JP2015194183A - Automatic transmission hydraulic control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an automatic transmission hydraulic control device capable of suppressing reduction in the engagement pressure of a corresponding engagement element even if voltage drop occurs during actuation of a hydraulic servomechanism by an electric oil pump, without increasing the number of components.SOLUTION: If a line pressure PL is supplied from a first hydraulic pressure supply unit 10, a switching valve 60 is set in a first state to accumulate the line pressure PL in an accumulator 50 via an oil passage h1. If the line pressure PL is not supplied from the first hydraulic pressure supply unit 10 and an electromagnetic pump pressure PEMOP is supplied from an electromagnetic pump 20, the switching valve 60 is set in a second state to supply the electromagnetic pump pressure PEMOP to a hydraulic servomechanism 4 via oil passages f1, f2, and d1 and accumulate the electromagnetic pump pressure PEMOP in the accumulator 50 via oil passages f1, f2, g1, b3, and h1.

Description

  The present invention relates to a hydraulic control device for an automatic transmission mounted on a vehicle, for example, and more specifically, a hydraulic control device for an automatic transmission having two types of oil pumps of a mechanical oil pump and an electric oil pump as a hydraulic supply source. About.

  In recent years, in order to improve fuel efficiency, for example, vehicles that perform a so-called idle stop that stops an internal combustion engine that is a drive source while the vehicle is stopped are being developed. In a vehicle drive device such as an automatic transmission or a hybrid drive device mounted on such a vehicle, a mechanical oil pump driven by the internal combustion engine generates hydraulic pressure used for hydraulic control, but the internal combustion engine is stopped. When that happens, the mechanical oil pump also stops. Here, if the transmission path of the vehicle drive device is formed by a hydraulic friction engagement element such as a clutch, the vehicle can be started with good response, so that the electric oil that can be driven independently from the mechanical oil pump Developed a hydraulic control device for a vehicle drive device that has a pump to generate hydraulic pressure and supply hydraulic pressure from the electric oil pump to the friction engagement element (first clutch C1) without using a manual valve. (See Patent Document 1).

  Further, in the hydraulic control device of this vehicle drive device, the forward range is connected to the oil passage connecting the input port of the linear solenoid valve capable of supplying the engagement pressure to the hydraulic servo and the output port of the forward range pressure of the manual valve. An accumulator capable of accumulating pressure is connected. As a result, when the travel range is switched from, for example, the D (drive) range to the N (neutral) range, even if the forward range pressure becomes zero, the hydraulic pressure accumulated in the accumulator is hydraulic via the linear solenoid valve. Since the servo is supplied to the servo, the transition to the released state of the first clutch C1 can be delayed.

JP 2013-174259 A

  However, in the hydraulic control apparatus described above, no accumulator is provided in the oil path from the electric oil pump to the hydraulic servo. For this reason, for example, when the starter motor is driven to start the internal combustion engine and the voltage of the battery drops to reduce the discharge amount of the electric oil pump, the engagement pressure of the first clutch C1 is reduced. May decrease and the engagement of the first clutch C1 may become unstable. In order to solve this, for example, a new accumulator may be added to the oil passage from the electric oil pump to the hydraulic servo, but in this case, the number of parts increases.

  Accordingly, to provide a hydraulic control device for an automatic transmission that can suppress a decrease in engagement pressure of a corresponding engagement element even when a voltage decrease occurs during operation of a hydraulic servo by an electric oil pump without increasing the number of parts. With the goal.

The hydraulic control device (2) of the automatic transmission (1) according to the present disclosure (see, for example, FIG. 1 (a)) can supply the first hydraulic pressure (PL) based on the drive of the mechanical oil pump (3). An automatic transmission (1) including a first hydraulic pressure supply section (10) and a second hydraulic pressure supply section (20) capable of supplying a second hydraulic pressure (PEMOP) based on driving of the electric oil pump. ) Hydraulic control device (2)
A solenoid valve (SL1) capable of supplying an engagement pressure (PSL1) to the hydraulic servo (4) for engaging / disengaging an engagement element for transmitting power based on the first oil pressure (PL); A switching valve (60) switchable to a second state, a check valve (40) capable of circulating hydraulic pressure in only one direction, and an accumulator (50) having a pressure accumulating oil chamber (50a) capable of accumulating hydraulic pressure The first oil passage connecting the first hydraulic pressure supply section (10) to the input port (SL1a) of the solenoid valve (SL1) through the check valve (40) and the switching valve (60) in order. (A1, b1 to b6), a second oil passage (c1) connected from the output port (SL1b) of the solenoid valve (SL1) to the switching valve (60), and the switching valve (60) A third oil passage (d1) connected to the hydraulic servo (4), and a fourth oil passage (f1, f2) connected from the second hydraulic pressure supply section (20) to the switching valve (60). The first oil passage (b3, b4) and the fourth oil passage between the check valve (40) and the switching valve (60) when at least the switching valve (60) is in the second state. (F2) and a fifth oil passage (g1), the first oil passage (b1 to b4) between the check valve (40) and the switching valve (60) or the fifth oil passage (g2). A sixth oil passage (h1) connecting the oil passage (g1) and the pressure accumulating oil chamber (50a) of the accumulator (50),
In the first state, the switching valve (60) communicates the first oil passages (b4, b5), the second oil passage (c1), the third oil passage (d1), , The fourth oil passage (f2) and the fifth oil passage (g1) are shut off, and in the second state, the first oil passage (b4, b5) is shut off, Blocking the second oil passage (c1), and communicating the third oil passage (d1), the fourth oil passage (f2), and the fifth oil passage (g1);
When the first hydraulic pressure (PL) is supplied from the first hydraulic pressure supply unit (10), the switching valve (60) is set to the first state, and the first hydraulic pressure (PL) is set to the first hydraulic pressure (PL). The engagement pressure (PSL1) output from the solenoid valve (SL1) is supplied to the solenoid valve (SL1) via the first oil passage (a1, b1 to b6), and the second oil passage ( c1) and the third oil passage (d1) to the hydraulic servo (4) and the first oil pressure (PL) to the accumulator (6) via the sixth oil passage (h1). 50)
When the first hydraulic pressure (PL) is not supplied from the first hydraulic pressure supply unit (10) and the second hydraulic pressure (PEMOP) is supplied from the second hydraulic pressure supply unit (20), With the switching valve (60) in the second state, the second hydraulic pressure (PEMOP) is transferred to the hydraulic servo (via the fourth oil passage (f1, f2) and the third oil passage (d1). 4) and supplying the second hydraulic pressure (PEMOP) to the fourth oil passage (f1, f2), the fifth oil passage (g1), the first oil passage (b3), The pressure is accumulated in the accumulator (50) through six oil passages (h1).

  Note that the reference numerals in the parentheses are for comparison with the drawings, but this is for convenience of understanding and does not affect the configuration of the claims in any way. Absent.

  According to the hydraulic control device of this automatic transmission, when the electric oil pump is driven, the accumulator communicates with the oil passage from which the hydraulic pressure is output from the electric oil pump, so there is a voltage drop when the hydraulic servo is operated by the electric oil pump. Also, a decrease in the engagement pressure of the corresponding engagement element can be suppressed. In addition, since the accumulator can be used for both the first hydraulic pressure accumulation based on the drive of the mechanical oil pump and the second hydraulic pressure accumulation based on the drive of the electric oil pump, an increase in the number of parts can be prevented. be able to. Also, for example, when the internal combustion engine is restarted from the idle stop, and the switching valve is switched from the second state to the first state, the accumulator is already accumulated by the electric oil pump. There is no need for refilling, and it is possible to prevent the controllability of the hydraulic servo from being lowered due to refilling.

It is the schematic of the hydraulic control apparatus which concerns on this Embodiment, (a) is a schematic hydraulic circuit diagram, (b) is sectional drawing of the switching valve cut | disconnected by the II line | wire in (a).

  Hereinafter, an embodiment according to the present invention will be described with reference to FIG.

  The hydraulic control device for an automatic transmission according to this embodiment includes at least one engagement element and two types of oil pumps, that is, a mechanical oil pump and an electric oil pump as a hydraulic supply source, and at least one for transmitting power. It is suitable for use in a hydraulic control device for an automatic transmission having two engaging elements. As an automatic transmission here, for example, it has four clutches, two brakes, and one one-way clutch, and among them, the eight forward speeds and the first reverse speed are selectively selected by simultaneously engaging two engagement elements. It is assumed that a multi-stage transmission that can be formed in the same manner can be used (see, for example, JP 2011-214644 A). The hydraulic control device for an automatic transmission according to the present invention is not limited to application to a multi-stage transmission, and can be similarly applied to, for example, a belt type continuously variable transmission (CVT), a hybrid drive device, and the like. is there.

  As shown in FIG. 1 (a), the automatic transmission 1 includes a hydraulic control device 2, a mechanical oil pump 3 connected to a drive source (internal combustion engine), and hydraulically operated to disengage the first clutch C1. A possible hydraulic servo 4 and a control unit (ECU) 5 that electrically controls each unit are provided.

  The hydraulic control device 2 includes a valve body, and includes a first hydraulic pressure supply unit 10, an electromagnetic pump (second hydraulic pressure supply unit) 20, a manual valve (traveling range pressure supply unit) 30, and a check valve 40. The accumulator 50, the switching valve 60, the linear solenoid valve (solenoid valve) SL1, and the orifice (delay means) 70 are provided.

  The first hydraulic pressure supply unit 10 includes a primary regulator valve that is controlled by the ECU 5 and regulates the original pressure generated by the mechanical oil pump 3 to the line pressure (first hydraulic pressure) PL. In addition, various source pressures such as the modulator pressure Pmod are regulated and generated. Thus, the first hydraulic pressure supply unit 10 supplies the line pressure PL to the oil passage a1 when the internal combustion engine is driven. The hydraulic control device 2 also includes a lubrication relay valve (not shown), a circulation modulator, in which the spool position is switched or controlled to selectively switch or adjust the hydraulic pressure based on various original pressures to the respective oil passages. Equipped with valves, lock-up relay valves, sequence valves, etc. Since the hydraulic circuit configuration for generating the line pressure PL, the modulator pressure Pmod, and the like is the same as that of a general hydraulic control device for an automatic transmission, detailed description thereof is omitted.

  The electromagnetic pump 20 is connected to, for example, a strainer installed in an oil pan (not shown), and is electrically driven to generate an electromagnetic pump pressure PEMOP when it is turned on to generate an electromagnetic pump pressure PEMOP. When it is output to the oil passage f1 and is controlled to be off, it is in a non-output state and shut off. In the present embodiment, the second hydraulic pressure supply unit is an electric oil pump and the electromagnetic pump 20 is applied. However, the present invention is not limited to this, and other types of electric oil pumps may be applied.

  The manual valve 30 includes a spool 30p that is moved by operating a shift lever (not shown), an input port 30a to which the line pressure PL is input via the oil passage a1, and a spool 30p that is in the D (drive) range position. The output port 30b that supplies the line pressure PL to the oil passage b1 as the forward range pressure PD (line pressure PL in a broad sense), and the forward range pressure PD and the electromagnetic pump pressure PEMOP to the oil passage b7 when the spool 30p is not in the D range position. , F4 and a discharge port 30c. That is, the manual valve 30 can be switched between an output state (for example, D range) capable of outputting a travel range pressure based on the line pressure PL and a drain state (for example, N range) capable of draining within a predetermined travel range. It has become. In this embodiment, the manual valve is applied as the travel range pressure supply unit. However, the present invention is not limited to this, and for example, a shift-by-wire travel range pressure supply unit may be used.

  The check valve 40 includes an input port 40a that communicates with the oil passage b2, an output port 40b that communicates with the oil passage b3, a sealing member 40p that can switch communication between the input port 40a and the output port 40b, and a compression coil. And a spring 40s made of a spring. Here, the spring 40s is set so as to urge the sealing member 40p so as to block the input port 40a and the output port 40b and to communicate the input port 40a and the output port 40b with a hydraulic pressure lower than the forward range pressure PD. Has been. For this reason, when the forward range pressure PD is input to the input port 40a, the sealing member 40p is switched against the spring 40s, and the input port 40a and the output port 40b communicate with each other. Hydraulic pressure can be distributed only in one direction.

  The accumulator 50 includes a movable member 50p, a spring 50s formed of a compression coil spring that presses the movable member 50p, and a pressure accumulation oil chamber 50a for pushing the movable member 50p against the spring 50s to accumulate pressure. Yes. The pressure accumulating oil chamber 50a is connected to the oil passage b3 via the oil passage h1, and can accumulate the forward range pressure PD or the electromagnetic pump pressure PEMOP supplied to the oil passage h1. When the internal combustion engine is stopped and the mechanical oil pump 3 is stopped, the accumulator 50 stops generating the line pressure PL and the forward range pressure PD disappears, or when the electromagnetic pump 20 is stopped, The hydraulic pressure corresponding to the forward range pressure PD is continuously supplied to the linear solenoid valve SL1.

  The switching valve 60 is a C1 apply relay valve in the present embodiment, and can be switched between a first state and a second state by a linear solenoid valve SL1. The switching valve 60 has a position indicated by the right half in the figure (first state, normal mode) (hereinafter referred to as “right half position”) and a position indicated by the left half in the figure (second state, eco-run mode) (hereinafter referred to as “running mode”). And a spring 60s formed of a compression coil spring that urges the spool 60p to the left half position. In addition, the switching valve 60 is connected from the oil passage b1 to the first input port 60c that inputs the forward range pressure PD from the oil passage b4, the second input port 60d that inputs the electromagnetic pump pressure PEMOP from the oil passage f2, and the oil passage c1. A third input port 60e that inputs the combined pressure PSL1 and a connection port 60f that communicates with the oil path f1, f2, and f4 via the oil path f3 and also communicates with the electromagnetic pump 20 are provided. Further, the switching valve 60 includes a first output port 60g communicating with the oil passage b5, a second output port 60h communicating with the oil passage g1, a third output port 60i communicating with the oil passage d1, and a discharge. And a port 60j. The switching valve 60 also has a first hydraulic oil chamber 60a that inputs a modulator pressure Pmod (line pressure PL in a broad sense) in a direction that presses the spool 60p to the right half position, and presses the spool 60p to the left half position. And a second hydraulic oil chamber 60b for inputting a signal pressure PSC2 from a solenoid valve SC2 (not shown) in the direction to be moved.

  When the spool 60p is in the first state of the right half position, the switching valve 60 communicates with the first input port 60c and the first output port 60g, and the second input port 60d and the second input port 60g. The output port 60h is blocked, the third input port 60e and the third output port 60i are communicated, and the connection port 60f and the discharge port 60j are communicated. In addition, when the spool 60p is in the second state of the left half position, the switching valve 60 is disconnected from the first input port 60c and the first output port 60g, and is connected to the second input port 60d and the second input port 60d. The output port 60h and the third output port 60i communicate with each other, the third input port 60e is blocked, and the connection port 60f and the discharge port 60j are blocked. That is, as to the oil passage connection relationship described later, in the first state, the switching valve 60 communicates the oil passages b4 and b5, communicates the oil passage c1 and the oil passage d1, and connects the oil passage f2 and the oil passage. In the second state, the oil passages b4 and b5 are shut off, the oil passage c1 is shut off, and the oil passage d1, the oil passage f2, and the oil passage g1 are communicated with each other. It has become.

  As shown in FIG. 1B, the first input port 60c and the first output port 60g of the switching valve 60 are formed by holes arranged at intervals in the circumferential direction with respect to the central axis of the spool 60p. In addition, they are arranged side by side with the same position in the central axis direction. As a result, when the switching valve 60 is in the second state, the forward range pressure PD supplied from the oil passage b4 to the first input port 60c urges the spool 60p with the urging force F so that the valve body To the wall surface 60w (dotted line portion). For this reason, since the clearance gap between the spool 60p and a valve body becomes small, the leakage amount of the hydraulic fluid from the said site | part can be reduced, and controllability can be improved. Moreover, since the two ports are arranged at the same position in the central axis direction, the length of the switching valve 60 can be shortened compared to the case where the two ports are arranged shifted in the axial direction.

  Similarly, the second input port 60d and the second output port 60h of the switching valve 60 are formed by holes that are spaced apart from each other in the circumferential direction with respect to the central axis of the spool 60p, and are positioned in the central axis direction. Are arranged side by side with the same. Further, both the connection port 60f and the discharge port 60j of the switching valve 60 are formed by holes arranged at intervals in the circumferential direction with respect to the central axis of the spool 60p, and are arranged side by side with the same position in the central axis direction. Has been. In either case, the controllability can be improved and the switching valve 60 can be shortened as described above.

  In the present embodiment, the first input port 60c and the first output port 60g, the second input port 60d and the second output port 60h, and the connection port 60f and the discharge port 60j described above are all hole-shaped. However, it is not limited to making all these ports hole-shaped, but some of these ports are hole-shaped and the rest are all-round ports, or all ports are all-round ports. It may be.

  The linear solenoid valve SL1 includes an input port SL1a to which the forward range pressure PD is input from the oil passage b6, an output port SL1b communicated with the third input port 60e by the oil passage c1, and a drain port SL1c. The forward range pressure PD is freely regulated and generated, and an engagement pressure PSL1 for supplying to the hydraulic servo 4 is generated and supplied from the output port SL1b to the oil passage c1.

  The orifice 70 is interposed in an oil passage e1 that connects the oil passages b5 and b6 between the input port SL1a of the linear solenoid valve SL1 and the first output port 60g of the switching valve 60 to the output port 30b of the manual valve 30. The hydraulic flow velocity in the oil passage e1 is delayed.

  Next, the oil passage in the hydraulic control device 2 will be described. The hydraulic control device 2 includes first to seventh oil passages.

  The first oil passage is connected from the first hydraulic pressure supply unit 10 to the solenoid valve SL1 through the manual valve 30, the check valve 40, and the switching valve 60 in order. That is, the first oil passage includes an oil passage a1 connected from the first hydraulic pressure supply unit 10 to the input port 30a of the manual valve 30, an oil passage b1 and b2 connected from the output port 30b to the check valve 40, and a check. Oil passages b3 and b4 connecting from the valve 40 to the first input port 60c of the switching valve 60, and oil passages b5 and b6 connecting from the first output port 60g to the input port SL1a of the linear solenoid valve SL1 are provided. ing.

  The second oil passage is provided with an oil passage c1 connected from the output port SL1b of the linear solenoid valve SL1 to the third input port 60e of the switching valve 60. The third oil passage is provided with an oil passage d <b> 1 connected from the third output port 60 i of the switching valve 60 to the hydraulic servo 4. The fourth oil passage includes oil passages f1 and f2 connected from the electromagnetic pump 20 to the second input port 60d of the switching valve 60. An oil passage f3 connected to the connection port 60f and an oil passage f4 connected to the discharge port 30c of the manual valve 30 are connected to the branch portions of the oil passages f1 and f2.

  In the fifth oil passage, the oil passages b3 and b4 are connected in order to connect the oil passages b3 and b4 between the check valve 40 and the switching valve 60 and the oil passage f2 with the switching valve 60 in the second state. An oil passage g1 that connects the branch portion and the second output port 60h is provided. The sixth oil passage includes an oil passage h <b> 1 that connects the branch portions of the oil passages b <b> 3 and b <b> 4 between the check valve 40 and the switching valve 60 and the pressure accumulation oil chamber 50 a of the accumulator 50. The sixth oil passage is not limited to the oil passage h1 that connects the branch portions of the oil passages b3 and b4 between the check valve 40 and the switching valve 60 and the pressure accumulation oil chamber 50a of the accumulator 50. An oil passage connecting the five oil passages g1 and the pressure accumulating oil chamber 50a of the accumulator 50 may be used. The seventh oil passage includes oil passages b1 and b2 between the manual valve 30 and the check valve 40 through an orifice 70 from a branch portion of the oil passages b5 and b6 between the linear solenoid valve SL1 and the switching valve 60. The oil path e1 connected to the branch part is provided.

  When the internal combustion engine is driven, the ECU 5 operates the first hydraulic pressure supply unit 10 to generate the line pressure PL, sets the switching valve 60 to the first state, and supplies the accumulator 50 with the line pressure PL (forward range pressure PD). Is now accumulating. In addition, the ECU 5 operates the electromagnetic pump 20 to generate the electromagnetic pump pressure PEMOP when the internal combustion engine is idle stopped, sets the switching valve 60 to the second state, and supplies the hydraulic servo 4 with hydraulic pressure to the accumulator 50. The electromagnetic pump pressure PEMOP is accumulated.

  Next, the operation of the hydraulic control device 2 of the automatic transmission 1 according to the present embodiment will be described in detail.

  When the internal combustion engine is driven, the ECU 5 supplies the line pressure PL from the first hydraulic pressure supply unit 10 to the input port 30a of the manual valve 30 via the oil passage a1, and the modulator pressure Pmod is supplied to the switching valve 60. The switching valve 60 is supplied to the first hydraulic oil chamber 60a and enters the first state.

  At this time, when the manual valve 30 is positioned in the D range, the forward range pressure PD is supplied from the output port 30b and is input to the input port 40a of the check valve 40 through the oil passages b1 and b2. The forward range pressure PD overcomes the spring 40s of the check valve 40, moves the sealing member 40p, and is output from the output port 40b. Further, the forward range pressure PD is supplied to the first input port 60c of the switching valve 60 through the oil passages b3 and b4, and the linear solenoid valve SL1 is supplied from the first output port 60g through the oil passages b5 and b6. It is supplied to the input port SL1a. When the first clutch C1 is engaged, the ECU 5 operates the linear solenoid valve SL1, outputs the engagement pressure from the output port SL1b, and from the third input port 60e of the switching valve 60 to the third output port 60i. Is supplied to the hydraulic servo 4. Part of the hydraulic pressure supplied to the oil passage b3 is supplied from the oil passage h1 to the pressure accumulation oil chamber 50a of the accumulator 50, and the hydraulic pressure is accumulated in the pressure accumulation oil chamber 50a against the spring 50s.

  When the manual valve 30 is switched to the N range, the forward range pressure PD output from the manual valve 30 becomes zero. At this time, since the internal combustion engine is driven, the modulator pressure Pmod is generated, and the switching valve 60 is in the first state. Here, the hydraulic pressure remaining in the hydraulic servo 4 is drained in order to release the first clutch C1 corresponding to the N range. In this case, the hydraulic pressure from the hydraulic servo 4 is input from the oil passages d1 and c1 to the discharge port 30c of the manual valve 30 through the oil passages b6, e1 and b7 via the linear solenoid valve SL1, and drained. Since the orifice 70 is provided in the oil passage e1, the speed of the drain is delayed.

  At this time, the hydraulic pressure accumulated in the accumulator 50 is released and supplied from the oil passage h1 to the oil passages b3 and b4. Since this hydraulic pressure is cut off by the check valve 40, it is supplied to the first input port 60c of the switching valve 60, and is supplied from the first output port 60g to the oil passages b5, b6, e1. Thereby, since drastic drainage of the hydraulic pressure from the hydraulic servo 4 can be suppressed, it is possible to extend the time during which the first clutch C1 can be controlled while draining.

  When the internal combustion engine is idle stopped, the mechanical oil pump 3 is stopped, so that the line pressure PL, the modulator pressure Pmod and the like are not generated, and the switching valve 60 is switched to the second state. Here, when shifting from the normal running state to the idle stop state, the signal pressure PSC2 from the solenoid valve SC2 is supplied to the second hydraulic oil chamber 60b of the switching valve 60 before the internal combustion engine is stopped. The switching valve 60 is set to the second state.

  The ECU 5 operates the electromagnetic pump 20 to generate the electromagnetic pump pressure PEMOP. The electromagnetic pump pressure PEMOP is supplied to the second input port 60d through the oil passages f1 and f2, and is supplied from the third output port 60i to the hydraulic servo 4 through the oil passage d1 to engage the first clutch C1. Can be combined.

  On the other hand, the electromagnetic pump pressure PEMOP supplied to the second input port 60d is supplied from the second output port 60h to the pressure accumulation oil chamber 50a of the accumulator 50 via the oil passages g1, b3, h1. As a result, the electromagnetic pump pressure PEMOP is accumulated in the accumulator 50. The electromagnetic pump pressure PEMOP supplied to the oil passage b3 is also supplied to the output port 40b of the check valve 40, but is blocked.

  Here, if the switching valve 60 sticks in the second state when the manual valve 30 is in the D range when the internal combustion engine is driven, the forward range pressure PD is supplied to the linear solenoid valve SL1. In other words, the hydraulic pressure is not output from the linear solenoid valve SL1, and the engagement pressure PSL1 is not supplied to the hydraulic servo 4. Further, since the electromagnetic pump 20 is not driven, the electromagnetic pump pressure PEMOP is not supplied to the hydraulic servo 4 from the second input port 60d. However, the forward range pressure PD output from the manual valve 30 is reversely input to the second output port 60h via the oil passages b1, b2, b3, g1. The forward range pressure PD is output from the third output port 60 i along the spool 60 p from the second output port 60 h and supplied to the hydraulic servo 4. At this time, a part of the hydraulic pressure supplied to the oil passage b3 is supplied from the oil passage h1 to the pressure accumulation oil chamber 50a of the accumulator 50, and the oil pressure is accumulated in the pressure accumulation oil chamber 50a against the spring 50s.

  As described above, according to the hydraulic control device 2 of the present embodiment, when the electromagnetic pump 20 is driven, the accumulator 50 communicates with the oil passages b3 and h1 where the electromagnetic pump pressure PEMOP is output from the electromagnetic pump 20. Even if there is a voltage drop when the hydraulic servo 4 is operated by the electromagnetic pump 20, a drop in the engagement pressure of the first clutch C1 can be suppressed.

  Further, according to the hydraulic control device 2 of the present embodiment, the accumulator 50 includes the accumulation of the forward range pressure PD based on the drive of the mechanical oil pump 3 and the accumulation of the electromagnetic pump pressure PEMOP based on the drive of the electromagnetic pump 20. Therefore, an increase in the number of parts can be prevented as compared with the case where each is constituted by a separate accumulator.

  Further, according to the hydraulic control device 2 of the present embodiment, for example, when the switching valve 60 switches from the second state to the first state when the internal combustion engine restarts from the idle stop time, the accumulator 50 is Since the electromagnetic pump pressure PEMOP has already been accumulated, there is no need for refilling by the mechanical oil pump 3, and it is possible to prevent the controllability of the hydraulic servo 4 from being lowered due to refilling.

  Further, in the hydraulic control device 2 of the present embodiment, the check valve 40 is disposed closer to the first hydraulic pressure supply unit 10 than the branching portion of the first oil passages b1 to b4 with the sixth oil passage h1. ing. For this reason, when accumulating the electromagnetic pump pressure PEMOP in the accumulator 50 when the electromagnetic pump 20 is driven, the electromagnetic pump pressure PEMOP is shut off by the check valve 40 in the oil passage b3, so that the hydraulic pressure that escapes from the oil passage b3 is almost all. Accumulated pressure can be effectively stored.

  Further, in the hydraulic control device 2 of the present embodiment, the electric oil pump is the electromagnetic pump 20. Therefore, the hydraulic servo 4 of the first clutch C1 can be operated efficiently and reliably, and the electromagnetic pump 20 is smaller in size than the motor-driven electric oil pump. As compared with the above, the hydraulic control device 2 can be made compact.

  In the hydraulic control device 2 of the present embodiment described above, the oil passage f2 and the oil passage g1 are shut off when the switching valve 60 is in the first state and communicated in the second state. It is not limited to. For example, if the oil passage f3 is not provided, the oil passage f2 and the oil passage g1 may be connected without using the switching valve 60. In this case, when the switching valve 60 is in the first state, the forward range pressure PD is supplied from the oil passage g1 to the oil passage f2, but by the electromagnetic pump 20 and the discharge port 30c of the manual valve 30 in the D range. Since it is a closed circuit, it can operate normally.

DESCRIPTION OF SYMBOLS 1 Automatic transmission 2 Hydraulic control apparatus 3 Mechanical oil pump 4 Hydraulic servo 10 1st hydraulic supply part 20 Electromagnetic pump (2nd hydraulic supply part, electric oil pump)
40 Check valve 50 Accumulator 50a Accumulated oil chamber 60 Switching valve a1 1st oil path b1-b6 1st oil path c1 2nd oil path d1 3rd oil path f1, f2 4th oil path g1 5th Oil path h1 Sixth oil path e1 Seventh oil path PEMOP Electromagnetic pump pressure (second hydraulic pressure)
PL line pressure (first hydraulic pressure)
PSL1 Engaging pressure SL1 Linear solenoid valve (solenoid valve)
SL1a input port SL1b output port

Claims (2)

A first hydraulic pressure supply unit capable of supplying a first hydraulic pressure based on driving of a mechanical oil pump; and a second hydraulic pressure supply unit capable of supplying a second hydraulic pressure based on driving of an electric oil pump. In the automatic transmission hydraulic control device provided,
A solenoid valve capable of supplying an engagement pressure to a hydraulic servo for engaging / disengaging an engagement element for transmitting power based on the first hydraulic pressure; and a switching valve capable of switching between a first state and a second state; The solenoid valve via the check valve capable of circulating the hydraulic pressure only in one direction, the accumulator having a pressure accumulating oil chamber capable of accumulating the hydraulic pressure, and the check valve and the switching valve from the first hydraulic pressure supply unit in order A first oil passage connected to the input port, a second oil passage connected from the output port of the solenoid valve to the switching valve, and a third oil passage connected from the switching valve to the hydraulic servo, A fourth oil passage connected from the second hydraulic pressure supply unit to the switching valve; and at least the switching valve in the second state, the check valve and the switching valve. A fifth oil passage connecting the first oil passage and the fourth oil passage between the check valve and the switching valve, or the first oil passage or the fifth oil passage between the check valve and the switching valve. A sixth oil passage connecting the oil passage and the pressure accumulating oil chamber of the accumulator,
In the first state, the switching valve communicates with the first oil passage, communicates the second oil passage with the third oil passage, and connects the fourth oil passage with the fifth oil passage. And in the second state, the first oil passage is shut off, the second oil passage is shut off, the third oil passage, the fourth oil passage, and the Communicate with the 5th oil passage,
When the first hydraulic pressure is supplied from the first hydraulic pressure supply unit, the switching valve is set to the first state, and the first hydraulic pressure is supplied to the solenoid valve via the first oil passage. The engagement pressure output from the solenoid valve is supplied to the hydraulic servo via the second oil passage and the third oil passage, and the first oil pressure is supplied to the sixth oil passage. Accumulating pressure on the accumulator via the road,
When the first hydraulic pressure is not supplied from the first hydraulic pressure supply unit and the second hydraulic pressure is supplied from the second hydraulic pressure supply unit, the switching valve is set to the second state and the second hydraulic pressure is supplied. 2 is supplied to the hydraulic servo via the fourth oil passage and the third oil passage, and the second oil pressure is supplied to the fourth oil passage, the fifth oil passage, and the second oil passage. Pressure is accumulated in the accumulator through one oil passage and the sixth oil passage;
A hydraulic control device for an automatic transmission. The electric oil pump is an electromagnetic pump.
The hydraulic control device for an automatic transmission according to claim 1.

Images