corresponding to the clutch C2. Lower than the output pressure. Thus, the maximum output pressure is not required for the B1 linear solenoid valve SLB1 during normal driving of the automobile 10, and the required output pressure to the B1 linear solenoid valve SLB1 is a value that is sufficiently lower than the maximum output pressure. It falls within the range where the upper limit pressure is the upper limit.

  As shown in FIG. 6, the electromagnetic pump 60 includes a sleeve 63 having a suction port 61 and a discharge port 62, a solenoid part 64 connected to the sleeve 63, and a shaft 65 moved forward and backward in the axial direction by the solenoid part 64. The suction check valve 66 is disposed in the sleeve 63 and connected to the tip of the shaft 65, and is disposed in the sleeve 63 so as to be positioned between the suction check valve 66 and the end plate 63e. A discharge check valve 67, a pump chamber 68 defined between the suction check valve 66 in the sleeve 63 and the discharge check valve 67, a suction check valve 66, and a discharge check valve 67 and a spring 69 that urges the shaft 65 toward the solenoid part 64 via the main body of the check valve 66 for suction. The shaft 65 moves from the end plate 63e side to the solenoid unit 64 side by the biasing force of the spring 69 when the energization to the coil of the solenoid unit 64 is off, and the energization to the coil of the solenoid unit 64 is on. Then, it moves from the solenoid part 64 side to the end plate 63e side against the urging force of the spring 69. Further, the suction check valve 66 is opened when the pressure in the pump chamber 68 becomes, for example, a negative pressure (or a pressure lower than the pressure on the suction port 61 side by a predetermined value), for example, to the pump chamber 68 from the suction port 61. When the pressure in the pump chamber 68 is, for example, a positive pressure (or exceeds a pressure higher by a predetermined value than the pressure on the suction port 61 side), the valve is closed and the pump from the suction port 61 is allowed. The flow of hydraulic oil into the chamber 68 is restricted. The discharge check valve 67 opens when the pressure in the pump chamber 68 is, for example, a positive pressure (or exceeds a pressure higher than the pressure on the discharge port 62 side by a predetermined value), and opens from the pump chamber 68 to the discharge port. When the hydraulic oil is allowed to flow out to 62 and the pressure in the pump chamber 68 becomes, for example, a negative pressure (or a pressure lower than the pressure on the discharge port 62 side by a predetermined value), the valve is closed and the discharge port 62 from the pump chamber 68 is closed. Regulating hydraulic oil spills to

  In the electromagnetic pump 60 configured as described above, when energization of the coil of the solenoid unit 64 is turned on and the coil 65 is deenergized, the shaft 65 moves from the end plate 63e side to the solenoid unit 64 side. Accordingly, the pressure in the pump chamber 68 becomes negative (decreases), for example, so that the suction check valve 66 is opened and the discharge check valve 67 is closed. The hydraulic oil is sucked into the pump chamber 68 through a strainer and a suction port 61 (not shown). In this state, when energization to the coil of the solenoid unit 64 is turned on, the shaft 65 moves from the solenoid unit 64 side to the end plate 63e side, and the pressure in the pump chamber 68 becomes positive pressure, for example. Therefore, the suction check valve 66 is closed and the discharge check valve 67 is opened. The hydraulic oil sucked into the pump chamber 68, that is, the hydraulic pressure Pemop, passes through the discharge check valve 67. Thus, the ink is discharged from the discharge port 62. Accordingly, when a rectangular wave current having a predetermined duty ratio is applied to the coil of the solenoid unit 64, the electromagnetic pump 60 can draw the hydraulic oil from the oil pan side and increase the pressure to discharge from the discharge port 62. .

  The switching valve 70 includes a spool 71 that is slidably disposed in the valve body, a spring 72 that biases the spool 71, and a first input port that communicates with an output port of the C1 linear solenoid valve SLC1 via an oil passage. 73, a second input port 74 communicating with the discharge port 62 of the electromagnetic pump 60 via the oil passage Lep, a first signal pressure input port 75 communicating with the output port of the modulator valve 52 via the oil passage, and B1 A second signal pressure input port 76 communicating with the output port of the linear solenoid valve SLB1 via an oil path; a third signal pressure input port 77 communicating with the drive range output port of the manual valve 53 via an oil path Lpd; An output port 78 communicating with the hydraulic inlet of the clutch C1 via an oil passage and a spring chamber in which the spring 72 is disposed leaks into the spring chamber. The the hydraulic oil and a port 79 for discharging. In the embodiment, the oil passage Lep connecting the discharge port 62 of the electromagnetic pump 60 and the second input port 74 of the switching valve 70, the drive range output port of the manual valve 53, and the third signal pressure input port of the switching valve 70. An oil passage Lpd that connects to 77 is connected via a check valve 56. The check valve 56 allows inflow of hydraulic oil (supply of hydraulic pressure) from the manual valve 53, that is, the oil path Lpd, and supplies inflow of hydraulic oil from the oil path Lep, that is, to the manual valve 53. (Supplying hydraulic pressure) is prohibited.

  In the embodiment, the mounting state of the switching valve 70 is the second state (the left half state in FIG. 5) in which the hydraulic pressure Pemop from the electromagnetic pump 60 can be supplied to the clutch C1. That is, in the mounted state of the switching valve 70, the spool 71 is biased upward in the figure by the biasing force of the spring 72, and the second input port 74 communicating with the discharge port 62 of the electromagnetic pump 60 via the oil passage Lep and the output A port 78 is communicated. Further, the switching valve 70 supplies the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 to the clutch C1 when the hydraulic control device 50 is normal and the oil pump 29 is driven by the power from the engine 12. The first state (the state on the right half in FIG. 5) is made possible. That is, when the hydraulic control device 50 is normal and the oil pump 29 is generating hydraulic pressure, the first input port 73 and the output port 78 that communicate with the output port of the linear solenoid valve SLC1 through the oil passage communicate with each other. Is done.

  As described above, when the oil pump 29 is driven by the power from the engine 12, the modulator pressure Pmod from the modulator valve 52 is supplied to the first valve pressure input port 75 as the signal pressure. When the forward travel shift range such as the drive range is selected, the line pressure PL (Pd) from the manual valve 53 is further supplied as the signal pressure to the third signal pressure input port 77, and the B1 linear solenoid valve SLB1 operates. If so, the B1 solenoid valve pressure Pslb1 is further supplied to the second signal pressure input port 76 as a signal pressure. Therefore, the spring constant of the spring 72 of the switching valve 70, the pressure receiving surface of the modulator pressure Pmod of the spool 71, the pressure receiving surface of the B1 solenoid valve pressure Pslb1, and the pressure receiving surface of the line pressure PL (Pd) facing the third signal pressure input port 77. When the oil pump 29, the hydraulic control device 50, etc. are normal and the oil pump 29 is driven by the power from the engine 12 and the drive range is selected (normal), the modulator pressure Pmod The thrust applied to the spool 71 by the action is based on the thrust applied to the spool 71 by the action of the urging force of the spring 72 and the B1 solenoid valve pressure Pslb1 (for example, a predetermined pressure slightly higher than the above-described normal upper limit pressure) and the manual valve 53. Line pressure PL (Pd: for example) supplied to the third signal pressure input port 77 It is determined that the thrust applied to the spool 71 is overcome by the action of the B1 solenoid valve pressure Pslb1 when the pressure is the predetermined pressure, and the first input port 73 and the output port 78 are communicated with each other. ing. As a result, when the supply state of the C1 solenoid valve pressure Pslc1 from the hydraulic control device 50, that is, the C1 linear solenoid valve SLC1, is normal, the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 with the engagement of the brake B1. Is supplied to the switching valve 70 as a signal pressure, the switching valve 70 does not execute switching from the first state to the second state.

  Furthermore, when the oil pump 29 is driven by the engine 12, the switching valve 70 of the embodiment causes the output pressure of the B1 linear solenoid valve SLB1 having a relatively low normal upper limit pressure to be higher than the normal upper limit pressure and the modulator pressure Pmod. By setting the switching pressure (for example, the maximum output pressure) that is higher and lower than the maximum output pressure of the B1 linear solenoid valve SLB1, the first input port 73 and the output port 78 communicate with each other from the first state. Switching to the second state in which the input port 74 and the output port 78 are communicated is performed. That is, the spring constant of the spring 72 of the switching valve 70, the pressure receiving surface of the modulator pressure Pmod of the spool 71, the pressure receiving surface of the B1 solenoid valve pressure Pslb1, and the pressure receiving surface of the line pressure PL (Pd) facing the third signal pressure input port 77 are: When the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 is set to the switching pressure, the urging force by the spring 72 and the B1 solenoid valve pressure Pslb1 (switching pressure) are satisfied. The spool is caused by the action of the thrust applied to the spool 71 by the action and the line pressure PL (Pd: line pressure when the B1 solenoid valve pressure Pslb1 is the switching pressure) supplied from the manual valve 53 to the third signal pressure input port 77. The thrust applied to 71 is the modulator pressure Pmod And overcomes the thrust applied to the spool 71, defined thereby so passed the output port 78 are communicated with the second input port 74 by use.

  Next, the operation of the hydraulic control device 50 when the forward travel shift range is selected by the driver of the automobile 10 equipped with the power transmission device 20 will be described.

  When the forward travel shift range such as the drive range is selected by the driver, the engine 12 is operated and the oil pump 29 is driven by the power from the engine 12, so that the line pressure PL is set by the primary regulator valve 51. The modulator valve 52 generates a constant modulator pressure Pmod, and at least one of the linear solenoid valves SLC1, SLC2, and SLB1 generates hydraulic pressure. If the hydraulic control device 50 is normal and the engine 12 is operating, even if the B1 linear solenoid valve SLB1 generates the B1 solenoid valve pressure Pslb1, it is applied to the spool 71 by the action of the modulator pressure Pmod. The thrust applied is applied to the spool 71 by the thrust applied to the spool 71 by the urging force of the spring 72 and the B1 solenoid valve pressure Pslb1 and the line pressure PL (Pd) from the third signal pressure input port 77. Therefore, the first input port 73 and the output port 78 of the switching valve 70 are communicated with each other. Therefore, if the C1 linear solenoid valve SLC1 generates the C1 solenoid valve pressure Pslc1, the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 is supplied to the clutch C1 via the switching valve 70 in the first state. Thereby, the clutch C1 is engaged.

  Further, for example, when the automobile 10 is stopped while waiting for a signal, the engine ECU 14 executes an automatic start / stop process to stop the operation of the engine 12. At this time, since the drive of the oil pump 29 is stopped along with the operation stop of the engine 12, the line pressure PL is lowered, and is engaged when the first speed (and the second speed) of the automatic transmission 30 is set. The C1 linear solenoid valve SLC1 corresponding to the clutch C1 serving as the starting clutch also cannot generate the hydraulic pressure (C1 solenoid valve pressure Pslc1). For this reason, the switching valve 70 according to the embodiment is configured so that the attached state is in the second state in which the hydraulic pressure Pemop from the electromagnetic pump 60 can be supplied to the clutch C1. That is, when the drive of the oil pump 29 is stopped and the line pressure PL decreases, the modulator pressure Pmod and the B1 solenoid valve pressure Pslb1 due to the B1 linear solenoid valve SLB1 also decrease, so the switching valve 70 is attached by the urging force of the spring 72. Returning to the state (second state), the second input port 74 and the output port 78 communicating with the discharge port 62 of the electromagnetic pump 60 and the oil passage Lep are thereby communicated.

  In the embodiment, the rotational speed of the engine 12 when the discharge pressure of the oil pump 29 becomes a predetermined value or less is determined as a threshold value Nref (for example, a value of about 1000 to 1500 rpm). Under control, the coil of the solenoid unit 64 of the electromagnetic pump 60 until the rotational speed of the engine 12 exceeds the threshold value Nref or a predetermined value slightly higher than the threshold value Nref after restart from the stage when the rotational speed of the engine 12 becomes equal to or less than the threshold value Nref. Is applied to the second input port 74 of the switching valve 70 via the discharge port 62 and the oil passage Lep. Will be. As a result, hydraulic oil (hydraulic pressure Pemop) from the electromagnetic pump 60 can be supplied to the clutch C1 via the switching valve 70, and the engine 12 is operated when the forward travel shift range such as the drive range is selected by the driver. Even if the operation is stopped, the hydraulic pressure Pemop from the electromagnetic pump 60 can be supplied to the clutch C1 which is a start clutch, and the automatic transmission 30 can be kept in the start standby state. Note that when the automatic start / stop processing is executed by the engine electronic control unit 14 and the operation of the engine 12 is stopped, it is not necessary to keep the clutch C1 in a completely engaged state. For this reason, in the embodiment, as the electromagnetic pump 60, the clutch C1 can be set to a state immediately before engagement (immediately before completion of engagement) while the operation of the engine 12 is stopped (to the extent that the stroke in the hydraulic actuator can be eliminated). The one that can generate the hydraulic pressure is used.

  Here, in the hydraulic control device 50 described above, a C1 linear solenoid valve such as a failure of the C1 linear solenoid valve SLC1 or a blockage of an oil passage between the output port of the C1 linear solenoid valve SLC1 and the first input port 73 of the switching valve 70 is obtained. If an abnormality occurs in the supply state of the C1 solenoid valve pressure Pslc1 from the SLC1, the C1 solenoid valve pressure Pslc1 cannot be supplied to the clutch C1. At this time, if no countermeasures are taken, the clutch C1 cannot be engaged, and there is a risk that the vehicle 10 may start and run. For this reason, the shift ECU 21 of the embodiment is abnormal in the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 based on the detection value of a pressure sensor (not shown) while the ignition switch of the automobile 10 is turned on. Is determined, and if it is determined that an abnormality has occurred in the supply state of the C1 solenoid valve pressure Pslc1, the engine 12 is operating, that is, the oil pump 29 is being driven. Under these conditions, the B1 linear solenoid valve SLB1 is controlled so that the B1 solenoid valve pressure Pslb1 becomes the switching pressure described above. Thus, when the B1 solenoid valve pressure Pslb1 is set to the switching pressure, the B1 solenoid valve pressure Pslb1 is supplied from the shuttle valve 54 as the maximum pressure Pmax to the primary regulator valve 51. Therefore, a line generated by the primary regulator valve 51 is generated. The pressure PL itself will also increase.

  Thus, when the B1 solenoid valve pressure Pslb1 is set to the switching pressure, the biasing force by the spring 72, the thrust applied to the spool 71 by the action of the B1 solenoid valve pressure Pslb1, that is, the switching pressure, and the third signal from the manual valve 53 The thrust applied to the spool 71 by the action of the line pressure PL (line pressure when the B1 solenoid valve pressure Pslb1 is the switching pressure) supplied to the pressure input port 77 is given to the spool 71 by the action of the modulator pressure Pmod. Thus, the switching valve 70 forms a second state in which the second input port 74 and the output port 78 are communicated. When the engine 12 is operated and a forward travel shift range such as a drive range is selected, no hydraulic pressure is generated by the electromagnetic pump 60, but the line pressure PL from the manual valve 53 is not a check valve. 56 and a part of the oil passage Lep are supplied to the second input port 74 of the switching valve 70, so that the oil pump 29 does not depend on the oil pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. The line pressure PL (Pd), which is a hydraulic pressure based on the hydraulic pressure, is supplied to the clutch C1.

  As a result, in the automobile 10 equipped with the power transmission device 20, the C1 linear solenoid valve SLC1 should fail, or the oil path between the output port of the C1 linear solenoid valve SLC1 and the first input port 73 of the switching valve 70. The line pressure PL (Pd) based on the hydraulic pressure from the oil pump 29 does not depend on the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1 to the clutch C1 via the switching valve 70 Therefore, it is possible to maintain the engagement of the clutch C1. At this time, the clutch C1 is engaged, and the brake B1 corresponding to the B1 linear solenoid valve SLB1 is engaged as the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 becomes the switching pressure. Combined. Therefore, according to the hydraulic control device 50, an abnormality occurs in the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1, and the C1 solenoid valve pressure Pslc1 is supplied from the C1 linear solenoid valve SLC1 to the clutch C1 due to the abnormality. Even if it is not possible, the second speed of the automatic transmission 30 is set by the switching valve 70 forming the second state as the B1 solenoid valve pressure Pslb1 is increased (see FIG. 3). Start and forward travel can be sufficiently ensured.

  As described above, in the hydraulic control apparatus 50 according to the embodiment, when the oil pump 29 is driven by the engine 12 and the supply state of the hydraulic pressure from the C1 linear solenoid valve SLC1 is normal, the clutch C1 has the C1 linear solenoid. A first state in which the C1 solenoid valve pressure Pslc1 from the valve SLC1 can be supplied is formed by the switching valve 70. Further, the switching valve 70 drives the B1 solenoid valve pressure from the B1 linear solenoid valve SLB1 when the oil pump 29 is driven by the engine 12 and an abnormality occurs in the hydraulic pressure supply state from the C1 linear solenoid valve SLC1. Using Pslb1 as a signal pressure, the clutch C1 can be supplied with a line pressure PL (Pd) based on the hydraulic pressure from the oil pump 29, which is a hydraulic pressure independent of the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. The second state is formed.

  Thus, when an abnormality occurs in the supply state of the hydraulic pressure from the C1 linear solenoid valve SLC1, the second state is formed by the switching valve 70, and the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. The line pressure PL (Pd), which is a hydraulic pressure that does not depend on the pressure, is supplied to the clutch C1, and the clutch C1 is thus engaged even if an abnormality occurs in the hydraulic pressure supply state from the C1 linear solenoid valve SLC1. Can be maintained. Then, when an abnormality occurs in the supply state of the hydraulic pressure from the C1 linear solenoid valve SLC1, the switching from the first state to the second state is performed using the hydraulic pressure from the B1 linear solenoid valve SLB1 as a signal pressure. If it does, it will become unnecessary to prepare the solenoid valve etc. for exclusive use at the time of abnormality occurrence for the switch from the said 1st state to a 2nd state, Thereby, a cost increase and the enlargement of an apparatus can be suppressed. Note that the hydraulic pressure supplied to the clutch C1 when an abnormality occurs in the supply state of the C1 solenoid valve pressure Pslc1 is not limited to the line pressure PL (Pd) from the manual valve 53, but the C1 linear solenoid valve SLC1. Other pressures such as the modulator pressure Pmod may be used as long as they are based on the oil pressure from the oil pump 29 that does not depend on the generation state of the oil pressure.

  Further, the switching valve 70 supplies the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 as the signal pressure with the engagement of the brake B1 when the hydraulic pressure supply state from the C1 linear solenoid valve SLC1 is normal. Even so, the switching from the first state to the second state is not performed. As a result, when the hydraulic pressure supply state from the C1 linear solenoid valve SLC1 is normal, the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1 is changed with the generation of the hydraulic pressure by the B1 linear solenoid valve SLB1. It is possible to prevent the line pressure PL (Pd) as an independent hydraulic pressure from being supplied to the clutch C1.

  Further, the switching valve 70 has a spool 71 that is biased by a spring 72 so as to form a second state when the oil pump 29 is not driven by the engine 12, and a modulator pressure Pmod, a B1 solenoid valve pressure Pslb1, and a manual operation. The spool valve is supplied with the line pressure PL (Pd) from the valve 53 as a signal pressure. Then, when the engine 12 is operated and the oil pump 29 is driven and the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 is normal, the hydraulic pressure control device 50 is driven by the modulator pressure Pmod. The thrust applied to 71 is applied to the spool 71 by the operation of the urging force of the spring 72 and the B1 solenoid valve pressure Pslb1, and the thrust applied to the spool 71 by the operation of the line pressure PL (Pd) from the manual valve 53. The switching valve 70 is configured to form the first state by overcoming the above. Further, the hydraulic control device 50 is operated by the shift ECU 21 when the engine 12 is operated and the oil pump 29 is driven and the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 is abnormal. With the control of the B1 linear solenoid valve SLB1, the line pressure PL and the B1 solenoid valve pressure Pslb1 are increased, the urging force by the spring 72, the thrust applied to the spool 71 by the action of the B1 solenoid valve pressure Pslb1, and the manual valve 53 The switching valve 70 is also configured to form the second state by overcoming the thrust applied to the spool 71 by the action of the modulator pressure Pmod with the thrust applied to the spool 71 by the action of the line pressure PL (Pd). ing.

  Thus, the supply of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 regardless of whether or not the B1 solenoid valve pressure Pslb1 is supplied from the B1 linear solenoid valve SLB1 to the brake B1 (the generation state of the B1 solenoid valve pressure Pslb1). The first state can be formed when the state is normal, and the second state can be formed when the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 is abnormal. . Further, when the line pressure PL (Pd) from the manual valve 53 is supplied as a signal pressure to the switching valve 70, an abnormality has occurred in the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1. The second state can be more reliably formed. Note that, for example, in a hydraulic control device that is driven by hydraulic pressure from a linear solenoid valve in which the primary regulator valve 51 regulates and outputs hydraulic oil from the oil pump 29 side, the B1 solenoid valve pressure Pslb1 becomes the switching pressure described above. When controlling the B1 linear solenoid valve SLB1, the linear solenoid valve may be controlled so that the line pressure PL increases together with the B1 solenoid valve pressure Pslb1 (however, only the B1 solenoid valve pressure Pslb1 is increased to increase the line pressure PL. May be omitted). Further, when the B1 solenoid valve pressure Pslb1 as the signal pressure can be set sufficiently high to execute the switching from the first state to the second state, the line pressure PL (Pd as the signal pressure for the switching valve 70 is set. ) May be omitted. Further, the signal pressure to the third signal pressure input port 77 of the switching valve 70 may be a pressure other than the line pressure PL (Pd).

  Further, the switching valve 70 described above is a single body, and when the oil pump 29 as a mechanical pump is driven by the engine 12 as a power generation source, the hydraulic pressure from the C1 linear solenoid valve SLC1 as the first solenoid valve. Can be supplied to the clutch C1 as the first hydraulic friction engagement element, and the hydraulic pressure Pemop from the electromagnetic pump 60 as the electric pump can be supplied to the clutch C1 when the oil pump 29 is not driven by the engine 12. When the pump 29 is driven by the engine 12 and an abnormality occurs in the hydraulic pressure supply state from the clutch C1, the oil pump 29 does not depend on the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. Line pressure PL (P ) And it is to be supplied to the clutch C1. Therefore, by adopting the switching valve 70, it is possible to further reduce the size of the hydraulic control device 50 and thus the entire power transmission device 20.

  Further, the clutch C1 is engaged when the first speed and the second speed of the automatic transmission 30 are set, and the brake B1 is set to the second speed of the automatic transmission 30. Sometimes engaged. Therefore, in the automobile 10 equipped with the power transmission device 20 including the hydraulic control device 50, hydraulic pressure is supplied from the C1 linear solenoid valve SLC1 to the clutch C1 due to an abnormality in the supply state of the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1. Even if it becomes impossible, the second state is formed by using the hydraulic pressure from the B1 linear solenoid valve SLB1, and the engagement of the clutch C1 is maintained by the line pressure PL (Pd) from the manual valve 53 and the brake B1 is engaged. In combination, it is possible to guarantee start and forward travel at the second speed.

  Moreover, in the said Example, what can generate | occur | produce the hydraulic pressure of the grade which can set the clutch C1 as a starting clutch to the state just before engagement as the electromagnetic pump 60 is employ | adopted. If the electromagnetic pump 60 having such a performance is employed, the automatic transmission 30 can be appropriately maintained in the start standby state between the time when the engine 12 is stopped and the time when the engine 12 is restarted. By reducing the performance (pump capacity) required for 60, the electromagnetic pump 60 and thus the entire power transmission device 20 can be reduced in size. In addition, by using the electromagnetic pump 60 as in the above-described embodiment, it is possible to further reduce the size of the hydraulic control device 50 and thus the entire power transmission device 20, but an electric pump is used instead of the electromagnetic pump 60. Needless to say, it may be. Further, in the hydraulic control device 50 of the embodiment, the oil passage Lep and the oil passage Lpd are connected via the check valve 56, but instead of the check valve 56, for example, C1 from the C1 linear solenoid valve SLC1. An open / close valve that is opened when it is determined that an abnormality has occurred in the supply state of the solenoid valve pressure Pslc1 may be disposed between the oil passage Lep and the oil passage Lpd.

  FIG. 7 is a system diagram showing a main part of a hydraulic control device 50B according to a modification. In the following description, the same reference numerals are assigned to the same elements as those described in relation to the automobile 10, the power transmission device 20, the hydraulic control device 50, etc., and the duplicate description is omitted. To do.

  The hydraulic control apparatus 50B according to the modification includes a first switching valve 701 and a second switching valve 702 instead of the single switching valve 70. The first switching valve 701 is a first slidably disposed in the valve body, a spool 711, a spring 721 that biases the spool 711, and an output port of the C1 linear solenoid valve SLC 1 through an oil passage. The input port 731 includes a second input port 741 communicating with the discharge port 62 of the electromagnetic pump 60 via an oil passage, and a signal pressure input port 751 communicating with the output port of the modulator valve 52 via an oil passage. The attached state of the first switching valve 701 is a state in which the hydraulic pressure Pemop from the electromagnetic pump 60 can be supplied to the output port 781 (the left half state in FIG. 7). That is, in the attached state of the first switching valve 701, the spool 711 is biased upward in the figure by the biasing force of the spring 721, and the second input port 741 communicated with the discharge port 62 of the electromagnetic pump 60 via the oil passage. The output port 781 is communicated. The first switching valve 701 is applied to the spool 711 by the action of the modulator pressure Pmod from the modulator valve 52 when the hydraulic control device 50B is normal and the oil pump 29 is driven by the power from the engine 12. The generated thrust overcomes the urging force of the spring 721, thereby forming a state in which the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 can be supplied to the output port 781 (the state on the right half in FIG. 7). It is configured. That is, when the hydraulic control device 50B is normal and the oil pump 29 is generating hydraulic pressure, the first input port 731 and the output port 781 communicate with the output port of the linear solenoid valve SLC1 via the oil passage. Is done.

  The second switching valve 702 includes a spool 712 that is slidably disposed in the valve body, a spring 722 that biases the spool 712, and a first input port 732 that communicates with the output port 781 of the first switching valve 701. The second input port 742 communicating with the drive range output port of the manual valve 53 via the oil path, the signal pressure input port 762 communicating with the output port of the B1 linear solenoid valve SLB1 via the oil path, and the clutch C1 An output port 782 communicating with the hydraulic inlet through an oil passage is included. The mounting state of the second switching valve 702 is a state where the hydraulic pressure from the first input port 732 can be supplied to the output port 782 (the left half state in FIG. 7). That is, when the second switching valve 702 is attached, the spool 712 is biased upward in the figure by the biasing force of the spring 722, and the first input port 732 and the output port 781 communicate with the output port 781 of the first switching valve 701. And communicated with each other.

  The second switching valve 702 is maintained in the mounted state when the oil pump 29 is driven by the engine 12 and the B1 solenoid valve pressure Pslb1 is generated by the B1 linear solenoid valve SLB1 as the brake B1 is engaged. In addition, when the output pressure of the B1 linear solenoid valve SLB1 is set to the above-described switching pressure when the oil pump 29 is driven by the engine 12, the hydraulic pressure from the second input port 742 can be supplied to the output port 782. (A state on the right half in FIG. 7). That is, the spring constant of the spring 722 of the second switching valve 702 and the pressure receiving surface of the B1 solenoid valve pressure Pslb1 of the spool 712 are generated by the B1 linear solenoid valve SLB1 when the B1 linear solenoid valve SLB1 is engaged with the brake B1. When the biasing force by the spring 722 overcomes the thrust applied to the spool 712 by the action of the B1 solenoid valve pressure Pslb1, the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 is set to the switching pressure. It is determined that the thrust applied to the spool 712 by the action of the solenoid valve pressure Pslb1 (switching pressure) overcomes the urging force of the spring 722, and the second input port 742 and the output port 782 are thereby communicated. .

  Thus, when the hydraulic control device 50B is normal and the oil pump 29 is driven by the power from the engine 12, the thrust applied to the spool 711 by the action of the modulator pressure Pmod overcomes the urging force of the spring 721. The first input port 731 and the output port 781 of the first switching valve 701 communicate with each other, and whether or not the B1 solenoid valve pressure Pslb1 is supplied from the B1 linear solenoid valve SLB1 to the brake B1 (generation of the B1 solenoid valve pressure Pslb1) Regardless of the state, the first input port 732 and the output port 782 of the second switching valve 702 communicate with each other. Therefore, when the hydraulic control device 50B is normal and the oil pump 29 is driven by the power from the engine 12, the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1 can be supplied to the clutch C1. When the hydraulic control device 50B is normal and the oil pump 29 is not driven by the power from the engine 12, the urging force of the spring 721 overcomes the thrust applied to the spool 711 by the action of the modulator pressure Pmod. The second input port 741 and the output port 781 of the switching valve 701 are in communication with each other, and the second switching valve 702 is maintained in an attached state in which the first input port 732 and the output port 782 are in communication. Therefore, when the hydraulic control device 50B is normal and the oil pump 29 is not driven by the power from the engine 12, the electromagnetic pump 60 is operated to switch the hydraulic pressure Pemop from the electromagnetic pump 60 to the first and second switching modes. Supply to the clutch C1 is possible via the valves 701 and 702. As a result, even if the engine 12 is stopped when the forward driving shift range such as the drive range is selected by the driver, the hydraulic pressure Pemop from the electromagnetic pump 60 is supplied to the clutch C1 that is the starting clutch to automatically shift. The machine 30 can be kept in the start standby state.

  Further, when it is determined that there is an abnormality in the supply state of the C1 solenoid valve pressure Pslc1, the B1 solenoid valve is operated on condition that the engine 12 is operated, that is, the oil pump 29 is driven. If the B1 linear solenoid valve SLB1 is controlled so that the pressure Pslb1 becomes the above-mentioned switching pressure, the thrust applied to the spool 712 by the action of the B1 solenoid valve pressure Pslb1 (switching pressure) overcomes the urging force of the spring 722. Thus, the second input port 742 and the output port 782 of the second switching valve 702 are communicated with each other. When the engine 12 is operated and the forward travel shift range such as the drive range is selected, no hydraulic pressure is generated by the electromagnetic pump 60, but the line pressure PL from the manual valve 53 is switched to the second level. Since it is supplied to the second input port 742 of the valve 702, the line pressure PL (Pd), which is the hydraulic pressure based on the hydraulic pressure from the oil pump 29 that does not depend on the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. ) Can be supplied to the clutch C1.

  As a result, even by the hydraulic control device 50B, the C1 linear solenoid valve SLC1 is broken or the oil path between the output port of the C1 linear solenoid valve SLC1 and the first input port 731 of the first switching valve 701 is blocked. However, the line pressure PL (Pd) based on the hydraulic pressure from the oil pump 29 does not depend on the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1 to the clutch C1 via the second switching valve 702. And the engagement of the clutch C1 can be maintained. As described above, when an abnormality occurs in the supply state of the hydraulic pressure from the C1 linear solenoid valve SLC1, an abnormality occurs if the state of the second switching valve 702 is switched using the hydraulic pressure from the B1 linear solenoid valve SLB1 as a signal pressure. There is no need to prepare a solenoid valve dedicated to the time, thereby suppressing an increase in cost and an increase in the size of the apparatus. Note that the hydraulic pressure supplied to the signal pressure input port 762 of the second switching valve 702 is not limited to the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1. Also in the modification, the hydraulic pressure supplied to the clutch C1 when the supply state of the C1 solenoid valve pressure Pslc1 is abnormal is not limited to the line pressure PL (Pd) from the manual valve 53.

  Here, the correspondence between the main elements of the embodiments and the modified examples and the main elements of the invention described in the column of means for solving the problems will be described. That is, in the above-described embodiments and modifications, the power applied to the input shaft 31 as the input member is changed to a plurality of speed ratios by engaging / disengaging the clutches C1 to C3 and the brakes B1 and B3, and the output as the output member is output. The hydraulic control devices 50 and 50B of the power transmission device 20 including the automatic transmission 30 capable of transmitting to the shaft 37 correspond to a “hydraulic control device”, and a C1 solenoid valve to the clutch C1 as a first hydraulic friction engagement element. The C1 linear solenoid valve SLC1 that generates the pressure Pslc1 corresponds to the “first solenoid valve”, and the B1 linear solenoid valve SLB1 that generates the B1 solenoid valve pressure Pslb1 to the brake B1 as the second hydraulic friction engagement element is “ Corresponding to "second solenoid valve", from C1 linear solenoid valve SLC1 When the pressure supply state is normal, a first state is established in which the clutch C1 can be supplied with the C1 solenoid valve pressure Pslc1 from the C1 linear solenoid valve SLC1, and the hydraulic pressure supply state from the C1 linear solenoid valve SLC1 is abnormal. Is generated, the B1 solenoid valve pressure Pslb1 from the B1 linear solenoid valve SLB1 is used as a signal pressure, and the clutch C1 has a hydraulic pressure that does not depend on the hydraulic pressure generation state of the C1 linear solenoid valve SLC1 and the B1 linear solenoid valve SLB1. The switching valve 70 and the second switching valve 702 that form a second state in which a certain line pressure PL (Pd) can be supplied correspond to a “switching valve”. However, the correspondence relationship between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is described in the column of means for the embodiment etc. to solve the problem. The embodiment for carrying out the invention is an example for specifically explaining the embodiment, and does not limit the elements of the invention described in the column of means for solving the problem. In other words, the examples and the like are merely specific examples of the invention described in the column of means for solving the problem, and the interpretation of the invention described in the column of means for solving the problem is not limited to that column. This should be done based on the description.

  As mentioned above, although the embodiment of the present invention has been described using examples, the present invention is not limited to the above-described examples, and various modifications can be made without departing from the scope of the present invention. Needless to say.

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

  10 automobiles, 12 engines, 14 electronic control units for engines (engine ECUs), 15 electronic control units for brakes (brake ECUs), 16 crankshafts, 18 front covers, 20 power transmission devices, 21 electronic control units for transmissions (transmission ECUs) ), 22 Transmission case, 23 Fluid transmission device, 24 Pump impeller, 25 Turbine runner, 26 Stator, 27 One-way clutch, 28 Lock-up clutch, 29 Oil pump, 30 Automatic transmission, 31 Input shaft, 32 Ravigneaux planetary gear mechanism 33a, 33b Sun gear, 34 Ring gear, 35a Short pinion gear, 35b Long pinion gear, 36 Carrier, 37 Output shaft, 38 Gear mechanism, 39 Differential mechanism, 5 , 50B Hydraulic control device, 51 Primary regulator valve, 52 Modulator valve, 53 Manual valve, 54 Shuttle valve, 55 Apply valve, 56 Check valve, 60 Electromagnetic pump, 61 Suction port, 62 Discharge port, 63 Sleeve, 63e End plate , 64 Solenoid part, 65 shaft, 66 check valve for suction, 67 check valve for discharge, 68 pump chamber, 69, 72, 721, 722 spring, 70 switching valve, 71, 711, 712 spool, 73, 731, 732 First input port, 74, 741, 742 Second input port, 75 First signal pressure input port, 76 Second signal pressure input port, 77 Third signal pressure input port, 78, 781, 782 Output port, 79 port 91 accelerator pedal, 92 accelerator pedal Pedal position sensor, 93 brake pedal, 94 master cylinder pressure sensor, 95 shift lever, 96 shift range sensor, 99 vehicle speed sensor, 701 first switching valve, 702 second switching valve, 751, 762 signal pressure input port, B1, B3 brake, C1, C2, C3 clutch, F2 one-way clutch, SLC1 C1 linear solenoid valve, SLC2 C2 linear solenoid valve, SLB1 B1 linear solenoid valve.

Claims (7)

In a hydraulic control device for a transmission that can transmit power applied to an input member to an output member by changing a gear ratio to a plurality of stages by engaging and disengaging a plurality of hydraulic friction engagement elements,
A first solenoid valve that generates hydraulic pressure to a first hydraulic friction engagement element of the plurality of hydraulic friction engagement elements;
A second solenoid valve for generating hydraulic pressure to a second hydraulic friction engagement element among the plurality of hydraulic friction engagement elements;
When the supply state of the hydraulic pressure from the first solenoid valve is normal, the first hydraulic friction engagement element forms a first state in which the hydraulic pressure from the first solenoid valve can be supplied, and When an abnormality occurs in the supply state of the hydraulic pressure from one solenoid valve, the first and second solenoids are applied to the first hydraulic friction engagement element by using the hydraulic pressure from the second solenoid valve as a signal pressure. A switching valve that forms a second state that enables supply of hydraulic pressure independent of the generation state of the hydraulic pressure of the valve;
A hydraulic control device comprising: The hydraulic control device according to claim 1,
The switching valve is normally supplied with the hydraulic pressure from the first solenoid valve, and the hydraulic pressure from the second solenoid valve is supplied as a signal pressure as the second hydraulic friction engagement element is engaged. The hydraulic control device is configured not to execute switching from the first state to the second state when being performed. In the hydraulic control device according to claim 2,
A regulator valve that regulates the hydraulic pressure from the hydraulic pressure source to generate line pressure;
A modulator valve that regulates the line pressure to generate a constant modulator pressure;
The first solenoid valve regulates the line pressure to generate a first solenoid valve pressure to the first hydraulic friction engagement element, and the second solenoid valve regulates the line pressure to adjust the second pressure. Generating a second solenoid valve pressure to the hydraulic friction engagement element;
The hydraulic pressure independent of the generation state of the hydraulic pressure of the first and second solenoid valves is the line pressure,
The switching valve has a spool biased by a spring, and is a spool valve to which at least the modulator pressure and the second solenoid valve pressure are supplied as signal pressures.
When the supply state of hydraulic pressure from the first solenoid valve is normal, the thrust applied to the spool by the action of the modulator pressure is applied to the spool by the biasing force of the spring and the action of at least the second solenoid valve pressure. The switching valve forms the first state by overcoming the thrust generated, and the second solenoid valve pressure is increased when an abnormality occurs in the hydraulic pressure supply state from the first solenoid valve. The switching valve is in the second state when the urging force of the spring and at least the thrust applied to the spool by the action of the second solenoid valve pressure overcome the thrust applied to the spool by the action of the modulator pressure. The hydraulic control device is configured to form . In the hydraulic control device according to claim 3,
The switching valve is further supplied with the line pressure as a signal pressure,
When the supply state of the hydraulic pressure from the first solenoid valve is normal, the thrust applied to the spool by the action of the modulator pressure is applied to the spool by the urging force of the spring and the action of the second solenoid valve pressure. The switching valve forms the first state by overcoming the thrust applied to the spool by the action of the line pressure and an abnormality in the hydraulic pressure supply state from the first solenoid valve. When at least the second solenoid valve pressure is increased, the biasing force by the spring, the line pressure, and the thrust applied to the spool by the action of the second solenoid valve pressure are caused by the action of the modulator pressure. By overcoming the thrust applied to the switching valve, the switching valve Hydraulic control apparatus characterized by being configured to form a state. The hydraulic control device according to claim 4,
The switching valve includes a first input port to which the first solenoid valve pressure is supplied, a second input port to which the line pressure is supplied, a first signal pressure input port to which the modulator pressure is supplied, A second signal pressure input port to which a second solenoid valve pressure is supplied; a third signal pressure input port to which the line pressure is supplied; and an output port in communication with a hydraulic inlet of the first hydraulic friction engagement element. And the thrust applied to the spool by the action of the modulator pressure is applied to the spool by the action of the biasing force by the spring and the action of the second solenoid valve pressure and the line pressure. The first input port communicates with the output port when the generated thrust is overcome, and the urging force by the spring and the second When the thrust applied to the spool by the action of the noid valve pressure and the thrust applied to the spool by the action of the line pressure overcome the thrust applied to the spool by the action of the modulator pressure, the second A hydraulic control apparatus, wherein an input port and the output port are communicated with each other. The hydraulic control device according to claim 5,
A manual valve that can switch the supply destination of the line pressure from the regulator valve according to a selected shift range;
The hydraulic pressure control device, wherein the line pressure is supplied to the second input port and the third signal pressure input port of the switching valve via the manual valve when the forward travel shift range is selected. . In the hydraulic control device according to any one of claims 1 to 6,
The first hydraulic friction engagement element is engaged at least when a first speed and a second speed of the transmission device are set, and the second hydraulic friction engagement element is at least the transmission device of the transmission device. A hydraulic control device that is engaged when the second speed is set.

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