JP2002168359A - Pressure regulator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce costs and the number of components by abolishing exclusive components for fixing a small diameter sleeve 5 of a control valve 1 to a large diameter sleeve 2. SOLUTION: In a solenoid composite control valve, the control valve 1 and a pilot valve 2 are integrated. A lid body part 44 for blocking an opening part of the large diameter sleeve 2 and setting a spring load of a first spring 11, and a cylinder wall part 45 inserted in an inner circumference of a cylinder wall part 29 of an opened end 19 side of the large diameter sleeve 2 are integrated on the small diameter sleeve 5 of the control valve 1. The cylinder wall part 45 is caulked by a caulking part 2a of the opened end 19 side of the large diameter sleeve 2. By this, the small diameter sleeve 5 is fixed to the inner circumference of the cylinder wall part 29 of the opened end 19 side of the large diameter sleeve 2. The small diameter sleeve 5 requiring high accuracy is manufactured by a metal injection mold which is metal molding method needing no cutting work. By this, manufacturing cost of the control valve 1 can be suppressed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure regulating valve having a variable characteristic capable of switching between an output oil pressure proportional to a pilot oil pressure and an output oil pressure equal to a supply pressure of a supply pressure source.

[0002]

2. Description of the Related Art Conventionally, a hydraulic system such as a hydraulic multi-plate clutch for interconnecting the components of a planetary gear set disposed between an input shaft and an output shaft of an automatic transmission mounted on a vehicle has been known. There is a hydraulic system circuit provided with a control valve that regulates an output hydraulic pressure supplied to a hydraulic circuit communicating with a hydraulic servo that connects and drives a coupling element (hereinafter referred to as a clutch) to a control pressure proportional to a pilot pressure. The circuit for controlling the clutch pressure of the hydraulic system circuit includes a pilot valve driven by a solenoid valve, a shift valve that receives and moves the modulator pressure output from the modulator valve, and the control valve described above. ing.

[0003]

However, in the conventional hydraulic system circuit, in order to regulate the output hydraulic pressure,
A pilot valve, a shift valve, and the like are required in addition to the control valve, and there is a problem that the size of the hydraulic system circuit is increased. Therefore, Japanese Patent Application No. 2000-93966 (filing date: March 30, 2000) has already been filed for the purpose of integrating the pilot valve, the relay valve, and the shift valve to reduce the size of the entire hydraulic system circuit. In the above-mentioned application, as shown in FIG. 7, the pressure regulating valve 10 having variable characteristics is applied.
1 proposes an electromagnetic compound control valve (prior art) in which a pilot pressure control valve 110 is integrated.

A small-diameter sleeve 103 is inserted into the inner periphery of a large-diameter sleeve 102 of the pressure regulating valve 101, and a small-diameter sleeve holding member (spring washer) 104 and a plug (lid-shaped) are provided at the open end of the small-diameter sleeve 103. Body) 10
5 is attached. The small-diameter sleeve 103 is fixed to the inner periphery of the large-diameter sleeve 102 by caulking and fixing the plug 105 and the large-diameter sleeve 102.
For this reason, a dedicated component (spring washer 104) for fixing the small diameter sleeve 103 to the large diameter sleeve 102.
Since the plug 105) is required, the number of parts constituting the pressure regulating valve 101 is increased, and there is a problem that the cost is increased.

Looking at the dimensional relationship between the large-diameter sleeve 102 and the small-diameter sleeve 103, the valve clearance between the large-diameter sleeve 102 and the small-diameter sleeve 103 and the coaxiality are added to the small-diameter sleeve 103 and the spool 106. It is set between the small-diameter land portion 107. That is, it is necessary to increase the clearance, but there has been a problem that the increase in the clearance increases the oil leakage flow rate.

[0006]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a pressure regulating valve capable of reducing the number of parts and reducing costs by eliminating a dedicated part for fixing a small diameter sleeve to a large diameter sleeve. is there. Another object of the present invention is to provide a pressure regulating valve which can be configured without increasing the clearance between the small diameter sleeve and the spool.

[0007]

According to the first aspect of the present invention, a small-diameter sleeve in which the lid and the cylindrical wall are integrated is provided with a spool in the large-diameter sleeve from the open end of the large-diameter sleeve. After the insertion, the small-diameter sleeve is inserted into the large-diameter sleeve from the open end of the large-diameter sleeve, and the cylindrical wall of the small-diameter sleeve is fixed to the inner periphery of the large-diameter sleeve. Spring washers, plugs, etc.) become unnecessary. As a result, the number of components constituting the pressure regulating valve can be reduced, so that the product cost of the pressure regulating valve can be reduced.

According to the second aspect of the present invention, the cylindrical wall of the small-diameter sleeve is fixed or press-fitted to the inner periphery of the large-diameter sleeve to fix the cylindrical wall of the large-diameter sleeve to the cylindrical wall of the small-diameter sleeve. Since the backlash (clearance) can be eliminated, the clearance between the cylindrical wall portion of the small diameter sleeve and the small diameter portion of the spool does not increase. Thereby, the leakage flow rate from the clearance between the cylindrical wall portion of the small diameter sleeve and the small diameter portion of the spool can be reduced. Also,
According to the third aspect of the present invention, a small-diameter sleeve that requires very high precision is manufactured by metal injection molding, so that a small-diameter sleeve that requires very high precision can be manufactured at low cost and with variations. And can be easily processed.

According to the fourth aspect of the present invention, the second spool constituting the three-port switching valve is built in the first spool of the pressure regulating valve, so that the second spool receives the pilot pressure and the feedback force. A pressure regulating valve having variable characteristics capable of switching between a control pressure proportional to the pilot pressure and a maximum pressure equal to the supply pressure by switching the hydraulic chamber that causes the pressure to communicate with either the hydraulic circuit or the drain can be configured. .

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [Configuration of First Embodiment] FIGS. 1 to 4 show a first embodiment of the present invention. FIG. It is a figure showing an electromagnetic compound control valve.

The hydraulic control device for an automatic transmission according to the present embodiment includes a hydraulic circuit (output circuit) which
By incorporating the sub-spool 4 constituting a port switching valve, the pilot pressure is received by the sub-spool 4 and a feedback oil chamber (hydraulic chamber) 1 that generates a feedback force
5 is switched to communicate with either the hydraulic circuit or the drain, and the hydraulic circuit switches between an output hydraulic pressure proportional to the pilot hydraulic pressure and an output hydraulic pressure equal to the supply pressure (line pressure) of the supply pressure source (hydraulic source). Control valve with variable characteristics capable of adjusting pressure (corresponding to pressure regulating valve of the present invention)
1 is provided with a hydraulic system circuit capable of supplying hydraulic oil via the hydraulic system. The hydraulic circuit is an oil passage that connects a control valve 1 with a hydraulic servo that connects and drives a hydraulic engagement element (for example, a clutch) of the automatic transmission of the vehicle.

In the present embodiment, a multi-plate friction clutch for selectively obtaining gears having different speed ratios between an input shaft and an output shaft of an automatic transmission mounted on a vehicle is used as a hydraulic engagement element. I'm using As a supply pressure source, an oil pump that is driven to rotate by an engine and discharges hydraulic oil sucked from an oil reservoir through an oil strainer to a supply pressure (line pressure) oil passage is used. In the present embodiment, a drain (low pressure) oil passage communicating with the first to third drains such as an oil reservoir provided in the oil pan is provided. Here, in the present embodiment, a pilot valve (pilot pressure control valve, linear solenoid valve) as an electromagnetic actuator for driving the control valve 1 is added to the control valve 1 having variable characteristics.
0 is adopted as an electromagnetic compound control valve.

The control valve 1 includes a cylindrical large-diameter sleeve 2 housed in a concave portion provided at a predetermined position of a valve body (not shown) forming a hydraulic system circuit of the automatic transmission, and a large-diameter sleeve. A cylindrical main spool 3 slidably housed in a sleeve 2;
A sub-spool 4 slidably housed therein, a small-diameter sleeve 5 fixed to the inner circumference at one end of the large-diameter sleeve 2,
A first spring 11 biases the main spool 3 to a first position (initial position), and a second spring 12 biases the sub spool 4 to a first position (initial position).

Further, the large-diameter sleeve 2 and the main spool 3
An output pressure oil chamber (circumferential groove formed on the outer periphery of the main spool 3) 14 is formed between them. A feedback oil chamber (a circumferential groove formed on the outer periphery of the main spool 3) 15 is formed between the large diameter sleeve 2 and the main spool 3. Furthermore, large diameter sleeve 2
Between the second spool oil chamber 16 and the main spool 3.
Are formed.

Large-diameter sleeve 2 of control valve 1
Is housed in a concave portion provided at a predetermined position of a valve body forming a hydraulic system circuit of the automatic transmission, and has a larger inside diameter than the small-diameter sleeve 5, and constitutes a housing of the control valve 1. The large-diameter sleeve 2 has a supply pressure port (corresponding to an input port of the present invention) 20 communicating with the supply pressure oil passage of the supply pressure source, and the first and second ports.
First and second drain ports 21 and 22 communicating with the drain oil passage of the drain, and a clutch pressure output port (corresponding to an output port of the present invention) 24 communicating with the hydraulic circuit are provided. A third drain port 23 is provided at one end of the large-diameter sleeve 2 of the control valve 1 for communicating the drain oil passage of the third drain with the pilot valve 10. Also, control valve 1
An open end 19 for inserting the main spool 3 and the sub-spool 4 into the large-diameter sleeve 2 is provided at the other end (tip) of the large-diameter sleeve 2.

The large diameter sleeve 2 has a pilot pressure input port 25 communicating with the pilot valve 10 and a modulator pressure input port 26 communicating the modulator pressure supply oil passage of the modulator valve with the pilot valve 10. I have. The modulator valve is a pressure control valve that generates a modulator pressure (for example, 0.6 MPa) lower than the supply pressure (line pressure) in the modulator pressure supply oil passage. A first stopper 27 that defines a first position of the main spool 3 is provided on the inner wall surface of the large-diameter sleeve 2 of the control valve 1. The large-diameter sleeve 2 has a cylindrical wall 28 for supporting the large-diameter lands 33 and 34 of the main spool 3 slidably in the axial direction, and a small-diameter land 35 of the main spool 3 in the axial direction. A cylindrical wall portion 29 for slidably supporting is provided.

The main spool 3 corresponds to the first spool of the present invention, and is a three-port switch that switches the hydraulic circuit with the large-diameter sleeve 2 so as to communicate with either the supply pressure source or the first drain. Configure a switching valve. This main spool 3 has an axial cylindrical hole 30 inside,
When the pilot oil pressure acting on one end rises and overcomes the biasing force of the second spring 12, the pilot oil moves to the left in the figure (the direction in which the pilot oil pressure acts). At one end of the cylindrical hole 30, a sub-spool stopper 31 that defines an initial position (first position) of the sub-spool 4 is provided.

On the outer circumference of the main spool 3, large-diameter lands (corresponding to the large-diameter portion of the present invention) 33, 34 having large outer diameters from one end to the other end are provided. A small-diameter land portion (corresponding to the small-diameter portion of the present invention) 35 having an outer diameter smaller than the diameter land portions 33 and 34 is formed. The large-diameter lands 33 and 34 are portions for adjusting the opening of the first drain port 21 and the supply pressure port 20 formed in the large-diameter sleeve 2. The first position of the main spool 3 is defined by locking the large-diameter land portion 33 to the first stopper 27, and the large-diameter land portion 3
4 is locked by a second stopper 47 to be described later.
Position is defined.

The cylindrical wall of the main spool 3 has an internal output port 38 communicating the clutch pressure output port 24 with the cylindrical hole 30, the feedback oil chamber 15 and the cylindrical hole 30.
And a drain port 40 that connects the second drain port 22 and the cylindrical hole 30 are formed. The internal output port 38
Is open in a concave portion between the large-diameter lands 33 and 34. The feedback port 39 is opened between the large land portion 34 and the small land portion 35. Further, a drain port 40 communicating the second drain port 22 and the cylindrical hole 30 is opened at the other end of the main spool 3. The main spool 3 and the sub-spool 4 of this embodiment are arranged coaxially with the solenoid shaft 56 and the pilot pressure control spool 57.

The sub-spool 4 corresponds to the second spool of the present invention, and constitutes a three-port switching valve for switching the feedback oil chamber 15 so as to communicate with either the hydraulic circuit or the second drain. This subspool 4
Is slidably housed in the cylindrical hole 30 of the main spool 3, and when the pilot oil pressure acting on one end rises and overcomes the urging force of the second spring 12, the left direction in the drawing (the direction in which the pilot oil pressure acts) Go to). A sub spool stopper 31 is provided at one end of the sub spool 4.
An annular plate-shaped retaining ring 41 is attached to the ring. Land portions 42 and 43 are provided on the outer periphery of the sub-spool 4 from one end to the other end. The cylindrical hole 30 is formed between the concave portion formed between the land portions 42 and 43 and the inner wall surface of the cylindrical wall portion of the main spool 3.

The feedback oil chamber 15 corresponds to the hydraulic chamber of the present invention, and includes the inner wall surface and the convex wall of the cylindrical wall of the large-diameter sleeve 2 and the large-diameter land portion 34 and the small-diameter land portion 35 of the main spool 3. And a counter pressure chamber for applying a thrust to the large-diameter land portion 34 of the main spool 3 in a direction (rightward in the figure) facing the pilot hydraulic pressure. When the sub-spool 4 is in the first position, a clutch pressure, which is an output oil pressure, is guided to the feedback oil chamber 15. When the sub spool 4 is in the first position, the feedback oil chamber 15 communicates with the drain oil passage of the second drain.

First spring 1 of control valve 1
1 has one end held by a step provided at the other end of the main spool 3, and the other end held by a small-diameter sleeve 5.
The first spring 11 is a coil spring that applies a biasing force to the main spool 3 in a direction (rightward in the figure) facing the pilot hydraulic pressure. One end of the second spring 12 of the control valve 1 is held by a retaining ring 41 fixed to one end of the sub-spool 4, and the other end is held by an inner circumferential projection provided at one end of the sub-spool 4. . The second spring 12 is a coil spring that applies an urging force in a direction (rightward in the drawing) facing the pilot hydraulic pressure to the sub-spool 4. In the present embodiment, the biasing force of the second spring 12 is set such that the pilot oil pressure is 0.5 MPa and the output oil pressure is switched.

A small-diameter sleeve 5 manufactured by cutting, metal injection molding, or the like is inserted into the inner periphery of a cylindrical wall portion (large-diameter sleeve portion) 29 on the open end 19 side of the large-diameter sleeve 2 of the control valve 1. Have been. As shown in FIGS. 1 to 3, the small-diameter sleeve 5 is a housing having an inner diameter smaller than that of the large-diameter sleeve 2, and a lid (retainer, plug) 44 for setting a spring load of the first spring 11. And a cylindrical wall portion (small diameter sleeve portion) 45 extending in the axial direction from the outer peripheral end of the lid portion 44 and fitted to the inner periphery of the large diameter sleeve 2. At the center of the lid 44, the drain port 4
0 and second drain oil chamber 16 and second drain port 2
2 is open.

The small-diameter sleeve 5 is caulked by the caulking portion 2a provided at the tip of the cylindrical wall portion 29 of the large-diameter sleeve 2, so that the lid portion 44 and the cylindrical wall portion 45 are fixed. A second stopper 47 that defines a second position of the main spool 3 is provided at one end of the cylindrical wall portion 45. The lid 44 partially closes an opening formed in the open end 19 of the large-diameter sleeve 2. In addition, on the inner periphery of the cylindrical wall portion 45, an inner peripheral convex portion 48 is provided so as to protrude more toward the center axis than the inner periphery of the cylindrical wall portion 29 on the opening end 19 side of the large-diameter sleeve 2. A small-diameter land portion 35 of the main spool 3 is slidably supported in the axial direction.

FIG. 2 is a view showing the dimensional relationship among the large-diameter sleeve 2, the main spool 3, and the small-diameter sleeve 5. As shown in FIG. In this embodiment, the clearance (gap) δ1 between the large-diameter land portion 34 of the main spool 3 and the cylindrical wall portion 28 of the large-diameter sleeve 2, the cylindrical wall portion 29 of the large-diameter sleeve 2 and the cylindrical wall portion 45 of the small-diameter sleeve 5 (Gap) δ2 between the large-diameter sleeve 2 and the small-diameter sleeve 5
3, the clearance (gap) δ4 between the small-diameter land 35 of the main spool 3 and the inner peripheral projection 48 of the cylindrical wall 45 of the small-diameter sleeve 5 is expressed by the following equation (1).

(Equation 1) However, δ1 is about 20 to 30 μm, δ3 is 10 to 20 μm
m.

In the present embodiment, as shown in FIG. 3A, the lid 44 for partially closing the opening of the large-diameter sleeve 2 with the small-diameter sleeve 5 and the large-diameter sleeve 2 A cylindrical wall portion 45 fitted on the inner periphery of the cylindrical wall portion 29 is integrated, a communication hole 46 is provided in a central portion of the lid body portion 44, and an inner peripheral convex portion 48 is provided on an inner periphery of the cylindrical wall portion 45. , FIG. 3 (b)
As shown in the figure, the entire inner peripheral surface of the cylindrical wall portion 45 of the small-diameter sleeve 5 is provided so as to protrude more toward the central axis than the inner peripheral surface of the cylindrical wall portion 29 on the opening end 19 side of the large-diameter sleeve 2. The small-diameter land portion 35 of the spool 3 may be slidably supported in the axial direction. In this case, the small-diameter sleeve 5 can be formed by metal injection molding, which is a metal forming method, and the manufacturing cost of the control valve 1 can be reduced.

The pilot valve 10 includes a cylindrical yoke 51 fixed to one end of the large-diameter sleeve 2 of the control valve 1, a coil bobbin 52 disposed on the inner periphery of the yoke 51, and an outer periphery of the coil bobbin 52. , And a solenoid coil 53 wound therearound. Further, a stator core (fixed iron core) 54 and a moving core (movable iron core, plunger) 55 arranged on the inner peripheral side of the coil bobbin 52, a solenoid shaft 56 that operates integrally with the moving core 55, the main spool 3, A pilot pressure control spool 57 that is arranged coaxially with the spool 4 and the solenoid shaft 56 and can move in conjunction with the solenoid shaft 56
And a leaf spring 58 for centering the moving core 55
And a cover 59 for closing an opening on one end side of the yoke 51, and a third spring 13 for urging in a direction opposite to the direction of the pilot hydraulic pressure.

The large-diameter sleeve 2 has a plug 62
Is provided in the pilot pressure oil chamber 63.
Further, a pilot pressure feedback oil chamber 64 is formed between the pilot pressure control spool 57 and the large diameter sleeve 2. The pilot pressure control spool 57 has an axial hole 65 and moves leftward in the figure (direction in which pilot hydraulic pressure acts) when the pressing force of the solenoid shaft 56 overcomes the urging force of the third spring 13. Also,
An internal control port 66 for communicating the axial hole 65 with either the third drain port 23 or the modulator pressure input port 26 is formed in the cylindrical wall of the pilot pressure control spool 57. A pilot pressure feedback port 67 communicating with the feedback oil chamber 64 is formed.

The third spring 13 of the pilot valve 10 has one end held by the concave portion of the pilot pressure control spool 57 and the other end held by the plug 62, the moving core 55, the solenoid shaft 56, and the pilot pressure control spool. 57 is a return spring that biases 57 toward the initial position. The plug 62 is fixed by press-fitting to the inner peripheral surface on one end side of the large-diameter sleeve 2, and is for setting a set load of the third spring 13. At the center of the plug 62, a communication hole 62a that opens the pilot pressure input port 25 of the control valve 1 and the pilot pressure oil chamber 63 of the pilot valve 10 is opened. The coil bobbin 52 is a resin primary molded product formed integrally with the resin in a substantially cylindrical shape, and a resin member (resin secondary molded product) 68 resin molded on the outer periphery of the solenoid coil 53 includes a yoke 51.
A connector 70 in which a terminal (external connection terminal) 69 for electrically connecting the solenoid coil 53 and the vehicle-mounted power supply is insert-molded is integrally formed in a portion more exposed to the outside.

[Operation of First Embodiment] Next, the operation of the control valve 1 having variable characteristics according to the present embodiment will be described with reference to FIG.
This will be briefly described with reference to FIG.

When the pilot hydraulic pressure is zero, the main spool 3 and the sub-spool 4 are driven by the first and second springs 11 and 12 by the pilot pressure input port 2.
It is arranged at the first position moved to the fifth side. That is, the large-diameter land portion 33 of the main spool 3 is located at an initial position (first position) where it comes into contact with the first stopper 27, and the retaining ring 41 of the sub-spool 4 comes into contact with the sub-spool stopper 31 (first position). Position).

Then, the energization of the solenoid coil 53 of the pilot valve 10 is started, and the moving core 55 and the solenoid shaft 5
6 and the pilot pressure control spool 57 are moved to the left in the drawing, so that the pilot pressure control spool 57
The axial hole 65 in the inside communicates with the modulator pressure input port 26, the hydraulic oil flows into the pilot pressure oil chamber 63, and the pressure in the pilot pressure oil chamber 63, so-called pilot oil pressure, rises.

At this time, the pilot pressure feedback oil chamber 64 is in the path of the modulator pressure input port 26 → the internal control port 66 → the axial hole 65 → the pilot pressure feedback port 67 or the pilot pressure oil chamber 63 → the axial hole 65 → The pilot pressure feedback port 67 communicates with the modulator pressure supply oil passage of the modulator valve through the path of the pilot pressure feedback port, guides the pilot hydraulic pressure, and generates a thrust in the opposite direction (rightward in the figure) to the thrust of the pilot hydraulic pressure applied to the pilot pressure control spool 57. generate. The pilot pressure control spool 57 moves to a position where “the sum of the feedback force in the pilot pressure feedback oil chamber 64 and the urging force of the third spring 13” and the “pilot oil pressure in the pilot pressure oil chamber 63” are balanced. As shown in the graph of FIG. 4, it is possible to generate a pilot oil pressure according to the current value to the solenoid coil 53.

Here, the energization of the solenoid coil 53 of the pilot valve 10 is started, and the pilot oil pressure in the pilot pressure oil chamber 63 rises. The operating position of the sub-spool 4 is maintained at the first position by overcoming the leftward thrust by the hydraulic pressure, and when the predetermined hydraulic pressure is exceeded, the operating position of the sub-spool 4 is shifted to the second position on the second spring 12 side. change. The biasing force of the second spring 12 is such that the pilot hydraulic pressure is 0.5 MPa,
It is set to switch to the output oil pressure.

Therefore, in the [pilot oil pressure range from zero to 0.5 MPa (relatively low pressure region)], the biasing force of the second spring 12 overcomes the leftward thrust by the pilot oil pressure, and the sub spool 4 Maintained in one position. At this time, the feedback oil chamber 15
Is the clutch pressure output port 24 → the output pressure oil chamber 14 → the internal output port 38 → the cylindrical hole 30 → the feedback port 3
Nine paths communicate with the hydraulic circuit, and a clutch pressure, which is an output hydraulic pressure, is guided.

Therefore, the main spool 3 is located at a position where "the thrust by the pilot oil pressure acting leftward in the figure" and "the sum of the feedback force by the output oil pressure acting rightward in the figure and the urging force of the first spring 11" are balanced. Go to
The output hydraulic pressure supplied to the hydraulic servo of the clutch via the hydraulic circuit is adjusted to an output hydraulic pressure proportional to the pilot hydraulic pressure, as shown in the graph of FIG. The output hydraulic pressure (main control pressure: Pout) at this time is represented by the following equation (2), and a clutch pressure lower than the output hydraulic pressure in the case of the conventional pressure regulating valve can be realized. Can be regulated precisely and precisely.

(Equation 2)

Here, Sp is the area for receiving the pilot oil pressure in the main spool 3, Sf is the area for receiving the oil pressure in the feedback oil chamber 15 in the main spool 3, Ppilot is the pilot oil pressure, and Fs1 is the first spring 11 Sp / Sf is the pressure amplification ratio.

[Pilot oil pressure is 0.5 MPa
In this case, the pilot hydraulic pressure received at one end of the sub-spool 4 overcomes the urging force of the second spring 12, and the sub-spool 4 moves to the second position on the second spring 12 side. At this time, the feedback oil chamber 15 communicates with the drain oil path of the second drain through the path of the feedback port 39 → the cylindrical hole 30 → the drain port 40 → the second drain oil chamber 16 → the second drain port 22.

Accordingly, since the feedback force of the feedback oil chamber 15 becomes zero, the main spool 3 moves until it comes into contact with the second stopper 47 by the leftward thrust by the pilot oil pressure, and the supply pressure port 20 and the clutch pressure. Since the output port 24 communicates with the output port 24, the output hydraulic pressure output to the hydraulic circuit is set to the control pressure equal to the supply pressure of the supply pressure source as shown in the graph of FIG.

[Effects of the First Embodiment] As described above, during the engagement control that requires precise pressure control of the clutch, the clutch pressure is controlled via the control valve 1 and when the engagement control ends. Even in the case where a high supply pressure is directly supplied to the clutch so that the clutch does not slip even with a large torque, the shift valve is separately provided from the control valve 1 by the compact control valve 1 as in the present embodiment. Since no switching valve is required, the number of parts can be reduced.

The hydraulic circuit (output circuit) has a variable characteristic capable of switching between an output oil pressure proportional to the pilot oil pressure and an output oil pressure equal to the supply pressure (line pressure) of the supply pressure source (oil pressure source). In the valve 1, the control valve 1 and the pilot valve 10 are arranged coaxially, and the large-diameter sleeve 2 of the control valve 1 is shared with the pilot valve 10. As a result, the size of the entire hydraulic system circuit of the automatic transmission can be significantly reduced, and the number of parts can be reduced. Thereby, the cost of the hydraulic system circuit of the automatic transmission can be reduced.

The small-diameter sleeve 5 fixed to the distal end of the large-diameter sleeve 2 of the control valve 1 partially closes the opening formed on the distal end side of the cylindrical wall portion 29 of the large-diameter sleeve 2. Cover 44 and large-diameter sleeve 2
The small-diameter sleeve 5 is fixed to the inner periphery of the cylindrical wall portion 29 on the opening end 19 side of the large-diameter sleeve 2 by integrating the cylindrical wall portion 45 fitted to the inner periphery of the cylindrical wall portion 29. Dedicated parts (spring washers, plugs, etc.) become unnecessary. Thus, the number of parts constituting the control valve 1 can be reduced, and the product cost of an electromagnetic compound control valve in which the control valve 1 and the pilot valve 10 are integrated can be reduced.

The small-diameter sleeve 103 of the pressure regulating valve 101 shown in FIG. 7 has a predetermined shape obtained by cutting a cylindrical metal member using a cutting tool.
As for No. 3, very high dimensional accuracy is desired in order to limit the flow rate of hydraulic oil leaking from the clearance between the small diameter sleeve 103 and the small diameter land portion 107 of the spool 106. Therefore, in order to form the conventional small-diameter sleeve 103,
Processing man-hours increased, and costs increased.

However, in this embodiment, the small-diameter sleeve 5 that requires high precision is manufactured by metal injection molding, which is a metal forming method that does not require cutting. The size of the small-diameter sleeve 5 does not vary due to the wear of the small-diameter sleeve 5, and the small-diameter sleeve 5 requiring high accuracy can be easily processed while suppressing the variation. As a result, the small-diameter sleeve 5 can be manufactured at low cost, so that the product cost of the electromagnetic compound control valve in which the control valve 1 and the pilot valve 10 are integrated can be reduced.

[Structure of the Second Embodiment] FIG. 5 shows a second embodiment of the present invention and is a view showing a dimensional relationship among a large diameter sleeve, a main spool and a small diameter sleeve.

The cylindrical wall portion 45 of the small diameter sleeve 5 according to the present embodiment.
A cylindrical wall portion 29 on the opening end side of the large-diameter sleeve 2
A male screw part (outer peripheral screw part) 72 that is screwed into a female screw part (inner peripheral screw part) 71 formed on the inner peripheral surface is formed.
After inserting the main spool 3 and the sub-spool 4 into the cylindrical wall portion 29 from the open end of the large-diameter sleeve 2,
The cylindrical wall portion 45 of the small diameter sleeve 5 is fastened and fixed to the cylindrical wall portion 29 on the opening end side of the large diameter sleeve 2.

Here, in the first embodiment, the large-diameter land portion 34 of the main spool 3 and the cylindrical wall portion 28 of the large-diameter sleeve 2
Δ1, the clearance δ2 between the cylindrical wall portion 29 of the large-diameter sleeve 2 and the cylindrical wall portion 45 of the small-diameter sleeve 5, and the deviation amount δ of coaxiality between the large-diameter sleeve 2 and the small-diameter sleeve 5.
3, the clearance δ4 between the small-diameter land portion 35 of the main spool 3 and the inner peripheral convex portion 48 of the cylindrical wall portion 45 of the small-diameter sleeve 5 is expressed as δ4 =
δ1 + δ2 + δ3, and the small-diameter land portion 35 of the main spool 3 and the inner peripheral convex portion 48 of the cylindrical wall portion 45 of the small-diameter sleeve 5
And the clearance δ4 between them increases.

For this reason, there arises a problem that the flow rate of the hydraulic oil leaking from the clearance δ4 becomes large. Therefore, as in the present embodiment, the cylindrical wall portion 45 of the large-diameter sleeve 2 is fixed by screws to the cylindrical wall portion 45 of the small-diameter sleeve 5 on the opening end side of the large-diameter sleeve 2.
The clearance δ2 between the small diameter sleeve 5 and the cylindrical wall portion 45 can be set to 0, δ4 = δ1 + δ3, and δ4 can be reduced.

Therefore, as in the present embodiment, the cylindrical wall 45 of the small-diameter sleeve 5 is screw-fixed to the cylindrical wall 29 of the large-diameter sleeve 2 on the opening end side. Since the clearance δ2 between the cylindrical wall portion 29 and the cylindrical wall portion 45 of the small-diameter sleeve 5 can be made zero, the clearance between the inner peripheral convex portion 48 of the cylindrical wall portion 45 of the small-diameter sleeve 5 and the small-diameter land portion 35 of the main spool 3 can be reduced. Can be reduced. Thereby, the cylindrical wall portion 45 of the small diameter sleeve 5 is formed.
Inner circumferential projection 48 and the small diameter land 35 of the main spool 3
, The leakage flow rate of the hydraulic oil from the clearance δ4 can be reduced.

[Structure of Third Embodiment] FIG. 6 shows a third embodiment of the present invention and is a view showing a dimensional relationship among a large diameter sleeve, a main spool and a small diameter sleeve.

The cylindrical wall portion 45 of the small diameter sleeve 5 according to the present embodiment.
A cylindrical wall portion 29 on the opening end side of the large-diameter sleeve 2
A press-fit portion 73 for press-fitting into the inner peripheral surface of is formed. After the main spool 3 and the sub-spool 4 are inserted into the cylindrical wall portion 29 from the open end of the large-diameter sleeve 2, the press-fit portion 73 of the cylindrical wall portion 45 of the small-diameter sleeve 5 is moved to the open end side of the large-diameter sleeve 2. It is fixed by being press-fitted into the cylindrical wall portion 29. Thereby, the same operation and effect as the second embodiment can be achieved.

[Other Embodiments] In the first to third embodiments, an adhesive may be inserted between the cylindrical wall portion 45 of the small diameter sleeve 5 and the cylindrical wall portion 29 of the large diameter sleeve 2 for adhesion. In the second and third embodiments, the cylindrical wall portion 45 of the small-diameter sleeve 5 may be fixed by caulking with the caulking portion 2a of the large-diameter sleeve 2 as in the first embodiment.

The hydraulic engagement element of the automatic transmission referred to in the present invention specifically connects the components of the planetary gear set disposed between the input shaft and the output shaft of the automatic transmission to each other. A hydraulic conical clutch, a hydraulic multi-disc clutch (multiple disc clutch), or a hydraulic conical clutch, a hydraulic multi-disc clutch, or a band brake for connecting a component to an input shaft or an output shaft. Or, it is a hydraulic multi-disc brake (multiple disc brake) for fixing components to a fixing member such as an automatic transmission case.

In this embodiment, an example in which the hydraulic servo for driving the hydraulic engagement element is applied to the hydraulic servo for connecting and driving the hydraulic multi-plate clutch has been described. The present invention may be applied to a hydraulic servo for driving a band brake or a hydraulic multi-plate brake. Also,
In the present embodiment, an example in which the hydraulic circuit is applied to a hydraulic circuit that connects a hydraulic servo that connects and drives a hydraulic multi-plate clutch of an automatic transmission of a vehicle to the control valve 1 has been described. The present invention may be applied to a hydraulic circuit that connects the control valve 1 with a hydraulic servo that drives the multiple disc brake.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an electromagnetic compound control valve in which a pilot valve is integrated with a control valve having variable characteristics (first embodiment).

FIG. 2 is an explanatory diagram showing a dimensional relationship among a large-diameter sleeve, a main spool, and a small-diameter sleeve (first embodiment).

FIGS. 3A and 3B are cross-sectional views showing a small-diameter sleeve (first embodiment).

FIG. 4 is a graph showing a change in pilot oil pressure and an output oil pressure of a control valve with respect to a current supplied to the pilot valve (first embodiment).

FIG. 5 is an explanatory diagram showing a dimensional relationship among a large-diameter sleeve, a main spool, and a small-diameter sleeve (second embodiment).

FIG. 6 is an explanatory diagram showing a dimensional relationship among a large-diameter sleeve, a main spool, and a small-diameter sleeve (third embodiment).

FIG. 7 is a sectional view showing an electromagnetic compound control valve in which a pilot pressure control valve is integrated with a pressure regulating valve having variable characteristics (prior art).

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 control valve (pressure regulating valve) 2 large diameter sleeve 3 main spool (first spool) 4 sub spool (second spool) 10 pilot valve 15 feedback oil chamber (hydraulic chamber) 19 open end 20 supply pressure port (input port) 21 1st drain port 22 2nd drain port 23 3rd drain port 24 Clutch pressure output port (output port) 27 1st stopper 33 Large diameter land part (large diameter part) 34 Large diameter land part (large diameter part) 35 Small diameter land Part (small diameter part) 44 lid part 45 cylinder wall part 46 communication hole 47 second stopper

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3H051 AA10 BB10 CC11 EE08 FF15 3H053 AA25 AA26 BD10 DA11 3H106 DA23 DA33 DB02 DB12 DB23 DB32 DC09 DD05 EE34 JJ03 KK17 3J552 MA01 NA01 NB01 PA65 QA15B QB08

Claims (4)

[Claims] 1. A spool having a large-diameter portion having a large diameter, a small-diameter portion having a smaller diameter than the large-diameter portion, and having an axially movable spool, and an open end for inserting the spool therein. A cylindrical large-diameter sleeve for supporting the large-diameter portion of the spool so as to be slidable in the axial direction; and a large-diameter sleeve inserted into the large-diameter sleeve from an open end of the large-diameter sleeve. A cylindrical small-diameter sleeve disposed so as to protrude more toward the center axis than the inner circumference of the spool, and for supporting the small-diameter portion of the spool slidably in the axial direction. A pressure regulating valve, comprising: a lid portion for partially closing an open end of a diameter sleeve; and a cylindrical wall portion fixed to an inner periphery of the large diameter sleeve. 2. The pressure regulating valve according to claim 1, wherein the cylindrical wall of the small-diameter sleeve is fixedly fastened or press-fitted to the inner periphery of the large-diameter sleeve. 3. The pressure regulating valve according to claim 1, wherein the small-diameter sleeve is manufactured by metal injection molding. 4. The pressure regulating valve according to claim 1, wherein the large-diameter sleeve has an input port communicating with a supply pressure source.
An output port communicating with a hydraulic circuit, and a drain port communicating with a drain, wherein the spool is slidably housed in the large-diameter sleeve, and moves in the axial direction by receiving a thrust force by pilot pressure. A first spool that switches the hydraulic circuit so as to communicate with either the supply pressure source or the drain, and is slidably housed in the first spool and receives a thrust force caused by pilot pressure. And a second spool that switches an oil pressure chamber that moves axially and applies a thrust to the first spool in a direction opposite to the pilot pressure to communicate with either the hydraulic circuit or the drain. And pressure regulating valve.