Hydraulic control device

This application is a National Stage of International Application No. PCT/JP2012/054993 filed Feb. 28, 2012, disclosure of Japanese Patent Application No. 2011-074004 filed on Mar. 30, 2011 including the specification, drawings and abstract is incorporated herein by reference in its entirety.

The present invention relates to a hydraulic control device for a speed change device capable of transferring power applied to an input member to an output member at a speed change ratio that is changeable in a plurality of stages by engaging and disengaging a plurality of hydraulic friction engagement elements.

Hitherto, there has been known a hydraulic control device including a first solenoid valve capable of supplying a first hydraulic pressure to a first friction engagement element, a second solenoid valve capable of supplying a second hydraulic pressure to a second friction engagement element, and a third solenoid valve capable of supplying a third hydraulic pressure to a third friction engagement element, in which the second friction engagement element is engaged at higher shift speeds, a low shift speed which is one of lower shift speeds is established through engagement of the first friction engagement element and the third friction engagement element, and a high shift speed which is one of the higher shift speeds is established through engagement of the second friction engagement element and the third friction engagement element (see Japanese Patent Application Publication No. 2010-84855 (JP 2010-84855 A), for example). In the hydraulic control device, the first to third solenoid valves are of a normally closed type, and thus do not output the first to third hydraulic pressures when the solenoid valves are not energized. The hydraulic control device also includes a solenoid valve of a normally open type that is energized during normal travel and that outputs a signal hydraulic pressure when the solenoid valve is not energized, a preliminary shift speed switching valve that is switched between a lower shift speed position, at which a first preliminary hydraulic pressure (forward range pressure) for the first friction engagement element is output, and a higher shift speed position, at which a second preliminary hydraulic pressure (forward range pressure) for the second friction engagement element is output, in accordance with the state of engagement of the second friction engagement element, and a hydraulic pressure supply switching valve that is switched from a normal-time position, at which the first to third hydraulic pressures may be supplied to the first to third friction engagement elements, respectively, to a failure-time position, at which the first and second preliminary hydraulic pressures may be supplied to the first and second friction engagement elements, respectively, and a line pressure may be supplied to the third friction engagement element, during a failure in which the solenoid valve outputs the signal hydraulic pressure (not energized).

In the hydraulic control device according to the related art described above, the hydraulic pressure supply switching valve is switched to the failure-time position when the solenoid valve which outputs the signal hydraulic pressure is not energized, even if the first solenoid valve or the second solenoid valve is energized. In such a case, the first preliminary hydraulic pressure or the second preliminary hydraulic pressure is supplied to the first friction engagement element or the second friction engagement element even if the first solenoid valve or the second solenoid valve can supply a hydraulic pressure to the first friction engagement element or the second friction engagement element, which may cause a shock along with switching in supplied hydraulic pressure.

Thus, it is a main object of the hydraulic control device according to the present invention to enable a hydraulic pressure from an alternative hydraulic pressure source to be supplied to a hydraulic friction engagement element corresponding to a pressure regulation valve during an abnormality in which a hydraulic pressure is not supplied from the pressure regulation valve as normal, and not to allow the hydraulic pressure from the alternative hydraulic pressure source to be supplied to the hydraulic friction engagement element when a hydraulic pressure is supplied from the pressure regulation valve as normal.

In order to achieve the foregoing main object, the hydraulic control device according to the present invention adopts the following means.

An aspect of the present invention provides

a hydraulic control device for a speed change device capable of transferring power applied to an input member to an output member at a speed change ratio that is changeable in a plurality of stages by engaging and disengaging a plurality of hydraulic friction engagement elements, the hydraulic control device characterized by including: a first pressure regulation valve that regulates a hydraulic pressure to be supplied to a first hydraulic friction engagement element; a second pressure regulation valve that regulates a hydraulic pressure to be supplied to a second hydraulic friction engagement element; a line pressure generation valve that regulates a hydraulic pressure from a hydraulic pressure generation source to generate a line pressure; and a switching valve that can establish a first supply state, in which the hydraulic pressure from the first pressure regulation valve can be supplied to the first hydraulic friction engagement element when the first pressure regulation valve is normal, and that can establish a second supply state, in which the line pressure from the line pressure generation valve can be supplied to the first hydraulic friction engagement element during an abnormality in which a hydraulic pressure is not supplied from the first pressure regulation valve as normal, wherein the switching valve is selectively supplied with a first hydraulic pressure and a second hydraulic pressure that is lower than the first hydraulic pressure as a holding pressure, and supplied with the second hydraulic pressure as the holding pressure and supplied with the hydraulic pressure from the second pressure regulation valve during the abnormality, and the switching valve establishes the first supply state, irrespective of presence or absence of the hydraulic pressure from the second pressure regulation valve, when the first hydraulic pressure is supplied as the holding pressure, establishes the first supply state when the second hydraulic pressure is supplied as the holding pressure and the hydraulic pressure from the second pressure regulation valve is not supplied, and establishes the second supply state when the second hydraulic pressure is supplied as the holding pressure and the hydraulic pressure from the second pressure regulation valve is supplied.

The hydraulic control device includes the switching valve which can establish the first supply state, in which the hydraulic pressure from the first pressure regulation valve can be supplied to the first hydraulic friction engagement element when the first pressure regulation valve is normal, and which can establish the second supply state, in which the line pressure from the line pressure generation valve can be supplied to the first hydraulic friction engagement element during an abnormality in which a hydraulic pressure is not supplied from the first pressure regulation valve as normal, and the switching valve is selectively supplied with the first hydraulic pressure and the second hydraulic pressure which is lower than the first hydraulic pressure as a holding pressure, and supplied with the second hydraulic pressure as the holding pressure and supplied with the hydraulic pressure from the second pressure regulation valve during the abnormality. The switching valve establishes the first supply state, irrespective of the presence or absence of the hydraulic pressure from the second pressure regulation valve, when the first hydraulic pressure is supplied as the holding pressure, establishes the first supply state when the second hydraulic pressure is supplied as the holding pressure and the hydraulic pressure from the second pressure regulation valve is not supplied, and establishes the second supply state when the second hydraulic pressure is supplied as the holding pressure and the hydraulic pressure from the second pressure regulation valve is supplied.

By thus supplying the second hydraulic pressure, which is lower than the first hydraulic pressure, as a holding pressure to the switching valve during the abnormality described above, the switching valve can be quickly switched from the first supply state into the second supply state by the hydraulic pressure from the second pressure regulation valve to supply the line pressure from the line pressure generation valve to the first hydraulic friction engagement element, which enables simultaneous engagement of the first hydraulic friction engagement element and the second hydraulic friction engagement element. If the first hydraulic pressure is supplied as a holding pressure to the switching valve when the hydraulic pressure is supplied from the first pressure regulation valve as normal, the switching valve is maintained in the first supply state irrespective of the presence or absence of the hydraulic pressure from the second pressure regulation valve, and the switching valve is maintained in the first supply state even if the second hydraulic pressure is supplied as a holding pressure unless the hydraulic pressure from the second pressure regulation valve is supplied. Thus, with the hydraulic control device, it is possible to supply the line pressure from the line pressure generation valve to the first hydraulic friction engagement element corresponding to the first pressure regulation valve during an abnormality in which a hydraulic pressure is not supplied from the first pressure regulation valve as normal, and not to supply the line pressure from the line pressure generation valve to the first hydraulic friction engagement element when the hydraulic pressure is supplied from the first pressure regulation valve as normal. As a result, it is possible to favorably suppress occurrence of a shock along with switching in supplied hydraulic pressure by suppressing erroneous supply of the line pressure from the line pressure generation valve to the first hydraulic friction engagement element when the hydraulic pressure is supplied from the first pressure regulation valve as normal.

In addition, the first hydraulic pressure may be the line pressure, and the second hydraulic pressure may be a modulator pressure obtained by reducing the line pressure. Consequently, by supplying the first hydraulic pressure to the switching valve as a holding pressure when a hydraulic pressure is supplied from the first pressure regulation valve as normal, it is possible to more reliably maintain the switching valve in the first supply state, and not to supply the line pressure from the line pressure generation valve to the first hydraulic friction engagement element.

The hydraulic control device may further include: a third pressure regulation valve that regulates a hydraulic pressure to be supplied to a third hydraulic friction engagement element that is normally not engaged at the same time as the second hydraulic friction engagement element; a second switching valve that can establish a blocked/discharge state, in which supply of the hydraulic pressure from the third pressure regulation valve to the third hydraulic friction engagement element is blocked and a hydraulic pressure can be discharged from the third hydraulic friction engagement element, and a communicated state, in which the hydraulic pressure from the third pressure regulation valve can be supplied to the third hydraulic friction engagement element, and that can receive a signal pressure for establishing the blocked/discharge state and the communicated state and a hydraulic pressure from the second pressure regulation valve; a third switching valve that can establish a first state, in which the hydraulic pressure from the third pressure regulation valve can be supplied to a fourth hydraulic friction engagement element that is normally not engaged at the same time as the third hydraulic friction engagement element, and a second state, in which the hydraulic pressure from the third pressure regulation valve can be supplied to the third hydraulic friction engagement element and a hydraulic pressure can be discharged from the fourth hydraulic friction engagement element; and a signal pressure output valve that outputs a signal pressure for switching the third switching valve from the first state into the second state when the hydraulic pressure from the third pressure regulation valve is supplied to the third hydraulic friction engagement element and during the abnormality. In the hydraulic control device, the third switching valve may be able to receive the line pressure and the modulator pressure, and supply the line pressure to the switching valve as the holding pressure and supply the line pressure to the second switching valve as the signal pressure when the first state is established, and may supply the modulator pressure to the switching valve as the holding pressure and supply the modulator pressure to the second switching valve as the signal pressure when the second state is established; and the second switching valve may establish the blocked/discharge state when the line pressure is supplied as the signal pressure, establish the communicated state when the modulator pressure is supplied as the signal pressure, and establish the blocked/discharge state when a hydraulic pressure from the second pressure regulation valve is input in the communicated state.

In the hydraulic control device, during an abnormality in which the hydraulic pressure is not supplied from the first pressure regulation valve as normal, the switching valve establishes the second state using the signal pressure from the signal pressure output valve. Consequently, the hydraulic pressure from the third pressure regulation valve can be supplied to the third hydraulic friction engagement element, and a hydraulic pressure can be discharged from the fourth hydraulic friction engagement element, which allows the modulator pressure to be supplied as a holding pressure from the third switching valve to the switching valve and allows the modulator pressure to be supplied as a signal pressure to the second switching valve. This enables the modulator pressure, which serves as the second hydraulic pressure which is lower than the line pressure serving as the first hydraulic pressure, to be supplied as a holding pressure to the switching valve during the abnormality described above. When the third switching valve establishes the second state, in addition, the hydraulic pressure from the third pressure regulation valve can be supplied to the third hydraulic friction engagement element, and the second switching valve is supplied with the modulator pressure as a signal pressure to establish the communicated state in which the hydraulic pressure from the third pressure regulation valve can be supplied to the third hydraulic friction engagement element. When the hydraulic pressure from the second pressure regulation valve is supplied to the second switching valve in the communicated state, however, the second switching valve establishes the blocked/discharge state in which supply of a hydraulic pressure from the third pressure regulation valve to the third hydraulic friction engagement element is blocked and a hydraulic pressure can be discharged from the third hydraulic friction engagement element. Thus, even if the hydraulic pressure is output from the second pressure regulation valve as a hydraulic pressure is no longer supplied from the first pressure regulation valve as normal, the second hydraulic friction engagement element and the third hydraulic friction engagement element are not engaged at the same time as each other.

Moreover, the switching valve may include a spool disposed so as to be axially movable and capable of establishing the first supply state and the second supply state, and a spring that urges the spool; and the spool may include a first pressure receiving surface that receives an urging force of the spring, a second pressure receiving surface that receives the hydraulic pressure from the second pressure regulation valve, and a holding pressure receiving surface that receives the holding pressure. In the case where the thus configured switching valve is used, the first supply state is established with the thrust applied to the spool by the effect of the first hydraulic pressure (line pressure) on the holding pressure receiving surface exceeding the sum of the thrust applied to the spool by the effect of the hydraulic pressure from the second pressure regulation valve on the second pressure receiving surface and the urging force of the spring applied to the spool, or with the thrust applied to the spool by the effect of the second hydraulic pressure (modulator pressure) on the holding pressure receiving surface exceeding the urging force of the spring applied to the spool. Meanwhile, the second supply state is established with the sum of the thrust applied to the spool by the effect of the hydraulic pressure from the second pressure regulation valve on the second pressure receiving surface and the urging force of the spring applied to the spool exceeding the thrust applied to the spool by the effect of the second hydraulic pressure (modulator pressure) on the holding pressure receiving surface.

Furthermore, the hydraulic pressure from the third pressure regulation valve may be applied to the first pressure receiving surface of the spool when the third switching valve establishes the second state. Consequently, during an abnormality in which the hydraulic pressure is not supplied from the first pressure regulation valve as normal, the hydraulic pressure from the third pressure regulation valve is applied to the first pressure receiving surface of the spool. Thus, the switching valve establishes the second supply state with the sum of the thrust applied to the spool by the effect of the hydraulic pressure from the third pressure regulation valve on the first pressure receiving surface, the thrust applied to the spool by the effect of the hydraulic pressure from the second pressure regulation valve on the second pressure receiving surface, and the urging force of the spring applied to the spool exceeding the thrust applied to the spool by the effect of the second hydraulic pressure (modulator pressure) on the holding pressure receiving surface. Thus, with this configuration, it is possible to reduce the urging force (rigidity) required for the spring when the switching valve is brought into the second supply state, which allows the switching valve to be more reliably maintained in the first supply state by the first hydraulic pressure (line pressure) or the second hydraulic pressure (modulator pressure) supplied as a holding pressure to the switching valve when the hydraulic pressure is supplied from the first pressure regulation valve as normal.

In addition, the first hydraulic friction engagement element may be engaged at least when the first speed and the second speed are established in the speed change device; and the second hydraulic friction engagement element may be engaged at least when the second speed is established in the speed change device. Thus, during an abnormality in which the hydraulic pressure is not supplied from the first pressure regulation valve as normal, start and forward travel of the vehicle at the second speed can be ensured by engaging the first hydraulic friction engagement element using the line pressure from the line pressure generation valve, and engaging the second hydraulic friction engagement element.

The hydraulic control device may further include a second hydraulic pressure generation source driven by electric power; the hydraulic pressure generation source may be a mechanical pump driven by power from a motor; the first pressure regulation valve may regulate the line pressure from the line pressure generation valve to generate the hydraulic pressure to be supplied to the first hydraulic friction engagement element; the switching valve may be configured to receive a hydraulic pressure from the second hydraulic pressure generation source via a first oil passage, and to supply the hydraulic pressure from the second hydraulic pressure generation source to the first hydraulic friction engagement element when the second supply state is established; and when the switching valve establishes the second supply state, the line pressure from the line pressure generation valve may be supplied to the first hydraulic friction engagement element by way of a second oil passage and the first oil passage, the second oil passage being connected to the first oil passage and having a valve provided in a middle of the second oil passage, the valve being configured to restrict entry of the hydraulic pressure from the second hydraulic pressure generation source.

Consequently, when the hydraulic pressure for the first hydraulic friction engagement element is no longer supplied by the first pressure regulation valve with operation of the motor stopped and with the hydraulic pressure generation source no longer generating a hydraulic pressure, the hydraulic pressure from the second hydraulic pressure generation source can be supplied to the first hydraulic friction engagement element by switching the switching valve into the second supply state and actuating the second hydraulic pressure generation source. In addition, since the line pressure from the line pressure generation valve can be supplied to the first hydraulic friction engagement element utilizing a part of the first oil passage which connects between the second hydraulic pressure generation source and the switching valve, it is possible to suppress an increase in number of oil passages and hence an increase in cost and device size. With the hydraulic control device according to the aspect of the present invention, it is possible to suppress erroneous supply of the line pressure from the line pressure generation valve to the first hydraulic friction engagement element when the hydraulic pressure is supplied from the first pressure regulation valve as normal as discussed above, and thus to favorably suppress application of the line pressure to the second hydraulic pressure generation source via the second oil passage and the first oil passage to adversely affect the second hydraulic pressure generation source when the hydraulic pressure is supplied from the first pressure regulation valve as normal. The valve described above may be a check valve, or an on-off valve controlled so as to be opened and closed.

Moreover, the second hydraulic pressure generation source may be an electric pump driven by electric power or an electromagnetic pump.

FIG. 1 shows a schematic configuration of an automobile 10 which is a vehicle incorporating a power transfer device 20 including a hydraulic control device 50 according to an embodiment of the present invention;

FIG. 2 shows a schematic configuration of the power transfer device 20 ;

FIG. 3 is an operation table showing the relationship between each shift speed of an automatic transmission 30 included in the power transfer device 20 and the respective operating states of clutches and brakes;

FIG. 4 is a collinear diagram illustrating the relationship between the respective rotational speeds of rotary elements forming the automatic transmission 30 ;

FIG. 5 is a system diagram showing the hydraulic control device 50 ;

FIG. 6 is a system diagram showing the hydraulic control device 50 ; and

FIG. 7 illustrates the relationship between a current applied to a lock-up solenoid valve SLU and a lock-up solenoid pressure Pslu.

Now, an embodiment of the present invention will be described below.

FIG. 1 shows a schematic configuration of an automobile 10 which is a vehicle incorporating a power transfer device 20 including a hydraulic control device 50 according to an embodiment of the present invention. FIG. 2 shows a schematic configuration of the power transfer device 20 . The automobile 10 shown in FIG. 1 includes an engine 12 serving as a power generation source which is an internal combustion engine that outputs power through explosive combustion of a mixture of a hydrocarbon fuel, such as gasoline and light oil, and air, an engine electronic control unit (hereinafter referred to as an “engine ECU”) 14 that controls the engine 12 , a brake electronic control unit (hereinafter referred to as a “brake ECU”) 15 that controls an electronically controlled hydraulic brake unit (not shown), and the power transfer device 20 which includes a fluid transmission apparatus (starting device) 23 , a stepped automatic transmission 30 , the hydraulic control device 50 which supplies and discharges hydraulic oil (a hydraulic fluid) to and from the fluid transmission apparatus 23 and the automatic transmission 30 , a speed change electronic control unit (hereinafter referred to as a “speed change ECU”) 21 that controls the fluid transmission apparatus 23 , the automatic transmission 30 , and the hydraulic unit 50 , and so forth. The power transfer device 20 is connected to a crankshaft 16 of the engine 12 to transfer power from the engine 12 serving as a power generation source to left and right drive wheels DW.

As shown in FIG. 1 , the engine ECU 14 receives inputs such as an accelerator operation amount Acc from an accelerator pedal position sensor 92 that detects the amount of depression (amount of operation) of an accelerator pedal 91 , a vehicle speed V from a vehicle speed sensor 99 , signals from various sensors such as a crankshaft position sensor (not shown) that detects rotation of the crankshaft 16 , and signals from the brake ECU 15 and the speed change ECU 21 . The engine ECU 14 controls an electronically controlled throttle valve, a fuel injection valve, an ignition plug, and so forth (none of which is shown) on the basis of the received signals. In addition, the engine electronic control unit 14 according to the embodiment is configured to execute automatic start/stop control (idle stop control) in which operation of the engine 12 is stopped normally when the engine 12 is brought into idle operation as the automobile 10 becomes stationary and in which the engine 12 is restarted in response to a request to start the automobile 10 made by depressing the accelerator pedal 91 .

The brake ECU 15 receives inputs such as a master cylinder pressure detected by a master cylinder pressure sensor 94 when a brake pedal 93 is depressed, the vehicle speed V from the vehicle speed sensor 99 , signals from various sensors (not shown), and signals from the engine ECU 14 and the speed change ECU 21 . The brake ECU 15 controls a brake actuator (hydraulic actuator) (not shown) on the basis of the received signals. The speed change ECU 21 of the power transfer device 20 is housed inside a transmission case 22 . The speed change ECU 21 receives inputs such as a shift range SR from a shift range sensor 96 that detects the operation position of a shift lever 95 used to select a desired shift range from a plurality of shift ranges (in the embodiment, a parking range, a reverse range, a neutral range, a drive range, a 2nd-speed range, and an L range), the vehicle speed V from the vehicle speed sensor 99 , signals from various sensors (not shown), and signals from the engine ECU 14 and the speed change ECU 15 . The speed change ECU 21 controls the fluid transmission apparatus 23 , the automatic transmission 30 , and so forth on the basis of the received signals.

Each of the engine ECU 14 , the brake ECU 15 , and the speed change ECU 21 discussed above is formed as a microcomputer including a CPU (not shown) as a main component, and includes a ROM that stores various programs, a RAM that temporarily stores data, input and output ports and a communication port (not shown), and so forth besides the CPU. Moreover, the engine ECU 14 , the brake ECU 15 , and the speed change ECU 21 are connected to each other via a bus line or the like so that data required for control are exchanged between the ECUs as required.

The power transfer device 20 includes the fluid transmission apparatus 23 housed inside the transmission case 22 , an oil pump (mechanical pump) 29 serving as a hydraulic pressure generation source, the automatic transmission 30 , and so forth. The fluid transmission device 23 is formed as a fluidic torque converter with a lock-up clutch. As shown in FIG. 2 , the fluid transmission device 23 includes a pump impeller 24 connected to the crankshaft 16 of the engine 12 via a front cover 18 , a turbine runner 25 fixed to an input shaft (input member) 31 of the automatic transmission 30 via a turbine hub, a stator 26 disposed inside the pump impeller 24 and the turbine runner 25 to rectify the flow of hydraulic oil (ATF) from the turbine runner 25 to the pump impeller 24 , a one-way clutch 27 that restricts rotation of the stator 26 to one direction, a lock-up clutch 28 having a damper mechanism (not shown), and so forth. The fluid transmission apparatus 23 functions as a torque amplifier through the action of the stator 26 when the difference in rotational speed between the pump impeller 24 and the turbine runner 25 is large, and functions as a fluid coupling when the difference in rotational speed between the pump impeller 24 and the turbine runner 25 is small. The lock-up clutch 28 can establish and release lock-up in which the front cover 18 and the input shaft 31 of the automatic transmission 30 are directly coupled to each other. If predetermined lock-up on conditions are met after the automobile 10 is started, the lock-up clutch 28 directly couples the front cover 18 and the input shaft 31 of the automatic transmission 30 to each other so that power from the engine 12 is mechanically and directly transferred to the input shaft 31 . In this event, variations in torque to be transferred to the input shaft 31 are absorbed by the damper mechanism (not shown).

The lock-up clutch 28 according to the embodiment is configured to establish and release lock-up by varying the pressure in a lock-up chamber 23 b that faces, via a lock-up piston 28 p , a fluid transmission chamber 23 a in which the pump impeller 24 and the turbine runner 25 of the fluid transmission apparatus 23 are disposed. That is, when the pressure in the lock-up chamber 23 b is higher than the pressure in the fluid transmission chamber 23 a , or when the pressure in the fluid transmission chamber 23 a and the pressure in the lock-up chamber 23 b are equal to each other, the lock-up piston 28 p is not moved to the engagement side, and thereby lock-up is not established (lock-up is released). When a pressure that is lower than the pressure in the fluid transmission chamber 23 a is supplied to the inside of the lock-up chamber 23 b to lower the pressure in the lock-up chamber 23 b , on the contrary, the lock-up piston 28 p is moved toward the front cover 18 to bring a friction member into pressure contact with an inner surface of the front cover 18 , and thereby lock-up is established (completed).

The oil pump 29 serving as a hydraulic pressure generation source is formed as a gear pump including a pump assembly including a pump body and a pump cover, and an externally toothed gear connected via a hub to the pump impeller 24 of the fluid transmission apparatus 23 , and connected to the hydraulic control device 50 . When the engine 12 is in operation, power from the engine 12 rotates the externally toothed gear, which causes the oil pump 29 to suck and discharge hydraulic oil reserved in an oil pan via a strainer (both not shown). Thus, during operation of the engine 12 , the oil pump 29 can generate a hydraulic pressure required by the fluid transmission apparatus 23 or the automatic transmission 30 , and supply hydraulic oil to portions to be lubricated such as various bearings.

The automatic transmission 30 is formed as a 4-speed transmission. As shown in FIG. 2 , the automatic transmission 30 includes a Ravigneaux type planetary gear device 32 and a plurality of clutches C 1 , C 2 , and C 3 , two brakes B 1 and B 3 , and a one-way clutch F 2 that change a power transfer path from the input side to the output side. The Ravigneaux type planetary gear mechanism 32 includes two sun gears 33 a and 33 b which are each an externally toothed gear, a ring gear 34 which is an internally toothed gear fixed to an output shaft (output member) 37 of the automatic transmission 30 , a plurality of short pinion gears 35 a meshed with the sun gear 33 a , a plurality of long pinion gears 35 b meshed with the sun gear 33 b and the plurality of short pinion gears 35 a and meshed with the ring gear 34 , and a carrier 36 that holds the plurality of short pinion gears 35 a and the plurality of long pinion gears 35 b , which are coupled to each other, so as to be rotatable about their respective axes and revolvable around a common axis and that is supported by the transmission case 22 via the one-way clutch F 2 . 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 C 1 is a hydraulic clutch capable of engaging and disengaging the input shaft 31 and the sun gear 33 a of the Ravigneaux type planetary gear device 32 with and from each other. The clutch C 2 is a hydraulic clutch capable of engaging and disengaging the input shaft 31 and the carrier 36 of the Ravigneaux type planetary gear device 32 with and from each other. The clutch C 3 is a hydraulic clutch capable of engaging and disengaging the input shaft 31 and the sun gear 33 b of the Ravigneaux type planetary gear device 32 with and from each other. The brake B 1 is a hydraulic clutch capable of fixing and unfixing the sun gear 33 b of the Ravigneaux type planetary gear device 32 to and from the transmission case 22 . The brake B 3 is a hydraulic clutch capable of fixing and unfixing the carrier 36 of the Ravigneaux type planetary gear device 32 to and from the transmission case 22 . The clutches C 1 to C 3 and the brakes B 1 and B 3 operate with hydraulic oil supplied thereto and discharged therefrom by the hydraulic control device 50 . FIG. 3 is an operation table showing the relationship between each shift speed of the automatic transmission 30 and the respective operating states of the clutches C 1 to C 3 , the brakes B 1 and B 3 , and the one-way clutch F 2 . FIG. 4 is a collinear diagram illustrating the relationship between the respective rotational speeds of rotary elements forming the automatic transmission 30 . The automatic transmission 30 provides first to fourth forward shift speeds and one reverse shift speed when the clutches C 1 to C 3 and the brakes B 1 and B 3 are brought into respective states shown in the operation table of FIG. 3 .

FIGS. 5 and 6 are each a system diagram showing the hydraulic control device 50 which supplies and discharges hydraulic oil to and from the fluid transmission apparatus 23 including the lock-up clutch 28 discussed above and the automatic transmission 30 . The hydraulic control device 50 is connected to the oil pump 29 discussed above which is driven by power from the engine 12 to suck and discharge hydraulic oil from the oil pan. As shown in FIG. 5 , the hydraulic control device 50 includes a primary regulator valve 51 that regulates the hydraulic oil from the oil pump 29 to generate a line 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 in accordance with the operating position of the shift lever 95 , a C 1 linear solenoid valve SLC 1 that regulates the line pressure PL from the manual valve 53 (primary regulator valve 51 ) to generate a C 1 solenoid pressure Pslc 1 for the clutch C 1 , a C 2 linear solenoid valve SLC 2 that regulates the line pressure PL from the manual valve 53 (primary regulator valve 51 ) to generate a C 2 solenoid pressure Pslc 2 for the clutch C 2 , and a B 1 linear solenoid valve SLB 1 that regulates the line pressure PL from the manual valve 53 (primary regulator valve 51 ) to generate a B 1 solenoid pressure Pslb 1 for the brake B 1 .

In addition, as shown in FIG. 5 , the hydraulic control device 50 according to the embodiment includes a shuttle valve (maximum pressure selection valve) 54 that is connected to respective output ports of the linear solenoid valves SLC 1 , SLC 2 , and SLB 1 and that outputs a maximum pressure Pmax that is the highest of the C 1 solenoid pressure Pslc 1 , the C 2 solenoid pressure Pslc 2 , and the B 1 solenoid pressure Pslb 1 . Further, as shown in FIG. 6 , in order to actuate the lock-up clutch 28 of the fluid transmission apparatus 23 , the hydraulic control device 50 includes a lock-up solenoid valve SLU that regulates the modulator pressure Pmod from the modulator valve 52 to generate a lock-up solenoid pressure (lock-up control pressure) Pslu, a lock-up control valve 55 that generates a lock-up pressure Plup to be supplied to the lock-up clutch 28 and corresponding to the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU, and a lock-up relay valve 56 capable of establishing a lock-up pressure supply state in which the lock-up pressure Plup can be supplied to the lock-up chamber 23 b of the fluid transmission apparatus 23 and a lock-up pressure block state in which supply of the lock-up pressure Plup to the lock-up chamber 23 b is blocked.

The primary regulator valve 51 receives as a signal pressure the maximum pressure Pmax from the shuttle valve 54 discussed above via a safety valve 59 to generate the line pressure PL corresponding to the maximum pressure Pmax. It should be noted, however, that the primary regulator valve 51 may be driven by a control pressure from a linear solenoid valve (not shown) that regulates the pressure of hydraulic oil from the oil pump 29 side (for example, the modulator valve 52 ) in accordance with the accelerator operation amount Acc or the operation amount of the throttle valve to output the control pressure. The modulator valve 52 according to the embodiment is a pressure regulation valve that regulates the line pressure PL from the primary regulator valve 51 using the urging force of a spring and a feedback pressure to generate the modulator pressure Pmod which is generally constant.

The manual valve 53 includes a spool that is axially slidable in conjunction with the shift lever 95 , an input port to which the line pressure PL is supplied, a drive range output port that communicates with respective input ports of the C 1 linear solenoid valve SLC 1 , the C 2 linear solenoid valve SLC 2 , and the B 1 linear solenoid valve SLB 1 via an oil passage, a reverse range output port that communicates with a hydraulic pressure entrance of the clutch C 3 via an oil passage, and so forth. When a driver selects one of the drive range, the 2nd-speed range, and the L range which are each a forward travel shift range, the spool of the manual valve 53 allows the input port to communicate with only the drive range output port so that the line pressure PL (drive range pressure Pd) is supplied to the C 1 linear solenoid valve SLC 1 , the C 2 linear solenoid valve SLC 2 , and the B 1 linear solenoid valve SLB 1 . When the driver selects the reverse range for reverse travel, the spool of the manual valve 53 allows the input port to communicate with only the reverse range output port so that the line pressure PL (Pr) is supplied to the clutch C 3 . When the driver selects the parking range or the neutral range, the spool of the manual valve 53 blocks communication between the input port and the drive range output port and the reverse range output port.

The C 1 linear solenoid valve SLC 1 is a normally open linear solenoid valve that regulates the line pressure PL from the manual valve 53 in accordance with the value of a current applied from an auxiliary battery (not shown) to generate the C 1 solenoid pressure Pslc 1 to be supplied to the clutch C 1 . The C 2 linear solenoid valve SLC 2 is a normally open linear solenoid valve that regulates the line pressure PL from the manual valve 53 in accordance with the value of a current applied from the auxiliary battery (not shown) to generate the C 2 solenoid pressure Pslc 2 to be supplied to the clutch C 2 . The B 1 linear solenoid valve SLB 1 is a normally closed linear solenoid valve that regulates the line pressure PL from the manual valve 53 in accordance with the value of a current applied from the auxiliary battery (not shown) to generate the B 1 solenoid pressure Pslb 1 to be supplied to the brake B 1 .

The linear solenoid valves SLC 1 , SLC 2 , and SLB 1 (respective currents applied thereto) are each controlled by the speed change ECU 21 . In the embodiment, from the viewpoint of the cost and the ease of design, the linear solenoid valves SLC 1 , SLC 2 , and SLB 1 have the same size and the same maximum output pressure. In the automatic transmission 30 according to the embodiment, further, the torque distribution ratio of the brake B 1 which is engaged to establish one of the second speed and the fourth speed is lower than the torque distribution ratio of the clutch C 1 which is engaged together with the brake B 1 to establish the second speed and the clutch C 2 which is engaged together with the brake B 1 to establish the fourth speed. Thus, during travel of the automobile 10 , the output pressure required for the B 1 linear solenoid valve SLB 1 corresponding to the brake B 1 is lower than the output pressure required for the C 1 linear solenoid valve SLC 1 corresponding to the clutch C 1 and the C 2 linear solenoid valve SLC 2 corresponding to the clutch C 2 . Consequently, the maximum output pressure is not required for the B 1 linear solenoid valve SLB 1 during normal travel of the automobile 10 , and the output pressure required for the B 1 linear solenoid valve SLB 1 falls within a range, the upper limit of which is defined by a normally used upper limit pressure which is sufficiently lower than the maximum output pressure.

In the embodiment, in addition, when friction torque is transferred from the turbine runner 25 side to the output shaft 37 with the first speed established in the automatic transmission 30 (with engine brake at the first speed in operation) as the driver selects the L range, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 corresponding to the clutch C 2 which is normally not engaged at the same time as the brake B 3 is supplied to the brake B 3 which is engaged at the same time as the clutch C 1 . Therefore, as shown in FIGS. 5 and 6 , in order to enable the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to be selectively supplied to the clutch C 2 and the brake B 3 , the hydraulic control device 50 according to the embodiment includes a C 2 /B 3 switching valve 60 , a B 3 switching valve 70 , and a normally closed solenoid valve S 1 that is controlled by the speed change ECU 21 and that regulates the modulator pressure Pmod from the modulator valve 52 to output a solenoid pressure Ps 1 serving as a signal pressure for the C 2 /B 3 switching valve 60 . The B 3 switching valve 70 according to the embodiment is configured to have a fail-safe function for suppressing simultaneous engagement of the brake B 1 , which is normally not engaged at the same time as the brake B 3 , and the brake B 3 , and to supply the line pressure PL (Pr) from the manual valve 53 to the brake B 3 which is engaged at the same time as the clutch C 3 when the reverse range is selected.

The lock-up solenoid valve SLU regulates the modulator pressure Pmod from the modulator valve 52 in accordance with the value of a current applied from the auxiliary battery (not shown) to generate the lock-up solenoid pressure Pslu, and is controlled by the transmission ECU 21 . FIG. 7 shows the relationship between a current applied to the lock-up solenoid valve SLU and the lock-up solenoid pressure Pslu. The lock-up control valve 55 is a spool valve that regulates a secondary pressure Psec from a secondary regulator valve (not shown), which regulates the pressure of hydraulic oil drained from the primary regulator valve 51 so as to be lower than the line pressure PL in accordance with the maximum pressure Pmax, in accordance with the lock-up solenoid pressure Pslu supplied from the lock-up solenoid valve SLU to generate the lock-up pressure Plup for the lock-up clutch 28 . The lock-up control valve 55 according to the embodiment generates the lock-up pressure Plup by reducing the secondary pressure Psec which is the source pressure to a greater degree as the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU is higher, and outputs the lock-up pressure Plup required for complete engagement of the lock-up clutch 28 when the lock-up solenoid pressure Pslu reaches a lock-up clutch complete engagement pressure P 1 (see FIG. 7 ) that is equal to or less than the modulator pressure Pmod.

The lock-up relay valve 56 includes a spool urged by a spring, and receives as a signal pressure the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU. The lock-up relay valve 56 according to the embodiment is configured to establish the lock-up pressure block state when the lock-up solenoid pressure Pslu is not supplied to allow only supply of the secondary pressure (circulation pressure) Psec from the secondary regulator valve to the lock-up chamber 23 b discussed above, and to establish the lock-up pressure supply state when the lock-up solenoid pressure Pslu is supplied to allow supply of the secondary pressure Psec to the fluid transmission chamber 23 a and supply of the lock-up pressure Plup to the lock-up chamber 23 b . In addition, the lock-up relay valve 56 according to the embodiment is supplied with the solenoid pressure Ps 1 from the solenoid valve S 1 discussed above. When the solenoid pressure Ps 1 from the solenoid valve S 1 is input, the lock-up relay valve 56 establishes the lock-up pressure block state to block (prohibit) supply of the lock-up pressure Plup to the lock-up chamber 23 b , that is, lock-up.

The hydraulic control device 50 according to the embodiment also includes an electromagnetic pump EMOP used to supply a hydraulic pressure to the clutch C 1 serving as a starting clutch to keep the automatic transmission 30 in a start stand-by state when operation of the engine 12 is stopped through the automatic start/stop control (idle stop control) discussed above and the line pressure PL from the primary regulator valve 51 is reduced as operation of the oil pump 29 is stopped, and a C 1 switching valve 80 capable of selectively supplying the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 and a hydraulic pressure Pemop from the electromagnetic pump EMOP to the clutch C 1 (see FIG. 5 for both the electromagnetic pump EMOP and the C 1 switching valve 80 ). In the embodiment, the rotational speed of the engine 12 at which the discharge pressure of the oil pump 29 becomes equal to or less than a predetermined value is determined as a threshold Nref (a value of about 1000 to 1500 rpm, for example). When the rotational speed of the engine 12 becomes equal to or less than the threshold Nref, the C 1 switching valve 80 is switched from a first supply state (the state in the right half of FIG. 5 ), in which the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 can be supplied to the clutch C 1 , into a second supply state (the state in the left half of FIG. 5 ), in which the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 , and a rectangular-wave current at a predetermined duty ratio is applied to a coil of a solenoid portion of the electromagnetic pump EMOP under control by the speed change electronic control unit 21 . Then, when the engine 12 is restarted and the rotational speed of the engine 12 becomes more than the threshold Nref or a predetermined value that is slightly larger than that, supply of a current to the electromagnetic pump EMOP is stopped, and the C 1 switching valve 80 is switched from the second supply state into the first supply state.

The electromagnetic pump EMOP has a well-known configuration to suck hydraulic oil from an oil pan and discharge the hydraulic oil to generate a hydraulic pressure as a rectangular-wave current is applied to the coil of the solenoid portion (not shown), and is controlled by the speed change ECU 21 . Here, when the engine electronic control unit 14 executes an automatic start/stop control process to stop operation of the engine 12 , it is not necessary that the clutch C 1 should be maintained in the completely engaged state. Therefore, the electromagnetic pump EMOP used in the embodiment is capable of generating a hydraulic pressure that is about enough to set the clutch C 1 to a state immediately before being engaged (immediately before being completely engaged) (about enough to eliminate the stroke of a hydraulic servo) while operation of the engine 12 is stopped. This makes it possible to more adequately keep the automatic transmission 30 in the start stand-by state during a period since operation of the engine 12 is started until the engine 12 is restarted, thereby reducing the performance (pump capacity) required for the electromagnetic pump EMOP to reduce the size of the electromagnetic pump EMOP and hence the entire power transfer device 20 . In the embodiment, the C 1 switching valve 80 , which switches the source of a hydraulic pressure to be supplied to the clutch C 1 discussed above, is configured to supply the line pressure PL from the primary regulator valve 51 to the clutch C 1 during an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 as normal.

Next, the C 2 /B 3 switching valve 60 , the B 3 switching valve 70 , and the C 1 switching valve 80 discussed above will be described in detail.

As shown in FIG. 6 , the C 2 /B 3 switching valve 60 includes a spool 601 disposed in a valve body so as to be axially movable, a spring 602 that urges the spool 601 , an input port 61 that communicates with an output port of the C 2 linear solenoid valve SLC 2 via an oil passage, a C 2 drain port 62 capable of discharging a hydraulic pressure from the clutch C 2 , a B 3 drain port 63 capable of discharging a hydraulic pressure from the brake B 3 , a signal pressure input port 64 that communicates with the drive range output port of the manual valve 53 via an oil passage, a line pressure input port 65 that communicates with the drive range output port of the manual valve 53 via an oil passage, a modulator pressure input port 66 that communicates with an output port of the modulator valve 52 via an oil passage, a first output port 67 that communicates with a hydraulic pressure entrance of the clutch C 2 via an oil passage, a second output port 68 capable of supplying the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to the brake B 3 , and a third output port 69 . Further, a spring chamber 603 houses the spring 602 of the C 2 /B 3 switching valve 60 , and communicates with an output port of the solenoid valve S 1 via a port and an oil passage (not shown).

In the embodiment, the state of attachment of the C 2 /B 3 switching valve 60 is a B 3 supply state (second state) in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 and a hydraulic pressure can be discharged from the clutch C 2 . That is, in the state of attachment of the C 2 /B 3 switching valve 60 (B 3 supply state), the spool 601 is urged by the spring 602 to be maintained in the state indicated by the dotted line in FIG. 6 . This allows communication between the input port 61 , which communicates with the output port of the C 2 linear solenoid valve SLC 2 , and the second output port 68 , allows communication between the first output port 67 , which communicates with the hydraulic pressure entrance of the clutch C 2 , and the C 2 drain port 62 , and allows communication between the modulator pressure input port 66 and the third output port 69 .

In addition, as discussed above, the signal pressure input port 64 of the C 2 /B 3 switching valve 60 communicates with the drive range output port of the manual valve 53 . When the line pressure PL is output from the primary regulator valve 51 with the forward travel shift range (drive range, 2nd-speed range, and L range) selected and with the oil pump 29 driven by power from the engine 12 , the drive range pressure Pd from the manual valve 53 , that is, the line pressure PL, is supplied to the signal pressure input port 64 . Further, when the brake B 3 is engaged (with engine brake at the first speed in operation) by supplying the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to the brake B 3 in order to transfer friction torque from the turbine runner 25 side to the output shaft 37 with the first speed established in the automatic transmission 30 as the L range is selected, the solenoid valve S 1 discussed above is controlled by the speed change ECU 21 so as to output the solenoid pressure Ps 1 serving as a signal pressure, and the solenoid pressure Ps 1 from the solenoid valve S 1 is supplied to the spring chamber 603 of the C 2 /B 3 switching valve 60 .

The spring constant of the spring 602 of the C 2 /B 3 switching valve 60 , the area of the pressure receiving surface of the spool 601 facing the signal pressure input port 64 , and the area of the pressure receiving surface of the spool 601 which receives the urging force of the spring 602 and the solenoid pressure Ps 1 from the solenoid valve S 1 are determined such that the spool 601 is brought into the state indicated by the solid line in FIG. 6 with the thrust applied to the spool 601 by the effect of the line pressure PL from the signal pressure input port 64 exceeding the urging force of the spring 602 when the line pressure PL is supplied to the signal pressure input port 64 and the solenoid pressure Ps 1 from the solenoid valve S 1 is not supplied to the spring chamber 603 , and such that the spool 601 is brought into the state indicated by the dotted line in FIG. 6 (B 3 supply state) with the sum of the urging force of the spring 602 and the thrust applied to the spool 601 by the effect of the solenoid pressure Ps 1 exceeding the thrust applied to the spool 601 by the effect of the line pressure PL when the solenoid pressure Ps 1 is supplied to the spring chamber 603 with the line pressure PL supplied to the signal pressure input port 64 .

Consequently, when the line pressure PL is supplied to the signal pressure input port 64 and the solenoid pressure Ps 1 from the solenoid valve S 1 is not supplied to the spring chamber 603 , the spool 601 is moved against the urging force of the spring 602 , and the C 2 /B 3 switching valve 60 establishes the C 2 supply state (first state) indicated by the solid line in FIG. 6 . In the C 2 supply state, the input port 61 , which communicates with the output port of the C 2 linear solenoid valve SLC 2 , and the first output port 67 , which communicates with the hydraulic pressure entrance of the clutch C 2 , are communicated with each other, the B 3 drain port 63 , which can discharge a hydraulic pressure from the brake B 3 , and the second output port 68 , which can supply the C 2 solenoid pressure Pslc 2 to the brake B 3 , are communicated with each other, and the line pressure input port 65 and the third output port 69 are communicated with each other. Consequently, if the C 2 linear solenoid valve SLC 2 is caused to output the C 2 solenoid pressure Pslc 2 when the C 2 /B 3 switching valve 60 establishes the C 2 supply state, the C 2 solenoid pressure Pslc 2 can be supplied to the clutch C 2 to engage the clutch C 2 , and a hydraulic pressure can be discharged from the brake B 3 as well.

Meanwhile, when the solenoid pressure Ps 1 is supplied to the spring chamber 603 with the line pressure PL supplied to the signal pressure input port 64 in order to engage the brake B 3 by supplying the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to the brake B 3 (with engine brake at the first speed in operation), the C 2 /B 3 switching valve 60 establishes the B 3 supply state indicated by the dotted line in FIG. 6 . Consequently, the input port 61 , which communicates with the output port of the C 2 linear solenoid valve SLC 2 , and the second output port 68 are communicated with each other, and the first output port 67 , which communicates with the hydraulic pressure entrance of the clutch C 2 , and the C 2 drain port 62 are communicated with each other. Thus, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 , and a hydraulic pressure can be discharged from the clutch C 2 .

As shown in FIG. 6 , the B 3 switching valve 70 includes a plunger 700 disposed in a valve body so as to be axially movable, a spool 701 disposed in the valve body coaxially with the plunger 700 so as to be movable, a spring 702 that urges the spool 701 , an input port 71 that communicates with the second output port 68 of the C 2 /B 3 switching valve 60 via an oil passage, an output port 72 that communicates with a hydraulic pressure entrance of the brake B 3 via an oil passage, a drain port 73 capable of discharging a hydraulic pressure from the brake B 3 , and a signal pressure input port 74 that communicates with the third output port 69 of the C 2 /B 3 switching valve 60 via an oil passage. In addition, a spring chamber 703 houses the spring 702 of the B 3 switching valve 70 , and communicates with an output port of the lock-up solenoid valve SLU via a port and an oil passage (not shown).

In the embodiment, further, in order to provide the B 3 switching valve 70 with the fail-safe function for suppressing simultaneous engagement of the brake B 1 and the brake B 3 discussed above, the plunger 700 and the spool 701 are configured to define an oil chamber 704 . The oil chamber 704 is communicated with an output port of the B 1 linear solenoid valve SLB 1 which outputs (regulates) the B 1 solenoid pressure Pslb 1 which is a hydraulic pressure to be supplied to the brake B 1 which is normally not engaged at the same time as the brake B 3 . The spool 701 includes a first pressure receiving surface 701 a that receives the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and a second pressure receiving surface 701 b formed on the opposite side from the first pressure receiving surface 701 a to receive the urging force of the spring 702 . In addition, the plunger 700 includes a pressure receiving surface 700 a that faces the first pressure receiving surface 701 a of the spool 701 to receive the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and a signal pressure receiving surface 700 b formed on the opposite side from the pressure receiving surface 700 a to receive a signal pressure supplied to the signal pressure input port 74 . In the embodiment, the first pressure receiving surface 701 a of the spool 701 and the pressure receiving surface 700 a of the plunger 700 have the same area as each other.

In the embodiment, the state of attachment of the B 3 switching valve 70 is a communicated state in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 . That is, in the state of attachment of the B 3 switching valve 70 (communicated state), the spool 701 and the plunger 700 are urged together by the spring 702 to be maintained in the state indicated by the dotted line in FIG. 6 . This allows communication between the input port 71 , which communicates with the second output port 68 of the C 2 /B 3 switching valve 60 , and the output port 72 , which communicates with the hydraulic pressure entrance of the brake B 3 .

In addition, as discussed above, the signal pressure input port 74 of the B 3 switching valve 70 communicates with the third output port 69 of the C 2 /B 3 switching valve 60 . When the C 2 /B 3 switching valve 60 establishes the C 2 supply state in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the clutch C 2 , the drive range pressure Pd from the manual valve 53 , that is, the line pressure PL, is supplied to the signal pressure input port 74 . In addition, when the C 2 /B 3 switching valve 60 establishes the B 3 supply state in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 , the modulator pressure Pmod from the modulator valve 52 is supplied to the signal pressure input port 74 . In the embodiment, further, when the C 2 /B 3 switching valve 60 is switched from the C 2 supply state into the B 3 supply state so that the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the brake B 3 , the solenoid valve S 1 is controlled by the speed change ECU 21 so as to output the solenoid pressure Ps 1 serving as a signal pressure for the C 2 /B 3 switching valve 60 , and the lock-up solenoid valve SLU is controlled by the speed change ECU 21 so as to output the lock-up solenoid pressure Pslu at a value P 2 (see FIG. 7 ) that is higher than the lock-up clutch complete engagement pressure P 1 discussed above determined in advance. When the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the brake B 3 , the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU is supplied to the spring chamber 703 of the B 3 switching valve 70 .

The spring constant of the spring 702 of the B 3 switching valve 70 , the area of the signal pressure receiving surface 700 b of the plunger 700 facing the signal pressure input port 74 , and the area of the second pressure receiving surface 701 b of the spool 701 which receives the urging force of the spring 702 and the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU are determined such that the plunger 700 and the spool 701 are brought together into the state indicated by the solid line in FIG. 6 (blocked/discharge state) with the thrust applied to the plunger 700 by the effect of the line pressure PL on the signal pressure receiving surface 700 b of the plunger 700 exceeding the sum of the urging force of the spring 702 applied to the spool 701 and the thrust applied to the spool 701 by the effect of the lock-up solenoid pressure Pslu on the second pressure receiving surface 701 b when the line pressure PL is supplied to the signal pressure input port 74 as a signal pressure and the lock-up solenoid pressure Pslu (a hydraulic pressure that is equal to or less than the lock-up clutch complete engagement pressure P 1 ) from the lock-up solenoid valve SLU is supplied to the spring chamber 703 as the lock-up clutch 28 executes lock-up, and such that the spool 701 and the plunger 700 are brought together into the state indicated by the dotted line in FIG. 6 (communicated state) with the sum of the urging force of the spring 702 applied to the spool 701 and the thrust applied to the spool 701 by the effect of the lock-up solenoid pressure Pslu exceeding the thrust applied to the plunger 700 by the effect of the modulator pressure Pmod when the modulator pressure Pmod is supplied to the signal pressure input port 74 and the lock-up solenoid pressure Pslu (a hydraulic pressure that is higher than the lock-up clutch complete engagement pressure P 1 ) from the lock-up solenoid valve SLU is supplied to the spring chamber 703 .

In the embodiment, further, the spring constant of the spring 702 of the B 3 switching valve 70 , the area of the first pressure receiving surface 701 a of the spool 701 facing the oil chamber 704 , and the area of the second pressure receiving surface 701 b of the spool 701 which receives the urging force of the spring 702 and the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU are determined such that the spool 701 is brought into the state indicated by the solid line in FIG. 6 (blocked/discharge state) with the thrust applied to the spool 701 by the effect of the B 1 solenoid pressure Pslb 1 on the first pressure receiving surface 701 a exceeding the sum of the urging force of the spring 702 applied to the spool 701 and the thrust applied to the spool 701 by the effect of the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU when the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied with the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 supplied to the brake B 3 to engage the brake B 3 .

Consequently, when the line pressure PL is supplied to the signal pressure input port 74 , that is, the C 2 /B 3 switching valve 60 establishes the C 2 supply state in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the clutch C 2 (during forward travel with engine brake at the first speed not in operation), the plunger 700 and the spool 701 are moved against the urging force of the spring 702 , and the B 3 switching valve 70 establishes the blocked/discharge state indicated by the solid line in FIG. 6 . In the blocked/discharge state, the output port 72 , which communicates with the hydraulic pressure entrance of the brake B 3 , is communicated with the drain port 73 , and thus supply of the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to the brake B 3 can be blocked, and a hydraulic pressure can be discharged from the brake B 3 .

Then, even if the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the oil chamber 704 of the B 3 switching valve 70 when the brake B 1 is to be engaged with the C 2 /B 3 switching valve 60 establishing the C 2 supply state (with the brake B 3 not engaged), that is, when the second speed or the fourth speed is to be established, or the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU (a hydraulic pressure equal to or less than the lock-up clutch complete engagement pressure P 1 ) is supplied to the C 2 /B 3 switching valve at the same time as the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 as the lock-up clutch 28 executes lock-up, movement of the plunger 700 and the spool 701 can be restricted by the line pressure PL which is high to more reliably maintain the B 3 switching valve 70 in the blocked/discharge state.

When the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the brake B 3 to engage the brake B 3 (with engine brake at the first speed in operation), on the other hand, the modulator pressure Pmod, which is lower than the line pressure PL, is supplied from the third output port 69 of the C 2 /B 3 switching valve 60 establishing the B 3 supply state to the signal pressure input port 74 of the B 3 switching valve 70 , and the lock-up solenoid pressure Pslu from the lock-up solenoid valve SLU is supplied to the spring chamber 703 . Consequently, the spool 701 and the plunger 700 are moved together with the sum of the urging force of the spring 702 applied to the spool 701 and the thrust applied to the spool 701 by the effect of the lock-up solenoid pressure Pslu exceeding the thrust applied to the plunger 700 by the modulator pressure Pmod, and thus the B 3 switching valve 70 establishes the communicated state indicated by the dotted line in FIG. 5 . In the communicated state, the output port 72 , which communicates with the hydraulic pressure entrance of the brake B 3 , is communicated with the input port 71 , which communicates with the second output port 68 of the C 2 /B 3 switching valve 60 , and thus the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 .

In addition, when the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the oil chamber 704 when some abnormality occurs with the brake B 3 thus engaged, the thrust applied to the spool 701 by the effect of the B 1 solenoid pressure Pslb 1 on the first pressure receiving surface 701 a exceeds the sum of the urging force of the spring 702 applied to the spool 701 and the thrust applied to the spool 701 by the effect of the lock-up solenoid pressure Pslu, and thus the B 3 switching valve 70 can be quickly switched from the communicated state into the blocked/discharge state with the spool 701 brought into the state indicated by the solid line in FIG. 6 by the B 1 solenoid pressure Pslb 1 . Consequently, the output port 72 and the drain port 73 can be communicated with each other by the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 to discharge a hydraulic pressure from the brake B 3 , thereby quickly releasing engagement of the brake B 3 . Thus, according to the hydraulic control device 50 , it is possible to favorably suppress simultaneous engagement of the brake B 1 and the brake B 3 by quickly releasing engagement of the brake B 3 even if the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the oil chamber 704 because of some abnormality with the brake B 3 engaged.

As shown in FIG. 5 , the C 1 switching valve 80 includes a spool 801 disposed in a valve body so as to be axially movable, a spring 802 that urges the spool 801 , a first input port 81 that communicates with an output port of the C 1 linear solenoid valve SLC 1 via an oil passage, a second input port 82 that communicates with a discharge port of the electromagnetic pump EMOP via an oil passage L 1 , a holding pressure input port 83 that communicates with the third output port 69 of the C 2 /B 3 switching valve 60 via an oil passage, a B 1 solenoid pressure input port 84 that communicates with an output port of the B 1 linear solenoid valve SLB 1 via an oil passage, a line pressure input port 85 that communicates with the drive range output port of the manual valve 53 via an oil passage, a port 86 that communicates with the second output port 68 of the C 2 /B 3 switching valve via an oil passage and that communicates with a spring chamber in which the spring 802 is disposed, a relay port 87 that can communicate with the line pressure input port 85 , and an output port 88 that communicates with a hydraulic pressure entrance of the clutch C 1 via an oil passage.

As shown in FIG. 5 , the spool 801 of the C 1 switching valve 80 includes a first pressure receiving surface 801 a that receives the urging force of the spring 802 , second pressure receiving surfaces 801 b and 801 c that are spaced from each other in the axial direction to face each other and that each receive the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and a holding pressure receiving surface 801 d that receives the line pressure PL or the modulator pressure Pmod serving as a holding pressure supplied from the third output port 69 of the C 2 /B 3 switching valve 60 . In the embodiment, of the second pressure receiving surfaces 801 b and 801 c which receive the B 1 solenoid pressure Pslb 1 , the second pressure receiving surface 801 c on the holding pressure receiving surface 801 d side is larger in area than the second pressure receiving surface 801 b on the first pressure receiving surface 801 a side as shown in FIG. 5 . In the hydraulic control device 50 according to the embodiment, further, an oil passage (first oil passage) L 1 that connects between the discharge port of the electromagnetic pump EMOP and the second input port 82 of the C 1 switching valve 80 and the relay port 87 of the C 1 switching valve 80 are connected via an oil passage (second oil passage) L 2 having a check valve 89 provided in the middle thereof. The check valve 89 allows entry of hydraulic oil (supply of a hydraulic pressure) from the relay port 87 into the oil passage L 1 , that is, the second input port 82 , and restricts (prohibits) entry of hydraulic oil (supply of a hydraulic pressure) from the oil passage L 1 into the oil passage L 2 , that is, the relay port 87 .

In the embodiment, the state of attachment of the C 1 switching valve 80 is the second supply state (the state in the left half in FIG. 5 ) in which the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 . That is, in the state of attachment of the C 1 switching valve 80 , the spool 801 is urged upward in the drawing by the urging force of the spring 802 . This causes the spool 801 to close the first input port 81 , which communicates with the output port of the C 1 linear solenoid valve SLC 1 , allows communication between the second input port 82 , which communicates with the discharge port of the electromagnetic pump EMOP via the oil passage L 1 , and the output port 88 , which communicates with the hydraulic pressure entrance of the clutch C 1 , and allows communication between the line pressure input port 85 and the relay port 87 . Consequently, when the C 1 switching valve 80 establishes the second supply state, the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 via the oil passage L 1 , the second input port 82 , and the output port 88 , and the line pressure PL from the manual valve 53 supplied to the line pressure input port 85 of the C 1 switching valve 80 can be supplied to the clutch C 1 via the oil passage L 2 (check valve 89 ), a part of the oil passage L 1 , the second input port 82 , and the output port 88 .

When the line pressure PL is supplied to the signal pressure input port 64 of the C 2 /B 3 switching valve 60 and the solenoid pressure Ps 1 from the solenoid valve S 1 is not supplied to the spring chamber 603 , that is, during forward travel with engine brake at the first speed not in operation, the drive range pressure Pd from the manual valve 53 , that is, the line pressure PL, is supplied as a holding pressure to the holding pressure input port 83 of the C 1 switching valve 80 via the third output port 69 of the C 2 /B 3 switching valve 60 establishing the C 2 supply state. When the solenoid pressure Ps 1 is supplied to the spring chamber 603 with the line pressure PL supplied to the signal pressure input port 64 of the C 2 /B 3 switching valve 60 , that is, with engine brake at the first speed in operation, on the contrary, the modulator pressure Pmod, which is lower than the line pressure PL, is supplied as a holding pressure to the holding pressure input port 83 of the C 1 switching valve 80 via the third output port 69 of the C 2 /B 3 switching valve 60 establishing the B 3 supply state, and the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the port 86 (spring chamber) of the C 1 switching valve 80 via the second output port 68 of the C 2 /B 3 switching valve 60 establishing the B 3 supply state. Further, when the brake B 1 is engaged (when the second speed or the fourth speed is set) or when some abnormality occurs in the B 1 linear solenoid valve SLB 1 or the like, the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the B 1 solenoid pressure input port 84 of the C 1 switching valve 80 .

The spring constant of the spring of the C 1 switching valve 80 and the respective areas of the first pressure receiving surface 801 a , the second pressure receiving surfaces 801 b and 801 c , and the holding pressure receiving surface 801 d are determined such that the spool 801 is brought into the state in the right half in FIG. 5 (first supply state) with the force applied to the spool 801 by the effect of the line pressure PL on the holding pressure receiving surface 801 d exceeding the sum of the force applied to the spool 801 by the effect of the B 1 solenoid pressure Pslb 1 on the second pressure receiving surfaces 801 b and 801 c and the urging force of the spring 802 applied to the spool 801 when the line pressure PL is supplied as a holding pressure from the C 2 /B 3 switching valve 60 to the holding pressure input port 83 , and such that the spool 801 is brought into the state in the right half in FIG. 5 (first supply state) with the force applied to the spool 801 by the effect of the modulator pressure Pmod on the holding pressure receiving surface 801 d exceeding the sum of the urging force of the spring 802 applied to the spool 801 and the force applied to the spool 801 by the effect of the C 2 solenoid pressure Pslc 2 on the first pressure receiving surface 801 a when the modulator pressure Pmod is supplied as a holding pressure from the C 2 /B 3 switching valve 60 to the holding pressure input port 83 .

In this way, when the C 1 switching valve 80 establishes the first supply state, the first input port 81 , which communicates with the output port of the C 1 linear solenoid valve SLC 1 , and the output port 88 , which communicates with the hydraulic pressure entrance of the clutch C 1 , are communicated with each other, the line pressure input port 85 is closed by the spool 801 , and the second input port 82 , which communicates with the discharge port of the electromagnetic pump EMOP, and the relay port 87 are communicated with the drain port. Consequently, when the C 1 switching valve 80 establishes the first supply state, it is possible to supply the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 to the clutch C 1 in order to engage the clutch C 1 , and not to supply the hydraulic pressure Pemop from the electromagnetic pump EMOP or the line pressure PL from the manual valve 53 (primary regulator valve 51 ) to the clutch C 1 .

In the embodiment, further, the spring constant of the spring of the C 1 switching valve 80 and the respective areas of the first pressure receiving surface 801 a , the second pressure receiving surfaces 801 b and 801 c , and the holding pressure receiving surface 801 d are determined such that the spool 801 is brought into the state in the left half in FIG. 5 (second supply state) with the sum of the urging force of the spring 802 applied to the spool 801 , the force applied to the spool 801 by the effect of the C 2 solenoid pressure Pslc 2 on the first pressure receiving surface 801 a , and the force applied to the spool 801 by the effect of the B 1 solenoid pressure Pslb 1 on the second pressure receiving surfaces 801 b and 801 c exceeding the force applied to the spool 801 by the effect of the modulator pressure Pmod on the holding pressure receiving surface 801 d when the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the B 1 solenoid pressure input port 84 with the modulator pressure Pmod supplied as a holding pressure from the C 2 /B 3 switching valve 60 to the holding pressure input port 83 .

Subsequently, operation of the hydraulic control device 50 at the time when the forward travel shift range is selected by the driver of the automobile 10 incorporating the power transfer 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 in operation, and the oil pump 29 is driven by power from the engine 12 , which causes the primary regulator valve 51 to generate the line pressure PL and causes the modulator valve 52 to generate the modulator pressure Pmod which is constant. Then, during forward travel with engine brake at the first speed not in operation with the hydraulic control device 50 operating normally, the drive range pressure Pd from the manual valve 53 , that is, the line pressure PL, is supplied as a holding pressure to the holding pressure input port 83 of the C 1 switching valve 80 via the third output port 69 of the C 2 /B 3 switching valve 60 establishing the C 2 supply state. Thus, when the line pressure PL is supplied as a holding pressure to the holding pressure input port 83 , the C 1 switching valve 80 establishes the first supply state in which the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 can be supplied to the clutch C 1 irrespective of the presence or absence of the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , which makes it possible to supply the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 to the clutch C 1 to engage the clutch C 1 .

With engine brake at the first speed in operation with the hydraulic control device 50 operating normally, meanwhile, the modulator pressure Pmod, which is lower than the line pressure PL, is supplied as a holding pressure to the holding pressure input port 83 of the C 1 switching valve 80 via the third output port 69 of the C 2 /B 3 switching valve 60 establishing the B 3 supply state, and the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the port 86 (spring chamber) via the second output port 68 of the C 2 /B 3 switching valve 60 . Also when the modulator pressure Pmod, which is lower than the line pressure PL, is thus supplied as a holding pressure to the holding pressure input port 83 , the C 1 switching valve 80 establishes the first supply state unless the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the B 1 solenoid pressure input port 84 , which makes it possible to supply the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 to the clutch C 1 to engage the clutch C 1 .

If the line pressure PL is thus supplied as a holding pressure to the C 1 switching valve 80 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal, the C 1 switching valve 80 is maintained in the first supply state irrespective of the presence or absence of the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and the C 1 switching valve 80 is maintained in the first supply state even if the modulator pressure Pmod is supplied as a holding pressure unless the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied. Thus, in the hydraulic control device 50 according to the embodiment, it is possible to more reliably suppress communication between the line pressure input port 85 and the relay port 87 with the C 1 switching valve 80 switched from the first supply state into the second supply state when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal. As a result, it is possible to favorably suppress occurrence of a shock along with switching in supplied hydraulic pressure by suppressing erroneous supply of the line pressure PL from the manual valve 53 (primary regulator valve 51 ) to the clutch C 1 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal, and to favorably suppress application of the line pressure to the electromagnetic pump EMOP via the oil passage L 2 (check valve 89 ) and the oil passage L 1 to adversely affect the electromagnetic pump EMOP (internal constituent part).

On the other hand, when the automobile 10 is stationary to wait for a traffic light to change, for example, the engine ECU 14 executes the automatic start/stop control process to stop operation of the engine 12 . In this event, because drive of the oil pump 29 is stopped as operation of the engine 12 is stopped, the line pressure PL and the modulator pressure Pmod are reduced, and also the C 1 linear solenoid valve SLC 1 corresponding to the clutch C 1 serving as a starting clutch that is engaged to establish the first speed (and the second speed) in the automatic transmission 30 becomes unable to generate a hydraulic pressure (C 1 solenoid pressure Pslc 1 ). Therefore, the state of attachment of the C 1 switching valve 80 according to the embodiment is the second supply state in which the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 . That is, when drive of the oil pump 29 is stopped, the line pressure PL or the modulator pressure Pmod supplied to the holding pressure input port 83 of the C 1 switching valve 80 is reduced, and thus the C 1 switching valve 80 is returned to its state of attachment (second supply state) by the urging force of the spring 802 , thereby allowing communication between the second input port 82 , which communicates with the discharge port of the electromagnetic pump EMOP via the oil passage L 1 , and the output port 88 , which communicates with the hydraulic pressure entrance of the clutch C 1 .

Consequently, the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 via the C 1 switching valve 80 , and the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 serving as a starting clutch to keep the automatic transmission 30 in the start stand-by state even if operation of the engine 12 is stopped when the forward travel shift range such as the drive range is selected by the driver. In the automobile 10 according to the embodiment, when the engine 12 is in operation and the forward travel shift range such as the drive range is selected, no hydraulic pressure is generated by the electromagnetic pump EMOP. When the engine 12 is restarted and the oil pump 29 is driven by power from the engine 12 , meanwhile, the C 1 switching valve 80 is switched from the second supply state into the first supply state by the line pressure PL or the modulator pressure Pmod supplied as a holding pressure.

Here, in the hydraulic control device 50 discussed above, when an abnormality occurs in the state of supply of the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 such as a failure of the C 1 linear solenoid valve SLC 1 or a blockage in an oil passage between the output port of the C 1 linear solenoid valve SLC 1 and the first input port 81 of the C 1 switching valve 80 , the C 1 solenoid pressure Pslc 1 may not be supplied to the clutch C 1 . Thus, if no measures are taken, the clutch C 1 may not be engaged during an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 as normal, which may constitute obstacles to start and travel of the automobile 10 .

Therefore, the speed change ECU 21 according to the embodiment determines whether or not an abnormality occurs in the state of supply of the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 on the basis of a value detected by a pressure sensor (not shown) or the like while an ignition switch of the automobile 10 is turned on. If it is determined that an abnormality occurs in the state of supply of the C 1 solenoid pressure Pslc 1 , and on condition that the engine 12 is in operation, that is, the oil pump 29 is driven, the speed change ECU 21 controls the solenoid valve S 1 so as to output the solenoid pressure Ps 1 if the solenoid pressure Ps 1 serving as a signal pressure for the C 2 /B 3 switching valve 60 and the lock-up relay valve 56 is not output from the solenoid valve S 1 (with engine brake at the first speed not in operation), and controls the B 1 linear solenoid valve SLB 1 , which has a relatively low normally used upper limit pressure, so as to output the B 1 solenoid pressure (switching pressure) Pslb 1 at a value (maximum output pressure, for example) that is more than the normally used upper limit pressure and the modulator pressure Pmod and that is equal to or less than the maximum output pressure of the B 1 linear solenoid valve SLB 1 .

By thus controlling the solenoid valve S 1 and the B 1 linear solenoid valve SLB 1 , the C 2 /B 3 switching valve 60 establishes the B 3 supply state, and the modulator pressure Pmod, which is lower than the line pressure PL, is supplied as a holding pressure to the holding pressure input port 83 of the C 1 switching valve 80 , the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the port 86 (spring chamber), and the B 1 solenoid pressure Pslb 1 (switching pressure) from the B 1 linear solenoid valve SLB 1 is supplied to the B 1 solenoid pressure input port 84 . Then, the C 1 switching valve 80 establishes the first supply state discussed above with the sum of the urging force of the spring 802 applied to the spool 801 , the force applied to the spool 801 by the effect of the C 2 solenoid pressure Pslc 2 on the first pressure receiving surface 801 a , and the force applied to the spool 801 by the effect of the B 1 solenoid pressure Pslb 1 on the second pressure receiving surfaces 801 b and 801 c exceeding the force applied to the spool 801 by the effect of the modulator pressure Pmod on the holding pressure receiving surface 801 d.

Consequently, the line pressure PL from the manual valve 53 supplied to the line pressure input port 85 of the C 1 switching valve 80 can be supplied to the clutch C 1 via the relay port 87 , the oil passage L 2 (check valve 89 ), a part of the oil passage L 1 , the second input port 82 , and the output port 88 to engage the clutch C 1 . In addition, since the line pressure PL from the manual valve 53 supplied to the line pressure input port 85 can be thus supplied to the clutch C 1 utilizing a part of the oil passage L 1 which connects between the electromagnetic pump EMOP and the C 1 switching valve 80 , it is possible to suppress an increase in number of oil passages and hence an increase in cost and device size. When the B 1 solenoid pressure Pslb 1 is set to the switching pressure discussed above, the B 1 solenoid pressure Pslb 1 is supplied as the maximum pressure Pmax from the shuttle valve 54 to the primary regulator valve 51 , and thus the line pressure PL itself generated by the primary regulator valve 51 is also increased.

As a result, in the automobile 10 incorporating the power transfer device 20 , even if an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 to the clutch C 1 as normal during travel at the first speed, the second speed can be established by the automatic transmission 30 by controlling the solenoid valve S 1 and the B 1 linear solenoid valve SLB 1 as discussed above, which satisfactorily ensures forward travel of the automobile 10 . Even if an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 to the clutch C 1 as normal during travel at the second speed, in addition, the second speed can be continuously established by the automatic transmission 30 by controlling the solenoid valve S 1 as discussed above and increasing the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 to the switching pressure described above, which satisfactorily ensures forward travel of the automobile 10 .

Even if an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 to the clutch C 1 as normal during travel at the third speed, further, the C 2 /B 3 switching valve 60 can be switched from the C 2 supply state into the B 3 supply state by controlling the solenoid valve S 1 and the B 1 linear solenoid valve SLB 1 as discussed above, and the B 3 switching valve 70 can be switched into the blocked/discharge state by inputting the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 . Consequently, the second speed is set by the automatic transmission 30 with engagement of the clutch C 2 released and engagement of the brake B 3 blocked, which satisfactorily ensures forward travel of the automobile 10 . When an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 to the clutch C 1 as normal during travel at the fourth speed, moreover, the second speed can be established by the automatic transmission 30 by controlling the solenoid valve S 1 as discussed above and increasing the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 to the switching pressure described above when the vehicle speed (the rotational speed of the engine 12 ) is reduced to some degree, which satisfactorily ensures forward travel of the automobile 10 . Even if an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 to the clutch C 1 as normal before the automobile 10 becomes stationary or while the automobile 10 is stationary, the second speed can be established by the automatic transmission 30 by controlling the solenoid valve S 1 and the B 1 linear solenoid valve SLB 1 as discussed above, which satisfactorily ensures start of the automobile 10 .

As has been described above, the hydraulic control device 50 according to the embodiment includes the C 1 switching valve 80 which is capable of establishing the first supply state, in which the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 can be supplied to the clutch C 1 , and the second supply state, in which the line pressure PL from the manual valve 53 (primary regulator valve 51 ) can be supplied to the clutch C 1 , which selectively receives the line pressure (first hydraulic pressure) PL and the modulator pressure (second hydraulic pressure) Pmod as a holding pressure for holding the first supply state, and which can receive the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 corresponding to the brake B 1 which is engaged at the same time as the clutch C 1 when an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 as normal. In addition, the C 1 switching valve 80 establishes the first supply state irrespective of the presence or absence of the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 when the line pressure PL is supplied as a holding pressure, establishes the first supply state when the modulator pressure Pmod is supplied as a holding pressure and the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is not supplied, and establishes the second supply state when the modulator pressure Pmod is supplied as a holding pressure and the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied. Then, during an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 as normal, the modulator pressure Pmod which is lower than the line pressure is supplied as a holding pressure to the C 1 switching valve 80 .

By thus supplying the modulator pressure Pmod, which is lower than the line pressure PL, as a holding pressure to the C 1 switching valve 80 during the abnormality described above, the C 1 switching valve 80 can be quickly switched from the first supply state into the second supply state by the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 to supply the line pressure PL from the primary regulator valve 51 to the clutch C 1 , which enables simultaneous engagement of the clutch C 1 and the brake B 1 . If the line pressure PL is supplied as a holding pressure to the C 1 switching valve 80 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal, meanwhile, the C 1 switching valve 80 is maintained in the first supply state irrespective of the presence or absence of the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and the C 1 switching valve 80 is maintained in the first supply state even if the modulator pressure Pmod is supplied as a holding pressure with engine brake at the first speed in operation unless the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied. Thus, with the hydraulic control device 50 according to the embodiment, it is possible to supply the line pressure PL from the primary regulator valve 51 to the clutch C 1 corresponding to the C 1 linear solenoid valve SLC 1 during an abnormality in which a hydraulic pressure is not supplied from the C 1 linear solenoid valve SLC 1 as normal, and not to supply the line pressure PL from the primary regulator valve 51 to the clutch C 1 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal. As a result, it is possible to favorably suppress occurrence of a shock along with switching in supplied hydraulic pressure by suppressing erroneous supply of the line pressure PL from the primary regulator valve 51 to the clutch C 1 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal. Then, by basically supplying the line pressure PL to the C 1 switching valve 80 as a holding pressure when a hydraulic pressure is supplied from the C 1 linear solenoid valve SLC 1 as normal, it is possible to more reliably maintain the C 1 switching valve 80 in the first supply state, and not to supply the line pressure PL from the primary regulator valve 51 to the clutch C 1 .

Further, in the hydraulic control device 50 according to the embodiment, during an abnormality in which the C 1 solenoid pressure Pslc 1 is not supplied from the C 1 linear solenoid valve SLC 1 as normal, the C 2 /B 3 switching valve 60 establishes the second state using the solenoid pressure (signal pressure) Ps 1 from the solenoid valve S 1 . Consequently, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 , and a hydraulic pressure can be discharged from the clutch C 2 , which allows the modulator pressure Pmod to be supplied as a holding pressure from the C 2 /B 3 switching valve 60 to the C 1 switching valve 80 and allows the modulator pressure Pmod to be supplied as a signal pressure to the B 3 switching valve 70 . This enables the modulator pressure, which is lower than the line pressure PL, to be supplied as a holding pressure to the C 1 switching valve 80 during the abnormality described above. When the C 2 /B 3 switching valve 60 establishes the second state, in addition, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 , and the B 3 switching valve 70 is supplied with the modulator pressure Pmod as a signal pressure to establish the communicated state in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 . When the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the B 3 switching valve 70 in the communicated state, however, the B 3 switching valve 70 establishes the blocked/discharge state in which supply of a hydraulic pressure from the C 2 linear solenoid valve SLC 2 to the brake B 3 is blocked and a hydraulic pressure can be discharged from the brake B 3 . Thus, even if the B 1 solenoid pressure Pslb 1 is output from the B 1 linear solenoid valve SLB 1 as a hydraulic pressure is no longer supplied from the C 1 linear solenoid valve SLC 1 as normal, the brake B 1 and the brake B 3 are not engaged at the same time as each other.

In the embodiment described above, in addition, the C 1 switching valve 80 includes the spool 801 disposed so as to be axially movable and capable of establishing the first supply state and the second supply state, and the spring 802 which urges the spool 801 , and the spool 801 includes the first pressure receiving surface 801 a which receives the urging force of the spring 802 , the second pressure receiving surfaces 801 b and 801 c which are spaced from each other in the axial direction to face each other and which each receive the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 , and the holding pressure receiving surface 801 d which receives the line pressure PL or the modulator pressure Pmod serving as a holding pressure. When the C 2 /B 3 switching valve 60 establishes the second state described above, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is applied to the first pressure receiving surface 801 a of the spool 801 of the C 1 switching valve 80 .

Consequently, during an abnormality in which the C 1 solenoid pressure Pslc 1 is not supplied from the C 1 linear solenoid valve SLC 1 as normal, the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is applied to the first pressure receiving surface 801 a of the spool 801 . Thus, the C 1 switching valve 80 establishes the second supply state with the sum of the thrust applied to the spool 801 by the effect of the C 2 solenoid pressure Pslc 2 on the first pressure receiving surface 801 a , the thrust applied to the spool 801 by the effect of the B 1 solenoid pressure Pslb 1 on the second pressure receiving surfaces 801 b and 801 c , and the urging force of the spring 802 applied to the spool 801 exceeding the thrust applied to the spool 801 by the effect of the modulator pressure Pmod on the holding pressure receiving surface. Thus, with the hydraulic control device 50 according to the embodiment, it is possible to reduce the urging force (rigidity) required for the spring 802 when the C 1 switching valve 80 is brought into the second supply state, which allows the C 1 switching valve 80 to be more reliably maintained in the first supply state by the line pressure PL or the modulator pressure Pmod supplied as a holding pressure to the C 1 switching valve 80 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal. It should be noted, however, that the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 may not be applied to the first pressure receiving surface 801 a of the spool 801 , depending on the rigidity of the spring 802 . Instead of forming the second pressure receiving surfaces 801 b and 801 c on the spool 801 , the C 1 switching valve 80 may be configured such that the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 is supplied to the port 86 (spring chamber) so that the first pressure receiving surface 801 a of the spool 801 also serves as the second pressure receiving surface which receives the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 .

In the embodiment described above, further, the clutch C 1 is engaged at least when the first speed and the second speed are established in the automatic transmission 30 , and the brake B 1 is engaged at least when the second speed is established in the automatic transmission 30 . Thus, with the hydraulic control device 50 according to the embodiment described above, during an abnormality in which the C 1 solenoid pressure Pslc 1 is not supplied from the C 1 linear solenoid valve SLC 1 as normal, start and forward travel of the vehicle at the second speed can be ensured by engaging the clutch C 1 using the line pressure PL from the primary regulator valve 51 , and engaging the brake B 1 .

With the hydraulic control device 50 according to the embodiment, when the C 1 solenoid pressure Pslc 1 for the clutch C 1 is no longer supplied by the C 1 linear solenoid valve SLC 1 with operation of the engine 12 stopped and with the oil pump 29 no longer generating a hydraulic pressure, the hydraulic pressure Pemop from the electromagnetic pump EMOP can be supplied to the clutch C 1 by switching the C 1 switching valve 80 into the second supply state and actuating the electromagnetic pump EMOP. In addition, since the line pressure PL from the primary regulator valve 53 can be supplied to the clutch C 1 utilizing a part of the oil passage L 1 which connects between the electromagnetic pump EMOP and the C 1 switching valve 80 , it is possible to suppress an increase in number of oil passages and hence an increase in cost and device size. With the hydraulic control device 50 according to the embodiment described above, it is possible to suppress erroneous supply of the line pressure PL from the primary regulator valve 51 to the clutch C 1 when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal as discussed above, and thus to favorably suppress application of the line pressure PL to the electromagnetic pump EMOP via the oil passage L 2 and the oil passage L 1 , which adversely affects the electromagnetic pump EMOP, when the C 1 solenoid pressure Pslc 1 is supplied from the C 1 linear solenoid valve SLC 1 as normal.

While using the electromagnetic pump EMOP as in the embodiment described above enables a reduction in size of the hydraulic control device 50 and hence the entire power transfer device 20 , it should be understood that an electric pump may be used in place of the electromagnetic pump EMOP. In the hydraulic control device 50 according to the embodiment, the check valve 89 is provided in the oil passage L 2 . In place of the check valve 89 , however, an on-off valve that is opened when it is determined that an abnormality has occurred in the state of supply of the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 , for example, may be disposed in the oil passage L 2 .

Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the “SUMMARY OF THE INVENTION” section will be described. In the embodiment described above, the hydraulic control device 50 of the automatic transmission 30 capable of transferring power applied to the front cover 18 to the output shaft 37 at a speed change ratio that is changeable in a plurality of stages by engaging and disengaging the plurality of clutches C 1 and C 2 and the brake B 1 etc. corresponds to the “hydraulic control device”. The C 1 linear solenoid valve SLC 1 which regulates the C 1 solenoid pressure Pslc 1 to be supplied to the clutch C 1 corresponds to the “first pressure regulation valve”. The B 1 linear solenoid valve SLB 1 which regulates the B 1 solenoid pressure Pslb 1 to be supplied to the brake B 1 which is engaged at the same time as the clutch C 1 during an abnormality in which the C 1 solenoid pressure Pslc 1 is not supplied from the C 1 linear solenoid valve SLC 1 as normal corresponds to the “second pressure regulation valve”. The primary regulator valve 51 which regulates a hydraulic pressure from the oil pump 29 to generate the line pressure PL corresponds to the “line pressure generation valve”. The C 1 switching valve 80 which is capable of establishing the first supply state, in which the C 1 solenoid pressure Pslc 1 from the C 1 linear solenoid valve SLC 1 can be supplied to the clutch C 1 , and the second supply state, in which the line pressure PL from the primary regulator valve 51 can be supplied to the clutch C 1 , and which can receive the line pressure PL or the modulator pressure Pmod serving as a holding pressure for holding the first supply state and a hydraulic pressure from the B 1 linear solenoid valve SLB 1 corresponds to the “switching valve”. The C 2 linear solenoid valve SLC 2 which regulates the C 2 solenoid pressure Pslc 2 to be supplied to the brake B 3 which is normally not engaged at the same time as the brake B 1 corresponds to the “third pressure regulation valve”. The B 3 switching valve 70 which is capable of establishing the blocked/discharge state, in which supply of the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 to the brake B 3 is blocked and a hydraulic pressure can be discharged from the brake B 3 , and the communicated state, in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 , and which can receive the line pressure PL or the modulator pressure Pmod serving as a signal pressure for establishing the blocked/discharge state and the communicated state and the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 corresponds to the “second switching valve”. The C 2 /B 3 switching valve 60 which is capable of establishing the first state, in which the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 can be supplied to the clutch C 2 which is not engaged at the same time as the brake B 3 , and the second state, in which the C 2 solenoid pressure from the C 2 linear solenoid valve SLC 2 can be supplied to the brake B 3 and a hydraulic pressure can be discharged from the clutch C 2 , corresponds to the “third switching valve”. The solenoid valve S 1 which outputs the solenoid pressure Ps 1 serving as a signal pressure for switching the C 2 /B 3 switching valve 60 from the first state into the second state when the C 2 solenoid pressure Pslc 2 from the C 2 linear solenoid valve SLC 2 is supplied to the brake B 3 and during the abnormality described above corresponds to the “signal pressure output valve”. The spool 801 disposed so as to be axially movable and capable of establishing the first supply state and the second supply state corresponds to the “spool”. The spring 802 which urges the spool 801 corresponds to the “spring”. The first pressure receiving surface 801 a which receives the urging force of the spring 802 corresponds to the “first pressure receiving surface”. The second pressure receiving surfaces 801 b and 801 c which receive the B 1 solenoid pressure Pslb 1 from the B 1 linear solenoid valve SLB 1 correspond to the “second pressure receiving surface”. The holding pressure receiving surface 801 d which receives the line pressure PL or the modulator pressure Pmod as a holding pressure corresponds to the “holding pressure receiving surface”. The electromagnetic pump EMOP driven by electric power corresponds to the “second hydraulic pressure generation source”. The oil pump 29 which is mechanical and driven by power from the engine 12 corresponds to the “hydraulic pressure generation source” and the “mechanical pump”. The oil passage L 1 corresponds to the “first oil passage”. The oil passage L 2 corresponds to the “second oil passage”. The check valve 89 corresponds to the “valve”.

The correspondence between the main elements of the embodiment etc. and the main elements of the invention described in the “SUMMARY OF THE INVENTION” section does not limit the elements of the invention described in the “SUMMARY OF THE INVENTION” section, because the embodiment etc. are examples given for the purpose of specifically describing the invention described in the “SUMMARY OF THE INVENTION” section. That is, the embodiment etc. are merely specific examples of the invention described in the “SUMMARY OF THE INVENTION” section, and the invention described in the “SUMMARY OF THE INVENTION” section should be construed on the basis of the description in that section.

While a mode for carrying out the present invention has been described above by way of an embodiment, it is a matter of course that the present invention is not limited to the embodiment in any way, and that the present invention may be modified in various ways without departing from the scope and sprit of the present invention.

The present invention can be utilized in the hydraulic control device manufacturing industry.