JP2007263152A - Hydraulic control device for automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To safely implement forward movement low-speed stage or backward movement stage even in a primary failure. <P>SOLUTION: A hydraulic control device for an automatic transmission comprises: first off-fail valves 24 switched to keep a spool position of a gear stage before a failure state and output D pressure/R pressure, in the failure state where no hydraulic pressure is output from any of SL1 to SL4; a lock valve 21 switching spool positions so as to output output pressure from a predetermined one of SL1 to SL4 or the D pressure/R pressure; an on-off solenoid valve S which can control a spool position of the lock valve according to an energization state; and a second off-fail valve 25 switching spool positions, so as to output the D pressure/R pressure from the first off-fail valve 24 to a predetermined one of engaging elements C1 to C3 in the failure state, and so as to output hydraulic pressure from the lock valve 21 to a predetermined one of engaging elements C1 to C3 in a normal state where hydraulic pressure sent from any of SL1 to SL4 as prescribed. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a hydraulic control device for an automatic transmission that uses an oil from a hydraulic power source to simultaneously engage and disengage an engagement element with a direct solenoid valve, and in particular, the vehicle travels in an off-fail state. The present invention relates to a hydraulic control device for an automatic transmission that engages a predetermined engagement element so as to be possible.

  2. Description of the Related Art In recent years, a hydraulic control device for an automatic transmission employs a so-called clutch-to-clutch control method in which an engagement element is simultaneously engaged and released by a direct solenoid valve (linear solenoid valve) using oil from a hydraulic source. A smooth and highly responsive shift feeling has been realized. In such a hydraulic control device for an automatic transmission, when a solenoid valve breaks down due to disconnection, disconnection of a connector, etc., and a so-called off-fail state in which no hydraulic pressure is output is set, a predetermined amount is set so that the vehicle can run. A technique for engaging the engaging elements has been proposed (see, for example, Patent Document 1).

In the hydraulic control circuit of the automatic transmission for a vehicle of Patent Document 1, the valve operating state at the time of off-failure is stored or maintained by the first switching valve (202 in FIG. 6 of the same document), and the second switching valve (of FIG. during off failure by 204) a predetermined source pressure P _D is supplied to the brake B3, and the first oil passage and (220 in the same drawing) and a second oil passage (224 in the figure) of the clutch C1 and the clutch C2, respectively The valve operating state is switched so as to be supplied to. As a result, when the vehicle running state at the time of off-fail is the low / medium speed side gear stage, the brake B3 and the clutch C1 are engaged to establish the low / medium speed side gear stage (third speed stage), and the high speed side If it is a gear stage, the brake B3 and the clutch C2 are engaged to establish a high speed side gear stage (fifth speed stage), and the vehicle travels appropriately regardless of the solenoid valve during off-fail. It is said that.

  Here, in the gear train of the automatic transmission, one of the two engagement elements for forming the reverse gear (R range) is also engaged at the time of the first forward gear (D range) 1st (generally a brake). The other is an engagement element (generally a clutch, used for 3rd, 5th, etc.) that is also fastened to a predetermined gear stage other than the first stage of the forward gear. In the hydraulic control device for a multi-stage automatic transmission, in order to avoid the configuration of the above-mentioned two engagement elements, that is, the reverse speed (hereinafter referred to as Rev), when the vehicle is moving forward, it is provided with a brake shared by 1st and Rev. -2 one-way clutch (hereinafter 1-2OWC) is installed, and the 1st and Rev common brakes are limited to the use of engine brakes (low coast) only when moving forward, fail safe is implemented, and the Rev configuration It is avoiding. However, if 1-2OWC is abolished, the cost will be greatly reduced, and the advantages of reducing the axial length of the automatic transmission and the weight of the automatic transmission will be great. In addition, when the number of stages is increased, even in the direct pressure control system, an increase in electromagnetic valves (such as linear solenoid valves) with respect to the engaging elements is disadvantageous in terms of cost and the structure space of the hydraulic control device. An electromagnetic valve having a small number of first brakes shared with other electromagnetic valves is disclosed (see, for example, Patent Documents 2 and 3).

  In the hydraulic control device for an automatic transmission of Patent Document 2, a solenoid valve (on / off solenoid valve) that switches between a low speed stage switching valve (51 in FIG. 4) and a high speed stage switching valve (52 in FIG. 4). SL1 is provided, and the hydraulic pressure of the hydraulic servo (82 in the figure) of the engagement element C-2 that is always engaged when the high speed stage is achieved is applied to the low speed stage switching valve and the high speed stage switching valve. When the hydraulic pressure detecting means S / W detects the hydraulic pressure of the hydraulic servos of the three or more engaging elements that cause the interlock, the solenoid valve SL1 is operated, and when the low speed stage is achieved, the predetermined speed stage on the low speed stage side is operated. When the high speed stage is achieved, it is configured to switch to a predetermined shift stage on the high speed stage side. Further, in order to reduce the linear solenoid valve (linear solenoid valve) by one, the output pressure of the linear solenoid valve SLC2 is set so that the linear solenoid valve SLC2 for the engagement element C-2 can also be used for the engagement element B-2. The solenoid valve SL1 is switched so that it is supplied to the input port of the engagement element C-2 or the switching valve (53 in the figure) by the switching valve (52 in the figure) by the switching operation. Further, the hydraulic pressure supplied to the engagement element B-2 by the switching valve (53 in the figure) by the switching operation of the solenoid valve SL2 is R pressure (line pressure PL supplied from the manual valve only in the R range) or SLC2 pressure (control hydraulic pressure output from linear solenoid valve SLC2) is selected to achieve engine braking or reverse at 1st. In Patent Document 2, since the hydraulic pressure is supplied to the engagement element C3 at a high speed, the hydraulic pressure is cut off by the high-speed stage switching valve (52 in the figure) at the low speed stage where the engagement element B2 operates. Since the configuration is avoided, it is not intended to eliminate the 1-2OWC (there is a one-way clutch F-1 in FIG. 1 of the same document), but the engagement element B2 for low coast control and reverse control, The purpose is to share the high-speed stage engaging element C2 with one linear solenoid valve SLC2.

  In the hydraulic control system for a 6-speed automatic transmission for a vehicle disclosed in Patent Document 3, a line pressure control unit (A in FIG. 4 of the same document) that varies the line pressure according to operating conditions while maintaining a constant hydraulic pressure, and a torque converter A start control unit (B in the figure) that performs torque increase distribution and control of the damper clutch, a pressure reduction control part (C in the figure) that supplies the line pressure as a control pressure, and a shift control unit (C) D) in the figure and a fail-safe control unit (E in the figure), and the shift control unit (D in the figure) is configured to reduce the decompression supplied from the reducing valve (22 in the figure) and the decompression. Forward pressure supplied from a manual valve (24 in the figure) controlled by first, second, third, and fourth solenoid valves (duty solenoid valves; SS1, SS2, SS3, SS4 in the figure) to be controlled. It is configured to include first, second, third, and fourth pressure control valves (control valves; 26, 28, 30, and 32 in the figure) that control the reverse pressure and supply hydraulic pressure to at least one friction member. ing. Further, in order to reduce the solenoid valve (linear solenoid valve) and the pressure control valve (control valve) by one set, the fourth solenoid valve (SS4 in the figure) for the third clutch C3 and the fourth pressure control valve (in the figure). 32) is switched by an on / off solenoid valve (SS5 in the figure) and a switch valve (switching valve; 40 in the figure) so that it can also be used for the first brake B1 (B2 in Document 1). A second fail-safe valve (44 in the figure) is arranged between the brake B1 and the switch valve (40 in the figure). As a result, the output pressure of the fourth pressure control valve (32 in the figure) controlled by the fourth solenoid valve (SS4 in the figure) is operated by the on / off solenoid valve (SS5 in the figure). 40) of the figure selects one of the input ports of the third clutch C3 and the second fail-safe valve (44 of the figure). The second fail-safe valve (44 in the figure) releases the first brake B1 when two or more pressures of the second brake B2 and the second clutch C2 are operated, and otherwise outputs the output pressure. The first brake B1 is connected. In Patent Document 3, the gear train is the same as that in Patent Document 2, and C2 in Patent Document 2 is described as C3, and B2 is also described as B1.

JP-A-2005-24059 JP 2005-140215 A Japanese Patent Laying-Open No. 2005-3191

  However, when the off-fail configuration such as the hydraulic control circuit of the automatic transmission for a vehicle in Patent Document 1 is installed in an automatic transmission for commercial and truck use, the clutch C1 is caused by a primary failure of the solenoid valve SL1 for the clutch C1. If hydraulic pressure is not supplied, 3rd traveling is possible in an off-fail state. However, unlike ATs for passenger cars, there is a possibility that the driving force will be insufficient at 3rd on a truck with a large load. Similarly, if the hydraulic control system pressure of the oil vehicle 6-speed automatic transmission is no longer supplied to the brake B3 due to the primary failure of the solenoid valve SL5 for the brake B3, the vehicle can travel 3rd or 5th when traveling forward. It becomes impossible to change the direction of the reverse and the work after the reverse on a truck with a large vehicle, so that not only the work cannot be performed but also the nearest service station may not be reached.

  Further, in the hydraulic control system for a 6-speed automatic transmission for a vehicle disclosed in Patent Document 3, during reverse travel, the second solenoid valve (SS2 in FIG. 4 of the same document) is duty-controlled, and the second fail-safe valve (44 in FIG. 4). ), The on / off solenoid valve (SS5 in the figure) or the switch valve (40 in the figure) has a primary failure, and the hydraulic pressure is supplied from the first brake B1 to the third. When switching to the clutch C3, there is a risk of traveling for 5th. Further, there is a possibility that the vehicle cannot move backward due to a failure of the solenoid valve or a primary failure of the pressure control valve. Further, during forward travel, the ON / OFF solenoid valve (SS5 in the figure) or the switch valve (40 in the figure) is finally broken during the 5th traveling of the high speed stage, and the hydraulic pressure supply is changed from the third clutch C3 to the first. When switching to the brake B1, the fail-safe valve (44 in the figure) operates to cut the B1 pressure, but the B1 pressure is supplied for a predetermined time until the predetermined pressure is reached, the reverse configuration is established, and the vehicle is suddenly decelerated, etc. Risk of danger.

  The main subject of this invention is enabling it to achieve a forward low-speed stage and a reverse stage safely even if a primary failure occurs.

  In an aspect of the present invention, an automatic transmission in which a gear position is switched by a combination of supply of hydraulic pressure to some of the engagement elements and discharge of hydraulic pressure from other engagement elements is provided. A hydraulic pressure control device that adjusts line pressure input to a supply port according to an energized state to generate a control hydraulic pressure, outputs the control hydraulic pressure as an output pressure from an output port, and corresponds to the control hydraulic pressure according to the control hydraulic pressure A plurality of control valves for controlling the engagement and disengagement of the engagement elements, and a spool, and a shift before entering the fail state when a fail state occurs in which no hydraulic pressure is output from any of the control valves. A first off-fail valve which is switched to output the line pressure while maintaining the spool position of the stage, and an output pressure from the predetermined control valve; A lock valve whose spool position is switched so as to output a line pressure, an on-off solenoid valve capable of controlling the spool position of the lock valve in accordance with an energized state, and the first off-fail valve in the fail state The line pressure from the lock valve is output toward the predetermined engagement element, and when the hydraulic pressure of the predetermined control valve is output, the hydraulic pressure from the lock valve is directed toward the predetermined engagement element. And a second off-fail valve whose spool position is switched so as to be output.

  In the hydraulic control apparatus for an automatic transmission according to the present invention, the predetermined engagement element that can receive the hydraulic pressure output from the second off-fail valve includes an engagement element used in a low / medium speed stage configuration, and a high speed It is preferable that an engagement element used in the stage configuration and an engagement element used in the reverse stage configuration are included.

  In the hydraulic control apparatus for an automatic transmission according to the present invention, a predetermined output pressure of the control valve is directed to an engagement element used at a high speed stage or an engagement element used at a low / medium speed stage and a reverse stage. And a second on / off solenoid valve capable of controlling the spool position of the relay valve according to the energized state, wherein the second off-fail valve is a forward gear. In the normal state, the line pressure at the forward stage is supplied to the predetermined control valve, and the line pressure at the forward stage is not supplied to the control valve at the failure state. The relay valve is an engagement element used when the output pressure of the predetermined control valve is at the low / medium speed stage and the reverse stage at the reverse stage. The line pressure at the reverse stage is supplied to the predetermined control valve when being output toward the predetermined position, and the output pressure of the predetermined control valve is output toward the engagement element used at the high speed stage. Engaging the line pressure (R pressure) at the time of the reverse speed and at the time of the low and medium speed speeds and at the reverse speed by shutting off the supply of the line pressure at the reverse speed to the predetermined control valve. The relay valve outputs a predetermined output pressure of the control valve at the high speed stage when hydraulic pressure is applied to the engaging element used at the high speed stage and the reverse stage at the forward stage. It is preferable to have a hydraulic chamber that switches to output towards the engagement element that is sometimes used.

  In the hydraulic control apparatus for an automatic transmission according to the present invention, the relay valve maintains a spool position when outputting a predetermined output pressure of the control valve toward an engagement element used at the high speed stage. It is preferable to have a hydraulic chamber that acts as such.

In the hydraulic control device for an automatic transmission according to the present invention, the relay valve is disposed in an oil passage that leads from the relay valve to an engagement element that is used during the low and medium speed stages and the reverse stage, and the output pressure of the relay valve; Or, it comprises an apply valve whose spool position is switched so as to output the line pressure at the reverse stage toward the engagement element used at the low and medium speed stages and the reverse stage,
When the apply valve is engaged at the same time as the engagement element used at the low and medium speed stages and the reverse stage when the output pressure of the relay valve is input at the forward stage, an interlock is generated. It is preferable to have a hydraulic chamber that acts so as not to output the output pressure of the relay valve toward the engagement element used at the low and medium speed stages and the reverse stage when the hydraulic pressure applied to the engagement element exceeds a predetermined value. .

  It should be noted that the reference numerals attached to the claims of the claims are only for the purpose of facilitating understanding, and are not intended to limit the present invention to the embodiments of the drawings.

  According to the present invention (Claims 1 and 2), even if the control valve unit (for example, SL1) is turned off, the lock valve is operated by the on / off solenoid and the predetermined engagement element (for example, C1) is connected to D. Since pressure can be supplied, it is possible to travel even at a low speed (for example, the second speed). Further, even when a control valve unit (for example, SL3) for a predetermined engagement element (for example, C3) is turned off during reverse gear travel, the lock valve is operated by the on / off solenoid S to operate the predetermined engagement element (for example, SL3). For example, since the R pressure can be supplied to C3), it is possible to travel backward.

  According to the present invention (Claim 3-5), it is possible to secure the reverse gear even if a predetermined control valve unit is turned off. Further, it is ensured that a reverse failure is caused by a primary failure at the time of forward movement, and even in the case of a secondary failure, the hydraulic pressure is supplied to one or both of the third friction clutch C3 and the second friction brake B2. Since it can be cut, it is possible to avoid a reverse configuration.

(Embodiment 1)
A hydraulic control device for an automatic transmission according to Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram showing the overall configuration of a hydraulic control device for an automatic transmission according to Embodiment 1 of the present invention. The hydraulic control device for the automatic transmission includes an automatic transmission 1, a hydraulic control unit 3, and an electronic control unit 4. The automatic transmission 1 is connected to an output shaft (not shown) of the engine 2. The hydraulic control unit 3 controls supply of hydraulic pressure to a hydraulically driven friction engagement element (not shown) incorporated in the automatic transmission 1. The electronic control unit 4 drives and controls a solenoid (not shown) provided in the hydraulic control unit 3.

  The electronic control unit 4 includes a microcomputer, and includes an engine speed sensor (Ne sensor) 5, an input shaft speed sensor (Nt sensor) 6, an output shaft speed sensor (No sensor) 7, an opening sensor (θ Sensor) 8 and position sensor 9. The engine speed sensor (Ne sensor) 5 detects the speed Ne of the output shaft of the engine 2. The input shaft rotational speed sensor (Nt sensor) 6 detects the rotational speed Nt of the input shaft 11 of the automatic transmission 1. The output shaft rotational speed sensor (No sensor) 7 detects the rotational speed (corresponding to the vehicle speed of the vehicle) No of the output shaft 12 of the automatic transmission 1. The opening sensor (θ sensor) 8 detects the throttle opening (corresponding to the engine load) θ of the engine 2. The position sensor 9 detects the position (traveling range) of the selector lever that is operated by the driver. The electronic control unit 4 controls energization to the control valve units SL1 to SL4 and the on / off solenoid valves S1 to S3 based on the outputs of the sensors 5 to 9. Thereby, a required gear stage is achieved (see FIG. 3).

  FIG. 2 is a skeleton diagram of the automatic transmission in the hydraulic control device for the automatic transmission according to the first embodiment of the present invention. The automatic transmission (1 in FIG. 1) includes a torque converter 10, an input shaft 11, an output shaft 12, a first row double pinion planetary gear G1, a second row single pinion planetary gear G2, and a third row single pinion planetary gear. G3. The torque converter 10 is connected to the output shaft of the engine (2 in FIG. 1). In addition, the torque converter 10 is a lock that directly connects the input-side pump impeller 10b and the output-side turbine runner 10a when the rotational difference between them is small in order to avoid power transmission loss due to fluid slip. An up clutch LU is provided. The input shaft 11 is an output shaft of the torque converter 10. The output shaft 12 is connected to the axle via a differential (not shown). The first row double pinion planetary gear G 1, the second row single pinion planetary gear G 2, and the third row single pinion planetary gear G 3 are connected to the input shaft 11. The automatic transmission 1 includes a first friction clutch C1, a second friction clutch C2, a third friction clutch C3, a first friction brake B1, and a second friction brake as a plurality of (six) friction engagement elements. B2 and the lockup clutch LU are incorporated. The automatic transmission 1 is connected to the first to third friction clutches C1 to C3 and the first and second friction brakes B1 and B2 by a hydraulic control unit (3 in FIG. 1) and an electronic control unit (4 in FIG. 1). By selecting the engagement / disengagement, the gear position and the shift pattern are switched. The lock-up clutch LU is engaged when the rotational difference between the pump impeller 10b and the turbine runner 10a is small under the control of the hydraulic control unit (3 in FIG. 1) and the electronic control unit (4 in FIG. 1). Match. In the third row single pinion planetary gear G3, a one-way clutch OWC is disposed in parallel with the second friction brake B2. The first to third friction clutches C1 to C3, the first and second friction brakes B1 and B2, and the lockup clutch LU are brought into an engaged state by being set to high pressure by the hydraulic control unit 3, respectively. The disengaged state is established by setting the pressure to low. The second friction brake B2 may be divided into two B2S and B2L.

  FIG. 3 shows engagement / non-engagement of the first to third friction clutches C1 to C3 and the first and second friction brakes B1 and B2 of the automatic transmission in the hydraulic control device for the automatic transmission according to the first embodiment of the present invention. It is a list figure which shows the relationship between engagement and the gear stage corresponding to it. The automatic transmission (1 in FIG. 1) can achieve a reverse speed, neutral, 1st to 4th speed underdrive, 5th speed and 6th speed overdrive, 6 forward speeds and 1 reverse speed. It is a simple transmission. That is, when only the third friction clutch C3 and the second friction brake B2 are engaged, the rotation of the output shaft (12 in FIG. 2) is reversed with respect to the input shaft (11 in FIG. 2) to reverse the vehicle. It is supposed to let you. Further, when only the second friction brake B2 is engaged, a neutral state is established. Further, when only the first friction clutch C1 (including the second friction brake B2 at the time of low coast control) is engaged, the first speed is achieved. When only the first friction clutch C1 and the first friction brake B1 are engaged, the second speed is achieved. When only the first and third friction clutches C1 and C3 are engaged, the third speed is achieved. When only the first and second friction clutches C1 and C2 are engaged, the fourth speed is achieved. When only the second and third friction clutches C2 and C3 are engaged, the fifth speed is achieved. When only the second friction clutch C2 and the first friction brake B1 are engaged, the sixth speed is achieved. FIG. 3 also shows the basic relationship between the driving range (R range, N range, D range) selected by the driver operating the manual lever (not shown) and the gear position.

  Here, a linear solenoid is generally avoided by disposing the 1-2OWC (one-way clutch) in the second friction brake B2 and separating the low-coast control for avoiding the reverse gear configuration and for the 1-2 shift. Can be reduced by one. As a result, the cost can be reduced, the shift shock can be reduced, the inability to travel the first time due to the OFF failure of the linear solenoid valve for B2, and the D → N accumulator for B2 can also be avoided. Can be abolished. Even if 1-2 OWC is arranged, there is an advantage that it is not necessary to add an engagement element for avoiding OWC lock.

  Next, a configuration of a hydraulic control unit and a control mode thereof in the hydraulic control device for an automatic transmission according to the first embodiment of the present invention will be described with reference to the drawings. FIG. 4 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in the hydraulic control device for an automatic transmission according to the first embodiment of the present invention.

  The hydraulic control unit 3 includes first to fourth control valve units SL1 to SL4, a lock valve 21, an on / off solenoid valve S, a first on-fail valve 22, a second on-fail valve 23, and a first off-fail. The valve 24, the second off-fail valve 25, the shuttle valve SB, the NR accumulator 26, and the DN accumulator 27 are included.

  The first control valve unit SL1 is a control valve unit for the first friction clutch C1, and is formed by integrating a linear solenoid valve and a control valve. The first control valve unit SL1 may have a configuration in which the linear solenoid valve and the control valve are separated. The first control valve unit SL1 supplies the line pressure PL (D pressure) output from a manual valve (not shown) in the D range to the normal first on-fail valve 22, the orifice and the check ball valve (main And a control oil pressure (SL1 pressure) is generated from the D pressure introduced according to the energization amount and output from the output port. The SL1 pressure is supplied to the second switching circuit 21f of the lock valve 21, the third switching circuit 24i of the first off-fail valve 24, and the third hydraulic chamber 24f. The first control valve unit SL1 is a normal low type (NL) that does not output the SL1 pressure in the non-energized state and outputs the SL1 pressure that increases as the energized current increases in the energized state. The first control valve unit SL1 communicates the output port and the discharge port (EX) in a non-energized state.

  The second control valve unit SL2 is a control valve unit for the second friction clutch C2, in which a linear solenoid valve and a control valve are integrated. The second control valve unit SL2 may have a configuration in which the linear solenoid valve and the control valve are separated. The second control valve unit SL2 introduces the D pressure, generates a control hydraulic pressure (SL2 pressure) from the D pressure introduced according to the energization amount, and outputs it. The SL2 pressure is supplied to the first hydraulic chamber 24d of the first off-fail valve 24, the third switching circuit 24i, and the C2 switching circuit 25j of the second off-fail valve 25. The second control valve unit SL2 is a normal low type (NL) that does not output the SL2 pressure in the non-energized state and outputs the SL2 pressure that increases as the energized current increases in the energized state. The second control valve unit SL2 communicates the output port and the discharge port (EX) in a non-energized state.

  The third control valve unit SL3 is a control valve unit for the third friction clutch C3, in which a linear solenoid valve and a control valve are integrated. The third control valve unit SL3 may have a configuration in which the linear solenoid valve and the control valve are separated. The third control valve unit SL3 introduces the PL pressure, generates a control hydraulic pressure (SL3 pressure) from the PL pressure introduced according to the energization amount, and outputs this. The SL3 pressure is supplied to the shuttle valve SB, the first switching circuit 21e of the lock valve 21, and the first hydraulic chamber 25e of the second off-fail valve 25. The third control valve unit SL3 is a normal low type (NL) that does not output the SL3 pressure in the non-energized state and outputs the SL3 pressure that increases as the energized current increases in the energized state. The third control valve unit SL3 communicates the output port and the exhaust port (EX) in a non-energized state.

  The fourth control valve unit SL4 is a control valve unit for the first friction brake B1, and includes a linear solenoid valve and a control valve. The fourth control valve unit SL4 may have a configuration in which the linear solenoid valve and the control valve are separated. The fourth control valve unit SL4 introduces the D pressure through the second on-fail valve 23 in a normal state and generates a control hydraulic pressure (SL4 pressure) from the D pressure introduced according to the energization amount. Is output. The SL4 pressure is supplied to the first friction brake B1 and the second hydraulic chamber 25f of the second off-fail valve 25. The fourth control valve unit SL4 is a normal low type (NL) that does not output SL4 pressure in the non-energized state and outputs SL4 pressure that increases as the energized current increases in the energized state. The fourth control valve unit SL4 communicates the output port and the discharge port (EX) in a non-energized state.

  The lock valve 21 is a switching valve that switches an oil passage, and is a spool that outputs an output pressure from predetermined control valve units SL1 and SL3 or a line pressure (D pressure, R pressure) according to a shift state. The position is switched. The lock valve 21 has a spool 21a, a spring 21b, a first hydraulic chamber 21c, and a second hydraulic chamber 21d in a valve body (not shown). The spool 21a is slidably arranged in a valve body (not shown). The spring 21b is disposed in the second hydraulic chamber 21d and urges the spool 21a toward the first hydraulic chamber 21c. The first hydraulic chamber 21c is a hydraulic chamber that acts to press the spool 21a against the second hydraulic chamber 21d side when the hydraulic pressure from the on / off solenoid valve S is introduced. The second hydraulic chamber 21d is a hydraulic chamber that acts to press the spool 21a against the first hydraulic chamber 21c by introducing the hydraulic pressure (C2 pressure) applied to the second friction clutch C2. The spool 21a has a second hydraulic chamber 21d side (“◯”) when the pressing force of the first hydraulic chamber 21c is higher than the resultant force of the urging force of the spring 21b and the pressing force of the second hydraulic chamber 21d. ) And when it is low, it slides toward the first hydraulic chamber 21c (“×”). The lock valve 21 communicates the output port of the third control valve unit SL3 and the C3 switching circuit 25k of the second off-fail valve 25 when “x”, and the shuttle valve SB and the second off-fail when “◯”. A first switching circuit 21e is provided for switching the C3 switching circuit 25k of the valve 25 so as to communicate with each other. The lock valve 21 communicates the output port of the first control valve unit SL1 with the C1 switching circuit 25i of the second off-fail valve 25 when “x”, and the first on-fail valve 22 when “◯”. And a second switching circuit 21f that switches the C1 switching circuit 25i of the second off-fail valve 25 to communicate with each other. An oil passage between the lock valve 21 and the first on-fail valve 22 has an orifice and a check ball valve.

  The on / off solenoid valve S switches the operating state of the spool 21a of the lock valve 21 in accordance with switching between energization and non-energization. The on / off solenoid valve S is a normal low type (NL) that does not supply signal pressure to the lock valve 21 in a non-energized state and supplies signal pressure to the lock valve 21 in an energized state.

  The first on-fail valve 22 is a switching valve that switches an oil passage, and has a first spool 22a, a second spool 22b, a sleeve 22c, a spring 22d, and a first hydraulic chamber in a valve body (not shown). 22e, a second hydraulic chamber 22f, and a third hydraulic chamber 22g. The first spool 22a is slidably arranged in a valve body (not shown). The second spool 22b is disposed in a valve body (not shown) so as to be slidable between the first spool 22a and the spring 22d. The sleeve 22c is disposed on the outer periphery of the second spool 22b and has an oil hole for introducing the hydraulic pressure (C2 pressure) applied to the second friction clutch C2 into the third hydraulic chamber 22g. The spring 22d is disposed in the third hydraulic chamber 22g and urges the first spool 22a and the second spool 22b toward the first hydraulic chamber 22e. The first hydraulic chamber 22e is a hydraulic chamber that acts to press the first spool 22a against the third hydraulic chamber 22g side when the PL pressure is introduced. The second hydraulic chamber 22f is a hydraulic chamber that acts to press the first spool 22a against the first hydraulic chamber 22e by introducing the hydraulic pressure (C3 pressure) applied to the third friction clutch C3. The third hydraulic chamber 22g is a hydraulic chamber that acts to press the first spool 22a and the second spool 22b against the first hydraulic chamber 22e side when the C2 pressure is introduced. In the first spool 22a, the pressing force due to the hydraulic pressure of the first hydraulic chamber 22e is greater than the resultant force of the pressing force due to the urging force of the spring 22d, the hydraulic pressure of the second hydraulic chamber 22f, and the pressing force due to the hydraulic pressure of the third hydraulic chamber 22g. When it is high, it slides toward the third hydraulic chamber 22g (“normal”), and when it is low, it slides toward the first hydraulic chamber 22e (“fail”). The first on-fail valve 22 supplies the D pressure introduced when “normal” to the supply port of the first control valve unit SL1 and the second switching circuit 21f of the lock valve 21 through the orifice and the check ball valve. In the case of “Fail”, the supply port of the first control valve unit SL1 and the second switching circuit 21f of the lock valve 21 are switched through the orifice and the check ball valve so as to communicate with the discharge port (EX). The first spool 22a and the second spool 22b of the first on-fail valve 22 may be integrated.

  The second on-fail valve 23 is a switching valve that switches an oil passage, and has a spool 23a, a spring 23b, a first hydraulic chamber 23c, and a second hydraulic chamber 23d in a valve body (not shown). . The spool 23a is slidably arranged in a valve body (not shown). The spring 23b is disposed in the second hydraulic chamber 23d and urges the spool 23a toward the first hydraulic chamber 23c. The first hydraulic chamber 23c is a hydraulic chamber that acts to press the spool 23a against the second hydraulic chamber 23d side when the PL pressure is introduced. The second hydraulic chamber 23d is a hydraulic chamber that acts to press the spool 23a against the first hydraulic chamber 23c side when the hydraulic pressure (C3 pressure) applied to the third friction clutch C3 is introduced. The spool 23a has a second hydraulic chamber 23d side ("normal") when the pressing force of the first hydraulic chamber 23c is higher than the resultant force of the urging force of the spring 23b and the pressing force of the second hydraulic chamber 23d. ) And slide toward the first hydraulic chamber 23c ("fail") when it is low. The second on-fail valve 23 supplies the D pressure to the supply port of the fourth control valve unit SL4 when “normal”, and the supply port and the discharge port (EX) of the fourth control valve unit SL4 when “fail”. ) To communicate.

  The first off-fail valve 24 is a switching valve for switching the oil passage, and the vehicle gear stage before the failure state is reached when a failure state in which no hydraulic pressure is output from any of the control valve units SL1 to SL4 is achieved. Is switched to output the line pressure while maintaining the spool position. The first off-fail valve 24 includes a first spool 24a, a second spool 24b, a spring 24c, a first hydraulic chamber 24d, a second hydraulic chamber 24e, and a third hydraulic pressure in a valve body (not shown). A chamber 24f. The first spool 24a is slidably arranged in a valve body (not shown). The second spool 24b is disposed in a valve body (not shown) so as to be slidable between the first spool 24a and the spring 24c. The spring 24c is disposed in the third hydraulic chamber 24f, and biases the first spool 24a and the second spool 24b toward the first hydraulic chamber 24d. The first hydraulic chamber 24d is configured to press the first spool 24a and the second spool 24b against the third hydraulic chamber 24f side by introducing the control hydraulic pressure (SL2 pressure) output from the second control valve unit SL2. It is a working hydraulic chamber. The second hydraulic chamber 24e is a hydraulic chamber that acts to press the second spool 24b against the third hydraulic chamber 24f side by introducing the hydraulic pressure output from the second switching circuit 24h. The third hydraulic chamber 24f is configured to press the first spool 24a and the second spool 24b against the first hydraulic chamber 24d side when the control hydraulic pressure (SL1 pressure) output from the first control valve unit SL1 is introduced. It is a working hydraulic chamber. In the second spool 24b, at least one of the pressing force by the hydraulic pressure of the first hydraulic chamber 24d and the pressing force by the hydraulic pressure of the second hydraulic chamber 24e is a pressing force by the urging force of the spring 24c and the hydraulic pressure of the third hydraulic chamber 24f. The first hydraulic chamber slides to the third hydraulic chamber 24f side ("5, 6") when the resultant force is higher than the resultant force (5, 6th speed) and lower (when 1-4th gear). Slide to the 24d side (“1-4”). The first off-fail valve 24 communicates the discharge port (EX) with the C1 switching circuit 25i of the second off-fail valve 25 when “5, 6”, and the second D pressure when the pressure is “1-4”. A first switching circuit 24g for switching to supply to the C1 switching circuit 25i of the off-fail valve 25 is provided. The first off-fail valve 24 supplies D pressure to the C2 switching circuit 25j and the second hydraulic chamber 24e of the second off-fail valve 25 when “5, 6”, and the discharge port when “1-4”. (EX) and a second switching circuit 24h that switches the C2 switching circuit 25j of the second off-fail valve 25 and the second hydraulic chamber 24e to communicate with each other. The first off-fail valve 24 supplies the SL2 pressure to the third hydraulic chamber 25g of the second off-fail valve 25 when "5, 6", and the SL1 pressure is the second off-fail when "1-4". A third switching circuit 24i that switches to supply to the third hydraulic chamber 25g of the valve 25 is provided.

  The second off-fail valve 25 is a switching valve for switching the oil path, and the line pressure (D from the first off-fail valve 24 when the hydraulic pressure is not output from any of the control valve units SL1 to SL4. Pressure, R pressure) is output toward a predetermined engagement element (C1, C2, C3), and the hydraulic pressure of a predetermined control valve unit (one or two of SL1 to SL4) is output. Sometimes the spool position is switched so that the output pressure from the predetermined lock valve units SL1 to SL4 is output toward a predetermined engagement element (one or two of C1, C2, C3). The second off-fail valve 25 includes a first spool 25a, a second spool 25b, a third spool 25c, a spring 25d, a first hydraulic chamber 25e, and a second hydraulic chamber in a valve body (not shown). 25f, a third hydraulic chamber 25g, and a fourth hydraulic chamber 25h. The first spool 25a is slidably arranged in a valve body (not shown). The second spool 25b is disposed in a valve body (not shown) so as to be slidable between the first spool 25a and the third spool 25c. The third spool 25c is slidably disposed in the valve body (not shown) and between the third spool 25c and the spring 25d. The spring 25d is disposed in the fourth hydraulic chamber 25h and biases the first to third spools 25a to 25c toward the first hydraulic chamber 25e. The first hydraulic chamber 25e is configured to press the first to third spools 25a to 25c toward the fourth hydraulic chamber 25h side when the control hydraulic pressure (SL3 pressure) output from the third control valve unit SL3 is introduced. It is a working hydraulic chamber. The second hydraulic chamber 25f is configured to press the second and third spools 25b and 25c against the fourth hydraulic chamber 25h side by introducing the control hydraulic pressure (SL4 pressure) output from the fourth control valve unit SL4. It is a working hydraulic chamber. The third hydraulic chamber 25g is a hydraulic chamber that acts to press the third spool 25c against the fourth hydraulic chamber 25h side when the hydraulic pressure output from the third switching circuit 24i of the first off-fail valve 24 is introduced. It is. The fourth hydraulic chamber 25h is a hydraulic chamber that communicates with the discharge port (EX). The third spool 25c receives at least one of the pressing force due to the hydraulic pressure of the first hydraulic chamber 25e, the pressing force due to the hydraulic pressure of the second hydraulic chamber 25f, and the pressing force due to the hydraulic pressure of the third hydraulic chamber 25g. When it is higher than the force, it slides toward the fourth hydraulic chamber 25h (“normal”), and when it is lower, it slides toward the first hydraulic chamber 25e (“fail”). The second off-fail valve 25 causes the second switching circuit 21f of the lock valve 21 to communicate with the first friction clutch C1 when “normal”, and the first switching circuit of the first off-fail valve 24 when “fail”. There is a C1 switching circuit 25i for switching so that 24g communicates with the first friction clutch C1. The second off-fail valve 25 allows the output port of the second control valve unit SL2 to communicate with the second friction clutch C2 when “normal”, and the second switching circuit of the first off-fail valve 24 when “fail”. A C2 switching circuit 25j that switches 24h and the second friction clutch C2 to communicate with each other is provided. The second off-fail valve 25 communicates the first switching circuit 21e of the lock valve 21 and the third friction clutch C3 when “normal”, and supplies the D pressure to the third friction clutch C2 when “fail”. C3 switching circuit 25k for switching as described above.

  The shuttle valve SB supplies SL3 pressure to the first switching circuit 21e of the lock valve 21 when the SL3 pressure and the R pressure are introduced and the SL3 pressure is higher than the R pressure, and the R pressure is higher than the SL3 pressure. This valve sometimes supplies R pressure to the first switching circuit 21e of the lock valve 21.

  The N-R accumulator 26 is a device that is provided in an oil passage on the R pressure input side of the shuttle valve SB, and cushions a hydraulic shock when changing from the N range to the R range. The D-N accumulator 27 is a device that is provided in an oil passage that leads from the first on-fail valve 22 to the second switching circuit 21f of the lock valve 21 and cushions a hydraulic shock when changing from the N range to the D range.

  In the R range, the R pressure output from the manual valve (not shown) is supplied to the second friction brake B2, and the second friction brake B2 is engaged.

  Next, the operation of the hydraulic control device for the automatic transmission according to the first embodiment will be described with reference to the drawings. 5 to 17 are partial hydraulic circuit diagrams for explaining the operation of the hydraulic control device for the automatic transmission according to the first embodiment of the present invention.

(Off-fail 3rd gear)
Referring to FIG. 5, during off-fail 3rd speed traveling, the first off-fail valve 24 is switched to the 1-4 side, and the second off-fail valve 25 is switched to the fail side. That is, in the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the D pressure is blocked by the second switching circuit 24h in the second hydraulic chamber 24e, and the third hydraulic chamber 24f Since SL1 pressure is not input, the pressure is switched to the 5th and 6th sides. In the second off-fail valve 25, SL3 pressure is not input to the first hydraulic chamber 25e, and SL4 pressure is not input to the second hydraulic chamber 25f. Since SL1 is not input to the hydraulic chamber 25g via the third switching circuit 24i of the first off-fail valve 24, and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the fail side. It should be noted that the lock valve 21 may be either the ◯ side or the X side. Further, during off-fail 3rd speed traveling, the vehicle is in the D range, the D pressure is output from the manual valve (not shown), and the R pressure is not output. In this state, the line pressure (D pressure) output from the manual valve (not shown) in the D range is changed to the first switching circuit 24g of the first off-fail valve 24 and the C1 switching of the second off-fail valve 25. The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the circuit 25i. At the same time, the D pressure is supplied to the third friction clutch C3 through the C3 switching circuit 25k of the second off-fail valve 25, and the third friction clutch C3 is engaged. As a result, the third speed can be achieved and the vehicle can continue to travel. In addition, since the shift from the low and medium speed stages to the third speed stage is performed, it is possible to avoid a shortage of driving force, and the shift can be performed quickly and the vehicle can be continuously traveled.

(Off-fail 5th gear)
Referring to FIG. 6, during off-fail 5th speed traveling, the first off-fail valve 24 is switched to the 5th and 6th sides, and the second off-fail valve 25 is switched to the fail side. That is, in the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is input to the second hydraulic chamber 24e, and the third hydraulic pressure Since the SL1 pressure is not input to the chamber 24f, it is switched to the 5th and 6th sides. In the second off-fail valve 25, the SL3 pressure is not input to the first hydraulic chamber 25e, and the SL4 pressure is not input to the second hydraulic chamber 25f. The SL2 pressure is not input to the third hydraulic chamber 25g via the third switching circuit 24i of the first off-fail valve 24, and the fourth hydraulic chamber 25h communicates with the discharge port, so that it is switched to the fail side. It should be noted that the lock valve 21 may be either the ◯ side or the X side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure (the line pressure output from the manual valve (not shown) in the D range) is changed to the second switching circuit 24h of the first off-fail valve 24 and the C2 switching of the second off-fail valve 25. It is supplied to the second friction clutch C2 through the circuit 25j and the second friction clutch C2 is engaged. At the same time, the D pressure is supplied to the third friction clutch C3 through the C3 switching circuit 25k of the second off-fail valve 25, and the third friction clutch C3 is engaged. As a result, it is possible to achieve the fifth speed and continue the vehicle travel. In addition, since the shift from the high speed stage to the fifth speed stage is performed, the engine speed is lower than that of the low and medium speed stages even during high speed traveling, and the engine speed is in an excessive rotation range (red zone). It is possible to continue traveling the vehicle promptly without rising.

(Normal 1st gear (OWC)) (1)
Referring to FIG. 7, during normal first speed (OWC) travel (1), SL1 is energized, SL2 is deenergized, SL3 is deenergized, SL4 is deenergized, S is deenergized, and lock valve 21 is X The first on-fail valve 22 is on the normal side, the second on-fail valve 23 is on the normal side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side. That is, in the lock valve 21, the signal pressure of the on / off solenoid valve S is not input to the first hydraulic chamber 21c, and the C2 pressure (the hydraulic pressure applied to the second friction clutch C2) is not input to the second hydraulic chamber 21d. It is switched to the side. In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is not input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g. Since the C2 pressure is not input to the normal side, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is not input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the normal side. In the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is not input to the second hydraulic chamber 24e, and the third hydraulic chamber Since SL1 pressure is input to 24f, it is switched to the 1-4 side. In the second off-fail valve 25, the SL3 pressure is not input to the first hydraulic chamber 25e, the SL4 pressure is not input to the second hydraulic chamber 25f, and the third switching of the first off-fail valve 24 is performed to the third hydraulic chamber 25g. Since the output pressure (SL1 pressure) of the circuit 24i is input and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 22, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 21f of the lock valve 21, the second switching circuit 21f. The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 25i of the 2-off fail valve 25. This achieves the first gear (OWC).

(Normal 1st speed (OWC)) (2)
Referring to FIG. 8, during normal first speed (OWC) travel (2), the on / off solenoid S is operated from the state of FIG. 7, that is, SL1 is energized, SL2 is de-energized, and SL3 is Deenergized, SL4 deenergized, S energized, Lock valve 21 is ◯ side, 1st on-fail valve 22 is normal side, 2nd on-fail valve 23 is normal side, 1st off-fail valve 24 is 1-4 side The second off-fail valve 25 is on the normal side. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 22, the second switching circuit 21f of the lock valve 21 and the C1 switching circuit 25i of the second off-fail valve 25, and is supplied to the first friction clutch C1. C1 engages. This achieves the first gear (OWC). Moreover, since D pressure can be supplied to the 1st friction clutch C1, torque capacity is securable. If the first control valve unit SL1 is in an off-fail state during normal first-speed (OWC) travel (1), (2), the vehicle goes to third-speed travel with an off-failure in FIG.

(During normal 2nd gear (1))
Referring to FIG. 9, during normal second speed traveling (1), SL1 is energized, SL2 is de-energized, SL3 is de-energized, SL4 is energized, S is de-energized, lock valve 21 is on the X side, The on-fail valve 22 is on the normal side, the second on-fail valve 23 is on the normal side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side. That is, in the lock valve 21, the signal pressure of the on / off solenoid valve S is not input to the first hydraulic chamber 21c, and the C2 pressure (the hydraulic pressure applied to the second friction clutch C2) is not input to the second hydraulic chamber 21d. It is switched to the side. In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is not input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g. Since the C2 pressure is not input to the normal side, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is not input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the normal side. In the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is not input to the second hydraulic chamber 24e, and the third hydraulic chamber Since SL1 pressure is input to 24f, it is switched to the 1-4 side. In the second off-fail valve 25, SL3 pressure is not input to the first hydraulic chamber 25e, SL4 pressure is input to the second hydraulic chamber 25f, and the third switching circuit of the first off-fail valve 24 is input to the third hydraulic chamber 25g. The output pressure (SL1 pressure) of 24i is input, and the fourth hydraulic chamber 25h communicates with the discharge port, so that it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 22, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 21f of the lock valve 21, the second switching circuit 21f. The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 25i of the 2-off fail valve 25. At the same time, the D pressure is supplied to the fourth control valve unit SL4 via the second on-fail valve 23, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear.

(Normal 2nd speed driving (2))
Referring to FIG. 10, during normal second speed traveling (2), the on / off solenoid S is operated from the state of FIG. 9, that is, SL1 is energized, SL2 is de-energized, SL3 is de-energized, SL4 is energized, S is energized, lock valve 21 is ◯ side, first on-fail valve 22 is normal side, second on-fail valve 23 is normal side, first off-fail valve 24 is 1-4 side, second off The fail valve 25 is on the normal side. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 22, the second switching circuit 21f of the lock valve 21 and the C1 switching circuit 25i of the second off-fail valve 25, and is supplied to the first friction clutch C1. C1 engages. At the same time, the D pressure is supplied to the fourth control valve unit SL4 via the second on-fail valve 23, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear. Moreover, since D pressure can be supplied to the 1st friction clutch C1, torque capacity is securable. In addition, even when only SL1 is in the off state during normal second speed travel (2), the normal second speed travel in FIG. 10 is maintained. Further, when SL4 is in an off-failure state, SL1 is de-energized to achieve the off-fail 3rd speed travel in FIG.

(Normal 3rd speed travel (1))
Referring to FIG. 11, during normal third speed travel (1), SL1 is energized, SL2 is deenergized, SL3 is energized, SL4 is deenergized, S is deenergized, lock valve 21 is on the X side, The on-fail valve 22 is on the normal side, the second on-fail valve 23 is on the fail side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side. That is, in the lock valve 21, the signal pressure of the on / off solenoid valve S is not input to the first hydraulic chamber 21c, and the C2 pressure (the hydraulic pressure applied to the second friction clutch C2) is not input to the second hydraulic chamber 21d. It is switched to the side. In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g is input. Since the C2 pressure is not input, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the fail side. In the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is not input to the second hydraulic chamber 24e, and the third hydraulic chamber Since SL1 pressure is input to 24f, it is switched to the 1-4 side. In the second off-fail valve 25, the SL3 pressure is input to the first hydraulic chamber 25e, the SL4 pressure is not input to the second hydraulic chamber 25f, and the third switching circuit of the first off-fail valve 24 is input to the third hydraulic chamber 25g. The output pressure (SL1 pressure) of 24i is input, and the fourth hydraulic chamber 25h communicates with the discharge port, so that it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 22, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 21f of the lock valve 21, the second switching circuit 21f. The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 25i of the 2-off fail valve 25. At the same time, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 21e of the lock valve 21 and the second off-fail valve 25. After being supplied to the third friction clutch C3 through the circuit 25k, the third friction clutch C3 is engaged. This achieves the third gear.

(Normal 3rd speed travel (2))
Referring to FIG. 12, in the normal third speed traveling (2), the on / off solenoid S is operated from the state of FIG. 11, that is, SL1 is energized, SL2 is de-energized, SL3 is energized, SL4 Is deenergized, S is energized, lock valve 21 is ◯ side, first on-fail valve 22 is normal side, second on-fail valve 23 is fail side, first off-fail valve 24 is 1-4 side, second off The fail valve 25 is on the normal side. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 22, the second switching circuit 21f of the lock valve 21 and the C1 switching circuit 25i of the second off-fail valve 25, and is supplied to the first friction clutch C1. C1 engages. At the same time, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the shuttle valve SB, the first switching circuit 21e of the lock valve 21, and the second off-fail valve. After being supplied to the third friction clutch C3 via the 25 C3 switching circuit 25k, the third friction clutch C3 is engaged. This achieves the third gear. Moreover, since D pressure can be supplied to the 1st friction clutch C1, torque capacity is securable. It should be noted that, even when only SL1 is in the off state during normal third speed travel (2), the normal third speed travel of FIG. 12 is maintained. In addition, when SL3 is off-failed, SL1 is de-energized to achieve the off-fail 3rd speed travel in FIG.

(Normal 4th gear)
Referring to FIG. 13, during normal 4th speed travel, SL1 is energized, SL2 is energized, SL3 is de-energized, SL4 is de-energized, lock valve 21 is on the X side, first on-fail valve 22 is on the normal side, The second on-fail valve 23 is on the normal side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side. That is, the lock valve 21 is switched to the X side because the C2 pressure (hydraulic pressure applied to the second friction clutch C2) is input to the second hydraulic chamber 21d regardless of whether the on / off solenoid valve S is energized or not. . In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is not input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g. Since the C2 pressure is input to this, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is not input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the normal side. In the first off-fail valve 24, the SL2 pressure is input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is not input to the second hydraulic chamber 24e, and the third hydraulic chamber 24f Since the SL1 pressure is input to, it is switched to the 1-4 side. In the second off-fail valve 25, the SL3 pressure is not input to the first hydraulic chamber 25e, the SL4 pressure is not input to the second hydraulic chamber 25f, and the third switching of the first off-fail valve 24 is performed to the third hydraulic chamber 25g. Since the output pressure (SL1 pressure) of the circuit 24i is input and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 22, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 21f of the lock valve 21, the second switching circuit 21f. The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 25i of the 2-off fail valve 25. At the same time, the D pressure is supplied to the second control valve unit SL2, and the output pressure (SL2 pressure) of the second control valve unit SL2 passes through the C2 switching circuit 25j of the second off-fail valve 25 to the second friction clutch C2. Supplied and the second friction clutch C2 is engaged. This achieves the fourth gear. Since the lock valve 21 is on the X side regardless of the on / off solenoid S, D pressure cannot be supplied to the first friction clutch C1. However, in order to simplify the oil passage and secure the torque capacity of the first friction clutch C1. The guide of the C2 pressure to the second hydraulic chamber 21d of the lock valve 21 may be eliminated. However, in that case, fail safe at the fifth gear and sixth gear is performed only on-fail.

(Normal 5th gear)
Referring to FIG. 14, during normal fifth speed traveling, SL1 is de-energized, SL2 is energized, SL3 is energized, SL4 is de-energized, lock valve 21 is on the X side, first on-fail valve 22 is on the fail side, The second on-fail valve 23 is on the fail side, the first off-fail valve 24 is on the 5, 6 side, and the second off-fail valve 25 is on the normal side. That is, the lock valve 21 is switched to the X side because the C2 pressure (hydraulic pressure applied to the second friction clutch C2) is input to the second hydraulic chamber 21d regardless of whether the on / off solenoid valve S is energized or not. . In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g is input. Since the C2 pressure is input, it is switched to the fail side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the fail side. In the first off-fail valve 24, the SL2 pressure is input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is input to the second hydraulic chamber 24e, and the third hydraulic chamber 24f is input. Since the SL1 pressure is not input, it is switched to the 5th and 6th sides. In the second off-fail valve 25, the SL3 pressure is input to the first hydraulic chamber 25e, the SL4 pressure is not input to the second hydraulic chamber 25f, and the third switching circuit of the first off-fail valve 24 is input to the third hydraulic chamber 25g. Since the SL2 pressure is inputted through 24i and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second control valve unit SL2, and the output pressure (SL2 pressure) of the second control valve unit SL2 passes through the C2 switching circuit 25j of the second off-fail valve 25 to the second friction clutch C2. Supplied and the second friction clutch C2 is engaged. At the same time, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 21e of the lock valve 21 and the second off-fail valve 25. After being supplied to the third friction clutch C3 through the circuit 25k, the third friction clutch C3 is engaged. This achieves the fifth gear. If it is desired to secure the torque capacity of the friction clutches C2 and C3, it is possible to cope with the off-fail 5th speed travel shown in FIG.

(Normal 6-speed driving)
Referring to FIG. 15, during normal 6th speed travel, SL1 is de-energized, SL2 is energized, SL3 is de-energized, SL4 is energized, lock valve 21 is on the X side, first on-fail valve 22 is on the normal side, The second on-fail valve 23 is on the normal side, the first off-fail valve 24 is on the 5th and 6th sides, and the second off-fail valve 25 is on the normal side. That is, the lock valve 21 is switched to the X side because the C2 pressure (hydraulic pressure applied to the second friction clutch C2) is input to the second hydraulic chamber 21d regardless of whether the on / off solenoid valve S is energized or not. . In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is not input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g. Since the C2 pressure is input to this, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is not input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the normal side. In the first off-fail valve 24, the SL2 pressure is input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is input to the second hydraulic chamber 24e, and the third hydraulic chamber 24f is input. Since the SL1 pressure is not input, it is switched to the 5th and 6th sides. In the second off-fail valve 25, SL3 pressure is not input to the first hydraulic chamber 25e, SL4 pressure is input to the second hydraulic chamber 25f, and the third switching circuit of the first off-fail valve 24 is input to the third hydraulic chamber 25g. Since the SL2 pressure is inputted through 24i and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the normal side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second control valve unit SL2, and the output pressure (SL2 pressure) of the second control valve unit SL2 passes through the C2 switching circuit 25j of the second off-fail valve 25 to the second friction clutch C2. Supplied and the second friction clutch C2 is engaged. At the same time, the D pressure is supplied to the fourth control valve unit SL4 via the second on-fail valve 23, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the sixth gear.

(Normal reverse gear travel (1))
Referring to FIG. 16, during normal reverse gear travel (1), SL1 is deenergized, SL2 is deenergized, SL3 is energized, SL4 is deenergized, S is deenergized, lock valve 21 is on the X side, The on-fail valve 22 is on the normal side, the second on-fail valve 23 is on the fail side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side. That is, in the lock valve 21, the signal pressure of the on / off solenoid valve S is not input to the first hydraulic chamber 21c, and the C2 pressure (the hydraulic pressure applied to the second friction clutch C2) is not input to the second hydraulic chamber 21d. So it is switched to the x side. In the first on-fail valve 22, the PL pressure is input to the first hydraulic chamber 22e, the C3 pressure (the hydraulic pressure applied to the third friction clutch C3) is input to the second hydraulic chamber 22f, and the third hydraulic chamber 22g is input. Since the C2 pressure is not input, it is switched to the normal side. In the second on-fail valve 23, the PL pressure is input to the first hydraulic chamber 23c and the C3 pressure is input to the second hydraulic chamber 23d, so that the second on-fail valve 23 is switched to the fail side. In the first off-fail valve 24, the SL2 pressure is not input to the first hydraulic chamber 24d, the output pressure (D pressure) of the second switching circuit 24h is not input to the second hydraulic chamber 24e, and the third hydraulic chamber Since SL1 pressure is not input to 24f, it is switched to the 1-4 side. In the second off-fail valve 25, the SL3 pressure is input to the first hydraulic chamber 25e, the SL4 pressure is not input to the second hydraulic chamber 25f, and the third switching circuit of the first off-fail valve 24 is input to the third hydraulic chamber 25g. Since the SL1 pressure is not input through 24i and the fourth hydraulic chamber 25h communicates with the discharge port, it is switched to the normal side. Here, in the R range, the R pressure is output from the manual valve (not shown), and the D pressure is not output. In this state, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 21e of the lock valve 21 and the second off-fail valve 25. After being supplied to the third friction clutch C3 through the circuit 25k, the third friction clutch C3 is engaged. At the same time, although not shown, the R pressure output from the manual valve (not shown) is supplied to the second friction brake B2, and the second friction brake B2 is engaged. This achieves the reverse gear. The R pressure is communicated with the NR accumulator 26 through an orifice and a check ball valve, and is shut off by the first switching circuit 21e of the lock valve 21 through the shuttle valve SB (R pressure> SL3 pressure).

(Normal reverse gear travel (2))
Referring to FIG. 17, in the normal reverse gear travel (2), the on-off solenoid S is operated from the state of FIG. 16, that is, SL1 is deenergized, SL2 is deenergized, SL3 is energized, SL4 Is deenergized, S is energized, lock valve 21 is ◯ side, first on-fail valve 22 is normal side, second on-fail valve 23 is fail side, first off-fail valve 24 is 1-4 side, second off The fail valve 25 is on the normal side. In this state, the R pressure becomes the third friction through the orifice, the check ball valve, the shuttle valve SB (R pressure> SL3 pressure), the first switching circuit 21e of the lock valve 21 and the C3 switching circuit 25k of the second off-fail valve 25. The third friction clutch C3 is engaged by being supplied to the clutch C3. At the same time, although not shown, the manual valve (not shown) is in the R range, and the R pressure output from the manual valve (not shown) is supplied to the second friction brake B2 to be supplied to the second friction brake B2. Engage. This achieves the reverse gear. Further, since the R pressure can be supplied to the third friction clutch C3, the torque capacity can be ensured.

  However, during normal reverse gear travel (2) in FIG. 17, if the third control valve unit SL3 is in an off failure, the second off-fail valve 25 causes the R pressure (orifice, check ball valve, shuttle valve SB (R pressure> SL3). Pressure) and R pressure that passed through the first switching circuit 21e of the lock valve 21 are cut off by the C3 switching circuit 25k of the second off-fail valve 25, and the third friction clutch C3 is not engaged. An example of this countermeasure is shown in FIGS. However, since there are various methods in this countermeasure example, the method is not limited to the methods in FIGS.

(Modification 1)
Modification 1 of FIG. 18 is an example in which a shuttle valve SB2 is provided in the oil passage from the output port of the third control valve unit SL3 to the first hydraulic chamber 25e of the second off-fail valve 25. The shuttle valve SB2 is supplied with the SL3 pressure and the R pressure, and supplies the SL3 pressure to the first hydraulic chamber 25e of the second off-fail valve 25 when the SL3 pressure is higher than the R pressure. It is a valve that supplies the R pressure to the first hydraulic chamber 25e of the second off-fail valve 25 when the pressure is higher. 17 is the same shift configuration as in the case of normal reverse gear traveling (2) in FIG. When the on-fail valve 22 is on the normal side, the second on-fail valve 23 is on the fail side, the first off-fail valve 24 is on the 1-4 side, and the second off-fail valve 25 is on the normal side), the third control valve Even if the unit SL3 is off-failed, in the first modification of FIG. 18, the R pressure is input to the first hydraulic chamber 25e of the second off-fail valve 25 via the shuttle valve SB2, and the second off-fail valve 25 is normal. Since it is maintained on the side, the reverse gear can be maintained.

(Modification 2)
Modification 2 of FIG. 19 is an example in which a shuttle valve SB3 is provided in the oil passage from the D pressure to the C3 switching circuit 25k of the second off-fail valve 25. The shuttle valve SB3 is introduced with D pressure, orifice, check ball valve, shuttle valve SB (R pressure> SL3 pressure), and R pressure via the first switching circuit 21e of the lock valve 21. In some cases, the D pressure is supplied to the C3 switching circuit 25k of the second off-fail valve 25, and the R pressure is supplied to the C3 switching circuit 25k of the second off-fail valve 25 in the R range. When the third control valve unit SL3 has an off failure during normal reverse gear travel (2) in FIG. 17, a shift configuration during normal reverse gear travel (2) in FIG. 17 as in Modification 2 of FIG. (SL1 is deenergized, SL2 is deenergized, SL3 is energized, SL4 is deenergized, S is energized, the lock valve 21 is ◯ side, the first on-fail valve 22 is normal side, and the second on-fail valve 23 is fail side The first off-fail valve 24 is 1-4 side and the second off-fail valve 25 is normal side), the second off-fail valve 25 is switched to the fail side, the R pressure is the orifice, check ball valve, shuttle valve SB (R pressure> SL3 pressure), supplied to the third friction clutch C3 via the first switching circuit 21e of the lock valve 21 and the C3 switching circuit 25k of the second off-fail valve 25. Since the engagement of the friction clutch C3 is maintained, it is possible to maintain the reverse gear.

  According to the first embodiment, even if the first control valve unit SL1 for the first friction clutch C1 is turned off, the lock valve 21 can be operated by the on / off solenoid S to supply D pressure to the first friction clutch C1. Therefore, it is possible to travel even at 2nd. Further, even if the third control valve unit SL3 for the third friction clutch C3 is turned off during reverse travel, the lock valve 21 can be operated by the on / off solenoid S to supply the R pressure to the third friction clutch C3. Reverse gear traveling is possible.

(Embodiment 2)
Next, a hydraulic control device for an automatic transmission according to a second embodiment of the present invention will be described with reference to the drawings. FIG. 20 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in the hydraulic control device for an automatic transmission according to the second embodiment of the present invention.

  In the first embodiment (FIG. 4), the ON / OFF solenoid S is an NL type, but it is an NH type (normally outputs SL1 pressure in a non-energized state and decreases SL1 pressure as the energized current increases in the energized state. If it is a low type), the lock valve 31 of the second embodiment (FIG. 20) may be used. About another structure, it is the same as that of Embodiment 1 (FIG. 4).

  The lock valve 31 is a switching valve that switches an oil passage, and is a spool that outputs an output pressure from predetermined control valve units SL1 and SL3 or a line pressure (D pressure, R pressure) according to a shift state. The position is switched. The lock valve 31 includes a first spool 31a, a second spool 31b, a spring 31c, a first hydraulic chamber 31d, a second hydraulic chamber 31e, and a third hydraulic chamber 31f in a valve body (not shown). Have. The first spool 31a is slidably arranged in a valve body (not shown). The second spool 31b is slidably disposed between the first spool 31a and the spring 31c in the valve body (not shown). The spring 31c is disposed in the third hydraulic chamber 31f and biases the first spool 31a and the second spool 31b toward the first hydraulic chamber 31d. The first hydraulic chamber 31d is a hydraulic chamber that acts to press the first spool 31a and the second spool 31b against the third hydraulic chamber 31f side when the hydraulic pressure from the on / off solenoid valve S is introduced. The second hydraulic chamber 31e is a hydraulic chamber that acts to press the second spool 31b against the third hydraulic chamber 31f side when the C2 pressure is introduced. The third hydraulic chamber 31f communicates with the discharge port (EX). The spool 31a has a third hydraulic chamber 31f side (at the time when at least one of the pressing force by the hydraulic pressure of the first hydraulic chamber 31d and the pressing force by the hydraulic pressure of the second hydraulic chamber 31e is higher than the biasing force of the spring 31c ( “X”), and slides toward the first hydraulic chamber 31d side (“◯”) when it is low. The lock valve 31 communicates the output port of the third control valve unit SL3 and the C3 switching circuit 25k of the second off-fail valve 25 when “x”, and the shuttle valve SB and the second off-fail when “◯”. A first switching circuit 31g that switches the C3 switching circuit 25k of the valve 25 to communicate is provided. The lock valve 31 communicates the output port of the first control valve unit SL1 with the C1 switching circuit 25i of the second off-fail valve 25 when “X”, and the first on-fail valve 22 when “O”. And a second switching circuit 31h for switching the C1 switching circuit 25i of the second off-fail valve 25 to communicate with each other. An oil passage between the lock valve 31 and the first on-fail valve 22 has an orifice and a check ball valve.

  According to the second embodiment, the same effects as those of the first embodiment are obtained.

(Embodiments 3 and 4)
Next, hydraulic control devices for automatic transmissions according to Embodiments 3 and 4 of the present invention will be described with reference to the drawings. FIG. 21 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in the hydraulic control device for an automatic transmission according to the third embodiment of the present invention. FIG. 22 is a partial hydraulic circuit diagram schematically showing the configuration of the hydraulic control unit in the hydraulic control device for an automatic transmission according to the fourth embodiment of the present invention.

  The first switching circuit 31g of the lock valve 31 and the output port of the second switching circuit 31h are not in communication with the control valve units SL3 and SL1 when the on / off solenoid valve S is not energized as in the second embodiment (FIG. 20). If it is more convenient to communicate during energization, FIG. 21 (Embodiment 3) may be used if the on / off solenoid S is an NL type, and FIG. 22 (Embodiment 4) may be used if the on / off solenoid S is an NH type. FIG. 21 (Embodiment 3) shows the NL type of the on / off solenoid valve S of FIG. 20 (Embodiment 2), and FIG. 22 (Embodiment 4) shows the on / off solenoid valve of FIG. 4 (Embodiment 1). S is an NH type. Other configurations are the same as those in the first embodiment.

  According to the third and fourth embodiments, the same effects as those of the first embodiment are obtained.

  In the first to fourth embodiments, when the third friction clutch C3 is engaged, the second on-fail valve 23 is configured to reduce the D pressure to the supply port of the fourth control valve unit SL4 for the first friction brake B1. The supply is shut off, and the first on-fail valve 22 is connected to the supply port of the first control valve unit SL1 for the first friction clutch C1 when the third friction clutch C3 and the second friction clutch C2 are engaged. Although the supply of pressure is cut off, for example, instead of the first control valve unit SL1, the supply port of the third control valve unit SL3 when the first friction clutch C1 and the second friction clutch C2 are engaged. An on-fail valve for shutting off the supply of the PL pressure may be provided, or another pattern may be used.

(Embodiment 5)
Next, a hydraulic control device for an automatic transmission according to Embodiment 5 of the present invention will be described with reference to the drawings. FIG. 23 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in the hydraulic control device for an automatic transmission according to the fifth embodiment of the present invention.

  In FIG. 23 (Embodiment 5), the present invention is applied to FIG. The first switching circuit 21e of the lock valve 21 and the B3 switching circuit 35m of the second off-fail valve 35 (second switching valve) are connected to each other. Similarly, the second switching circuit 21f of the lock valve 21 and the second off-fail valve 35 ( The second switching valve) is connected to the C1 switching circuit 35k. In order to maintain the connection between the third friction brake B3 and the fifth control valve unit SL5 during the third speed travel when the off-fail is not performed (C1 is engaged by SL1, B3 is engaged by SL5). A shuttle valve SB for connecting the first and third ports from the top of the first switching circuit 21e of the valve 21 is installed. Further, the C2 pressure is input to the second hydraulic chamber 21d of the lock valve 21 so that the hydraulic pressure is not supplied to the first friction clutch C1 due to the failure of the on / off solenoid valve S at the fifth speed stage and the sixth speed stage. .

  In the fifth embodiment, SL5 is used instead of SL3 of the first embodiment, SL3 is used instead of SL4, and B3 is used instead of C3. In the fifth embodiment, instead of the second off-fail valve 25 of the first embodiment, when SL5 pressure is input to the first hydraulic chamber 35f, when SL4 pressure is input to the second hydraulic chamber 35g, SL3 When the pressure is input to the third hydraulic chamber 35h, or when the SL2 pressure or SL1 pressure is input to the fourth hydraulic chamber 35i, the C1 switching circuit 35k, the C2 switching circuit 35l, and the B3 switching circuit The second off-fail valve 35 switches 35 m to the normal side. Other configurations are the same as those of the first embodiment.

  According to the fifth embodiment, the same effects as those of the first embodiment are obtained.

(Embodiment 6)
Next, a hydraulic control device for an automatic transmission according to Embodiment 6 of the present invention will be described with reference to the drawings. FIG. 24 is a partial hydraulic circuit diagram schematically showing the configuration of the hydraulic control unit in the hydraulic control device for an automatic transmission according to the sixth embodiment of the present invention.

  The hydraulic control unit 3 includes first to fourth control valve units SL1 to SL4, a lock valve 41, a first on-off solenoid valve S1, a first on-fail valve 42, a second on-fail valve 43, and a first Off-fail valve 44, second off-fail valve 45, shuttle valve SB4, NR accumulator 46, DN accumulator 47, cut-off valve 48, shuttle valve SB5, relay valve 49, first valve It has a 2 on / off solenoid valve S2, an apply valve 50, and a B2 accumulator 51.

  The first control valve unit SL1 is a control valve unit for the first friction clutch C1, and is formed by integrating a linear solenoid valve and a control valve. The first control valve unit SL1 may have a configuration in which the linear solenoid valve and the control valve are separated. The first control valve unit SL1 supplies the line pressure PL (D pressure) output from a manual valve (not shown) in the D range to a normal first on-fail valve 42, an orifice and a check ball valve (main The control hydraulic pressure (SL1 pressure) is generated from the D pressure introduced according to the energization amount, and is output from the output port. The SL1 pressure is supplied to the second switching circuit 41h of the lock valve 41. The first control valve unit SL1 is a normal low type (NL) that does not output the SL1 pressure in the non-energized state and outputs the SL1 pressure that increases as the energized current increases in the energized state. The first control valve unit SL1 communicates the output port and the discharge port (EX) in a non-energized state.

  The second control valve unit SL2 is a control valve unit for the second friction clutch C2, in which a linear solenoid valve and a control valve are integrated. The second control valve unit SL2 may have a configuration in which the linear solenoid valve and the control valve are separated. The second control valve unit SL2 introduces the D pressure or R pressure from the shuttle valve SB5, and generates a control hydraulic pressure (SL2 pressure) from the D pressure or R pressure introduced according to the energization amount and outputs it. To do. The SL2 pressure is supplied to the first switching circuit 49j and the second switching circuit 49k of the relay valve 49. The second control valve unit SL2 is a normal low type (NL) that does not output the SL2 pressure in the non-energized state and outputs the SL2 pressure that increases as the energized current increases in the energized state. The second control valve unit SL2 communicates the output port and the discharge port (EX) in a non-energized state.

  The third control valve unit SL3 is a control valve unit for the third friction clutch C3, in which a linear solenoid valve and a control valve are integrated. The third control valve unit SL3 may have a configuration in which the linear solenoid valve and the control valve are separated. The third control valve unit SL3 introduces the PL pressure, generates a control hydraulic pressure (SL3 pressure) from the PL pressure introduced according to the energization amount, and outputs this. The SL3 pressure is supplied to the first switching circuit 41g of the lock valve 41 and the first hydraulic chamber 45e of the second off-fail valve 45. The third control valve unit SL3 is a normal low type (NL) that does not output the SL3 pressure in the non-energized state and outputs the SL3 pressure that increases as the energized current increases in the energized state. The third control valve unit SL3 communicates the output port and the exhaust port (EX) in a non-energized state.

  The fourth control valve unit SL4 is a control valve unit for the first friction brake B1, and includes a linear solenoid valve and a control valve. The fourth control valve unit SL4 may have a configuration in which the linear solenoid valve and the control valve are separated. The fourth control valve unit SL4 introduces the D pressure through the second on-fail valve 43 in a normal state and generates a control hydraulic pressure (SL4 pressure) from the D pressure introduced according to the energization amount. Is output. The SL4 pressure is supplied to the first friction brake B1, the second hydraulic chamber 45f of the second off-fail valve 45, and the first hydraulic chamber 50g of the apply valve 50. The fourth control valve unit SL4 is a normal low type (NL) that does not output SL4 pressure in the non-energized state and outputs SL4 pressure that increases as the energized current increases in the energized state. The fourth control valve unit SL4 communicates the output port and the discharge port (EX) in a non-energized state.

  The lock valve 41 is a switching valve that switches an oil passage, and is a spool that outputs an output pressure from predetermined control valve units SL1 and SL3 or a line pressure (D pressure, R pressure) according to a shift state. The position is switched. The lock valve 41 includes a first spool 41a, a second spool 41b, a spring 41c, a first hydraulic chamber 41d, a second hydraulic chamber 41e, and a third hydraulic chamber 41f in a valve body (not shown). Have. The first spool 41a is slidably arranged in a valve body (not shown). The second spool 41b is slidably disposed between the first spool 41a and the spring 41c in the valve body (not shown). The spring 41c is arranged in the third hydraulic chamber 41f and biases the first spool 41a and the second spool 41b toward the first hydraulic chamber 41d. The first hydraulic chamber 41d is a hydraulic chamber that acts to press the first spool 41a and the second spool 41b against the third hydraulic chamber 41f side when the hydraulic pressure from the first on / off solenoid valve S1 is introduced. The second hydraulic chamber 41e is a hydraulic chamber that acts to press the second spool 41b against the third hydraulic chamber 41f side when the C2 pressure is introduced. The third hydraulic chamber 41f communicates with the discharge port (EX). The first spool 41a has a third hydraulic chamber 41f when at least one of the pressing force by the hydraulic pressure of the first hydraulic chamber 41d and the pressing force by the hydraulic pressure of the second hydraulic chamber 41e is higher than the urging force of the spring 41c. Slide to the side (“◯”), and slide to the first hydraulic chamber 41d side (“×”) when it is low. The lock valve 41 causes the output port of the third control valve unit SL3 to communicate with the C3 switching circuit 45l of the second off-fail valve 45, the shuttle valve SB4, and the fourth hydraulic chamber 49i of the relay valve 49 when “O”. , The R pressure input through the orifice and the check ball valve at the time of “x” is supplied to the C3 switching circuit 45l of the second off-fail valve 45, the shuttle valve SB4, and the fourth hydraulic chamber 49i of the relay valve 49. A first switching circuit 41g for switching is provided. Further, the lock valve 41 causes the output port of the first control valve unit SL1 to communicate with the C1 switching circuit 45j of the second off-fail valve 45 when “O”, and the first on-fail valve 42 when “X”. And a second switching circuit 41h that switches the C1 switching circuit 45j of the second off-fail valve 45 to communicate with each other. An oil passage between the lock valve 41 and the first on-fail valve 42 has an orifice and a check ball valve.

  The first on / off solenoid valve S1 switches the operating state of the first spool 41a and the second spool 41b of the lock valve 41 in accordance with switching between energization and non-energization. The first on / off solenoid valve S1 is a normal low type (NL) that does not supply a signal pressure to the lock valve 41 in a non-energized state and supplies a signal pressure to the lock valve 41 in an energized state.

  The first on-fail valve 42 is a switching valve that switches an oil passage, and has a first spool 42a, a second spool 42b, a sleeve 42c, a spring 42d, and a first hydraulic chamber in a valve body (not shown). 42e, a second hydraulic chamber 42f, and a third hydraulic chamber 42g. The first spool 42a is slidably arranged in a valve body (not shown). The second spool 42b is slidably disposed between the first spool 42a and the spring 42d in the valve body (not shown). The sleeve 42c is disposed on the outer periphery of the second spool 42b and has an oil hole for introducing the hydraulic pressure (C2 pressure) applied to the second friction clutch C2 into the third hydraulic chamber 42g. The spring 42d is disposed in the third hydraulic chamber 42g and biases the first spool 42a and the second spool 42b toward the first hydraulic chamber 42e. The first hydraulic chamber 42e is a hydraulic chamber that acts to press the first spool 42a against the third hydraulic chamber 42g side when the PL pressure is introduced. The second hydraulic chamber 42f is a hydraulic chamber that acts to press the first spool 42a against the first hydraulic chamber 42e side by introducing the hydraulic pressure (C3 pressure) applied to the third friction clutch C3. The third hydraulic chamber 42g is a hydraulic chamber that acts to press the first spool 42a and the second spool 42b against the first hydraulic chamber 42e side when the C2 pressure is introduced. In the first spool 42a, the pressing force by the hydraulic pressure of the first hydraulic chamber 42e is greater than the resultant force of the pressing force by the urging force of the spring 42d, the hydraulic pressure of the second hydraulic chamber 42f, and the pressing force by the hydraulic pressure of the third hydraulic chamber 42g. When it is high, it slides toward the third hydraulic chamber 42g (“normal”), and when it is low, it slides toward the first hydraulic chamber 42e (“fail”). The first on-fail valve 42 supplies the D pressure introduced when “normal” to the supply port of the first control valve unit SL1 and the second switching circuit 41h of the lock valve 41 through the orifice and the check ball valve. In the case of “Fail”, the supply port of the first control valve unit SL1 and the second switching circuit 41h of the lock valve 41 are switched to communicate with the discharge port (EX) through the orifice and the check ball valve.

  The second on-fail valve 43 is a switching valve that switches an oil passage, and has a spool 43a, a spring 43b, a first hydraulic chamber 43c, and a second hydraulic chamber 43d in a valve body (not shown). . The spool 43a is slidably arranged in a valve body (not shown). The spring 43b is arranged in the second hydraulic chamber 43d and urges the spool 43a toward the first hydraulic chamber 43c. The first hydraulic chamber 43c is a hydraulic chamber that acts to press the spool 43a against the second hydraulic chamber 43d side when the PL pressure is introduced. The second hydraulic chamber 43d is a hydraulic chamber that acts to press the spool 43a against the first hydraulic chamber 43c side by introducing the hydraulic pressure (C3 pressure) applied to the third friction clutch C3. The spool 43a has a second hydraulic chamber 43d side ("normal") when the pressing force by the hydraulic pressure of the first hydraulic chamber 43c is higher than the resultant force of the urging force of the spring 43b and the pressing force by the hydraulic pressure of the second hydraulic chamber 43d. ) And when it is low, it slides toward the first hydraulic chamber 43c (“fail”). The second on-fail valve 43 supplies the D pressure to the supply port of the fourth control valve unit SL4 when “normal”, and the supply port and the exhaust port (EX) of the fourth control valve unit SL4 when “fail”. ) To communicate.

  The first off-fail valve 44 is a switching valve for switching the oil path, and the vehicle gear stage before the fail state is reached when a fail state in which no hydraulic pressure is output from any of the control valve units SL1 to SL4 is achieved. Is switched to output the line pressure while maintaining the spool position. The first off-fail valve 44 includes a first spool 44a, a second spool 44b, a spring 44c, a first hydraulic chamber 44d, a second hydraulic chamber 44e, and a third hydraulic pressure in a valve body (not shown). A chamber 44f. The first spool 44a is slidably arranged in a valve body (not shown). The second spool 44b is slidably disposed between the first spool 44a and the spring 44c in the valve body (not shown). The spring 44c is disposed in the third hydraulic chamber 44f and biases the first spool 44a and the second spool 44b toward the first hydraulic chamber 44d. The first hydraulic chamber 44d presses the first spool 44a and the second spool 44b against the third hydraulic chamber 44f side when the hydraulic pressure (SL2 pressure) output from the first switching circuit 49j of the relay valve 49 is introduced. It is the hydraulic chamber which acts as follows. The second hydraulic chamber 44e is a hydraulic chamber that acts to press the second spool 44b against the third hydraulic chamber 44f side by introducing the hydraulic pressure (D pressure) output from the second switching circuit 44h. The third hydraulic chamber 44f is configured to press the first spool 44a and the second spool 44b against the first hydraulic chamber 44d side when the control hydraulic pressure (SL1 pressure) output from the first control valve unit SL1 is introduced. It is a working hydraulic chamber. In the second spool 44b, at least one of the pressing force due to the hydraulic pressure of the first hydraulic chamber 44d and the pressing force due to the hydraulic pressure of the second hydraulic chamber 44e is the pressing force due to the urging force of the spring 44c and the hydraulic pressure of the third hydraulic chamber 44f. The first hydraulic chamber slides toward the third hydraulic chamber 44f ("5, 6") when the resultant force is higher than the resultant force (5, 6th speed) and lower (when 1-4th gear). Slide to the 44d side (“1-4”). The first off-fail valve 44 causes the discharge port (EX) to communicate with the C1 switching circuit 45j of the second off-fail valve 45 when “5, 6”, and the D pressure is set to the second pressure when “1-4”. A first switching circuit 44g that switches to supply to the C1 switching circuit 45j of the off-fail valve 45 is provided. The first off-fail valve 44 supplies the D pressure to the C2 switching circuit 45k and the second hydraulic chamber 44e of the second off-fail valve 45 when “5, 6”, and the discharge port when “1-4”. (EX) and a second switching circuit 44h that switches the C2 switching circuit 45k of the second off-fail valve 45 and the second hydraulic chamber 44e to communicate with each other. The first off-fail valve 44 communicates the first switching circuit 49j of the relay valve 49 with the third hydraulic chamber 45g of the second off-fail valve 45 when “5, 6”, and when “1-4”. A third switching circuit 44i that switches to supply the SL1 pressure to the third hydraulic chamber 45g of the second off-fail valve 45 is provided.

  The second off-fail valve 45 is a switching valve for switching the oil path, and the line pressure (D from the first off-fail valve 44 in a fail state in which no hydraulic pressure is output from any of the control valve units SL1 to SL4. Pressure, R pressure) is output toward a predetermined engagement element (C1, C2, C3), and the hydraulic pressure of a predetermined control valve unit (one or two of SL1 to SL4) is output. Sometimes the spool position is switched so that the output pressure from the predetermined lock valve units SL1 to SL4 is output toward a predetermined engagement element (one or two of C1, C2, C3). The second off-fail valve 45 includes a first spool 45a, a second spool 45b, a third spool 45c, a spring 45d, a first hydraulic chamber 45e, and a second hydraulic chamber in a valve body (not shown). 45f, a third hydraulic chamber 45g, and a fourth hydraulic chamber 45h. The first spool 45a is slidably arranged in a valve body (not shown). The second spool 45b is slidably arranged between the first spool 45a and the third spool 45c in the valve body (not shown). The third spool 45c is slidably disposed in the valve body (not shown) between the third spool 45c and the spring 45d. The spring 45d is disposed in the fourth hydraulic chamber 45h and biases the first to third spools 45a to 45c toward the first hydraulic chamber 45e. The first hydraulic chamber 45e is configured to press the first to third spools 45a to 45c toward the fourth hydraulic chamber 45h side by introducing the control hydraulic pressure (SL3 pressure) output from the third control valve unit SL3. It is a working hydraulic chamber. The second hydraulic chamber 45f is configured to press the second and third spools 45b and 45c against the fourth hydraulic chamber 45h side by introducing the control hydraulic pressure (SL4 pressure) output from the fourth control valve unit SL4. It is a working hydraulic chamber. The third hydraulic chamber 45g is a hydraulic chamber that acts to press the third spool 45c against the fourth hydraulic chamber 45h side when the hydraulic pressure output from the third switching circuit 44i of the first off-fail valve 44 is introduced. It is. The fourth hydraulic chamber 45h is a hydraulic chamber that communicates with the discharge port (EX). The third spool 45c is provided with at least one of the pressing force by the hydraulic pressure of the first hydraulic chamber 45e, the pressing force by the hydraulic pressure of the second hydraulic chamber 45f, and the pressing force by the hydraulic pressure of the third hydraulic chamber 45g. When it is higher than the force, it slides toward the fourth hydraulic chamber 45h (“normal”), and when it is lower, it slides toward the first hydraulic chamber 45e (“fail”). The second off-fail valve 45 supplies a D pressure to the shuttle valve SB5 when “normal” and switches a D pressure switching circuit 45i to switch the shuttle valve SB5 and the discharge port (EX) to communicate with each other when “fail”. Have The second off-fail valve 45 causes the second switching circuit 41h of the lock valve 41 to communicate with the first friction clutch C1 when “normal”, and the first switching circuit of the first off-fail valve 44 when “fail”. There is a C1 switching circuit 45j for switching 44g to communicate with the first friction clutch C1. The second off-fail valve 45 communicates the first switching circuit 49j of the relay valve 49 and the second friction clutch C2 when “normal”, and the second switching circuit of the first off-fail valve 44 when “fail”. 44h and a second friction clutch C2 for switching so as to communicate with each other. The second off-fail valve 45 communicates the first switching circuit 41g of the lock valve 41 and the third friction clutch C3 when “normal” and communicates the shuttle valve SB4 and the third friction clutch C3 when “fail”. C3 switching circuit 45l for switching so as to be performed.

  When the output pressure (R pressure or SL3 pressure) of the first switching circuit 41g of the lock valve 41 and the D pressure are introduced and the output pressure of the first switching circuit 41g is higher than the D pressure, the shuttle valve SB4 The output pressure of the first switching circuit 41g is supplied to the C3 switching circuit 45l of the second off-fail valve 45, and when the D pressure is higher than the output pressure of the first switching circuit 41g, the D pressure is supplied to the second off-fail valve 45. This is a valve supplied to the C3 switching circuit 45l.

  The N-R accumulator 46 is a device that is provided in an oil path on the R pressure input side of the first switching circuit 41g of the lock valve 41, and that cushions a hydraulic shock when changing from the N range to the R range. The DN accumulator 47 is a device that is provided in an oil passage that leads from the first on-fail valve 42 to the second switching circuit 41h of the lock valve 41, and that buffers hydraulic shock when changing from the N range to the D range.

  The cut-off valve 48 is a switching valve that switches an oil passage, and has a first spool 48a, a second spool 48b, a spring 48c, a first hydraulic chamber 48d, and a second hydraulic pressure in a valve body (not shown). It has a chamber 48e and a third hydraulic chamber 48f. The first spool 48a is slidably arranged in a valve body (not shown). The second spool 48b is slidably disposed between the first spool 48a and the spring 48c in the valve body (not shown). The spring 48c is disposed in the third hydraulic chamber 48f and biases the first spool 48a and the second spool 48b toward the first hydraulic chamber 48d. The first hydraulic chamber 48d is a hydraulic chamber that acts to press the first spool 48a and the second spool 48b against the third hydraulic chamber 48f side when the C3 pressure is introduced. The second hydraulic chamber 48e is a hydraulic chamber that acts to press the first spool 48a against the first hydraulic chamber 48d side when the C2 pressure is introduced. The third hydraulic chamber 48f is a hydraulic chamber that communicates with the discharge port (EX). The second spool 48b has a third hydraulic chamber 48f when one or both of the pressing force by the hydraulic pressure of the first hydraulic chamber 48d and the pressing force by the hydraulic pressure of the second hydraulic chamber 48e are higher than the urging force of the spring 48c. Slide to the side (“◯”), and slide to the first hydraulic chamber 48d side (“×”) when it is low. The cut-off valve 48 supplies the D pressure introduced when “◯” to the third hydraulic chamber 50 i of the apply valve 50, and the “D” indicates that the third hydraulic chamber 50 i of the apply valve 50 is discharged from the discharge port ( EX) is switched to communicate. The first spool 48a and the second spool 48b of the cut-off valve 48 may be integrated.

  The shuttle valve SB5 is supplied with the output pressure (R pressure) of the third switching circuit 49l of the relay valve 49 and the output pressure (D pressure) of the D pressure switching circuit 45i of the second off-fail valve 45, and the third When the output pressure of the switching circuit 49l is higher than the output pressure of the D pressure switching circuit 45i, the output pressure of the third switching circuit 49l is supplied to the supply port of the second control valve unit SL2, and the output pressure of the D pressure switching circuit 45i. Is a valve that supplies the output pressure of the D pressure switching circuit 45i to the supply port of the second control valve unit SL2 when is higher than the output pressure of the third switching circuit 49l.

  The relay valve 49 is a switching valve that switches an oil path, and a first spool 49a, a second spool 49b, a third spool 49c, a sleeve 49d, a spring 49e, a first valve 49, and a second valve 49 (not shown). The first hydraulic chamber 49f, the second hydraulic chamber 49g, the third hydraulic chamber 49h, and the fourth hydraulic chamber 49i are provided. The first spool 49a is slidably arranged in a valve body (not shown). The second spool 49b is slidably disposed in the valve body (not shown) between the first spool 49a and the spring 49e. The third spool 49c is slidably disposed in the valve body (not shown) on the opposite side of the spring 49e to the second spool 49b side. The sleeve 49d is disposed on the outer periphery of the third spool 49c, and has an oil hole for introducing the output pressure (R pressure or SL3 pressure) of the first switching circuit 41g of the lock valve 41 into the fourth hydraulic chamber 49i. The spring 49e is disposed in the third hydraulic chamber 49h, biases the first spool 49a and the second spool 49b toward the first hydraulic chamber 49f, and biases the third spool 49c toward the fourth hydraulic chamber 49i. . The first hydraulic chamber 49f is a hydraulic chamber that acts to press the first to third spools 49a to 49c against the fourth hydraulic chamber 49i side by introduction of the signal pressure from the second on / off solenoid valve S2. . The second hydraulic chamber 49g is a hydraulic chamber that acts to press the second and third spools 49b and 49c against the fourth hydraulic chamber 49i side when the R pressure is introduced. The third hydraulic chamber 49h is a hydraulic chamber that acts to press the first and second spools 49a, 49b against the first hydraulic chamber 49f side when the output pressure (SL2 pressure) of the first switching circuit 49j is introduced. It is. The fourth hydraulic chamber 49i pushes the first to third spools 49a to 49c toward the first hydraulic chamber 49f by introducing the output pressure (R pressure or SL3 pressure) of the first switching circuit 41g of the lock valve 41. It is a hydraulic chamber that acts to attach. In the second spool 49b, one or both of the pressing force due to the hydraulic pressure of the first hydraulic chamber 49f and the pressing force due to the hydraulic pressure of the second hydraulic chamber 49g are caused by the biasing force of the spring 49e and the hydraulic pressure of the third hydraulic chamber 49h. When it is higher than the resultant force of the pressing force and the pressing force by the hydraulic pressure of the fourth hydraulic chamber 49i, it slides to the fourth hydraulic chamber 49i side (“◯”), and when it is lower, the first hydraulic chamber 49f side (“×” ”). When the relay valve 49 is “◯”, the third hydraulic chamber 49h, the first hydraulic chamber 44d of the first off-fail valve 44, the third switching circuit 44i, and the C2 switching circuit 45k of the second off-fail valve 45 are discharged. The port (EX) is communicated, and when it is “x”, the SL2 pressure is applied to the third hydraulic chamber 49h, the first hydraulic chamber 44d of the first off-fail valve 44, the third switching circuit 44i, and the second off-fail valve 45. A first switching circuit 49j for switching to supply to the C2 switching circuit 45k is provided. The relay valve 49 supplies the SL2 pressure to the switching circuit of the apply valve 50 and the second hydraulic chamber 50h when “◯”, and the R pressure to the switching circuit of the apply valve 50 and the second hydraulic chamber when “x”. A second switching circuit 49k that switches to supply to 50h is provided. The relay valve 49 has a third switching circuit 49l that switches the R valve to supply the R pressure to the shuttle valve SB5 when “◯” and to connect the shuttle valve SB5 and the discharge port (EX) when “X”. The first spool 49a and the second spool 49b of the relay valve 49 may be integrated.

  The second on / off solenoid valve S2 switches the operating states of the spools 49a to 49c of the relay valve 49 according to switching between energization and non-energization. The second on / off solenoid valve S2 is a normal low type (NL) that does not supply the signal pressure to the relay valve 49 in the non-energized state and supplies the signal pressure to the relay valve 49 in the energized state.

  The apply valve 50 is a switching valve that switches an oil passage. A first spool 50a, a second spool 50b, a third spool 50c, a fourth spool 50d, and a sleeve 50e are provided in a valve body (not shown). , A spring 50f, a first hydraulic chamber 50g, a second hydraulic chamber 50h, a third hydraulic chamber 50i, a fourth hydraulic chamber 50j, and a fifth hydraulic chamber 50k. The first spool 50a is slidably arranged in a valve body (not shown). The second spool 50b is slidably disposed between the first spool 50a and the third spool 50c in the valve body (not shown). The third spool 50c is slidably disposed in the valve body (not shown) between the second spool 50a and the spring 50f. The fourth spool 50d is slidably disposed in the valve body (not shown) on the opposite side of the spring 50f to the third spool 50c side. The sleeve 50e is disposed on the outer periphery of the fourth spool 50d and has an oil hole for introducing the PL pressure into the fifth hydraulic chamber 50k. The spring 50f is arranged in the fourth hydraulic chamber 50j, and biases the first to third spools 50a to 50c toward the first hydraulic chamber 50g, and biases the fourth spool 50d toward the fifth hydraulic chamber 50k. The first hydraulic chamber 50g is a hydraulic chamber that acts to press the first to fourth spools 50a to 50d against the fifth hydraulic chamber 50k side when the SL4 pressure is introduced. The second hydraulic chamber 50h pushes the second to fourth spools 50b to 50d toward the fifth hydraulic chamber 50k by introducing the output pressure (SL2 pressure or R pressure) of the second switching circuit 49k of the relay valve 49. It is a hydraulic chamber that acts to attach. The third hydraulic chamber 50i is a hydraulic chamber that acts to press the third and fourth spools 50c, 50d against the fifth hydraulic chamber 50k side when the output pressure (D pressure) of the cutoff valve 48 is introduced. is there. The fourth hydraulic chamber 50j is a hydraulic chamber that communicates with the discharge port (EX). The fifth hydraulic chamber 50k is a hydraulic chamber that acts to press the first to fourth spools 50a to 50d against the first hydraulic chamber 50g side when the PL pressure is introduced. The third spool 50c is configured so that at least one force of the pressing force due to the hydraulic pressure in the first hydraulic chamber 50g and the pressing force due to the hydraulic pressure in the second hydraulic chamber 50h, and the pressing force due to the hydraulic pressure in the third hydraulic chamber 50i is generated by the spring 50f. When higher than one or both of the resultant force of the urging force and the pressing force due to the hydraulic pressure of the fourth hydraulic chamber 50j and the pressing force due to the hydraulic pressure of the fifth hydraulic chamber 50k, the fifth hydraulic chamber 50k side (“◯”) Slide and slide to the first hydraulic chamber 50g side ("X") when the pressure is low. The apply valve 50 supplies the R pressure to the second friction brake B2 and the B2 accumulator 51 when “◯”, and the output pressure (SL2 pressure or R) of the second switching circuit 49k of the relay valve 49 when “X”. The pressure is switched so as to be supplied to the second friction brake B2 and the B2 accumulator 51. The first spool 50a to the fourth spool 50d of the apply valve 50 may be integrated.

  The B2 accumulator 51 is a device that is provided in an oil passage that communicates from the apply valve 50 to the second friction brake B2, and cushions a hydraulic shock when the output pressure of the apply valve 50 is supplied to the second friction brake B2.

  The operation of the hydraulic control device for an automatic transmission according to the sixth embodiment will be described with reference to the drawings. 25 to 39 are partial hydraulic circuit diagrams for explaining the operation of the hydraulic control device for the automatic transmission according to the sixth embodiment of the present invention. In the sixth embodiment, a case will be described in which there is no one-way clutch OWC attached to the second friction brake B2 in the skeleton diagram of the automatic transmission in FIG.

  The difference between the operation of the sixth embodiment and the operation of the first embodiment will be described with reference to FIG. During the control of the second friction clutch C2, the second on / off solenoid valve S2 is deenergized, and the SL2 pressure from the second control valve unit SL2 passes through the first switching circuit 49j of the relay valve 49 to the third hydraulic chamber 49h, The first hydraulic chamber 44d of the first off-fail valve 44, the third switching circuit 44i, and the C2 switching circuit 45k of the second off-fail valve 45 are supplied to finally reach the second friction clutch C2. When the second friction brake B2 is controlled, the second on / off solenoid valve S2 is energized, and the SL2 pressure from the second control valve unit SL2 passes through the second switching circuit 49k of the relay valve 49 and the switching circuit of the apply valve 50. The second friction chamber B2 is reached only when the second hydraulic chamber 50h is reached and the fail operation is not performed ("◯" side).

  Here, in the D range, since the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off fail valve 45 and the shuttle valve SB5, the second off fail valve 45 is “ In the “fail” state, the D pressure can be cut off. On the other hand, in the R range, the R friction is supplied to the second control valve unit SL2 via the shuttle valve SB5 only when passing through the third switching circuit 49l of the relay valve 49 in the “normal” state. The SL2 pressure is not supplied to the clutch C2.

  Further, at the time of forward movement, the SL3 pressure via the first switching circuit 41g of the lock valve 41 is introduced into the fourth hydraulic chamber 49i of the relay valve 49, so that the relay valve 49 can be operated to the “fail” state. At the time of reverse travel, the relay valve 49 is set to the “normal” state by introducing the R pressure into the second hydraulic chamber 49g opposite to the SL3 pressure introduced into the fourth hydraulic chamber 49i. That is, the relay valve 49 can be operated by the second on / off solenoid valve S2 regardless of the SL3 pressure.

  Further, the apply valve 50 is provided with a second switching circuit 49k of the relay valve 49 in the D range separately from the fail means at the time of the 1-2 shift in which the B2 pressure is released by the B2 pressure itself and the SL4 pressure (B1 pressure). The cut-off valve 48 that outputs the D pressure by the action of the C2 pressure and the C3 pressure that pass through is configured to maintain communication between the second friction brake B2 and the R pressure oil passage. Further, when the SL1 pressure is cut off by the lock valve 41 by the action of the first on / off solenoid valve S1, the SL3 pressure can be cut off to cut the C3 pressure.

(Normal 1st gear)
Referring to FIG. 25, during normal first speed travel, SL1 is energized, SL2 is energized, SL3 is de-energized, SL4 is de-energized, S1 is energized, lock valve 41 is on the o side, and the first on-fail valve 42 Is the normal side, the second on-fail valve 43 is the normal side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, the cutoff valve 48 is the X side, and the relay valve 49 is the ○ side , S2 is energized, and the apply valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, C3 pressure is not input to the first hydraulic chamber 48d, C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It is switched to the side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 41h of the lock valve 41, the second The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied. Is supplied to the second friction brake B2 via the second switching circuit 49k and the apply valve 50 of the relay valve 49, and the second friction brake B2 is engaged. This achieves the first gear.

(Normal 2nd gear)
Referring to FIG. 26, during normal second speed travel, SL1 is energized, SL2 is de-energized, SL3 is de-energized, SL4 is energized, S1 is energized, lock valve 41 is on the o side, and the first on-fail valve 42 Is the normal side, the second on-fail valve 43 is the normal side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, S2 is de-energized, and the cut-off valve 48 is the X side, Apply The valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is not input to the first hydraulic chamber 45e, the SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, C3 pressure is not input to the first hydraulic chamber 48d, C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It is switched to the side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 41h of the lock valve 41, the second The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the second on-fail valve 43, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear. Here, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5. Even if the SL2 pressure is supplied to the second switching circuit 49k and the apply valve 50 of the relay valve 49 due to the primary failure of the second control valve unit SL2, the SL4 pressure is input to the first hydraulic chamber 50g for the apply valve 50. The output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the output pressure (D pressure) of the cutoff valve 48 is not input to the third hydraulic chamber 50i. Since the fourth hydraulic chamber 50j communicates with the discharge port (EX) and the PL pressure is input to the fifth hydraulic chamber 50k and is switched to the ◯ side, the SL2 pressure does not reach the second friction brake B2.

(Normal 3rd gear)
Referring to FIG. 27, during normal third speed travel, SL1 is energized, SL2 is de-energized, SL3 is energized, SL4 is de-energized, S1 is energized, lock valve 41 is on the o side, and first on-fail valve 42 Is the normal side, the second on-fail valve 43 is the fail side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, the cut-off valve 48 is the ◯ side, and the relay valve 49 is the X side. , S2 is not energized, and the apply valve 50 is on the o side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 41h of the lock valve 41, the second The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 41g of the lock valve 41 and the second off-fail valve 45. It is supplied to the third friction clutch C3 through the circuit 45l and the third friction clutch C3 is engaged. This achieves the third gear. Here, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5. Even if the SL2 pressure is supplied to the second switching circuit 49k of the relay valve 49 due to the primary failure of the second control valve unit SL2, the relay valve 49 is switched to the X side, and the relay valve 49 is Even if the SL2 pressure is supplied to the apply valve 50 via the second switching circuit 49k of the relay valve 49, the SL2 pressure does not reach the second friction brake B2 because the apply valve 50 is on the ◯ side.

(Normal 4th gear)
Referring to FIG. 28, during normal 4th speed driving, SL1 is energized, SL2 is energized, SL3 is de-energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the o side, first on-fail valve 42 is the normal side, the second on-fail valve 43 is the normal side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, the cutoff valve 48 is the ◯ side, and the relay valve 49 is × Side, S2 is de-energized, and the apply valve 50 is ◯ side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched to. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is input to the first hydraulic chamber 44d, and the output pressure (D of the second switching circuit 44h is input to the second hydraulic chamber 44e. Pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, the C3 pressure is not input to the first hydraulic chamber 48d, the C2 pressure is input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 41h of the lock valve 41, the second The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied. Is supplied to the second friction clutch C2 through the first switching circuit 49j of the relay valve 49 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. This achieves the fourth gear. Here, even if the SL2 pressure is supplied to the apply valve 50 via the second switching circuit 49k of the relay valve 49 due to the primary failure of the relay valve 49, the SL2 pressure is switched because the apply valve 50 is switched to the ◯ side. Does not reach the second friction brake B2. Therefore, a downshift from the fourth gear to the first gear does not occur.

(Normal 5th gear)
Referring to FIG. 29, during normal fifth speed traveling, SL1 is de-energized, SL2 is energized, SL3 is energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the ◯ side, first on-fail valve 42 is the fail side, the second on-fail valve 43 is the fail side, the first off-fail valve 44 is the 5, 6 side, the second off-fail valve 45 is the normal side, the cut-off valve 48 is the ◯ side, and the relay valve 49 is × Side, S2 is de-energized, and the apply valve 50 is ◯ side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is input to the first hydraulic chamber 44d, and the output pressure (D of the second switching circuit 44h is input to the second hydraulic chamber 44e. Pressure) and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 5th and 6th sides. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL2 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cutoff valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 Is supplied to the second friction clutch C2 through the first switching circuit 49j of the relay valve 49 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. At the same time, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 41g of the lock valve 41 and the second off-fail valve 45. It is supplied to the third friction clutch C3 through the circuit 45l and the third friction clutch C3 is engaged. This achieves the fifth gear. Here, even if the SL2 pressure is supplied to the apply valve 50 via the second switching circuit 49k of the relay valve 49 due to the primary failure of the relay valve 49, the SL2 pressure is switched because the apply valve 50 is switched to the ◯ side. Does not reach the second friction brake B2. Therefore, a shift from the fifth gear to the reverse gear does not occur.

(Normal 6-speed driving)
Referring to FIG. 30, during normal 6th speed travel, SL1 is de-energized, SL2 is energized, SL3 is de-energized, SL4 is energized, S1 is de-energized, lock valve 41 is on the o side, first on-fail valve 42 is the normal side, the second on-fail valve 43 is the normal side, the first off-fail valve 44 is the 5th and 6th side, the second off-fail valve 45 is the normal side, the cut-off valve 48 is the ◯ side, and the relay valve 49 is × Side, S2 is de-energized, and the apply valve 50 is ◯ side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched to. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is input to the first hydraulic chamber 44d, and the output pressure (D of the second switching circuit 44h is input to the second hydraulic chamber 44e. Pressure) and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 5th and 6th sides. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL2 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, the C3 pressure is not input to the first hydraulic chamber 48d, the C2 pressure is input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. The output pressure (D pressure) of the cut-off valve 48 is input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. ing. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 Is supplied to the second friction clutch C2 through the first switching circuit 49j of the relay valve 49 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the second on-fail valve 43, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the sixth gear. Here, even if the SL2 pressure is supplied to the apply valve 50 through the second switching circuit 49k of the relay valve 49 due to the primary failure of the relay valve 49 and reaches the second friction brake B2, the first valve Since the SL4 pressure (B1 pressure) is input to the hydraulic chamber 50g and the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h and switched to the ○ side, SL2 The pressure does not reach the second friction brake B2. That is, the interlock between the first friction brake B1 and the second friction brake B2 can be avoided.

(Off-fail 3rd gear)
Referring to FIG. 31, during off-fail 3rd speed travel, SL1 is de-energized, SL2 is de-energized, SL3 is de-energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the X side, first The on-fail valve 42 is on the normal side, the second on-fail valve 43 is on the fail side, the first off-fail valve 44 is on the 1-4 side, the second off-fail valve 45 is on the fail side, the cut-off valve 48 is on the ○ side, and the relay valve 49 is the X side, S2 is not energized, and the Apply valve 50 is the ◯ side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input, and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL2 pressure) of the circuit 44i is not inputted and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the fail side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 through the first switching circuit 44g of the first off-fail valve 44 and the C1 switching circuit 45j of the second off-fail valve 45, and the first friction clutch C1 is engaged. To do. At the same time, the D pressure is supplied to the third friction clutch C3 through the C3 switching circuit 45l of the shuttle valve SB4 and the second off-fail valve 45, and the third friction clutch C3 is engaged. This achieves the third gear. At this time, since the supply of the D pressure is cut off by the D pressure switching circuit 45i of the second off-fail valve 45, the D pressure is not supplied to the second control valve unit SL2, and the second friction brake B2 is not fastened.

(Off-fail 5th gear)
Referring to FIG. 32, in the off-fail 5th speed travel, SL1 is de-energized, SL2 is de-energized, SL3 is de-energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the ○ side, first The on-fail valve 42 is on the fail side, the second on-fail valve 43 is on the fail side, the first off-fail valve 44 is on the 5 and 6 side, the second off-fail valve 45 is on the fail side, the cut-off valve 48 is on the ○ side, and the relay valve 49 is the X side, S2 is not energized, and the Apply valve 50 is the ◯ side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is input, and the SL1 pressure is not input to the third hydraulic chamber 44f. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL2 pressure) of the circuit 44i is not inputted and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the fail side. In the cutoff valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second friction clutch C2 through the second switching circuit 44h of the first off-fail valve 44 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. To do. At the same time, the D pressure is supplied to the third friction clutch C3 through the C3 switching circuit 45l of the shuttle valve SB4 and the second off-fail valve 45, and the third friction clutch C3 is engaged. This achieves the fifth gear. At this time, since the D pressure is shut off by the D pressure switching circuit 45i of the second off-fail valve 45, the D pressure is not supplied to the second control valve unit SL2, and the second friction brake B2 is There is no conclusion. After the vehicle stops, once the range is switched or the ignition is turned off, the latch of the first off-fail valve 44 (the input of the output pressure (D pressure) of the second switching circuit 44h to the second hydraulic chamber 44e) is released. Therefore, at the time of re-starting, the off-fail 3rd speed traveling of FIG. 31 is performed.

(When the 1st gear C1 line pressure is locked)
Referring to FIG. 33, SL1 is energized, SL2 is energized, SL2 is energized, and SL3 is energized when the C1 line pressure is locked at the first gear (when the maximum output pressure of the linear solenoid SL1 cannot secure the torque capacity in the first gear). Deenergized, SL4 deenergized, S1 deenergized, Lock valve 41 is X side, 1st on-fail valve 42 is normal side, 2nd on-fail valve 43 is normal side, 1st off-fail valve 44 is 1-4 The second off-fail valve 45 is on the normal side, the cutoff valve 48 is on the X side, the relay valve 49 is on the O side, S2 is energized, and the Apply valve 50 is on the X side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, C3 pressure is not input to the first hydraulic chamber 48d, C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It is switched to the side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 42, the orifice, the check ball valve, the second switching circuit 41h of the lock valve 41, and the C1 switching circuit 45j of the second off-fail valve 45. Thus, the first friction clutch C1 is engaged (C1 line pressure lock). At the same time, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied. Is supplied to the second friction brake B2 via the second switching circuit 49k and the apply valve 50 of the relay valve 49, and the second friction brake B2 is engaged. This achieves the first gear. In this case, the supply of hydraulic pressure to the third friction clutch C3 is blocked by the lock valve 41, so that the 1-2 shift and the 1-4 shift can be controlled, but the reverse gear configuration in which C3 and B2 are engaged is employed. It is possible to avoid it.

(When C1 line pressure is locked at 2nd gear)
Referring to FIG. 34, when the C1 line pressure is locked at the 2nd speed (when C1 torque capacity is required such as 2nd start), SL1 is energized, SL2 is deenergized, SL3 is deenergized, SL4 is energized, and S1 is non-energized. Energized, lock valve 41 is X side, first on-fail valve 42 is normal side, second on-fail valve 43 is normal side, first off-fail valve 44 is 1-4 side, second off-fail valve 45 is normal side The cut-off valve 48 is on the x side, the relay valve 49 is on the x side, S2 is de-energized, and the apply valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is not input to the first hydraulic chamber 45e, the SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, C3 pressure is not input to the first hydraulic chamber 48d, C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It is switched to the side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 42, the orifice, the check ball valve, the second switching circuit 41h of the lock valve 41, and the C1 switching circuit 45j of the second off-fail valve 45. Thus, the first friction clutch C1 is engaged (C1 line pressure lock). At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the second on-fail valve 43, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear. In this case, since the supply of hydraulic pressure to the third friction clutch C3 is blocked by the lock valve 41, the shift of 2⇔1, 2⇔4 can be controlled, but the reverse gear configuration in which C3 and B2 are engaged is employed. It is possible to avoid it.

(N (C1) C3 forced cut)
Referring to FIG. 35, SL1 is energized at the time of C3 forced cut of N (C1) in which only the first friction clutch C1 is engaged (C3 forced cut when the C1 line pressure is locked at the first speed stage and the second speed stage). SL2 is de-energized, SL3 is energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is X side, first on-fail valve 42 is normal, second on-fail valve 43 is normal, first off-fail The valve 44 is on the 1-4 side, the second off-fail valve 45 is on the normal side, the cutoff valve 48 is on the x side, the relay valve 49 is on the x side, S2 is de-energized, and the apply valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the cut-off valve 48, C3 pressure is not input to the first hydraulic chamber 48d, C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It is switched to the side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. Since the output pressure (D pressure) of the cut-off valve 48 is not input to the fourth hydraulic chamber 50j, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been switched. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 42, the orifice, the check ball valve, the second switching circuit 41h of the lock valve 41, and the C1 switching circuit 45j of the second off-fail valve 45. Thus, the first friction clutch C1 is engaged (C1 line pressure lock). Other engaging elements are not engaged. As a result, a neutral state (N (C1)) in which only the first friction clutch C1 is engaged is obtained. In this case, even if SL3 pressure is output, it is not fastened to C3. Even if this state occurs due to a primary failure, it is possible to travel at the third speed by using the third gear of the off-fail in FIG.

(During normal reverse gear)
Referring to FIG. 36, during normal reverse gear travel, SL1 is de-energized, SL2 is energized, SL3 is energized, SL4 is de-energized, S1 is energized, lock valve 41 is ◯ side, and first on-fail valve 42 is Normal side, second on-fail valve 43 is on the fail side, first off-fail valve 44 is on the 1-4 side, second off-fail valve 45 is on the normal side, cut-off valve 48 is on the o side, relay valve 49 is on the o side, S2 is energized, and the apply valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input, and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. The output pressure (SL1 pressure) of 44i is not input, and the fourth hydraulic chamber 45h communicates with the discharge port, so that it is switched to the normal side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is input to the second hydraulic chamber 49g, and the output pressure of the first switching circuit 49j is input to the third hydraulic chamber 49h. Since (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, it is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the R range, the R pressure is output from the manual valve (not shown), and the D pressure is not output. The PL pressure is input to the hydraulic control unit 3 even in the R range. In this state, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 41g of the lock valve 41 and the second off-fail valve 45. It is supplied to the third friction clutch C3 through the circuit 45l and the third friction clutch C3 is engaged. At the same time, the R pressure is supplied to the second control valve unit SL2 via the third switching circuit 49l of the relay valve 49 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied to the relay valve 49. It is supplied to the second friction brake B2 through the second switching circuit 49k and the apply valve 50, and the second friction brake B2 is engaged. This achieves the reverse gear. In the relay valve 49, the R pressure is input to the second hydraulic chamber 49g, and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i. The state of the relay valve 49 can be switched by controlling the signal pressure of the solenoid valve S2 (the signal pressure input to the first hydraulic chamber 49f). Even if the apply valve 50 fails due to a primary failure (failed on the circle side), the R pressure is supplied to the second friction brake B2 via the apply valve 50, so that the engagement state of the second friction brake B2 is changed. Can be maintained.

(When reverse C3 line pressure is locked)
Referring to FIG. 37, when the reverse C3 line pressure is locked, SL1 is de-energized, SL2 is energized, SL3 is energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the X side, and the first on-fail Valve 42 is on the normal side, second on-fail valve 43 is on the fail side, first off-fail valve 44 is on the 1-4 side, second off-fail valve 45 is on the normal side, cutoff valve 48 is on the ◯ side, and relay valve 49 is on ○ side, S2 is energized, and the apply valve 50 is the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input, and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. The output pressure (SL1 pressure) of 44i is not input, and the fourth hydraulic chamber 45h communicates with the discharge port, so that it is switched to the normal side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is input to the second hydraulic chamber 49g, and the output pressure of the first switching circuit 49j is input to the third hydraulic chamber 49h. Since (SL2 pressure) is not input and the output pressure (R pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, it is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the R range, the R pressure is output from the manual valve (not shown), and the D pressure is not output. The PL pressure is input to the hydraulic control unit 3 even in the R range. In this state, the R pressure is supplied to the third friction clutch C3 via the first switching circuit 41g of the lock valve 41 and the C3 switching circuit 45l of the second off-fail valve 45, and the third friction clutch C3 is engaged (C3 line). Pressure lock). At the same time, the R pressure is supplied to the second control valve unit SL2 via the third switching circuit 49l of the relay valve 49 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied to the relay valve 49. It is supplied to the second friction brake B2 through the second switching circuit 49k and the apply valve 50, and the second friction brake B2 is engaged. This achieves the reverse gear. Even if the apply valve 50 fails due to a primary failure (failed on the ◯ side), the R pressure is supplied to the second friction brake B2 through the apply valve 50, so that the engagement state of the second friction brake B2 is changed. Can be maintained.

(When the reverse B2 line pressure is locked)
Referring to FIG. 38, when the reverse B2 line pressure is locked, SL1 is de-energized, SL2 is de-energized, SL3 is energized, SL4 is de-energized, S1 is energized, lock valve 41 is ◯ side, and the first on-fail Valve 42 is on the normal side, second on-fail valve 43 is on the fail side, first off-fail valve 44 is on the 1-4 side, second off-fail valve 45 is on the normal side, cutoff valve 48 is on the ◯ side, and relay valve 49 is on The x side, S2 is not energized, and the apply valve 50 is the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input, and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. The output pressure (SL1 pressure) of 44i is not input, and the fourth hydraulic chamber 45h communicates with the discharge port, so that it is switched to the normal side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (R pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the R range, the R pressure is output from the manual valve (not shown), and the D pressure is not output. The PL pressure is input to the hydraulic control unit 3 even in the R range. In this state, the PL pressure is supplied to the third control valve unit SL3, and the output pressure (SL3 pressure) of the third control valve unit SL3 is the C3 switching of the first switching circuit 41g of the lock valve 41 and the second off-fail valve 45. It is supplied to the third friction clutch C3 through the circuit 45l and the third friction clutch C3 is engaged. At the same time, the R pressure is supplied to the second friction brake B2 via the second switching circuit 49k and the apply valve 50 of the relay valve 49, and the second friction brake B2 is engaged (B2 line pressure lock). This achieves the reverse gear. Even if the apply valve 50 fails due to a primary failure (failed on the ◯ side), the R pressure is supplied to the second friction brake B2 through the apply valve 50, so that the engagement state of the second friction brake B2 is changed. Can be maintained.

(When C3 and B2 line pressure is locked in reverse)
Referring to FIG. 39, when the reverse stage C3 and B2 line pressures are locked, SL1 is de-energized, SL2 is de-energized, SL3 is de-energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the X side, The first on-fail valve 42 is on the normal side, the second on-fail valve 43 is on the fail side, the first off-fail valve 44 is on the 1-4 side, the second off-fail valve 45 is on the fail side, the cut-off valve 48 is on the ○ side, The relay valve 49 is on the x side, S2 is de-energized, and the apply valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is not input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the fail side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input, and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is not input to the first hydraulic chamber 45e, the SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 is performed to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is not input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the fail side. In the cut-off valve 48, the C3 pressure is input to the first hydraulic chamber 48d, the C2 pressure is not input to the second hydraulic chamber 48e, and the third hydraulic chamber 48f communicates with the discharge port (EX). It has been switched to. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (R pressure) of the first switching circuit 41g of the lock valve 41 is input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (R pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the cut-off valve 48 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. It has been. Here, in the R range, the R pressure is output from the manual valve (not shown), and the D pressure is not output. The PL pressure is input to the hydraulic control unit 3 even in the R range. In this state, the R pressure is supplied to the third friction clutch C3 via the first switching circuit 41g of the lock valve 41, the shuttle valve SB4, and the C3 switching circuit 45l of the second off-fail valve 45, and the third friction clutch C3 is engaged. (C3 line pressure lock). At the same time, the R pressure is supplied to the second friction brake B2 via the second switching circuit 49k and the apply valve 50 of the relay valve 49, and the second friction brake B2 is engaged (B2 line pressure lock). As a result, the reverse gear can be ensured even if all the lines are disconnected.

  According to the sixth embodiment, it is possible to secure the reverse gear even if the control valve unit is in an off failure. Further, it is ensured that a reverse failure is caused by a primary failure at the time of forward movement, and even in the case of a secondary failure, the hydraulic pressure is supplied to one or both of the third friction clutch C3 and the second friction brake B2. Since it can be cut, it is possible to avoid a reverse configuration. Further, the 1-2 shift can be performed using the second control valve unit SL2.

(Embodiment 7)
Next, a hydraulic control device for an automatic transmission according to Embodiment 7 of the present invention will be described with reference to the drawings. FIG. 40 is a partial hydraulic circuit diagram schematically showing the configuration of the hydraulic control unit in the hydraulic control device for an automatic transmission according to the seventh embodiment of the present invention.

  In the seventh embodiment, the cutoff valve (48 in FIG. 24) in the sixth embodiment is abolished, and the function of the cutoff valve (48 in FIG. 24) is given to the second on-fail valve 53 as a substitute. That is, the second on-fail valve 53 operates on the apply valve 50 so as to output the D pressure at the time of failure, and supplies the R pressure to the second friction brake B2. Other configurations are the same as those of the sixth embodiment.

  The second on-fail valve 53 is a switching valve that switches an oil passage, and has a spool 53a, a spring 53b, a first hydraulic chamber 53c, and a second hydraulic chamber 53d in a valve body (not shown). . The spool 53a is slidably arranged in a valve body (not shown). The spring 53b is disposed in the second hydraulic chamber 53d, and biases the spool 53a toward the first hydraulic chamber 53c. The first hydraulic chamber 53c is a hydraulic chamber that acts to press the spool 53a against the second hydraulic chamber 53d side when the PL pressure is introduced. The second hydraulic chamber 53d is a hydraulic chamber that acts to press the spool 53a against the first hydraulic chamber 53c side by introducing the hydraulic pressure (C3 pressure) applied to the third friction clutch C3. The spool 53a has a second hydraulic chamber 53d side ("normal") when the pressing force by the hydraulic pressure of the first hydraulic chamber 53c is higher than the resultant force of the urging force of the spring 53b and the pressing force by the hydraulic pressure of the second hydraulic chamber 53d. ) And when it is low, it slides toward the first hydraulic chamber 53c ("fail"). The second on-fail valve 53 supplies the D pressure to the supply port of the fourth control valve unit SL4 when “normal”, and the supply port and the discharge port (EX) of the fourth control valve unit SL4 when “fail”. ) Are switched so as to communicate with each other. The second on-fail valve 53 allows the third hydraulic chamber 50i of the apply valve 50 to communicate with the discharge port (EX) when “normal”, and the D pressure is applied to the third hydraulic chamber of the apply valve 50 when “fail”. A second switching circuit 53f for switching to supply to 50i.

  The operation of the hydraulic control device for an automatic transmission according to the seventh embodiment will be described with reference to the drawings. 41 and 42 are partial hydraulic circuit diagrams for explaining the operation of the hydraulic control device for the automatic transmission according to the seventh embodiment of the present invention. In the seventh embodiment, a case will be described in which there is no one-way clutch OWC attached to the second friction brake B2 in the skeleton diagram of the automatic transmission in FIG. Also, the same operations as those in the sixth embodiment are omitted, and only different ones are described.

(Normal 4th gear)
Referring to FIG. 41, during normal 4th speed travel, SL1 is energized, SL2 is energized, SL3 is de-energized, SL4 is de-energized, S1 is de-energized, lock valve 41 is on the o side, the first on-fail valve 42 is the normal side, the second on-fail valve 53 is the normal side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, the relay valve 49 is the X side, and S2 is de-energized. The valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched to. In the second on-fail valve 53, the PL pressure is input to the first hydraulic chamber 53c and the C3 pressure is not input to the second hydraulic chamber 53d, so that the second on-fail valve 53 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is input to the first hydraulic chamber 44d, and the output pressure (D of the second switching circuit 44h is input to the second hydraulic chamber 44e. Pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i. The output pressure (D pressure) of the second switching circuit 53f of the second on-fail valve 53 is not input to the fourth hydraulic chamber 50j in communication with the discharge port (EX), and the PL pressure is applied to the fifth hydraulic chamber 50k. Is switched to the X side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 41h of the lock valve 41, the second The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied. Is supplied to the second friction clutch C2 through the first switching circuit 49j of the relay valve 49 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. This achieves the fourth gear. Here, the difference between the seventh embodiment (FIG. 41) and the normal fourth speed traveling (see FIG. 28) of the sixth embodiment is that the cut-off valve (48 in FIG. 28) is activated in the sixth embodiment. In contrast to the operation of the valve (50 in FIG. 28), in Embodiment 7, the second on-fail valve 53 is not operated, so the apply valve 50 is inactive. Therefore, in the seventh embodiment, the relay valve 49 is prevented from outputting to the second friction brake B2 side only by the latch holding by the C2 pressure. In the seventh embodiment, there is a possibility that the fourth failure from the fourth gear is caused by the second failure of the latch holding and the second failure of the second on / off solenoid S2 or the relay valve 49. However, in the control, for example, the second control It is possible to de-energize the valve unit SL2 to the neutral N (C1) in which only the first friction clutch C1 is engaged, and then to set an appropriate gear position.

(Normal 6-speed driving)
Referring to FIG. 42, during normal 6th speed travel, SL1 is de-energized, SL2 is energized, SL3 is de-energized, SL4 is energized, S1 is de-energized, lock valve 41 is on the o side, and the first on-fail valve 42 is the normal side, the second on-fail valve 53 is the normal side, the first off-fail valve 44 is the 5, 6 side, the second off-fail valve 45 is the normal side, the relay valve 49 is the X side, and S2 is de-energized, Apply The valve 50 is on the x side. That is, in the lock valve 41, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 41d, the C2 pressure is input to the second hydraulic chamber 41e, and the third hydraulic chamber 41f is the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is input to the third hydraulic chamber 42g. It has been switched to. In the second on-fail valve 53, the PL pressure is input to the first hydraulic chamber 53c and the C3 pressure is not input to the second hydraulic chamber 53d, so that the second on-fail valve 53 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is input to the first hydraulic chamber 44d, and the output pressure (D of the second switching circuit 44h is input to the second hydraulic chamber 44e. Pressure) and the SL1 pressure is not input to the third hydraulic chamber 44f, so that the pressure is switched to the 5th and 6th sides. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL2 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 41g of the lock valve 41 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. The output pressure (D pressure) of the second switching circuit 53f of the second on-fail valve 53 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is applied to the fifth hydraulic chamber 50k. Since it is input, it is switched to the x side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 Is supplied to the second friction clutch C2 through the first switching circuit 49j of the relay valve 49 and the C2 switching circuit 45k of the second off-fail valve 45, and the second friction clutch C2 is engaged. At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the first switching circuit 53e of the second on-fail valve 53, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1. And the first friction brake B1 is engaged. This achieves the sixth gear. Here, the difference between the seventh embodiment (FIG. 42) and the normal sixth speed traveling (see FIG. 30) of the sixth embodiment is that the second on-fail valve 53 is operating as in the fourth speed. Therefore, the apply valve 50 is inactive. Similarly to the fourth speed stage (see FIG. 41), the output pressure (SL2 pressure) of the second control valve unit SL2 does not reach the apply valve 50 unless a secondary failure occurs. Even if the SL2 pressure reaches the apply valve 50, the apply valve 50 is operated by the B1 pressure and the SL2 pressure, and the SL2 pressure does not reach the second friction brake B2.

  According to the seventh embodiment, the same effects as in the sixth embodiment are obtained.

(Embodiment 8)
Next, a hydraulic control device for an automatic transmission according to an eighth embodiment of the present invention will be described with reference to the drawings. FIG. 43 is a partial hydraulic circuit diagram schematically showing the configuration of the hydraulic control unit in the hydraulic control device for an automatic transmission according to the eighth embodiment of the present invention.

  In the eighth embodiment, similarly to the seventh embodiment, the cutoff valve (48 in FIG. 24) in the sixth embodiment is abolished, and the lock valve 61 has a function of the cutoff valve (48 in FIG. 24) instead. ing. That is, the lock valve 61 operates the apply valve 50 so as to output the D pressure when it is not operated, and supplies the R pressure to the second friction brake B2. Other configurations are the same as those of the sixth embodiment.

  The lock valve 61 is a switching valve that switches an oil passage, and is a spool that outputs an output pressure from predetermined control valve units SL1 and SL3 or a line pressure (D pressure, R pressure) according to a shift state. The position is switched. The lock valve 61 includes a first spool 61a, a second spool 61b, a spring 61c, a first hydraulic chamber 61d, a second hydraulic chamber 61e, and a third hydraulic chamber 61f in a valve body (not shown). Have. The first spool 61a is slidably arranged in a valve body (not shown). The second spool 61b is slidably disposed between the first spool 61a and the spring 61c in the valve body (not shown). The spring 61c is disposed in the third hydraulic chamber 61f and biases the first spool 61a and the second spool 61b toward the first hydraulic chamber 61d. The first hydraulic chamber 61d is a hydraulic chamber that acts to press the first spool 61a and the second spool 61b against the third hydraulic chamber 61f side when the hydraulic pressure from the first on / off solenoid valve S1 is introduced. The second hydraulic chamber 61e is a hydraulic chamber that acts to press the second spool 61b against the third hydraulic chamber 61f side when the C2 pressure is introduced. The third hydraulic chamber 61f communicates with the discharge port (EX). The spool 61a has a third hydraulic chamber 61f side when at least one of the pressing force by the hydraulic pressure of the first hydraulic chamber 61d and the pressing force by the hydraulic pressure of the second hydraulic chamber 61e is higher than the urging force of the spring 61c. "O"), and slides toward the first hydraulic chamber 61d side ("X") when it is low. The lock valve 61 supplies D pressure to the third hydraulic chamber 50i of the apply valve 50 when “◯”, and communicates the third hydraulic chamber 50i of the apply valve 50 with the discharge port (EX) when “X”. A D-pressure switching circuit 61g that performs switching so that the The lock valve 61 causes the output port of the third control valve unit SL3 to communicate with the C3 switching circuit 45l of the second off-fail valve 45, the shuttle valve SB4, and the fourth hydraulic chamber 49i of the relay valve 49 when “O”. , The R pressure input through the orifice and the check ball valve when “x” is supplied to the C3 switching circuit 45l of the second off-fail valve 45, the shuttle valve SB4, and the fourth hydraulic chamber 49i of the relay valve 49. A first switching circuit 61h for switching is provided. Further, the lock valve 41 causes the output port of the first control valve unit SL1 to communicate with the C1 switching circuit 45j of the second off-fail valve 45 when “O”, and the first on-fail valve 42 when “X”. And a second switching circuit 61i that switches the C1 switching circuit 45j of the second off-fail valve 45 to communicate with each other. An oil passage between the lock valve 61 and the first on-fail valve 42 has an orifice and a check ball valve.

  The operation of the hydraulic control device for an automatic transmission according to the eighth embodiment will be described with reference to the drawings. 44 to 47 are partial hydraulic circuit diagrams for explaining the operation of the hydraulic control device for the automatic transmission according to the eighth embodiment of the present invention. Also, the same operations as those in the sixth embodiment are omitted, and only different ones are described.

(N (C1) time)
Referring to FIG. 44, in the neutral N (C1) in which only the first friction clutch C1 is engaged, SL1 is energized, SL2 is energized, SL3 is deenergized, SL4 is deenergized, S1 is energized, and the lock valve 61 is o The first on-fail valve 42 is normal, the second on-fail valve 43 is normal, the first off-fail valve 44 is 1-4, the second off-fail valve 45 is normal, and the relay valve 49 is ○ , S2 is energized, and the apply valve 50 is on the o side. That is, in the lock valve 61, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 61d, the C2 pressure is not input to the second hydraulic chamber 61e, and the third hydraulic chamber 61f is connected to the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 61h of the lock valve 61 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. Since the output pressure (D pressure) of the D pressure switching circuit 61g of the lock valve 61 is input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. Switched to the ○ side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 61i of the lock valve 61, The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. Other engaging elements are not engaged. As a result, a neutral state (N (C1)) in which only the first friction clutch C1 is engaged is obtained. In the sixth embodiment (FIG. 25), although it is the first speed stage, the lock valve 61 is not operated as shown in FIG. 44, so that the D pressure is output from the lock valve 61, and the SL2 pressure is input to the apply valve 50 However, the second friction brake B2 is not reached. Further, in the eighth embodiment, when the first speed stage is configured, the following C1 line pressure lock is used.

(When the 1st gear C1 line pressure is locked)
Referring to FIG. 45, when the C1 line pressure is locked at the first gear (when the start of the stall cannot secure the torque capacity with the maximum output pressure of the linear solenoid SL1 in the first gear), SL1 is energized, SL2 is energized, and SL3 is Deenergized, SL4 deenergized, S1 deenergized, Lock valve 61 is X side, 1st on-fail valve 42 is normal side, 2nd on-fail valve 43 is normal side, 1st off-fail valve 44 is 1-4 The second off-fail valve 45 is on the normal side, the relay valve 49 is on the O side, S2 is energized, and the Apply valve 50 is on the X side. That is, in the lock valve 61, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 61d, the C2 pressure is not input to the second hydraulic chamber 61e, and the third hydraulic chamber 61f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, SL3 pressure is not input to the first hydraulic chamber 45e, SL4 pressure is not input to the second hydraulic chamber 45f, and the third switching of the first off-fail valve 44 to the third hydraulic chamber 45g. Since the output pressure (SL1 pressure) of the circuit 44i is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the output of the first switching circuit 49j is output to the third hydraulic chamber 49h. Since no pressure (SL2 pressure) is input and the output pressure (SL3 pressure) of the first switching circuit 61h of the lock valve 61 is not input to the fourth hydraulic chamber 49i, the pressure is switched to the ◯ side. In the apply valve 50, the SL4 pressure is not input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is input. The output pressure (D pressure) of the D pressure switching circuit 61g of the lock valve 61 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. So it is switched to the x side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 42, the orifice, the check ball valve, the second switching circuit 61i of the lock valve 61, and the C1 switching circuit 45j of the second off-fail valve 45. Thus, the first friction clutch C1 is engaged (C1 line pressure lock). At the same time, the D pressure is supplied to the second control valve unit SL2 via the D pressure switching circuit 45i of the second off-fail valve 45 and the shuttle valve SB5, and the output pressure (SL2 pressure) of the second control valve unit SL2 is supplied. Is supplied to the second friction brake B2 via the second switching circuit 49k and the apply valve 50 of the relay valve 49, and the second friction brake B2 is engaged. This achieves the first gear. Note that when 1-2 (OWC) is abolished in the eighth embodiment, the first friction clutch C1 cannot be controlled by the first control valve unit SL1 in N → D, and therefore accumulator control is performed in this pattern.

(Normal 2nd gear)
Referring to FIG. 46, during normal second speed travel, SL1 is energized, SL2 is de-energized, SL3 is de-energized, SL4 is energized, S1 is energized, lock valve 61 is on the o side, and the first on-fail valve 42 Is the normal side, the second on-fail valve 43 is the normal side, the first off-fail valve 44 is the 1-4 side, the second off-fail valve 45 is the normal side, the relay valve 49 is the X side, S2 is de-energized, the apply valve 50 is the ◯ side. That is, in the lock valve 61, the signal pressure of the first on / off solenoid valve S1 is input to the first hydraulic chamber 61d, the C2 pressure is not input to the second hydraulic chamber 61e, and the third hydraulic chamber 61f is connected to the discharge port ( EX), so it is switched to the circle side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is not input to the first hydraulic chamber 45e, the SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 61h of the lock valve 61 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. Since the output pressure (D pressure) of the D pressure switching circuit 61g of the lock valve 61 is input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. Switched to the ○ side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first control valve unit SL1 via the first on-fail valve 42, and the output pressure (SL1 pressure) of the first control valve unit SL1 is the second switching circuit 61i of the lock valve 61, The first friction clutch C1 is engaged by being supplied to the first friction clutch C1 through the C1 switching circuit 45j of the 2-off fail valve 45. At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the second on-fail valve 43, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear. Here, with respect to FIG. 46, the difference from the normal second speed traveling of the sixth embodiment (see FIG. 26) is that because the lock valve 61 is inactive and the D pressure is output and the apply valve 50 is activated, 2 → 1 shift is not possible. To implement the 2 → 1 shift, the following 2nd speed C1 line pressure lock is used.

(When C1 line pressure is locked at 2nd gear)
Referring to FIG. 47, when the C1 line pressure is locked at the 2nd speed (when C1 torque capacity is required such as 2nd start), SL1 is energized, SL2 is deenergized, SL3 is deenergized, SL4 is energized, and S1 is non-energized. Energized, lock valve 61 is X side, first on-fail valve 42 is normal side, second on-fail valve 43 is normal side, first off-fail valve 44 is 1-4 side, second off-fail valve 45 is normal side The relay valve 49 is on the x side, S2 is de-energized, and the apply valve 50 is on the x side. That is, in the lock valve 61, the signal pressure of the first on / off solenoid valve S1 is not input to the first hydraulic chamber 61d, the C2 pressure is not input to the second hydraulic chamber 61e, and the third hydraulic chamber 61f is the discharge port. Since it communicates with (EX), it is switched to the X side. In the first on-fail valve 42, the PL pressure is input to the first hydraulic chamber 42e, the C3 pressure is not input to the second hydraulic chamber 42f, and the C2 pressure is not input to the third hydraulic chamber 42g. It has been switched. In the second on-fail valve 43, the PL pressure is input to the first hydraulic chamber 43c and the C3 pressure is not input to the second hydraulic chamber 43d, so that the second on-fail valve 43 is switched to the normal side. In the first off-fail valve 44, the output pressure (SL2 pressure) of the first switching circuit 49j of the relay valve 49 is not input to the first hydraulic chamber 44d, and the output pressure of the second switching circuit 44h ( D pressure) is not input and the SL1 pressure is input to the third hydraulic chamber 44f, so that the pressure is switched to the 1-4 side. In the second off-fail valve 45, the SL3 pressure is not input to the first hydraulic chamber 45e, the SL4 pressure is input to the second hydraulic chamber 45f, and the third switching circuit of the first off-fail valve 44 is input to the third hydraulic chamber 45g. Since the output pressure 44i (SL1 pressure) is input and the fourth hydraulic chamber 45h communicates with the discharge port, it is switched to the normal side. In the relay valve 49, the signal pressure of the second on / off solenoid valve S2 is not input to the first hydraulic chamber 49f, the R pressure is not input to the second hydraulic chamber 49g, and the first switching circuit 49j is connected to the third hydraulic chamber 49h. Since the output pressure (SL2 pressure) is not input and the output pressure (SL3 pressure) of the first switching circuit 61h of the lock valve 61 is not input to the fourth hydraulic chamber 49i, it is switched to the x side. In the apply valve 50, the SL4 pressure is input to the first hydraulic chamber 50g, the output pressure (SL2 pressure) of the second switching circuit 49k of the relay valve 49 is not input to the second hydraulic chamber 50h, and the third hydraulic chamber 50i is not input. The output pressure (D pressure) of the D pressure switching circuit 61g of the lock valve 61 is not input, the fourth hydraulic chamber 50j communicates with the discharge port (EX), and the PL pressure is input to the fifth hydraulic chamber 50k. So it is switched to the x side. Here, in the D range, D pressure is output from a manual valve (not shown), and R pressure is not output. In this state, the D pressure is supplied to the first friction clutch C1 via the first on-fail valve 42, the orifice, the check ball valve, the second switching circuit 61i of the lock valve 61, and the C1 switching circuit 45j of the second off-fail valve 45. Thus, the first friction clutch C1 is engaged (C1 line pressure lock). At the same time, the D pressure is supplied to the fourth control valve unit SL4 through the second on-fail valve 43, and the output pressure (SL4 pressure) of the fourth control valve unit SL4 is supplied to the first friction brake B1 to be the first. The friction brake B1 is engaged. This achieves the second gear. Note that, similarly to N → D (first speed), N → D (second speed) controls the accumulator (DN accumulator 47) in this pattern.

  According to the eighth embodiment, the same effect as in the sixth embodiment is obtained.

It is the schematic which showed the whole structure of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. 1 is a skeleton diagram of an automatic transmission in a hydraulic control device for an automatic transmission according to Embodiment 1 of the present invention. FIG. Engagement / disengagement of the first to third friction clutches C1 to C3 and the first and second friction brakes B1 and B2 of the automatic transmission in the hydraulic control device for the automatic transmission according to the first embodiment of the present invention; It is a list figure which shows the relationship with the gear stage corresponding to it. 1 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to Embodiment 1 of the present invention. FIG. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of 3rd speed driving | running | working of the off-fail of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of 5th speed driving | running | working of the off-fail of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 1st speed (OWC) driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 1st speed (OWC) driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 2nd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 2nd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 3rd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal 3rd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 4th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 5th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 6th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal reverse gear travel (1) of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. It is a partial hydraulic circuit diagram for demonstrating operation | movement at the time of normal reverse gear travel (2) of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 1 of this invention. FIG. 5 is a partial hydraulic circuit diagram schematically illustrating a configuration of a first modification of the hydraulic control unit in the hydraulic control device for the automatic transmission according to the first embodiment of the present invention. FIG. 5 is a partial hydraulic circuit diagram schematically illustrating a configuration of a second modification of the hydraulic control unit in the hydraulic control device for the automatic transmission according to the first embodiment of the present invention. FIG. 5 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to a second embodiment of the present invention. FIG. 5 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to a third embodiment of the present invention. FIG. 9 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to a fourth embodiment of the present invention. FIG. 9 is a partial hydraulic circuit diagram schematically showing a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to a fifth embodiment of the present invention. It is the partial hydraulic circuit figure which showed typically the structure of the hydraulic control part in the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 1st speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 2nd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 3rd speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 4th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 5th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 6-speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of 3rd speed driving | running | working of the off-fail of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of 5th speed driving | running | working of the off-fail of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of the C1 line pressure lock of the 1st speed stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of C1 line pressure lock of the 2nd speed stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of C3 forced cut of N (C1) of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal reverse drive of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of C3 line pressure lock of the reverse stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of B2 line pressure locking of the reverse stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of C3 and B2 line pressure locking of the reverse stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 6 of this invention. FIG. 10 is a partial hydraulic circuit diagram schematically illustrating a configuration of a hydraulic control unit in a hydraulic control device for an automatic transmission according to a seventh embodiment of the present invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 4th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 7 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 6th speed driving | running | working of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 7 of this invention. It is the partial hydraulic circuit figure which showed typically the structure of the hydraulic control part in the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 8 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of N (C1) of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 8 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of the C1 line pressure lock of the 1st speed stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 8 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of normal 2nd speed driving | running of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 8 of this invention. It is a partial hydraulic circuit diagram for demonstrating the operation | movement at the time of the C1 line pressure lock of the 2nd speed stage of the hydraulic control apparatus of the automatic transmission which concerns on Embodiment 8 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Automatic transmission 2 Engine 3 Hydraulic control part 4 Electronic control part 5 Engine speed sensor 6 Input shaft speed sensor 7 Output shaft speed sensor 8 Opening sensor 9 Position sensor 10 Torque converter 10a Turbine runner 10b Pump impeller 11 Input shaft 12 output shaft 21 lock valve 21a spool 21b spring 21c first hydraulic chamber 21d second hydraulic chamber 21e first switching circuit 21f second switching circuit 22 first on-fail valve 22a first spool 22b second spool 22c sleeve 22d spring 22e first 1 hydraulic chamber 22f second hydraulic chamber 22g third hydraulic chamber 23 second on-fail valve 23a spool 23b spring 23c first hydraulic chamber 23d second hydraulic chamber 24 first off-fail valve 24a first spool 24b second sp 24c Spring 24d First hydraulic chamber 24e Second hydraulic chamber 24f Third hydraulic chamber 24g First switching circuit 24h Second switching circuit 24i Third switching circuit 25 Second off-fail valve 25a First spool 25b Second spool 25c Second spool 25c 3 spool 25d spring 25e first hydraulic chamber 25f second hydraulic chamber 25g third hydraulic chamber 25h fourth hydraulic chamber 25i C1 switching circuit 25j C2 switching circuit 25k C3 switching circuit 26 N-R accumulator 27 D-N accumulator 31 lock valve 31a First spool 31b Second spool 31c Spring 31d First hydraulic chamber 31e Second hydraulic chamber 31f Third hydraulic chamber 31g First switching circuit 31h Second switching circuit 35 Second off-fail valve 35a First spool 35b Second spool 35c Second spool 3 spool 35 Fourth spool 35e Spring 35f First hydraulic chamber 35g Second hydraulic chamber 35h Third hydraulic chamber 35i Fourth hydraulic chamber 35j Fifth hydraulic chamber 35k C1 switching circuit 35l C2 switching circuit 35m B3 switching circuit 41 Lock valve 41a First spool 41b Second spool 41c spring 41d first hydraulic chamber 41e second hydraulic chamber 41f third hydraulic chamber 41g first switching circuit 41h second switching circuit 42 first on-fail valve 42a first spool 42b second spool 42c sleeve 42d spring 42e first 1 hydraulic chamber 42f second hydraulic chamber 42g third hydraulic chamber 43 second on-fail valve 43a spool 43b spring 43c first hydraulic chamber 43d second hydraulic chamber 44 first off-fail valve 44a first spool 44b second spool 44c spring 44d first hydraulic chamber 44e second hydraulic chamber 44f third hydraulic chamber 44g first switching circuit 44h second switching circuit 44i third switching circuit 45 second off-fail valve 45a first spool 45b second spool 45c third spool 45d Spring 45e First hydraulic chamber 45f Second hydraulic chamber 45g Third hydraulic chamber 45h Fourth hydraulic chamber 45i D pressure switching circuit 45j C1 switching circuit 45k C2 switching circuit 45l C3 switching circuit 46 N-R accumulator 47 DN accumulator 48 cut Off valve (blocking means)
48a First spool 48b Second spool 48c Spring 48d First hydraulic chamber 48e Second hydraulic chamber 48f Third hydraulic chamber 49 Relay valve 49a First spool 49b Second spool 49c Third spool 49d Sleeve 49e Spring 49f First hydraulic chamber 49g Second hydraulic chamber 49h Third hydraulic chamber 49i Fourth hydraulic chamber 49j First switching circuit 49k Second switching circuit 49l Third switching circuit 50 Apply valve 50a First spool 50b Second spool 50c Third spool 50d Fourth spool 50e Sleeve 50f Spring 50g First hydraulic chamber 50h Second hydraulic chamber 50i Third hydraulic chamber 50j Fourth hydraulic chamber 50k Fifth hydraulic chamber 51 B2 accumulator 53 Second on-fail valve 53a Spool 53b Spring 53c First hydraulic chamber 53d Second hydraulic chamber 53e First switching circuit 53f Second switching circuit (blocking means)
61 lock valve 61a first spool 61b second spool 61c spring 61d first hydraulic chamber 61e second hydraulic chamber 61f third hydraulic chamber 61g D pressure switching circuit (blocking means)
61h 1st switching circuit 61i 2nd switching circuit SL1 1st control valve unit (control valve)
SL2 Second control valve unit (control valve)
SL3 Third control valve unit (control valve)
SL4 4th control valve unit (control valve)
SL5 5th control valve unit (control valve)
S On-off solenoid valve S1 1st on-off solenoid valve S2 2nd on-off solenoid valve SB Shuttle valve SB2 Shuttle valve SB3 Shuttle valve SB4 Shuttle valve SB5 Shuttle valve

Claims (5)

A hydraulic control device for an automatic transmission in which a gear position is switched by a combination of supply of hydraulic pressure to some of the plurality of engagement elements and discharge of hydraulic pressure from other engagement elements,
Adjusting the line pressure input to the supply port according to the energized state to generate a control oil pressure, outputting the control oil pressure as an output pressure from the output port, and engaging the corresponding engagement element by the control oil pressure; A plurality of control valves (SL1 to SL4) for controlling disengagement;
A spool is provided and is switched to output the line pressure while maintaining the spool position of the shift stage before the failure state when a failure state in which no hydraulic pressure is output from any of the control valves is entered. 1 off-fail valve (24, 44);
A lock valve (21, 31, 41, 61) whose spool position is switched so as to output a predetermined output pressure from the control valve or a line pressure;
An on / off solenoid valve (S, S1) capable of controlling the spool position of the lock valve in accordance with an energized state;
The lock valve is output in a normal state in which the line pressure from the first off-fail valve is output toward a predetermined engagement element in the fail state and a predetermined hydraulic pressure of the control valve is output. A second off-fail valve (25, 35, 45) in which the spool position is switched so as to output the hydraulic pressure from a predetermined direction toward the engagement element;
A hydraulic control device for an automatic transmission, comprising:   The predetermined engagement element that can receive the hydraulic pressure output from the second off-fail valve includes an engagement element (C1, C3) used in the low / medium speed stage configuration and an engagement element used in the high speed stage configuration. 2. The hydraulic control device for an automatic transmission according to claim 1, further comprising: (C2, C3) and an engagement element (C3) used in a reverse gear configuration. A predetermined output pressure of the control valve (SL2) is output toward the engagement element (C2) used at the high speed stage or the engagement element (B2) used at the low / medium speed stage and the reverse stage. A relay valve (49) whose spool position is switched to
A second on / off solenoid valve (S2) capable of controlling the spool position of the relay valve in accordance with an energized state;
With
The second off-fail valve supplies the line pressure (D pressure) at the forward stage to the predetermined control valve (SL2) at the forward stage when the forward stage is in the normal state, and at the fail state. Shut off the supply of the line pressure (D pressure) at the forward stage to the control valve (SL2);
The relay valve is in the reverse stage,
When the predetermined output pressure of the control valve (SL2) is output toward the engagement element (B2) used at the low / medium speed stage and the reverse stage, the line pressure (R pressure) at the reverse stage is set. Supplying the predetermined control valve (SL2), and
When the output pressure of the predetermined control valve (SL2) is output toward the engagement element (C2) used at the high speed stage, the line pressure (R pressure) at the reverse stage is set to the predetermined control valve. (SL2) is cut off, and the line pressure (R pressure) at the reverse stage is output toward the engagement element (B2) used at the low and medium speed stages and the reverse stage,
The relay valve controls the output pressure of the predetermined control valve (SL2) when the hydraulic pressure is applied to the engagement element (C3) used at the high speed stage and the reverse stage at the forward stage. The hydraulic control device for an automatic transmission according to claim 1 or 2, further comprising a hydraulic chamber (49i) for switching so as to output toward an engagement element (C2) used sometimes.   The relay valve acts to maintain the spool position when outputting a predetermined output pressure of the control valve (SL2) toward the engagement element (C2) used at the high speed stage. The hydraulic control device for an automatic transmission according to claim 3, further comprising: (49 h). The relay valve is disposed in an oil passage that communicates with the engagement element (B2) used at the low / medium speed stage and the reverse stage, and the output pressure of the relay valve or the line pressure (R Pressure) is applied toward the engagement element (B2) used at the low and medium speed stages and the reverse stage, and an apply valve (50) whose spool position is switched is provided.
When the apply valve (50) is engaged at the same time as the engaging element (B2) used in the low and medium speed stages and the reverse stage when the output pressure of the relay valve is input in the forward stage, When the hydraulic pressure applied to the engaging element (B1) that causes the interlock becomes equal to or higher than a predetermined value, the output pressure of the relay valve is output toward the engaging element (B2) used in the low and medium speed stages and the reverse speed stage. The hydraulic control device for an automatic transmission according to claim 3 or 4, further comprising a hydraulic chamber (50g, 50h) acting so as not to operate.

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