WO2007144962A1

WO2007144962A1 - Hydraulic control device for automatic transmission

Info

Publication number: WO2007144962A1
Application number: PCT/JP2006/312174
Authority: WO
Inventors: Nobuhiro Sato; Takuya Fujimine; Kazuyuki Noda; Minoru Todo; Kazuhisa Ozaki; Kazutoshi Nozaki; Masafumi Kinoshita; Atsushi Honda; Akiharu Abe
Original assignee: Aisin Aw Co., Ltd.; Toyota Jidosha Kabushiki Kaisha
Priority date: 2006-06-16
Filing date: 2006-06-16
Publication date: 2007-12-21
Also published as: CN101233347A; CN101233347B; DE112006002125T5

Abstract

A hydraulic control device (11) for an automatic transmission has a linear solenoid valve (SLT) for outputting a control pressure, a primary regulator valve (7) for regulating a line pressure (PL) according to the control pressure, and a secondary regulator valve (8) for regulating a secondary pressure (PSEC) according to the control pressure (PSLT). The secondary pressure (PSEC) is supplied to both a lock-up clutch (3) and a torque converter (2). A spool (8p) of the secondary regulator valve (8) is formed to have a large-diameter section (8pA) and a small-diameter section (8pB). The hydraulic control device is constructed so that, without installation of parts including a sleeve, the line pressure (PL) can be inputted in an oil chamber (8c) formed between the large-diameter section (8pA) and the small-diameter section (8pB). Although the gain of the secondary regulator valve (8) can be set greater than 1, the hydraulic control device (11) has a simple structure and compact size.

Description

Specification

Hydraulic control device for automatic transmission

Technical field

[0001] The present invention relates to a hydraulic control device for an automatic transmission mounted on, for example, a vehicle or the like, and more specifically, an automatic transmission that supplies a secondary pressure of a second pressure regulating valve force to a torque converter and a lockup clutch. The present invention relates to a hydraulic control device for a transmission.

Background art

[0002] Generally, for example, an automatic transmission mounted on a vehicle or the like is provided with a fluid transmission device for fluid transmission of an engine output to an input shaft of a transmission mechanism, that is, the fluid transmission device includes: A torque converter is provided that can allow a difference in rotational speed between the output shaft (crankshaft) of the engine and the input shaft of the transmission mechanism. In recent years, in such a fluid transmission device for an automatic transmission, a lock-up clutch capable of directly connecting (locking up) an engine output shaft and a transmission mechanism input shaft in order to improve fuel efficiency. Those equipped with are becoming mainstream.

By the way, the automatic transmission is provided with a clutch brake for forming a power transmission path of the transmission gear mechanism, and a hydraulic control device for controlling engagement / disengagement of the clutch and the brake. It has been. This hydraulic control device is provided with a solenoid valve that outputs a control pressure in accordance with the throttle opening, and a primary regulator valve that is controlled based on the control pressure. The pressure is regulated and the line pressure is supplied to the clutch and brake hydraulic servos. On the other hand, the torque converter and the lock-up clutch described above have a secondary pressure that is reduced by a secondary regulator valve that is similarly controlled based on the control pressure in order to improve the durability of the torque comparator. Is generated, and the secondary pressure is supplied.

[0004] However, if the required amount of transmission torque capacity of the lock-up clutch is large, for example, when the engine output is large, the secondary pressure needs to be increased, that is, the line pressure is increased unnecessarily. Will cause adverse effects on fuel efficiency, etc. There is a fear. Therefore, the control pressure of the above solenoid valve force is simultaneously input to the two oil chambers of the secondary regulator valve, thereby increasing the gain of the secondary regulator valve and preventing unnecessary increase in line pressure. What has been proposed has been proposed (for example, see Japanese Laid-Open Patent Publication No. 2003-42287).

Here, an example of a conventional hydraulic control device for an automatic transmission will be briefly described. FIG. 4 is a diagram showing an example of a conventional hydraulic control device for an automatic transmission.

[0006] The automatic transmission includes a fluid transmission device 4 having a torque converter 2 and a lock-up clutch 3. As shown in FIG. 4, a hydraulic control device 50 of the automatic transmission includes a strainer 5, an oil pump 6 , Linear solenoid valve SLT, Solenoid valve SI, Primary regulator valve 7, Secondary regulator valve 58, Lockup relay valve 59, Lockup control valve 10, Check valve 12, Orifice 19, Oil cooler 30, Lubricating oil passage (LUBE) 31 is provided.

[0007] For example, when the oil pump 6 is driven by a driving force of an engine (not shown), the oil is sucked from the oil pan (not shown) via the strainer 5 and then the primary regulator via the oil passage al. Hydraulic pressure is supplied to the valve 7. The linear solenoid valve SLT receives a modulator pressure P from a not shown modulator valve and based on the throttle opening.

MOD

Outputs the control pressure P from the output port SLTb to the oil passages cl, c2, c3, c4. And the above

SLT

The primary regulator valve 7 has a spool position that depends on the urging force of the spring 7s and the control pressure P input to the oil chamber 7a via the oil passage c2 and the feedback pressure input to the oil chamber 7b.

SLT

By adjusting the position, the oil pressure in the oil passages al, a2, a3, and a4 is adjusted to the line pressure P corresponding to the throttle opening while adjusting the oil pressure that is returned to the oil pump 6 through the oil passage dl. .

L

[0008] On the other hand, in the secondary regulator valve 58, the valve hole 22 formed in the valve body 20 includes a spool 58p, a spring 58s, a plunger 58j, and a lid portion 58g having a sleeve portion 58i in the arrow X direction. The lid portion 58g is fixed to the valve body 20 with a key 58h, thereby forming a first oil chamber 58a, a second oil chamber 58b, and a third oil chamber 58c. . In addition, the land 58pl and the plunger 58j of the spool 58p are formed with an outer diameter D3, and the land 58pl, the land 58pl, and the land 58pl are formed with an outer diameter D4.

2 3 4

Has been. [0009] When the lock-up clutch 3 is released, the solenoid valve SI is controlled so as not to output the signal pressure P, thereby causing the spool 59p of the lock-up relay valve 59 to

S1

In the state shown in the left half of the figure, the control pressure P supplied from the linear solenoid valve SLT via the oil passage c4 is cut off by the lockup relay valve 59. This

SLT

The secondary regulator valve 58 has a control pressure P via the oil passage c3 to the first oil chamber 58a.

SLT

Then, only the feedback pressure is input to the second oil chamber 58b.

[0010] The secondary regulator valve 58 is based on the biasing force of the spring 58s, the control pressure P input to the first oil chamber 58a, and the feedback pressure input to the second oil chamber 58b.

SLT

By adjusting the position of the spool 58p, the oil passage bl, b2, b3, b4, b5, connected to the port 58f is adjusted while adjusting the hydraulic pressure returned to the oil pump 6 from the port 58d via the oil passage d2. Secondary pressure P where b6's hydraulic pressure is greatly reduced from line pressure P according to throttle opening

L SEC

Adjust pressure.

[0011] It should be noted that the secondary pressure in this state is a state in which the pressure is adjusted to a lower pressure than the engagement state of the lock-up clutch 3 described later, and thus is set to the low secondary pressure PLo. Also, receive the outer diameter D3.

SEC

The pressure area is A3 (i.e., D3 ² π / 4), and the spring 58s biasing force is F.

SP

The pressure P Lo is expressed by the following formula: A3 · P Lo = A3 -P + F and P Lo = P + F

SEC SEC SLT SP SEC SLT

Since it is ZA3, the gain (control pressure P to the secondary regulator valve 58)

SP SLT

The input / output ratio of secondary pressure P to 1) is 1.

SEC

[0012] This low secondary pressure P Lo is supplied from the oil passage b5 through the lock-up relay valve 59.

SEC

Supplied to converter 2. In this way, the line pressure P is greatly increased in the torque converter 2.

Shi

Low secondary pressure P Lo is supplied, so high pressure is not applied and durability is improved.

SEC

Is planned. The low secondary pressure P Lo is adjusted according to the throttle opening.

SEC

Even if the engine output increases according to the throttle opening, the torque transmission capacity of the torque converter 2 also increases, so that torque transmission is performed normally.

[0013] On the other hand, when the lockup clutch 3 is engaged, the solenoid valve S1 is controlled to output the signal pressure P, and thereby the spool 59p of the lockup relay valve 59 is output.

SI

Is shown in the right half position in the figure. Then, the port 591 and the port 59m of the lockup relay valve 59 communicate with each other and are supplied from the linear solenoid valve SLT through the oil passage c4. The control pressure P enters the third oil chamber 58c of the secondary regulator valve 58 via the oil passage tl.

SLT

It is powered. As a result, the secondary regulator valve 58 receives the control pressure P in the first oil chamber 58a, the feedback pressure in the second oil chamber 58b, and the control pressure P in the third oil chamber 58c.

SLT SLT

The

[0014] The control pressure P input to the third oil chamber 58c includes a plunger 58j having an outer diameter D3 and an outer diameter D4.

SLT

Press the spool 58p in the direction of the arrow X in accordance with the difference in pressure receiving area with the land 58pl

Four

Acts like As a result, the oil pressure to be reduced to the oil pump 6 is reduced from the port 58d through the oil passage d2, and the oil pressure in the oil passages bl, b2, b3, b4, b5, b6 connected to the port 58f is adjusted according to the throttle opening. Secondary pressure higher than the low secondary pressure P Lo (hereinafter referred to as “high

SEC

Adjust pressure to P Hi.

SEC

[0015] The pressure receiving area of the outer diameter D3 is A3 (ie, ϋ3 ² π Ζ4), the pressure receiving area of the outer diameter D4 is A4 (ie, D4 ² π / 4), and the biasing force of the spring 58s is F. Pressure P Hi

SP SEC

A3 -P Hi = A3 -P + (A4-A3) · Ρ + F, P Hi = A4 / A

SEC SLT SLT SP SEC

3 · Ρ + F ZA3, so the gain as the secondary regulator valve 58 (input

SLT SP

The output ratio is Α4ΖΑ3 (Α4> Α3), that is, greater than 1.

[0016] This high secondary pressure P Hi is applied to the lockup control valve 10 and the opening from the oil passage b6.

SEC

Supplied to the lockup clutch 3 via the backup relay valve 59. The high secondary pressure P Hi supplied from the oil passage b5 is reduced by the orifice 19 and the check valve 12.

SEC

After being pressed, the torque converter 2 is supplied. For this reason, the lockup clutch 3 is engaged by the differential pressure between the supply pressure of the lockup clutch 3 and the supply pressure of the torque converter 2.

In this way, by making the gain of the secondary regulator valve 58 larger than 1, the secondary pressure P can be made higher than the input control pressure P, and the linear solenoid

SLT SEC

Without increasing the control pressure P of the id valve SLT unnecessarily, that is, increasing the line pressure P unnecessarily.

SLT

Therefore, the lockup clutch 3 can secure the necessary transmission torque capacity and improve fuel efficiency.

Disclosure of the invention

[0018] However, in the case where the control pressure is input to the two oil chambers 58a and 58c of the secondary regulator valve 58 described above, the control pressure P input to the third oil chamber 58c is particularly effective.

SLT Therefore, in order to increase the gain, it is necessary to form the land portion 58pl located at the intermediate portion of the spool 58p with a larger diameter than the plunger 58j (that is, D4> D3).

Four

[0019] In addition, when the land portion 58pl of the spool 58p is formed to have the same diameter as the land portion 58pl, a particularly low

14

Gandari pressure P Lo gain decreases (P Lo = A3 / A4-P + F ZA4)

SEC SEC SLT SP

When the throttle opening increases, the torque transmission capacity of the torque converter 2 may be insufficient compared to the increase in engine output.

[0020] In general, each valve of a hydraulic control device is configured as a valve by forming a valve hole in a plate-like valve body, and sealing the spool with a lid-like member after inserting the spool. If the land 58pl located in the middle part of the spool 58p as described above has a large diameter, the portion of the spool 58p that is inserted and the part located on the rear end side (in the insertion direction)

Four

Since a gap is generated between the lube hole 22, it is necessary to provide a member such as the sleeve 58i as described above.

[0021] Further, for example, when the sleeve 58i is provided between the valve hole 22 and the spool 58p, the axial center of the valve hole 22 and the axial center of the sleeve 58p are not necessarily concentric. If the spool 58p is simply extended as it is, problems such as an increase in contact resistance between the spool 58p and the sleeve 58p and a gap may occur due to eccentricity. Therefore, it is necessary to provide a plunger 5¾ that slides concentrically with respect to the sleeve 58i, and to press the sleeve 58p through the plunger 5¾.

[0022] Thus, in order to increase the gain at the time of high secondary pressure output of the secondary regulator valve to be larger than 1, the number of parts is increased by providing a sleeve and a plunger, the manufacturing process is increased, and the cost is reduced. This causes problems such as hindrance to the secondary leg and the enlargement of the secondary leg and the torque associated with the increase in the spool diameter (i.e., the land part 58pl).

Four

There has been a problem that the compactness of the hydraulic control device of the dynamic transmission is hindered.

Therefore, the present invention provides a hydraulic control device for an automatic transmission that has a simple configuration and can be made compact while allowing the gain of the second pressure regulating valve to be larger than 1. Is intended to provide.

[0024] The present invention (see, for example, FIGS. 1 to 3) outputs a control pressure (P) according to the throttle opening. A control valve (SLT) for controlling and a first pressure regulating the line pressure (P) according to the control pressure (P).

SLT

A pressure control valve (7) and a second pressure lower than the line pressure (P) according to the control pressure (P)

SLT

A second pressure regulating valve (8) for regulating the re-pressure (P), and the secondary pressure (P)

SEC SEC

In a hydraulic control device (1) for an automatic transmission that supplies a fluid transmission (4) having a knock-up clutch (3) and a torque converter (2),

The second pressure regulating valve (8)

It is formed in a shaft shape and has a large-diameter land (8pl, 8pl) on one side in the axial direction (for example, the arrow Y direction)

, 8pl) and the large diameter part (8ρΑ) formed on the other side in the axial direction (for example, the arrow X direction side)

twenty three

Small-diameter part (8ρΒ) with a smaller-diameter land part (8pl) than the diameter land part (8pl, 8pl, 8pl)

1 2 3 4

), And a spool (8ρ) with

A pressure adjusting section (8d, 8e, 8f) that adjusts the secondary pressure (Ρ) to increase in response to the spool (8ρ) moving to one side in the axial direction (for example, the direction of the arrow Υ);

SEC

From the end of the spool (8p) on the other axial side (for example, the direction of the arrow X), the control pressure (P

S

) Act the first oil chamber (8a),

T

A second oil chamber (8b) for applying a feedback pressure of the secondary pressure (P) from an end on one axial side of the spool (8p) (for example, in the direction of arrow Y);

SEC

A third oil chamber (8c) formed between the large diameter portion (8pA) and the small diameter portion (8pB),

The third oil chamber (8c) has a gay of the second pressure regulating valve (8) with respect to the control pressure (P).

SLT

Gain increasing pressure input means (for example, el, e3, or S2, a2, a5, si, 13) is provided.

[0025] This makes it possible to make the gain of the second pressure regulating nozzle larger than 1, but it is not necessary to provide a sleeve or a plunger. A pressure regulating valve can be configured, and the number of parts can be reduced, the manufacturing process can be simplified, and compaction can be achieved.

In addition, the present invention (see, for example, FIGS. 1 to 3) is a first solenoid that can output a first signal pressure (P 1).

S1

The noid valve (S1),

Based on the first signal pressure (P) of the first solenoid valve (S1), the lockup clutch The secondary pressure (P) is output to the hose (3) and the secondary pressure (P) is shut off.

SEC SEC

A first switching valve (9) for switching between states.

[0027] Thereby, the engagement / disengagement of the lockup clutch can be controlled by controlling the first solenoid valve.

More specifically (see, for example, FIGS. 1 and 2), the first solenoid valve (S1) inputs the line pressure (P) as a source pressure of the first signal pressure (P). And the first signal pressure (P

SI L

) Output the line pressure (P) as it is as the first signal pressure (P).

SI L S1 The gain increasing pressure input means is a first signal pressure (P) of the first solenoid valve (S1).

The first oil passage (el, e3) inputs S1 into the third oil chamber (8c).

[0029] Thereby, the line pressure can be supplied as a pressure at which the gain of the second pressure regulating nozzle is greater than 1. In addition, since the first signal pressure of the first solenoid valve makes the gain of the second pressure regulating valve greater than 1, the gain of the second pressure regulating valve is greater than 1 in conjunction with the engagement of the lockup clutch. Can be controlled.

[0030] More specifically (see, for example, FIG. 3), the gain increase pressure input means includes:

A second solenoid valve (S2) capable of outputting a second signal pressure (P),

S2

A second oil passage (a2, a5, si) for conducting the line pressure (P) to the third oil chamber (8c);

Shi

The second oil passage (a2, a5, si) is interposed in the second oil passage (a) based on the second signal pressure (P).

S2

2, a5, si) and a second switching valve (13) for switching between a state in which the second oil passage (a2, a5, si) is shut off,

Consists of.

Thereby, the line pressure can be supplied as a pressure at which the gain of the second pressure regulating nozzle is greater than 1. Also, since the gain of the second pressure regulating valve is made larger than 1 by the second signal pressure of the second solenoid valve, the gain of the second pressure regulating valve is greater than 1 regardless of the engagement operation of the lockup clutch. Can be controlled to be larger.

[0032] It should be noted that the reference numerals in Katsuko are for comparison with the drawings. This is for convenience to facilitate understanding of the invention and has no effect on the structure of the claims. It does not affect. Brief Description of Drawings

FIG. 1 is a diagram showing a hydraulic control device for an automatic transmission according to a first embodiment.

FIG. 2 is a diagram showing the relationship between the SLT pressure, the line pressure, and the secondary pressure in the hydraulic control device for an automatic transmission according to the present invention.

FIG. 3 is a diagram showing a hydraulic control device for an automatic transmission according to a second embodiment.

FIG. 4 is a diagram showing an example of a conventional hydraulic control device for an automatic transmission.

BEST MODE FOR CARRYING OUT THE INVENTION

[0034] <First embodiment>

A first embodiment according to the present invention will be described below with reference to the drawings. FIG. 1 is a diagram showing a hydraulic control device for an automatic transmission according to a first embodiment.

[0035] For example, an automatic transmission (generally omitted) mounted on a vehicle or the like includes an input shaft that can be connected to an engine crankshaft, and a fluid transmission device that can fluidly transmit rotation (driving force) of the input shaft. 4 and a speed change mechanism that changes the speed of rotation input through the fluid transmission device 4 by a gear mechanism or a friction engagement element (clutch or brake) and transmits it to the output shaft. The hydraulic control device 1 of the automatic transmission according to the present invention is configured to hydraulically control the engagement state of the friction engagement element and the fluid transmission device.

[0036] As shown in Fig. 1, the fluid transmission device 4 is rotated by receiving a flow of oil from the pump impeller 2a that inputs rotation of the input shaft and the pump impeller 2a (fluid transmission) ) It is equipped with a turbine runner 2b and a torque converter 2 having a stator 2c that rectifies the oil returning from the turbine runner 2b to the pump impeller 2a and produces a torque increasing effect. A lockup clutch 3 is provided to directly connect the shaft and the turbine runner 2b. The stator 2c is fixed by the one-way clutch F in a state where the rotation of the turbine runner 2b is lower than the rotation of the pump impeller 3a, and receives a reaction force against the oil flow to produce a torque increasing effect. If the rotation of the turbine runner 2b is exceeded, the engine runs idle and the oil flow does not act in the negative direction.

[0037] Next, the hydraulic control device 1 for an automatic transmission according to the present invention will be described. As shown in Fig. 1, the hydraulic control device 1 of the automatic transmission consists of a strainer 5, an oil pump 6, a linear Solenoid valve (control valve) SLT, primary regulator valve (first pressure regulating valve) 7, secondary regulator valve (second pressure regulating valve) 8, solenoid valve (first solenoid valve) Sl, lock-up relay The valve (first switching valve) 9, lockup control valve 10, check valve 12, orifice 19, oil cooler 30, lubricating oil passage (LUBE) 31, etc.

In addition to the parts shown in FIG. 1, the automatic transmission hydraulic control device 1 includes various valves and oil passages for supplying hydraulic pressure to the hydraulic servos of the clutches and brakes of the transmission mechanism. However, for convenience of explanation, the explanation is omitted except for the main part of the present invention.

[0039] As shown in FIG. 1, the hydraulic control device 1 of the automatic transmission includes an oil pump 6 that is driven in conjunction with the rotation of the engine, and an oil pan (not shown) is driven by the oil pump 6. The oil pressure is generated by sucking the oil through the strainer 5. The hydraulic pressure generated by the oil pump 6 is output from the output port 6a to the oil passages al, a2, a3, and a4, and is adjusted by a primary regulator valve 7 described later in detail.

[0040] The linear solenoid valve SLT has a linear drive section 11A and a pressure regulating valve section 11B. The linear drive unit 11A is provided with a plunger ΙΑ ΙΑρ whose position is electronically controlled (linear drive) in accordance with the throttle opening based on a signal from an electronic control device (not shown). The valve section 11B includes a spool Ι ΙΒρ, a spring 1 IBs that urges the spool Ι ΙΒρ toward the plunger 1 ΙΑρ side (upper side in the figure), and a modulator pressure P force S

MOD

An input port SLTa for input and an output port SLTb are provided.

For example, when an accelerator pedal in a driver's seat (not shown) is depressed and the throttle opening is increased, the plunger Ι ΙΑρ is moved and driven downward in the figure by electronic control in accordance with the throttle opening. If the spool 上記 ΙΒρ force is moved downward in the figure against the urging force of the spring 1 ΙΒρ by the pressing drive of the plunger 11 Ap, the communication state between the input port SLTa and the output port SLTb is changed to the spool. 1 Open with the travel of ΙΒρ !, te! /, And so the output port SLTb force is also controlled by the control pressure P force S in proportion to the throttle opening.

SLT

Is output.

The primary regulator valve 7 includes a spool 7p and a spring 7s that biases the spool 7p downward, and an oil chamber 7a and a spool 7p above the spool 7p. An oil chamber 7b, a pressure regulating port 7c, a discharge port 7d, and an output port 7e are provided below the bottom. The control pressure P is input to the oil chamber 7a through the oil passages cl and c2 from the linear solenoid valve SLT, and the line pressure P, which will be described in detail later, is supplied to the oil chamber 7b. The

SLT

And input as feedback pressure.

[0043] The urging force of the spring 7s and the control pressure P act on the spool 7p of the primary regulator valve 7 in opposition to the feedback pressure. That is, the position of the spool 7p is

SLT

It is mainly controlled by the magnitude of the control pressure P. The spool 7p is in the upper side in the figure

SLT

If the pressure adjustment port 7c and the discharge port 7d are in communication with each other, and the spool 7p is controlled to move to the lower side in the figure, the communication amount between the pressure adjustment port 7c and the discharge port 7d ( (Aperture amount) is reduced (blocked). In other words, it depends on the magnitude of the control pressure P input to the oil chamber 7a.

SLT

Therefore, the spool 7p is controlled to move downward, and the hydraulic pressure discharged from the discharge port 7d is adjusted to adjust the hydraulic pressure in the pressure adjustment port 7c. The hydraulic pressures a2, a3, and a4 are adjusted as the line pressure P corresponding to the throttle opening.

Shi

[0044] The hydraulic pressure discharged from the discharge port 7d is returned to the port 6b of the oil pump 6 and becomes the original pressure of the oil pump 6. As a result, the oil pump 6 reduces the necessary driving force, It is possible to prevent wasteful energy consumption and contribute to improving the fuel consumption of a vehicle equipped with the hydraulic control device 1 for the automatic transmission.

[0045] The line pressure P is also supplied to the modulator valve via an oil passage (not shown).

Shi

If the line pressure P is below a predetermined pressure, the modulator valve

Shi

When the hydraulic pressure is output as the modulator pressure P and the line pressure P exceeds a predetermined pressure,

MOD L

The oil pressure adjusted to a constant pressure is output as the modulator pressure P.

MOD

[0046] In the secondary regulator valve 8, after inserting the spring 8s and the spool 8p into the hole portion 21 formed in the valve body 20 in the direction of the arrow Y, the lid member 8g is inserted, and the lid member 8g Is fixed by a key member 8h, whereby the spool 8p is urged upward by a spring 8s, an oil chamber 8a is provided below the spool 8p, and an upper portion of the spool 8p. The oil chamber 8b, an oil chamber 8c, which will be described in detail later, a pressure adjusting port (pressure adjusting portion) 8f, a discharge port (pressure adjusting portion) 8d, and an output port (pressure adjusting portion) 8e are formed. It has been done. [0047] The spool 8p is formed in an axial shape with respect to the arrow X—Y direction, and has a large-diameter portion 8ρΑ formed with three land portions 8pl, 8pl, 8pl having an outer diameter D1, and an outer diameter. Smaller diameter than D1

one two Three

And a small-diameter portion 8ρΒ formed with a land portion 8pl having an outer diameter D2. Also this big

Four

An oil chamber 8c is formed between the diameter portion 8ρΑ and the small diameter portion 8ρΑ. Thus, the oil chamber 8 b is pressure-receiving area Dl ^2/4 based on the outer diameter D1 '[pi (hereinafter, referred to as "pressure receiving area Al") the pressure receiving area D2 ^2/4 is the oil chamber 8a based on the outer diameter D2 'π (hereinafter referred to as “pressure-receiving area Α2”), the oil chamber 8c has a pressure-receiving area (Dl ² — D2 ² ) / 4' π (hereinafter referred to as the pressure difference between the outer diameter D1 and the outer diameter D2). “Pressure-receiving area Al—Α2”). The control pressure P is input to the oil chamber 8a through the oil passages cl and c3 from the linear solenoid valve SLT described above.

SLT

The oil chamber 8b is also input as a secondary pressure P force idback pressure described later in detail.

SEC

Furthermore, the line pressure P is input to the oil chamber 8c when the lockup clutch 3 is engaged from a solenoid valve S1 described later.

L

[0048] When the position of the spool 8p of the secondary regulator valve 8 is in the lower side in the figure, the pressure regulating port 8f and the discharge port 8d communicate with each other, and the spool 8p is in the upper side in the figure. When the movement is controlled to the side state, the communication amount (throttle amount) between the pressure adjusting port 8f and the discharge port 8d is reduced (blocked). In other words, depending on the magnitude of the control pressure P input to the oil chamber 8a,

SLT

The movement of the pool 8p is controlled, and the hydraulic pressure discharged from the discharge port 8d is adjusted, so that the oil pressure S of the pressure adjustment port 8f is adjusted and the oil passages bl, b2, b3, b4, The oil pressures b5 and b6 are adjusted as the secondary pressure P corresponding to the throttle opening.

SEC

[0049] Since the hydraulic pressure discharged from the discharge port 8d is returned to the port 6b of the oil pump 6 in the same way as the hydraulic pressure discharged from the primary regulator valve 7 described above, it becomes the original pressure of the oil pump 6. As a result, the oil pump 6 reduces the required driving force, preventing wasteful energy consumption and contributing to improved fuel consumption of vehicles equipped with the hydraulic control device 1 for automatic transmissions. It becomes possible to do.

[0050] The solenoid valve S1 (for example, normally closed) has an input port Sla and an output port Sib, and the line pressure P adjusted by the primary regulator valve 7 described above is supplied to the input port Sla as oil. Input via route a4. The solenoid valve S1 is OFF

Shi

In the state (non-energized state), the input port Sla and the output port Sib are shut off, not shown The input port Sla communicates with the output port Sib based on the signal of the electronic control device power of the input port Sla and the output port Sib. The line pressure P input to the input port Sla from the output port Sib is changed to the signal pressure ( The first signal pressure (P) is output as it is. Output port Sib

L SI

The signal pressure P (line pressure P) output from the

SI L

In addition to being input to the oil chamber 9a of the relay valve 9, it is supplied to the oil chamber 8c of the secondary regulator valve 8 described above via oil paths (gain increasing pressure input means, first oil path) el, e3.

[0051] The solenoid valve S1 is a force that explains the so-called normally closed type in which the input port Sla and the output port Sib are cut off when the power is not supplied. Conversely, the input port Sla and the output port Sib are connected when the power is not supplied. In this case, it is energized without the signal pressure P being output.

S1

[0052] The lockup relay valve 9 includes a spool 9p and a spool 9s that urges the spool 9p upward, and an oil chamber 9a, a port 9c, and a port 9d above the spool 9p. A port 9e, a port 9f, a port 9g, a port 9h, a port 9i, a port 9j, and a port 9k.

[0053] The oil chamber 9a is connected to the output port Sla of the solenoid valve SI via the oil passages el and e2, and when the signal pressure P (line pressure P) is output from the solenoid valve S1.

SI L

The signal pressure P is input. That is, the lock-up relay valve 9 is the solenoid valve.

S1

When no signal pressure p is output from si, the position shown in the left half of the figure (hereinafter referred to as ``

S1

In the state where the signal pressure p is output from the solenoid valve si

S1

The position indicated by the right half in the figure (hereinafter referred to as the “right half position”).

[0054] When the spool 9p of the lockup relay valve 9 is in the left half position, the port 9g and the port 9h, the port 9f and the port 9e, the port 9j and the drain port EX are in communication with each other, and the spool 9p In the right half position, port 9i and port 9c, port 9d and port 9e, port 9f and drain port EX, port 9g and port 9j, and port 9k and port 9h are in communication.

[0055] When the solenoid valve S1 is in the OFF state, no hydraulic pressure is input to the oil chamber 9a, and the spool 9p is in the left half position based on the urging force of the spring 9s. Then, the secondary pressure P input to the port 9g through the oil passage b5 is output from the port 9h, and then through the oil passage fl. The pressure is supplied to the input port 4 a of the fluid transmission device 4, that is, the secondary pressure P is supplied into the torque converter 2. Oil supplied into the torque converter 2 is discharged from the discharge port 4b.

SEC

The oil is discharged, input to the port 9f of the lockup relay valve 9 through the oil passage il, further output from the port 9e, and input to the oil cooler (COOLER) 30. The oil input to the oil cooler 30 is cooled by the oil cooler 30 and then discharged to an oil pan (not shown) and again sucked into the oil pump 6 through the strainer 5.

[0056] When the solenoid valve S1 is ON, the signal pressure P is applied to the oil chamber 9a.

S1 is applied, and the spool 9p is in the right half position against the biasing force of the spring 9s. Then, the secondary pressure P input to the port 9g via the oil passage b 5 is output from the port ¾ and

SEC

Supplied to chair 19, oilway gl, g2, g3, g4.

[0057] The oil passage g4 is connected to a check valve 12 having a plunger 12p and a spring 12s for urging the plunger 12p upward, and when the secondary pressure P becomes equal to or higher than a predetermined pressure, the oil passage g4

SEC

The plunger 12p is pushed downward by overcoming the urging force of the pulling 12s, and the drain port EX of the check valve 12 is opened and drained), so the secondary in the oil passages gl, g2, g3, g4 The pressure P is reduced to a predetermined pressure. In other words, this reduced secondary pressure

SEC

P is input to the port 9k and the oil of the lockup control valve 10 described later.

SEC

Input to chamber 10a.

[0058] The reduced secondary pressure P input to the port 9k is the same as described above from the port 9h.

SEC

It is supplied into the torque converter 2 through the oil passage fl. The oil discharged from the discharge port 4b and input to the port 9f of the lockup relay valve 9 through the oil passage il is drained from the drain port EX of the lockup relay valve 9 as it is.

[0059] On the other hand, the lockup control valve 10 includes a spool 10p and a spring 10s that urges the spool 10p downward (via the plunger), and an oil chamber 10a below the spool, Above the spool 10p, there are provided an oil chamber 10b, an oil chamber 10c formed by a difference in the diameter of the land portion of the spool 10p (a difference in pressure receiving area), a port 10d, and a port 10e.

[0060] In the oil chamber 10a, as described above, when the lock-up relay valve 9 is in the right half position, The secondary pressure P reduced to a predetermined pressure by the pressure valve 12 is input, and the oil chamber 10c

SEC

Control pressure P force S based on electronic control from linear solenoid valve SLU (not shown)

SLU

Entered. In addition, a lockup engagement pressure described later output from the port 10e is input to the oil chamber 10b as a feedback pressure via the oil passages hl and h2.

[0061] The spool ΙΟρ of the lock-up control valve 10 is obtained when the secondary pressure P is reduced to the oil chamber 10a and the control pressure P is gradually input to the oil chamber 10c.

SEC SLU

As a result, the spool 10p is controlled to move upward (from the right half position to the left half position in the figure) against the urging force of the spring 10s and the feedback pressure. Then, as the spool 10p moves upward, the port 10d and the port 10e gradually communicate with each other (the amount of restriction decreases), and the secondary pressure P input to the port 10d through the oil passage b6 gradually increases. To rise

SEC

Is output to oil passages hi, h2, and h3 from port 10e. Further, when the control pressure P becomes a predetermined pressure or higher, the port 10d and the port 10 of the lockup control valve 10

SLU

10e is almost completely connected, and the secondary pressure P is directly output to the oil passages hi, h2, h3.

SEC

It is powered.

[0062] The secondary pressure P output to the oil passage h3 is a lock in which the spool 9p is in the right half position.

SEC

Input to port 9i of up-relay valve 9 and input to port 4c of fluid transmission device 4 from port 9c via oil passage jl. The pressure is input to the port 4c from the reduced secondary pressure P supplied to the torque converter 2 (that is, from the hydraulic pressure of the input port 4a).

SEC

When the hydraulic pressure increases, the friction plate 3a of the lock-up clutch 3 is pressed to the right side in the figure, whereby the lock-up clutch 3 is engaged.

[0063] After that, when the solenoid valve S1 is turned OFF and the spool 9p of the lockup relay valve 9 is moved to the left half position by the bias of the spring 9s, the port 9c and the drain port EX communicate with each other, and the oil passage The hydraulic pressure of the lockup clutch 3 is drained through jl and port 4c. Also, the secondary pressure P force input to the oil chamber 10a via the oil passage g2

SEC

When the oil passage g2 is drained through the port ¾ and connected to the drain port EX, the spool 10p of the lockup control valve 10 is placed in the right half position, and the port 10e and the drain port are blocked. EX communicates with the oil pressure in the oil passages hi, h2, and h3. [0064] Next, the secondary pressure P, which is the main part of the present invention, will be explained.

SEC

Light up. In the hydraulic control apparatus 1 for an automatic transmission according to the first embodiment of the present invention, the oil that connects the output port Sib of the solenoid valve S1 and the oil chamber 8c of the secondary regulator valve 8 as described above. Road el, e3 is provided. As described above, when the solenoid valve S1 outputs the signal pressure P (line pressure P), the lockup relay valve 9

SI L

Switch from half position to left half position and supply secondary pressure P force to clutch 3

SEC

If the solenoid valve S1 does not output the signal pressure P, the lockup clutch 3

S1

The supply of the secondary pressure P is cut off. That is, the oil chamber 8c of the secondary regulator valve 8

SEC

The line pressure P is input while the lockup clutch 3 is engaged, and the lockup clutch 3

Shi

Hydraulic pressure is not input when latch 3 is released.

[0065] When the signal pressure P (line pressure P) is not output from the solenoid valve S1, the second

SI L

Dariregulator valve 8 oil chamber 8a has control pressure P from linear solenoid valve SLT.

s is input, and the feedback pressure of the secondary pressure P is input to the oil chamber 8b. this

LT SEC

In this state, the secondary pressure P that is regulated at the pressure regulating port 8f of the secondary regulator valve 8 is controlled in the range of the relatively lower position of the spool 8p.

SEC

The amount of restriction between 8d and the pressure regulating port 8f is small (the amount of communication is large), resulting in a low pressure secondary pressure (hereinafter referred to as “low secondary pressure”) P Lo.

SEC

[0066] Here, the urging force of the spring 8s is F, and this low secondary pressure P Lo is expressed by a mathematical expression.

SP SEC

Α1 · Ρ Lo = A2-P + F and P Lo = A2 / Al -P + F ZAl

SEC SLT SP SEC SLT SP

Therefore, the gain (input / output ratio) as the secondary regulator valve 8 is A2ZA1 (A1> A2), that is, the gain is smaller than 1 (see FIG. 2).

[0067] On the other hand, when the signal pressure P (line pressure P) is output from the solenoid valve S1,

SI L

s is input and the feedback pressure of the secondary pressure P is input to the oil chamber 8b

LT SEC

In this state, the line pressure P is input to the oil chamber 8c. In this state, the secondary leg

Shi

The secondary pressure P to be adjusted to the pressure adjustment port 8f of

SEC

Since it is controlled in the range of the upper position, the amount of throttle between the discharge port 8d and the pressure adjustment port 8f is large (the amount of communication is small), and the high pressure secondary pressure (hereinafter referred to as “high secondary pressure”) P

SEC Hi.

[0068] Similarly, the biasing force of the spring 8s is F, and this high secondary pressure P Hi is expressed by a mathematical expression.

SP SEC

Α1 · Ρ Ηί = Α2 · Ρ + (Α1 -Α2) · Ρ + F and Ρ Ηί = Α2 / Α1 · Ρ

SEC SLT L SP SEC SLT

+ (Α1 -Α2) / Α1 · Ρ + F ZA1, where P = α · は is a coefficient), P

L SP L SLT SE

Hi = {A2 + a (Α1 -Α2)} / Α1 · Ρ + F / Al

The gain (input / output ratio) of the C SLT SP single valve 8 is A2ZA1 (A1> Α2, α> 1), that is, the gain is greater than 1 (see Fig. 2).

Here, for example, the low secondary pressure P Lo is supplied to the lockup clutch 3 as it is.

SEC

If the hydraulic pressure B1 as shown in Fig. 2 needs to be output to secure the necessary torque capacity as the transmission torque of the lockup clutch 3, the linear solenoid valve SLT is controlled to increase the control pressure P. To increase the low secondary pressure P Lo to the hydraulic pressure B1

SLT SEC

Become. At this time, the control pressure P is supplied through the oil passage c2 to the oil chamber 7 of the primary leg turret 7.

SLT

Since it is also input to a, the line pressure P is increased to the hydraulic pressure A1.

Shi

[0070] Further, for example, as in the prior art, the control pressure P is applied to the oil chamber 8c of the secondary regulator valve 8.

SLT

When secondary pressure P with a gain of 1 is supplied to lockup clutch 3,

SEC

Even if it is necessary to output the hydraulic pressure B2 (secondary pressure is the same as the hydraulic pressure B1) as shown in Fig. 2 in order to secure the required torque capacity as the transmission torque of the lockup clutch 3, the control pressure P Therefore, the line pressure P is increased to the hydraulic pressure A2.

SLT

However, in the hydraulic control device 1 for an automatic transmission according to the present invention, the gain of the secondary regulator valve 8 is greater than 1 in the oil chamber 8c of the secondary regulator valve 8 as described above. Since the line pressure P is input as the pressure that increases, the hydraulic pressure B3 (

Shi

Even if it is necessary to output the secondary pressure is the same as the hydraulic pressure Bl, B2, the control pressure P is not required.

SLT

The line pressure P becomes the hydraulic pressure A3, that is, the line pressure P increases unnecessarily.

Lion

Will be prevented.

[0072] As described above, according to the hydraulic control device 1 for the automatic transmission according to the first embodiment of the present invention, the spool 8p of the secondary regulator valve 8 includes the large-diameter portion 8pA and the small-diameter portion 8pB. In other words, an intermediate portion is formed so as not to have a larger diameter than both end portions of the spool 8p, and an oil chamber 8c is formed between the large diameter portion 8pA and the small diameter portion 8pB. In Since the pressure that makes the gain of the secondary regulator valve 8 greater than 1 can be input, the gain of the secondary regulator valve 8 can be made larger than 1, and the line pressure P can be increased unnecessarily. While it can prevent the rise,

Shi

The provision of a sleeve and a plunger can be eliminated, and the secondary regulator valve 8 can be configured with a simple configuration, so that the number of parts can be reduced, the manufacturing process can be simplified, and compactness can be achieved.

[0073] Further, the solenoid valve S1 that can output the signal pressure P, and the signal pressure P of the solenoid valve S1

S1

The secondary pressure P is output to the lockup clutch 3 based on the

SI SEC

It is equipped with a lock-up relay valve 9 that switches between the states that shut off P.

SEC

By controlling the noid valve SI, it is possible to control the engagement / disengagement (engagement or release) of the lockup clutch 3.

[0074] Further, the solenoid valve S1 inputs the line pressure P as the source pressure of the signal pressure P and

SI L

When the signal pressure P is output, the line pressure P is output as it is as the signal pressure P.

SI L S1

Since there is an oil passage e3 that inputs the signal pressure P of the valve S1 to the oil chamber 8c, the secondary leg

S1

The line pressure P can be supplied as the pressure at which the gain of the urerator valve 8 is greater than 1.

Shi

wear. Also, the secondary regulator valve 8 is controlled by the signal pressure P of the solenoid valve S1.

S1

Therefore, the gain of the secondary leg tanner lev 8 can be controlled to be larger than 1 in conjunction with the engagement of the lock-up clutch 3. It is possible to prevent the line pressure P from being increased unnecessarily during engagement.

Shi

The

[0075] <Second embodiment>

Next, a second embodiment obtained by partially changing the first embodiment will be described with reference to FIG. FIG. 3 is a diagram showing a hydraulic control device for an automatic transmission according to the second embodiment. In the second embodiment, the same reference numerals are given to the same parts as those in the first embodiment except for some changed parts, and the description thereof is omitted.

As shown in FIG. 3, the hydraulic control device 1 for the automatic transmission according to the second embodiment

2

For the hydraulic control device 1 of the automatic transmission described above, the oil passage e3 is eliminated, and the pressure regulating port 7c of the primary regulator valve 7 and the oil chamber 8c of the secondary regulator valve 8 are connected. Oil passage (gain increasing pressure input means, second oil passage) for conducting (supplying) line pressure P to the oil chamber 8c

2, a5, si and relay valve (gain increasing pressure input means, second switching valve) 13 interposed between the oil passages a2, a5, si and the spool position of the relay valve 13 are controlled. The solenoid valve (second solenoid valve) S2 that can output the signal pressure (second signal pressure) P of

S2

It is prepared.

More specifically, the solenoid valve S2 (eg, normally closed) has an input port S 2a and an output port S2b, and the above-described modulator pressure P is applied to the input port S2a.

MOD

Is input via the oil path ql. When the solenoid valve S2 is in the OFF state (non-energized state), the input port S2a and the output port S2b are shut off, and when the solenoid valve S2 enters the ON state (energized state) based on a signal from an electronic control device (not shown). The input port S2a communicates with the output port S2b, and the modulator pressure P input to the input port S2a from the output port S2b is output as the signal pressure P substantially as it is. The signal output from the output port S2b

MOD S2

The signal pressure P (modulator pressure P) enters the oil chamber 13a of the relay valve 13 via the oil passage rl.

S2 MOD

It is powered.

[0078] The solenoid valve S2 is a force that explains the so-called normally closed type in which the input port S2a and the output port S2b are cut off when the power is not supplied. In this case, it is energized without the signal pressure P being output.

S2

[0079] The relay solenoid 13 includes a spool 13p and a spring 13s that urges the spool 13p upward, and an oil chamber 13a, a port 13c, and a port 13d above the spool 13p. It has. The oil chamber 13a is connected to an output port S2a of the solenoid valve S2 via an oil passage rl. When a signal pressure P is output from the solenoid valve S2, the oil chamber 13a

S2

Signal pressure P is input. That is, the relay valve 13 has a signal pressure higher than that of the solenoid valve S2.

S2

When P is not output, the valve is in the left half position, and the signal pressure P from the solenoid valve S2

S2

When is output, the position is the right half. The spool 13p of the relay valve 13 is in the left half

S2

In the position, the port 13c and the port 13d are blocked, and the port 13c and the drain port EX are in communication with each other. When the spool 13p is in the right half position, the port 13c and the port 13d are in communication with each other. Become. [0080] When the solenoid valve S2 is in the OFF state, no hydraulic pressure is input to the oil chamber 13a, and the spool 13p is in the left half position based on the urging force of the spring 13s. Then, the line pressure P input to the port 13d through the oil passages a2 and a5 is cut off, and the secondary leg

However, the hydraulic pressure is not input to the oil chamber 8c of the one-tablet 8 (drained via the oil passage si).

[0081] When the solenoid valve S2 is turned on, the signal pressure P is input to the oil chamber 13a, and the

S2

Spool 13p is in the right half position against the bias of pull 13s. Then, the line pressure P input to the port 13d via the oil passages a2 and a5 is supplied from the port 13c connected to the oil passage si.

L

In other words, the pressure regulating port 7c of the primary regulator valve 7 and the oil chamber 8c of the secondary regulator valve 8 communicate with each other, and the line pressure P is input to the oil chamber 8c. Secondary

Shi

When the line pressure P is input to the oil chamber 8c of the reguille tan lev 8, the first embodiment above

Shi

In the same way as the state, the gain of the secondary regulator valve 8 is greater than 1 and can output a high secondary pressure P Hi, thus preventing an unnecessary increase in the line pressure P.

SEC L

Can do.

[0082] Depending on the output state of the signal pressure P of the solenoid valve S2, the secondary regulator

S2

Since the state where the line pressure P is input to the oil chamber 8c of the valve 8 and the state where the line pressure P is not input are switched,

Shi

Regardless of the output state of signal pressure P of solenoid valve S1, the lockup relay

si

Engagement of the lock-up clutch 3 by switching the valve 9 'The gain of the secondary leg tan- nore 8 can be switched to a state larger than 1 or smaller than 1 regardless of the switching of release. That is, when the torque capacity transmitted by the lockup clutch 3 is low and the line pressure P is required to be high, the low secondary pressure P Lo can be output.

L SEC

It is possible to prevent the high secondary pressure P Hi from being output.

It is possible to improve the durability of SEC unit 2.

[0083] As described above, the hydraulic control device 1 for the automatic transmission according to the second embodiment of the present invention includes

According to Fig. 2, the spool 8p of the secondary regulator valve 8 is formed to have a large diameter portion 8pA and a small diameter portion 8pB, that is, the intermediate portion is formed so as not to have a large diameter from both end portions of the spool 8p. An oil chamber 8c is formed between the large-diameter portion 8pA and the small-diameter portion 8pB, and a pressure at which the gain of the secondary regulator valve 8 is greater than 1 can be input to the oil chamber 8c. The gain of the ureter valve 8 can be made larger than 1, While it can prevent the line pressure P from being increased unnecessarily,

Shi

[0084] Further, the solenoid valve S2 capable of outputting the signal pressure P and the line pressure P are conducted to the oil chamber 8c.

S2 L

The oil passage a5, si is connected to the oil passage a5, si, and communicates with the oil passage a5, si based on the signal pressure P.

S2

Therefore, the line pressure P is applied as a pressure at which the gain of the secondary regulator valve 8 is greater than 1.

Can be paid. Also, the secondary regulator is controlled by the signal pressure P of solenoid valve S2.

S2

Since the gain of the regulator valve 8 is larger than 1, the gain of the secondary regulator valve 8 can be controlled to be larger than 1 regardless of the engagement operation of the lockup clutch 3. This prevents unnecessary increases in the secondary pressure P.

SEC

Thus, the durability of the torque converter 2 can be improved.

Note that, in the first and second embodiments described above, the force described for what can input the line pressure P to the oil chamber 8c of the secondary regulator valve 8 is not limited to this.

Shi

If a pressure greater than the control pressure P can be input, the secondary regulator valve

SLT

8 gain can be greater than unity.

[0086] In the first and second embodiments, the description has been given of the case where the modulator pressure P is used as the source pressure of the linear solenoid valve SLT and the solenoid valve S2.

MOD

As long as it can output hydraulic pressure that can function as control pressure P and signal pressure P

SLT S2

Various source pressures may be used.

[0087] In the first and second embodiments, the force described for the fluid transmission device 4 including the three ports 4a, 4b, and 4c includes only the two ports, and the lock Even if the secondary pressure is supplied to the torque converter from the direction not pressing the friction plate when the up-clutch is released, and the secondary pressure is supplied from the direction pressing the friction plate when the lock-up clutch is engaged. The present invention can be applied.

Industrial applicability

[0088] The hydraulic circuit device according to the present invention is an automatic mounted on a passenger car, a truck, a nose, an agricultural machine, etc. It can be used for transmissions, motors, hybrid drive systems, etc., and is particularly suitable for applications where the gain of the pressure regulating valve that regulates the hydraulic pressure supplied to the lockup clutch or the like is required to be large. Therefore, the pressure regulating valve is suitable for those requiring reduction of the number of parts, simplification of the manufacturing process, compactness, and the like.

Claims

The scope of the claims

[1] A control valve that outputs a control pressure according to the throttle opening, a first pressure regulating valve that regulates a line pressure according to the control pressure, and a secrecy lower than the line pressure according to the control pressure A hydraulic control device for an automatic transmission, comprising: a second pressure regulating valve that regulates a secondary pressure; and supplying the secondary pressure to a fluid transmission device having a lock-up clutch and a torque converter.

The second pressure regulating valve is

A large-diameter portion formed in a shaft shape and having a large-diameter land portion formed on one side in the axial direction; A spool with

A pressure adjusting unit that adjusts the secondary pressure to increase in response to the spool moving to one side in the axial direction;

A first oil chamber that applies the control pressure from an end portion on the other side in the axial direction of the spool; a second oil chamber that applies a feedback pressure of the secondary pressure from an end portion on the one side in the axial direction of the spool;

A third oil chamber formed between the large diameter portion and the small diameter portion;

Have

The third oil chamber is provided with gain increasing pressure input means capable of inputting a pressure at which the gain of the second pressure regulating valve with respect to the control pressure is greater than 1.

A hydraulic control apparatus for an automatic transmission.

[2] a first solenoid valve capable of outputting a first signal pressure;

A first switching valve that switches between a state in which the secondary pressure is output to the lockup clutch and a state in which the secondary pressure is shut off based on a first signal pressure of the first solenoid valve;

The hydraulic control device for an automatic transmission according to claim 1.

[3] The first solenoid valve receives the line pressure as an original pressure of the first signal pressure, and outputs the line pressure as the first signal pressure as it is when the first signal pressure is output. , The gain increasing pressure input means is a first oil passage force for inputting the first signal pressure of the first solenoid valve to the third oil chamber.

The hydraulic control device for an automatic transmission according to claim 2.

The gain increasing pressure input means includes

A second solenoid valve capable of outputting a second signal pressure;

A second oil passage that conducts the line pressure to the third oil chamber;

A second switching valve that is interposed in the second oil passage and switches between a state in which the second oil passage is communicated and a state in which the second oil passage is shut off based on the second signal pressure;

Consist of,