JPH10267115A - Hydraulic pressure controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the number of parts, lower cost, decrease weight and an installation space by performing different functions under different setting hydraulic presser in one valve. SOLUTION: While a valve disk 5d of a hydraulic operating valve 5 moves from a position α for shutting off an inlet port 5a to a position β for opening an outlet port 5b, a low spring load of a first spring 5f' is exerted on the valve disk 5d. While the valve disk 5d moves from the position β to a position γfor opening an exhaust port 5c, a high composite spring load of the first and second springs 5f' and 5f" is exerted on the valve disk 5d. At the position αof the valve disk 5d when hydraulic pressure is not introduced to the inlet port 5a, hydraulic fluid is prevented from passing. At the position β of the valve disk 5d when the hydraulic pressure is introduced to the inlet port 5a, the hydraulic fluid is flowed to an oil cooler from the outlet port 5b. At the position γ of the valve disk 5d when the hydraulic pressure of not lower than a prescribed value is introduce, to the inlet port 5a, the hydraulic pressure introduced to the inlet port 5a is adjusted to the prescribed value.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention belongs to the technical field of a hydraulic control device for controlling various hydraulic operating devices by hydraulic pressure, such as a hydraulic control device for an automatic transmission mounted on an automobile.

[0002]

2. Description of the Related Art For example, in an automatic transmission mounted on an automobile, a torque converter, a fluid coupling,
2. Description of the Related Art Hydraulic pressure is used to operate various hydraulic actuators such as a hydraulic servo of a friction engagement element of a lock-up clutch, a clutch and a brake. In this case, the hydraulic pressures required for the various hydraulic actuators are different, and the operation timings of the various hydraulic actuators are different. It is necessary to control the supply and discharge of hydraulic pressure. Accordingly, a hydraulic control device is provided in the automatic transmission.

An example of such a hydraulic control device for an automatic transmission is disclosed, for example, in Japanese Patent Application Laid-Open No. Hei 2-225877. According to the hydraulic control device disclosed in this publication, the oil pressure boosted by the oil pump is adjusted as a line pressure, and this line pressure is supplied to and discharged from, for example, a hydraulic servo of a friction engagement element. Thereby, engagement and release of the friction engagement element are controlled. Further, the line pressure is adjusted as a lower secondary pressure, and the secondary pressure is supplied to and discharged from, for example, a fluid coupling and a lock-up clutch of a torque converter. In such a case, the release is controlled.

By the way, in such a hydraulic control device, when the engine is driven, the hydraulic oil constantly flows through the torque converter, so that the temperature of the hydraulic oil rises. Therefore, it is necessary to cool and drain the heated hydraulic oil. For this purpose, an oil cooler is provided in a conventional hydraulic control device such as the hydraulic control device disclosed in the aforementioned publication. In this case, if the oil pressure applied to the oil cooler exceeds a predetermined value, an extremely large load acts on the oil cooler.Therefore, a cooler bypass valve is provided, and the hydraulic oil is drained by the cooler bypass valve to the oil cooler. Attempts are not made to introduce hydraulic oil with a hydraulic pressure higher than the value. This prevents a large load from acting on the oil cooler.

[0005] In a torque converter, when the engine is stopped, the hydraulic oil escapes from the fluid coupling. Therefore, it is necessary to prevent the hydraulic oil from dropping out. For this purpose, a check valve is provided in the conventional hydraulic control device such as the hydraulic control device disclosed in the above-mentioned publication, and the check valve is provided with the check valve. Has been prevented.

FIG. 8 is a partial circuit diagram showing an example of a hydraulic control circuit provided with a cooler bypass valve and a check valve in the hydraulic control circuit in such a conventional hydraulic control apparatus. In the hydraulic control circuit shown in FIG. 8, the installation position of the check valve is different from the installation position of the check valve in the hydraulic control circuit of the above-mentioned publication, but each operation of the cooler bypass valve and the check valve is substantially. Is the same.

As shown in FIG. 8, a torque converter 71 of a hydraulic control circuit is connected to an oil cooler 73 via a check valve 72, and an oil passage 74 between the check valve 72 and the oil cooler 73 is provided. It is connected to a drain tank (not shown) via a cooler bypass valve 75. That is, the torque converter 71 is directly connected to the drain tank via the check valve 72 and the cooler bypass valve 75, bypassing the oil cooler 73.

The check valve 72 includes an inflow port 72 a connected to the torque converter 71, and an oil cooler 7.
Outflow port 72b connected to the bottom 3 and a bottomed cylindrical valve body 7
2c, a valve seat 72d on which the valve body 72c can be seated, and a check valve spring 72e that constantly urges the valve body 72c in a direction to seat the valve body 72c on the valve seat 72d.
This spring 72e is used when no oil pressure is generated when the engine is stopped or when there is only a slight residual oil pressure on the torque converter 71 side and the oil pressure does not substantially act on the valve body 72c. As shown by the right half of the check valve 72 in FIG.
2d, the inflow port 72a and the outflow port 72b
When a relatively low oil pressure acts on the valve body 72c from the inflow port 72a, the valve body 72c immediately separates from the valve seat 72d as shown by the left half of the check valve 72 in FIG. A relatively small spring constant is set so that the inflow port 72a and the outflow port 72b communicate with each other.

The cooler bypass valve 75 has an inlet port 75a connected to an oil passage 74 between the check valve 72 and the oil cooler 73, a first discharge port 75b connected to the drain tank, and a drain tank 75. A second discharge port 75c to be connected and a piston-like valve body 75
d, a valve seat 75e on which the valve element 75d can be seated, and a cooler bypass valve spring 75f that constantly urges the valve element 75d in a direction of seating the valve element 75d on the valve seat 75e. When no hydraulic pressure acts on the valve element 75d, the spring 75f seats the valve element 75d on the valve seat 75e as shown by the right half of the cooler valve 75 in FIG. 2 discharge port 75
b and 75c, but when a relatively high oil pressure acts on the valve body 75d from the inflow port 75a, the valve body 75d is separated from the valve seat 75e as shown by the left half of the cooler bypass valve 75 in FIG. The spring constant of the spring 72e is set to be larger than that of the spring 72e so as to sit and communicate the inflow port 75a with the first and second discharge ports 75b and 75c.

In the conventional hydraulic control circuit configured as above, when the engine stops, the oil pump also stops, so that no hydraulic pressure is generated in the working oil. Accordingly, in the check valve 72 of the negative pressure control circuit, the valve body 72c is seated on the valve seat 72d as shown by the right half in the figure, so that the inflow port 72a and the outflow port 72b are shut off, and the cooler bypass valve 75 In the same manner, as shown in the right half of the figure, the valve body 75d is seated on the valve seat 75e, and the inflow port 75a and the first and second discharge ports
5b and 75c are cut off. Thus, check valve 7
Since the valve 2 is closed, the hydraulic oil does not escape from the torque converter 71 toward the oil cooler 73.

When the engine is driven, the oil pump is also driven, so that the hydraulic oil generates hydraulic pressure. Therefore, the operating oil that has generated the hydraulic pressure operates the torque converter 71, and then is introduced into the inflow port 72a of the check valve 72 and acts on the valve body 72c. For this reason, as shown in the left half of the figure, the valve body 72c separates upward from the valve seat 72d against the spring force of the spring 72e, and the inflow port 72
a communicates with the outflow port 72b. Thereby, the hydraulic oil is introduced from the inflow port 72a to the oil cooler 73 through the outflow port 72b, and is cooled by the oil cooler 73. At this time, the hydraulic oil introduced into the oil cooler 73 is supplied to the inflow port 7 of the cooler bypass valve 75.
5a acts on the valve body 75d, but since the hydraulic pressure of the hydraulic oil has not risen so high, the valve body 75d is moved to the valve seat 75e.
, And the cooler bypass valve 75 remains closed.

When the hydraulic pressure of the working oil introduced into the oil cooler 73 rises to the opening pressure of the cooler bypass valve 75, the valve body 75d of the cooler bypass valve 75 opposes the spring force of the spring 75f and the valve seat 75e. From the inlet port 75a and the first and second discharge ports 75.
b, 75c communicate with each other. As a result, the hydraulic oil flows from the inflow port 75a to the first and second discharge ports 75b, 75b.
c to the drain tank. in this way,
When the hydraulic pressure of the hydraulic oil introduced into the oil cooler 73 becomes equal to or higher than a predetermined pressure, the hydraulic oil from the torque converter 71 bypasses the oil cooler 73 and is directly drained to the drain tank. Therefore, the oil cooler 7
No large load acts on 3.

[0013]

In such a conventional hydraulic control device, the check valve 72 and the cooler bypass valve 75 are separately provided.
This is because the check valve 72 has a function of preventing the hydraulic oil from leaking when the engine is stopped, that is, has a function of preventing the discharge of the hydraulic oil when the engine is not operating, whereas the cooler bypass valve 75 has Since the function of preventing the introduction of the hydraulic oil, that is, the function of adjusting the hydraulic oil pressure at the time of operation, has a function not only of the two valves 72 and 75, but also the magnitude of the set hydraulic pressure is completely different from each other. , These valves 72,7
5 must be provided separately.

However, providing the check valve 72 and the cooler bypass valve 75 separately as described above increases the number of parts, thereby increasing not only the cost but also the weight and increasing the installation space. I need it.

Therefore, these two valves 72 and 75 are connected by one.
Although it is conceivable to construct with one valve, both valves 7
The 2,75 not only has different functions as described above,
Since the set hydraulic pressures are also different, there is a problem that it is extremely difficult to configure with one valve.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide a single valve that performs different functions with different set hydraulic pressures, thereby reducing the number of parts and reducing costs. An object of the present invention is to provide a hydraulic control device capable of reducing the weight while reducing the weight, and further reducing the installation space.

[0017]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a first aspect of the present invention provides an inflow port into which hydraulic oil is introduced, an outflow port through which hydraulic oil is discharged, and a discharge port through which hydraulic oil is discharged. Port, a valve body on which hydraulic pressure of hydraulic oil introduced into the inflow port acts, and biasing means for biasing the valve body, wherein when no oil pressure is acting on the valve body, the valve When the body is urged by the urging force of the urging means to block the inflow port and hydraulic pressure acts on the valve body, the valve body is pressed against the urging force of the urging means. By moving the stroke value to communicate the inflow port and the outflow port, hydraulic oil is derived from the outflow port, and when a hydraulic pressure of a predetermined value or more acts on the valve body, the valve body is The outflow port further moves against the urging force of the urging means. It is characterized in that it comprises a hydraulic valve for pressurizing regulating the hydraulic pressure of the hydraulic fluid to be introduced into the inlet port by communicating the discharge port to a predetermined value.

According to a second aspect of the present invention, the urging means includes:
A first spring and a second spring, while the valve body moves to the predetermined stroke value, only the first spring urges the valve body, and the valve body is When the movement is equal to or more than the predetermined stroke value, both the first spring and the second spring bias the valve body.

Further, according to a third aspect of the present invention, the first spring and the second spring are both coil springs, and a winding direction of the coil of the first spring and a winding direction of the coil of the second spring. Are set to be opposite to each other.

Further, according to a fourth aspect of the present invention, the urging means is a coil spring, and the coil spring comprises a dense pitch portion having a small coil pitch and a coarse pitch portion having a large coil pitch. Features.

Further, the invention according to claim 5 is characterized in that the dense pitch portion is provided at both ends of the coil spring, and the coarse pitch portion is provided at a central portion of the coil spring.

According to a sixth aspect of the present invention, in the hydraulic control device for an automatic transmission having a torque converter and an oil cooler, the hydraulically operated valve is disposed in an oil passage leading from the torque converter to the oil cooler. An oil passage from the torque converter is connected to an inflow port of the hydraulically operated valve, and an oil passage to the oil cooler is connected to an outflow port of the hydraulically operated valve.

[0023]

In the hydraulic control apparatus according to the first aspect of the present invention, a small residual hydraulic pressure is applied to the inflow port of the hydraulic valve so that no hydraulic pressure is introduced or the valve body is not stroked. When the hydraulic pressure is not substantially introduced into the inflow port only by being introduced, the hydraulic pressure does not substantially act on the valve body, and the valve body shuts off the inflow port by the biasing means. Therefore, the discharge of the hydraulic oil upstream of the inflow port can be reliably prevented.

When the hydraulic pressure is substantially introduced into the inflow port, the hydraulic pressure substantially acts on the valve element. In this case, the valve body moves by a predetermined stroke value, and the inflow port and the outflow port communicate with each other, so that hydraulic oil can be derived from the outflow port. At this time,
Since the hydraulic oil is filled upstream of the inflow port by shutting off the inflow port, the valve element immediately moves when hydraulic pressure is substantially introduced into the inflow port.

Further, when the hydraulic pressure introduced into the inflow port becomes equal to or more than a predetermined value, the valve body moves to a predetermined stroke value or more and the inflow port and the discharge port communicate with each other. It is discharged from the discharge port. As a result, the hydraulic pressure introduced into the inflow port is adjusted, and the load on the device to which the hydraulic oil is derived from the outflow port and the load on the supply source of the hydraulic oil can be reduced, and the hydraulic fluid introduced into the inflow port can be reduced. It is possible to stably maintain the hydraulic pressure to be maintained within a predetermined value. Further, since only the inflow port, the outflow port, the discharge port, the valve element, and the urging means are provided, the configuration of the hydraulically operated valve is simplified.

Therefore, a single hydraulically actuated valve having a simple configuration can fulfill both functions of preventing discharge of hydraulic oil during non-operation and regulating pressure of hydraulic oil during operation. Thus, the number of components can be reduced, the cost can be reduced, the weight can be reduced, and the installation space can be reduced.

According to the second aspect of the present invention, by providing the first spring and the second spring,
The urging force applied to the valve body can be independently set according to the respective functions of preventing the discharge of the hydraulic oil and adjusting the hydraulic pressure. As a result, the pressure adjustment can be performed optimally.

Further, according to the third aspect of the present invention, the first spring and the second spring are constituted by coil springs having different winding directions, so that the first spring and the second spring can be operated when the hydraulic valve is operated. And the springs do not become entangled with each other, and the hydraulic oil can be stably derived and regulated.

Further, according to the invention of claim 4, the spring is constituted by a dense pitch portion having a small spring constant and a coarse pitch portion having a large spring constant. By providing the dense pitch portion and the coarse pitch portion in this way, the urging force applied to the valve body can be independently controlled according to the respective functions of preventing the discharge of the hydraulic oil and adjusting the hydraulic pressure. Can be set. As a result, the pressure adjustment can be performed optimally. In addition, since only one spring is required, an increase in the number of components can be prevented.

Further, according to the fifth aspect of the present invention, the pitch dense portion is provided at both ends of the coil spring, and the coarse pitch portion is provided at the center of the coil spring, so that the coil can be stored in the lot when the spring is assembled. Since the entanglement between the springs can be suppressed, assembling workability is improved.

Further, in the invention of claim 6,
A check valve function used to prevent hydraulic oil from flowing out of the torque converter when the engine is stopped, and a cooler that regulates and holds the oil pressure in the oil cooler to a predetermined value or less, which was used in the hydraulic control device of the automatic transmission. The function of the bypass valve can be constituted by one valve. Thus, the cost of the hydraulic control unit of the automatic transmission can be reduced, the weight can be reduced, and the hydraulic control unit can be downsized.

[0032]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a diagram partially showing a first example of an embodiment in which a hydraulic control device according to the present invention is applied to a hydraulic control device of an automatic transmission.

As shown in FIG. 1, the hydraulic control device 1 of the first embodiment is provided with a hydraulic valve 5 in a connection oil passage 4 between a torque converter 2 and an oil cooler 3. The hydraulically operated valve 5 includes an inlet port 5a connected to the torque converter 2, an outlet port 5b connected to the oil cooler 3, an outlet port 5c connected to a drain tank (not shown), and a bottomed cylindrical valve. It comprises a body 5d, a valve seat 5e on which the valve body 5d can be seated, and a spring 5f which constantly biases the valve body 5d in a direction for seating on the valve seat 5e.

The outlet port 5b is provided at a position adjacent to the valve seat 5e, and the discharge port 5c is connected to the valve seat 5e.
From the outflow port 5b. Accordingly, the valve body 5d is stroked downward by a first predetermined value from the position α shown by the solid line on the left side of FIG. 1 where the valve body 5d is seated on the valve seat 5e, and is set to the position β shown by the two-dot chain line on the right side of FIG. Then, the inflow port 5a and the outflow port 5b communicate with each other, the inflow port 5a and the discharge port 5c are kept in a disconnected state, and the valve element 5d is further moved from the position β of the two-dot chain line to the second predetermined position. Stroke more than the value
Is set to the position γ shown by the solid line on the right side of the figure, the inflow port 5a not only communicates with the outflow port 5b, but also communicates with the discharge port 5c.

As described above, the hydraulic valve 5 is such that the stroke at the position α where the valve element 5d is seated on the valve seat 5e is the first predetermined value between 0 and the position β indicated by the two-dot chain line. One stage and a second stage in which the valve element 5d strokes by a second predetermined value or more from the position β of the two-dot chain line to the position γ of the solid line on the right in FIG. 1 are set. The valve body 5d at the position γ on the right side of FIG. 1 is shown as not being guided at all,
Of the valve body 5d so that the axial movement of the valve element 5d can be performed smoothly and reliably.

As shown in FIG. 2, the spring 5f is composed of a coil spring, and upper and lower ends of the coil spring are pitch dense portions 5f ₁ and 5f ₂ having a small coil pitch, respectively. the center portion is a pitch coarse portion 5f ₃ large pitch winding. In such a coil spring, with the spring constant of the pitch dense portion 5f _1, 5f ₂ is small, the spring constant of the pitch rough portion 5f ₃ is larger.

In the first stage of the hydraulically operated valve 5,
When the stroke at which the valve element 5d is seated on the valve seat 5e is 0, the load of the spring 5f is set to be extremely small. When the valve element 5d starts a stroke, the spring 5f reduces both the pitch dense parts 5f ₁ and 5f _{2 having} a small spring constant and the pitch coarse part 5f ₃ having a large spring constant with respect to the stroke of the valve element 5d. The reduction amount of the pitch dense portions 5f ₁ and 5f ₂ having a small spring constant is larger than the reduction amount of the pitch coarse portion 5f _{3 having} a large spring constant. This first
The equivalent spring constant of the spring 5f at the stage is the same as the equivalent spring constant when springs having different spring constants are connected in series, and the spring load is compared with the stroke of the valve element 5d as shown in FIG. It changes gradually. Thus, when the hydraulic pressure is applied, the valve element 5d immediately separates from the valve seat 5e and strokes by the first predetermined value to reach the position shown by the two-dot chain line in the right half of FIG. 1, and the inflow port 5a and the outflow port 5b Will be communicated with.

At this time, the springs 5f have the fine pitch portions 5f ₁ , 5f ₂ and the coarse pitch portions 5f ₃ both reduced in size, so that the oil of the torque converter 1 is similar to the spring 72e of the conventional check valve 72 described above. An equivalent spring constant obtained by combining the pitch dense portions 5f ₁ , 5f ₂ and the pitch coarse portion 5f ₃ in series is set to a small value so as to function as a check unit for preventing slippage.

[0039] Then, the stroke of the valve body 5d in the first stage, the pitch of the spring 5f dense portion 5f _1, 5
Since the reduced amount is large yet winding pitch of f ₂ is small, the reduction of the pitch dense portion 5f _1, 5f _2, the pitch coarse portion 5f ₃
The reduction limit is reached sooner. In this case, in the hydraulically actuated valve 5 of the present example, when the valve element 5d strokes by the first predetermined value and moves to the position β indicated by the two-dot chain line, the dense pitch portions 5f ₁ and 5f ₂ of the spring 5f are at the reduction limit. And the reduction is completed. In this case, the pitch coarse portion 5f ₃ of the spring 5f is not reached reduction limit, so that the reduced is continued.

In the second stage of the hydraulically operated valve 5, when the valve element 5d further strokes from the position β indicated by the two-dot chain line, the spring 5f has completed the reduction of the dense pitch portions 5f ₁ and 5f ₂ . since, the relative stroke of the valve body 5d only large pitch coarse portion 5f ₃ of the spring constant is so reduced, a relatively large its spring load with respect to the stroke of the valve body 5d as shown in FIG. 3 It will change. Then, when the valve element 5d strokes from the position β by the second predetermined value, the position becomes the position γ of the solid line on the right side in FIG. 1, and the inflow port 5a communicates with the outflow port 5b and the discharge port 5c.

The spring 5f At this time, since the reduced its pitch rough portion 5f _3, cooler prevents Similarly load increase of the oil cooler 3 and the spring 75f in a conventional cooler bypass valve 75 mentioned above - as a bypass section to function, the spring constant of the pitch rough portion 5f ₃ is set to a large value. In this case, the spring load at the position where the valve element 5d opens the discharge port 5c shown on the right side of FIG. 1 is a pressure adjustment point at which the oil pressure to the oil cooler 3 starts to be adjusted as shown in FIG.

As shown in FIG. 4, the hydraulically operated valve 5 has an inflow port 5a connected to the torque converter 2 via a lock-up relay valve 6 provided in a hydraulic control circuit of the automatic transmission. The lock-up relay valve 6 is further connected to a lock-up control valve 7, and the lock-up relay valve 6 and the lock-up control valve 7
The operation is controlled by a lock-up operation control signal from a lock-up linear solenoid valve (SLU) 8.

Then, the primary regulator valve 9
Adjusts the discharge pressure from the oil pump 10 to a line pressure corresponding to the throttle opening based on the throttle pressure from the linear solenoid throttle valve (SLT) 11 and discharges the secondary pressure of the surplus oil. The regulator valve 12 sets this secondary pressure to S
Based on the throttle pressure from LT11, the pressure is adjusted to a predetermined torque converter operating oil pressure corresponding to the throttle opening, and the predetermined torque converter operating oil pressure is supplied to lock-up relay valve 6 and lock-up control valve 7. . Further, the SLU 8 outputs a lock-up operation control signal corresponding to the throttle opening based on the throttle modulator pressure from the throttle modulator valve 13.

In the hydraulic control device of the present embodiment thus configured, when the valve element 5d of the hydraulic actuating valve 5 is located between the position α and the position β, the hydraulic control device 1 moves to the first stage. Is set. When the engine is stopped, no hydraulic pressure is generated as described above. For this reason, the hydraulic pressure does not act on the valve element 5a of the hydraulic actuation valve 5 or only a small residual oil pressure remaining in the torque converter 2 that does not stroke the valve element 5d acts. Substantially does not act on the body 5d and the valve body 5a
Is seated on the valve seat 5e with a small spring load of the spring 5f. Therefore, the oil is prevented from coming off from the torque converter 2.

When the engine is driven, the oil pump 1
0 is driven to generate pump discharge pressure. As described above, the pump discharge pressure is adjusted to the line pressure and the secondary pressure by the primary regulator valve 9, and the secondary pressure is adjusted to a predetermined torque converter operating oil pressure by the secondary regulator valve 12. When the lock-up is off, the lock-up relay valve 6 is set on the left side in FIG. 4 and the lock-up control valve 7 is set on the right side. Port 6a, port 6b of lock-up relay valve 6, port 2a of torque converter 2, torque converter 2, port 2b of torque converter, port 6c of lock-up relay valve 6, port 6d of lock-up relay valve 6, hydraulic valve 5 flows into the inflow port 5a. Since the hydraulic pressure of the hydraulic oil that has flowed into the inflow port 5a acts on the valve element 5d of the hydraulic operating valve 5, the valve element 5d starts to stroke and moves to the position β. At this time, since the increase in the load of the spring 5f is small with respect to the increase in the stroke of the valve element 5d, the valve element 5d immediately strokes by the first predetermined value. As a result, the inflow port 5a and the outflow port 5b communicate with each other, and the hydraulic oil from the torque converter 1 is quickly introduced into the oil cooler 3, where it is cooled and drained. Thus, the hydraulic oil is reliably cooled.

[0046] From the state the valve body 5d of the hydraulic valve 5 is in the position β, the hydraulic valve 5 is a second stage, the spring 5f in this second stage by reducing the pitch rough portion 5f ₃ spring Since the load increases, even if the pressure of the hydraulic oil from the torque converter 2 increases, the valve element 5d does not immediately move any further. When the oil pressure from the torque converter 2 increases by a predetermined pressure or more, the valve element 5d further strokes downward to reach the position γ. Accordingly, the inflow port 5a communicates with the discharge port 5c in addition to the communication with the outflow port 5b, and the hydraulic oil from the torque converter 1 is drained to the drain tank through the discharge port 5c, and the hydraulic pressure from the torque converter 2 is reduced. The rise is suppressed and adjusted to a predetermined pressure and held. Thus, the load on the oil cooler 3 is reduced.

On the other hand, when the lock-up is ON, the lock-up relay valve 6 is set to the right side and the lock-up control valve 7 is set to the left side in FIG. Of the lock-up relay valve 6, the port 6c of the lock-up relay valve 6, the port 2b of the torque converter 2, the torque converter 2, the port 2c of the torque converter, the port 6b of the lock-up relay valve 6, the lock It is drained through the port 7a of the up-control 7 and the port 7a of the lock-up control 7. Therefore, the pressure on the torque converter side of the piston of the lock-up clutch of the lock-up clutch LC becomes higher than that on the opposite side, so that the lock-up clutch LC is engaged and is in a directly connected state. At this time, surplus oil from the secondary regulator valve 12 is supplied to the port 6e of the lock-up relay valve 6, the port 6d of the lock-up relay valve 6, the inflow port 5a of the hydraulic valve 5, the outflow port 5b of the hydraulic valve 5, And is drained through an oil cooler 3.

According to the hydraulic control apparatus 1 of this embodiment, when the engine is stopped, the inflow port 5a is shut off by the valve element 5d, so that the hydraulic oil on the torque converter 2 side is discharged through the oil cooler 3. Is reliably prevented from being performed. Thereby, the inflow port 5
a, the hydraulic oil fills the torque converter 2 side.
When the operation is started by driving the engine, the valve element 5d can be immediately stroked by the pressure of the hydraulic oil toward the torque converter 2, and the torque converter 2 can operate normally.

Further, when the hydraulic pressure is being introduced into the inflow port 5a, the hydraulic oil can be reliably introduced into the oil cooler 3, so that the hydraulic oil can be reliably cooled.

[0050] Further, when the hydraulic pressure from the torque converter 2 rises above a predetermined value, the spring 5f, large pitch coarse portion 5f ₃ of the spring constant is reduced, through the discharge port 5c of the hydraulic oil boosted Since the hydraulic fluid is drained, the hydraulic oil from the torque converter 2 can be reliably adjusted to a predetermined value. As a result, the load on the oil cooler 3 and the torque converter 2 can be reduced, and the hydraulic pressure of the working oil can be stably maintained within a predetermined value.

Further, the single hydraulically actuated valve 5 can fulfill both functions of preventing discharge of hydraulic oil when not operating and regulating pressure of hydraulic oil during operation. Thus, the number of parts can be reduced, the cost can be reduced, the weight can be reduced, and the installation space can be reduced.

In the illustrated example, the dense pitch portions 5f ₁ , 5f
_Although the axial lengths of the pitch dense portions 5f ₁ and 5f ₂ are set to be different from each other, the axial lengths of the pitch dense portions 5f ₁ and 5f ₂ are not limited thereto. Can also.

Also, at both upper and lower ends of the spring 5f,
Although the dense pitch portions 5f ₁ and 5f ₂ are provided, the dense pitch portions may be provided on either one of the upper and lower ends of the spring 5f. However, pitch dense portion 5f _1, 5
Who provided f ₂ at both ends of the upper and lower spring 5f it is desirable because assembling workability is suppressed entangled spring each other to be stored in the lot when assembling the spring 5f is improved. Further, as shown in FIG. 5, the spring 5f has a coil diameter D _{3 of the} coarse pitch portion and a coil diameter D ₄ of the fine pitch portion.
May be formed differently from each other.

FIG. 6 is a view similar to FIG. 1, showing a second embodiment of the present invention. The same components as those in the first example shown in FIG. 1 are denoted by the same reference numerals, and a detailed description thereof will be omitted.

In the first example shown in FIG. 1, the spring 5f for urging the valve element 5d is constituted by one spring having dense pitch portions 5f ₁ and 5f ₂ and coarse pitch portions 5f _3. However, in the hydraulic valve 5 of the second example,
As shown in FIG. 6, the spring 5f for urging the valve element 5d includes two first and second coil springs 5f 'and 5f ".
It is composed of In that case, as shown in FIGS. 7A and 7B, the first coil spring 5f '
The winding pitch of the coil is set to the same pitch, the winding pitch of the second coil spring 5f "is also set to the same pitch, and the first and second coil springs 5f ', 5f" The winding directions are set to be opposite to each other.

The spring constant of the first coil spring 5f 'is the same as the spring 7 of the above-described conventional check valve 72.
The spring constant of the second coil spring 5f ″ is set relatively large similarly to the spring constant of the spring 75f of the conventional cooler bypass valve 75, while the spring constant of the second coil spring 5f ″ is set relatively small similarly to the spring constant 2e. , First
'Together with the outer diameter D ₁ of the is set to be slightly smaller than the inner diameter D ₂ of the second coil spring 5f ", the first coil spring 5f' coil spring 5f axial length of L ₁
There "As shown in is set to be longer than the axial length L ₂ of. FIG. 7 (c), the the first and second coil springs 5f ', 5f" second coil spring 5f, the second coil The first coil spring 5f 'is fitted in the inner peripheral hole of the spring 5f ".

As shown in FIG. 6, the first and second coil springs 5f 'and 5f "are fitted into the inner peripheral hole of the cylindrical valve element 5d. In this case, the valve element 5d
Is in the position α seated on the valve seat 5e, only the first coil spring 5f 'is slightly reduced and comes into contact with the valve element 5d, and the second coil spring 5f "is not in contact with the valve element 5d and is free. Therefore, in this state, the valve element 5d is urged toward the valve seat 5e by a relatively small spring load of the first coil spring 5f '.

When the valve element 5d reaches a position β shown by a two-dot chain line on the right side of FIG. 6 in which the valve element 5d has moved downward from the position α by a first predetermined value, the valve element 5d comes into contact with the second spring 5f ″. Therefore, during the stroke of the valve element 5d from the position α to the position β, only the first spring 5f ′ contracts, and the second spring 5f ″ does not contract at all. Only a relatively small spring load of the spring 5f 'acts, and no large spring load of the second spring 5f "acts. That is, at this time, the hydraulic valve 5 of the second example is set to the first stage described above. As a result, the spring load applied to the valve element 5d changes slightly with respect to the stroke of the valve element 5d as shown in FIG.

The first and second springs 5f ', 5 are moved while the valve element 5d strokes further downward from the position β to the position γ shown by the solid line on the right side of FIG.
f ″ are both reduced, and during this time, a relatively large resultant force of the spring loads of the first and second springs 5f ′ and 5f ″ acts on the valve element 5d. That is, at this time, the hydraulic actuated valve 5 of the second example is set to the above-described second stage, and the spring load received by the valve element 5d is larger than the stroke of the valve element 5d as shown in FIG. It will change. Other configurations of the hydraulic control device 1 of the second example are the same as those of the above-described first example.

In the operation of the hydraulic control device 1 of the second example, while the valve element 5d strokes from the position α to the position β, a small spring load of the first spring 5f 'acts on the valve element 5d. During the stroke of the valve element 5d from the position β to the position γ, a large combined spring load of the first and second springs 5f ′ and 5f ″ acts on the valve element 5d. The hydraulic control device 1 of the second example The other operations are the same as in the first example.

Further, according to the hydraulic control device 1 of the second example,
Since the first and second springs 5f 'and 5f "are provided, the load of each spring load acting on the valve element 5d is determined according to the respective functions of preventing the hydraulic oil from coming off and adjusting the hydraulic pressure. The biasing force can be set independently,
Optimum pressure adjustment can be performed.

The first and second springs 5f ',
5f ″, the winding directions of the springs 5f ″ are opposite to each other.
f ′, 5f ″ do not become entangled with each other, and it is possible to reliably introduce hydraulic oil to the oil cooler 3 and to perform stable pressure regulation. Another effect of the hydraulic control device 1 of the second example is as follows.
This is the same as the first example except for the effect due to the difference in the configuration of the spring.

Further, in the first and second examples of the hydraulic control device 1 described above, the case where both are applied to the hydraulic control device of the automatic transmission has been described, but the present invention is not limited to this. Rather, it has one inflow port and two outflow ports, the valve body operates at a first predetermined pressure, the inflow port communicates with one of the outflow ports, and a second pressure is higher than the first predetermined oil pressure. The present invention can be applied to any hydraulic control device as long as the valve body is further operated at a predetermined pressure of 2 so that the inflow port communicates with both of the outflow ports.

[Brief description of the drawings]

FIG. 1 is a diagram partially showing a first example of an embodiment in which a hydraulic control device according to the present invention is applied to a hydraulic control device of an automatic transmission.

FIG. 2 is a sectional view showing a spring used in the hydraulic valve of the first example shown in FIG.

FIG. 3 is a view showing a load characteristic of the spring of the first example shown in FIG. 1;

FIG. 4 is a diagram partially showing a hydraulic control circuit in the hydraulic control device of the automatic transmission to which the hydraulic control device of the present invention is applied.

FIG. 5 is a sectional view showing a modification of the spring of the first example shown in FIG. 1;

FIG. 6 is a diagram partially showing a second example of an embodiment in which the hydraulic control device according to the present invention is applied to a hydraulic control device of an automatic transmission.

7 shows a second example spring shown in FIG. 6,
(A) is a cross-sectional view showing a first coil spring, (b) is a cross-sectional view showing a second coil spring, and (c) is a cross-sectional view showing a state where the second coil spring is fitted into the first coil spring and assembled. It is.

FIG. 8 is a view partially showing a hydraulic control device in a conventional automatic transmission.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Hydraulic control device, 2 ... Torque converter, 3 ... Oil cooler, 4 ... Connection oil path, 5 ... Hydraulic valve, 5a ... Inflow port, 5b ... Outflow port, 5c ... Discharge port, 5d ... Valve element, 5e ... valve seat, 5f ... spring, 5f _1, 5f ₂ ... pitch dense portion, 5f ₃ ... pitch coarse portion, 5f '... first coil spring, 5f "... second coil spring

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takayuki Kuno 10 Takane, Fujii-cho, Anjo, Aichi Prefecture Inside Aisin AW Co., Ltd.・ AW Co., Ltd. (72) Inventor Noriyuki Takahashi 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation (72) Inventor Masafumi Kinoshita 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation ( 72) Inventor Ryoji Habuchi 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation

Claims (6)

[Claims] An inflow port into which hydraulic oil is introduced, an outflow port through which hydraulic oil is discharged, a discharge port through which hydraulic oil is discharged, a valve body on which hydraulic pressure of the hydraulic oil introduced into the inflow port acts, Urging means for urging the valve element, and when no oil pressure is acting on the valve element, the valve element is
When the oil pressure is applied to the valve body by being urged by the urging force of the urging means to block the inflow port, the valve body moves a predetermined stroke value against the urging force of the urging means. By connecting the inflow port and the outflow port, hydraulic oil is derived from the outflow port, and when a hydraulic pressure equal to or more than a predetermined value acts on the valve body, the valve body is actuated by the urging means. A hydraulic actuating valve for adjusting the oil pressure of the operating oil introduced into the inflow port to a predetermined value by further moving against the urging force of the fluid to communicate the outflow port and the discharge port. Hydraulic control device. 2. The urging means includes a first spring,
A second spring, while the valve body moves to the predetermined stroke value, only the first spring urges the valve body, and the valve body moves by the predetermined stroke value or more. 2. The method according to claim 1, wherein the first spring and the second spring both urge the valve body when the pressure is applied.
The hydraulic control device as described. 3. The first spring and the second spring both comprise coil springs, and
3. The hydraulic control device according to claim 2, wherein the winding direction of the coil of the second spring and the winding direction of the coil of the second spring are set to be opposite to each other. 4. The coil spring according to claim 1, wherein said biasing means comprises a coil dense portion having a small coil pitch and a coarse portion having a large coil pitch. The hydraulic control device as described. 5. The hydraulic control according to claim 4, wherein the dense pitch portion is provided at both ends of the coil spring, and the coarse pitch portion is provided at a central portion of the coil spring. apparatus. 6. An oil pressure control device for an automatic transmission including a torque converter and an oil cooler, wherein the hydraulically actuated valve is disposed in an oil passage leading from the torque converter to the oil cooler. The inflow port of the hydraulically operated valve is connected to an oil passage, and the outflow port of the hydraulically operated valve is connected to an oil passage to the oil cooler.
The hydraulic control device according to any one of the above.