JP6156095B2 - Spool control valve - Google Patents

Description

  The present invention relates to a spool control valve that performs switching control of a supply / discharge (input, output, discharge, feedback) port of a fluid such as oil.

Conventionally, for example, a sleeve having a cylindrical peripheral wall formed with a plurality of oil supply / discharge ports through which oil used in a hydraulic circuit of an automatic transmission flows in and out is fitted into the peripheral wall of the sleeve so as to be reciprocally slidable. A spool that is supported together, a return spring that biases the spool toward the base end side (solenoid side) of the sleeve, and a solenoid actuator that drives the spool to the tip end side (spring side) in the axial direction of the peripheral wall of the sleeve (hereinafter referred to as solenoid) ) Is well known.
The solenoid drives the spool to one side in the axial direction from the proximal end side of the circumferential wall of the sleeve toward the distal end side of the circumferential wall of the sleeve by attracting the movable core to the magnetic attraction portion of the fixed core by the magnetic force generated by the coil. It is configured as follows.

Further, as shown in FIGS. 8 and 9, a guide hole through which the spool 101 slides directly is provided in the peripheral wall of the sleeve.
The plurality of oil supply / discharge ports communicate the inside and the outside of the peripheral wall of the sleeve 102. These oil supply / discharge ports are an input (IN) port 103 for inputting oil input pressure from the oil pump to the inside of the guide hole, and the oil input pressure is adjusted to a predetermined output pressure and output from the inside of the guide hole. And an output (DRAIN) port 105 for discharging oil flowing in from the IN port 103 or the OUT port 104 to a low pressure side such as an oil pan.

Incidentally, foreign matter such as metal powder (contamination) generated due to wear of the transmission mechanism of the automatic transmission is mixed in the oil flowing into the peripheral wall of the sleeve 102 of the electromagnetic spool control valve. When such foreign matter flows into the guide hole together with the oil via the IN port 103 or the OUT port 104, the sliding between the land (111 to 113) of the spool 101 and the peripheral wall of the sleeve 102 is particularly important. When foreign matter enters the clearance, smooth (smooth) movement of the spool 101 with respect to the peripheral wall of the sleeve 102 is hindered, making it difficult to perform appropriate hydraulic control.
Therefore, an electromagnetic spool control valve in which an IN port filter (hereinafter referred to as a strainer) 121 for preventing foreign matter from entering the inside of the guide hole is provided in an opening provided on the radially outer side of the IN port 103 has been proposed ( For example, see Patent Document 1).

The strainer 121 described in Patent Document 1 is formed in an arc shape corresponding to the opening shape of the IN port 103 so as to cover the opening portion of the IN port 103, and is provided at both ends in the circumferential direction of the strainer 121. The inwardly bent portion is fitted into the groove on the outer periphery of the peripheral wall of the sleeve 102 to be attached to the outer periphery of the peripheral wall of the sleeve 102.
Here, a communication chamber provided in the spool 101 as an F / B flow path for sending the oil output pressure from the communication chamber (oil chamber) 114 communicating with the OUT port 104 to the feedback (F / B) chamber 115. A slanted slant hole 116 that obliquely penetrates the large-diameter land 112 that partitions 114 and the F / B chamber 115 is formed.

However, in the electromagnetic spool control valve described in Patent Document 1, since the OUT port filter is not attached, it is not possible to prevent entry of foreign matter contained in the oil flowing into the communication chamber 114 from the OUT port 104. There is.
Further, since it is necessary to drill the slanted slant hole 116 in the large-diameter land 112 of the spool 101, there is a problem that the manufacturing cost of the electromagnetic spool control valve becomes expensive.
Further, there is a problem that the reliability of the fixing method in which the bent portion of the strainer 121 is fixed in the outer peripheral wall of the sleeve 102 by fitting the bent portion in the concave groove is low.

By the way, in the oil passage that connects the oil pump and the IN port 103, pressure fluctuation of the oil discharge pressure (pressure pulsation of a predetermined frequency: hereinafter referred to as oil pulse) is generated due to the pressure feeding operation of the oil pump. When the amplitude of the oil pulse flowing from the IN port 103 into the communication chamber is large when the IN port 103 and the OUT port 104 are in communication, the oil pulse output from the OUT port 104 to the clutch or brake is also growing. In such a case, the feedback hydraulic pressure of the oil that is guided from the OUT port 104 to the F / B chamber 115 through the F / B oil passage (116) and acts on the large-diameter land 112 of the spool 101, that is, the IN port 103 and the OUT The influence of the oil vein on the F / B force biased toward the side (arrow direction shown in the figure) that reduces the communication area with the port 104 increases.
The electromagnetic spool control valve (conventional example 1) described in Patent Document 1 is in the hydraulic path from the oil pump to the F / B chamber 115 through the oil passage → IN port 103 → communication chamber 114 → spool slant hole 116. Only one strainer 121 is installed.

Therefore, in the structure of the conventional example 1, since the discharge pressure of the oil discharged from the oil pump is guided to the F / B chamber 115 through only one of the strainers 121 covering the opening of the IN port 103, oil feedback The oil vein for hydraulic pressure cannot be sufficiently suppressed, and stable characteristics cannot be obtained.
That is, since only one strainer 121 is installed in the hydraulic path from the oil pump to the F / B chamber 115, the effect of damping the discharge pressure pulsation of the oil pump is small, and the oil discharged from the OUT port 104 is discharged. There is a problem that the followability (characteristic) from the rise of pressure to the target value of the feedback hydraulic pressure deteriorates.
There is also a problem that delicate hydraulic control cannot be performed.

On the other hand, an electromagnetic spool control valve has been proposed in which an OUT port filter (hereinafter referred to as strainer) 122 is installed in an opening provided on the radially outer side of the OUT port 104 to prevent foreign matter from entering the inside of the guide hole. For example, see Patent Document 2).
The strainer 122 described in Patent Document 2 is formed in an arc shape corresponding to the opening shape of the OUT port 104 so as to cover the opening portion of the OUT port 104, and is a filter provided at both ends in the circumferential direction of the strainer 122. A hook bent at a substantially right angle inside is fitted into a recess on the outer periphery of the peripheral wall of the sleeve 102, so that the hook is attached to a mounting groove on the outer peripheral wall of the sleeve 102.

Note that the oil output pressure is spooled on the peripheral wall of the sleeve 102 for the purpose of preventing fluctuations in the output pressure of oil output from the OUT port 104 due to fluctuations in the input pressure of oil input from the IN port 103. A feedback (F / B) port 106 is also provided for effecting feedback on the outer diameter portion of 101.
Here, as an F / B flow path for sending the output pressure of oil from the communication chamber 114 communicating with the OUT port 104 to the F / B chamber 115 communicating with the F / B port 106, the oil output pressure is outside the peripheral wall of the sleeve 102. The provided F / B oil passage (117) is formed in a valve body or the like for fitting and fixing the electromagnetic spool control valve.

However, in the electromagnetic spool control valve described in Patent Document 2 (conventional example 2), since the strainer 121 is not mounted, intrusion of foreign matter contained in oil flowing from the IN port 103 into the guide hole (communication chamber). There is a problem that cannot be prevented.
Further, there is a problem that the reliability of the fixing method in which the hook of the strainer 122 is fitted into the mounting groove and fixed to the outer periphery of the peripheral wall of the sleeve 102 is low.
Further, a strainer 122 is provided in the hydraulic path from the oil pump to the oil passage → IN port 103 → communication chamber 114 → OUT port 104 → F / B oil passage (117) → F / B port 106 through the F / B port 106. Only one is installed.

Therefore, in the structure of the conventional example 2, the discharge pressure of the oil discharged from the oil pump is guided to the F / B chamber 115 through only one of the strainers 122 covering the opening of the OUT port 104, and the spool 101 is large. The oil pressure acting on the radial land 112, that is, the oil pulse against the F / B force urging to the side (arrow direction in the figure) that reduces the communication area between the IN port 103 and the OUT port 104 cannot be sufficiently suppressed. Stable characteristics cannot be obtained.
That is, since only one strainer 122 is installed in the hydraulic path from the oil pump to the F / B chamber 115, the effect of damping the discharge pressure pulsation of the oil pump is small, and the output of oil output from the OUT port 104 There is a problem that the followability (characteristic) from the rise of pressure to the target value of the feedback hydraulic pressure deteriorates.
There is also a problem that delicate hydraulic control cannot be performed.

Japanese Patent No. 3324140 JP 2013-170620 A

  An object of the present invention is to provide a spool control valve capable of improving the foreign matter resistance of an input port and an output port. Another object of the present invention is to provide a spool control valve that can reduce the manufacturing cost by eliminating the need for drilling the spool and reducing the cost of processing the spool. It is another object of the present invention to provide a spool control valve that can improve the followability (characteristic) from the rise of the output pressure of the fluid output from the output port to the target value of the feedback pressure.

According to the first aspect of the present invention (spool control valve), the first circumferential groove is formed in the first outer circumferential groove formed over the entire circumference of the sleeve so as to cover the first opening of the input port of the sleeve. A strainer is wound and attached, and a belt-like second strainer is wound and attached to a second outer circumferential groove formed over the entire circumference of the sleeve so as to cover the second opening of the output port of the sleeve .
The output port exists between the input port and the feedback port in the axial direction, and the second outer circumferential groove and the feedback port communicate with each other through an axial groove formed in the outer circumferential wall of the sleeve. .
Accordingly , foreign matter can be reliably prevented from entering the inner hole of the sleeve, so that the foreign matter resistance of the input port and the output port can be improved.
In addition, since it is not necessary to drill a hole in the spool and the processing cost of the spool can be suppressed, the manufacturing cost can be reduced.
Furthermore, followability (characteristics) from the rise of the output pressure of the fluid output from the output port to the target value of the feedback pressure (a value that can reduce the pressure fluctuation of the output pressure of the fluid output from the output port) Can be improved.

(A) is sectional drawing which showed the N / O type linear solenoid valve, (b) is an expanded sectional view of the principal part enclosed with the broken line in (a) (Example 1). (A)-(c) is the side view which showed the external appearance shape of the N / O type linear solenoid valve (Example 1). (Example 1) which is the F / B oil path of the N / O type linear solenoid valve at the time of OUT (control) pressure rise (apply evaluation). (Example 1) which is the F / B oil path of the N / O type linear solenoid valve at the time of OUT (control) pressure fall (drain evaluation). (Example 2) which is sectional drawing which showed the N / C type linear solenoid valve. (A)-(c) is the side view which showed the external appearance shape of the N / C type linear solenoid valve (Example 2). 6A is a sectional view taken along the line VII (a) -VII (a) in FIG. 6B, and FIG. 6B is a sectional view taken along the line VII (b) -VII (b) in FIG. ). It is explanatory drawing which showed the position of the spool with respect to the sleeve, and F / B oil path at the time of the output (OUT) pressure rise (applied evaluation: electromagnetic spool control valve which installed the filter for N / O type IN ports). Example 1). It is explanatory drawing which showed the position of the spool with respect to the sleeve, and F / B oil path in the time of output (OUT) pressure rise (applied evaluation: electromagnetic spool control valve which installed the filter for N / O type OUT ports). Example 2).

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

[Configuration of Example 1]
1 to 4 show a linear solenoid valve (Embodiment 1) to which a spool control valve of the present invention is applied.

The linear solenoid valve (electromagnetic spool control valve, solenoid valve) of this embodiment is installed in a hydraulic control device of an automatic transmission.
The hydraulic control device is used for shift control of an automatic transmission mounted on a vehicle such as an automobile. The hydraulic control device includes an oil pump (not shown) that sucks and pumps oil in an oil pan, a valve body (not shown) having a plurality of oil passages, and a valve body attached to the valve body. A plurality of linear solenoid valves that form a hydraulic circuit together with an oil passage of the body, and a control unit (TCU: not shown) that controls energization of the plurality of linear solenoid valves so as to realize a shift state requested by a driver or the like. I have.

The housing of the automatic transmission is configured by combining an automatic transmission case (transmission case) and an oil pan.
Inside the automatic transmission case, a torque converter including a pump, a turbine, a stator, and the like, and a multi-stage gear type transmission mechanism connected to the turbine of the torque converter are housed. The transmission mechanism includes a plurality of friction engagement elements (clutch or brake) that are engaged or released according to the hydraulic pressure supplied from the hydraulic control device.
In the automatic transmission, the shift range is switched according to the combination of engagement or release of the friction engagement elements. Thereby, the shift control of the automatic transmission is executed.

The oil pump is rotationally driven by an engine crankshaft (or an electric motor), and in an oil pan (or an oil tank) that is a storage tank in which hydraulic oil (oil) used for an automatic transmission is stored. Oil pressure generating means for sucking oil and pumping it. An oil supply passage (oil passage) is connected to the discharge side of the oil pump, and a plurality of linear solenoid valves are installed at the downstream end of the oil supply passage.
At least one of these linear solenoid valves includes a spool valve (hereinafter referred to as a spool control valve) that regulates and outputs the hydraulic pressure of hydraulic oil (oil) that is a pressure fluid, and a valve body of the spool control valve. (Valve spool: hereinafter spool 5) is constituted by a linear solenoid S which is an electromagnetic actuator for driving one side in the axial direction thereof.

  The spool control valve includes a cylindrical valve sleeve (hereinafter referred to as a sleeve) 1 that is fitted and disposed in a valve insertion groove (recessed portion) of the valve body, and foreign matter inside the inner hole (hereinafter referred to as a guide hole) 2 of the sleeve 1. Ring-shaped first and second strainers (hereinafter referred to as strainers) 3 and 4, a spool 5 fitted and supported so as to be reciprocally movable (slidable) in the guide hole 2 of the sleeve 1, and the spool 5 Is provided with a return spring 6 that urges the solenoid toward the solenoid side (base end side, rear side, default side) and an adjustment screw 7 that adjusts the spring load of the return spring 6.

  The linear solenoid S includes a magnetic plunger (movable core) 9 connected to the spool 5 through a non-magnetic shaft 8 so as to be integrally movable, and a solenoid coil (hereinafter referred to as magnetic flux) that generates magnetic flux when energized. Coil) 10, a coil inner peripheral fixed core (stator cores 11 and 12, magnetoresistive portion 13) that forms a magnetic path on the inner peripheral side of the coil 10, and a coil outer periphery that forms a magnetic path on the outer peripheral side of the coil 10. A side fixed core (bottomed cylindrical yoke 14) and an external connection connector 15 for connecting the coil 10 and an external circuit (external power supply or external control circuit: TCU) are provided.

The linear solenoid S includes a magnetic ring core (a part of a fixed core that covers the other end in the axial direction of the coil 10) 16 between the coil 10 and the bottom plate of the yoke 14, and the ring core 16 is connected to the bottom plate of the yoke 14. A wave washer 17 for generating an elastic force to be pressed to the side is provided.
The sleeve 1 is made of a nonmagnetic metal. An opening end on the base end side of the sleeve 1 is provided with a coupling end surface coupled to the linear solenoid S and an annular flange 18 extending to the outer peripheral side of the coupling end surface.

The sleeve 1 includes a cylindrical outer peripheral wall 19 that surrounds the periphery of the guide hole 2 in the circumferential direction and extends in the axial direction from the proximal end side (solenoid side) to the distal end side (spring side) of the sleeve 1. Yes. The outer peripheral wall 19 includes first to fourth peripheral walls.
A guide hole 2 having a circular cross section that extends straight in the axial direction is formed in the outer peripheral wall 19 of the sleeve 1. The guide hole 2 is a sliding hole (guide hole, inner hole) through which the spool 5 of the spool control valve supports the spool 5 so as to be slidable in the axial direction of the sleeve 1 and the spool 5 slides directly.
A plurality of oil supply / discharge ports (21 to 26) through which oil flows in and out of the outer peripheral wall 19 of the sleeve 1 are arranged in the axial direction of the guide hole 2 between the outside of the outer peripheral wall 19 of the sleeve 1 and the inside of the guide hole 2. On the other hand, it communicates in a substantially perpendicular radius (radiation) direction.

  The plurality of oil supply / discharge ports (21 to 26) are an input port (oil supply port: hereinafter referred to as IN port) 21 for inputting the input pressure of oil from the oil pump to the inside of the guide hole 2 through the first oil passage L1; An output port (hereinafter referred to as OUT port) 22 that adjusts the oil input pressure to a predetermined output pressure and outputs the oil pressure from the inside of the guide hole 2 to the hydraulic servo of the clutch (or brake) via the second oil passage L2, and the IN port And a drain (discharge) port (hereinafter referred to as DRAIN port) 23 for discharging oil flowing into the guide hole 2 from the 21 or OUT port 22 from the inside of the guide hole 2 to the oil pan through the third oil passage L3. ing.

Further, the spool control valve has a fluctuation (oil pulse) of the input pressure of oil input from the IN port 21 due to the pressure pulsation (oil pulse) of the discharge pressure of oil discharged from the oil pump. As a result, there is a problem that the output pressure fluctuation (oil pulse) of the oil output from the OUT port 22 occurs.
Therefore, as an oil supply / discharge port, the output pressure of the oil is set to the spool 5 for the purpose of preventing the fluctuation of the output pressure of the oil output from the OUT port 22 due to the fluctuation of the input pressure of the oil input from the IN port 21. The large-diameter land 41, the small-diameter land 42, and the constricted portion 44 are provided with a feedback port (hereinafter referred to as F / B port) 24. The F / B port 24 is connected via a fourth oil passage (feedback oil passage: hereinafter referred to as F / B oil passage) L4 communicating with the OUT port 22.

  Further, on the proximal end side of the outer peripheral wall 19 of the sleeve 1, lubricating oil is supplied to a plunger sliding portion (sliding clearance) between the coil inner peripheral fixed core (11 to 13) and the plunger 9. A sub-drain (discharge) port (hereinafter referred to as DRAIN port) 25 is provided. The DRAIN port 25 discharges oil from the inside of the guide hole 2 to the oil pan through a fifth oil passage (not shown).

In addition, an oil pan and a spring accommodating chamber 28 are provided on the distal end side of the outer peripheral wall 19 of the sleeve 1 in order to ensure the flow of oil in the spring accommodating chamber 28 due to the displacement of the spool 5 in the guide hole 2. A sub-drain (discharge) port (hereinafter referred to as DRAIN port) 26 for communication is provided. The DRAIN port 26 discharges oil from the inside of the guide hole 2 (spring accommodating chamber 28) to the oil pan through a sixth oil passage (not shown).
When the spool 5 is displaced from the left side (tip side) in the figure to the right side (base side) in the guide hole 2 of the outer peripheral wall 19 of the sleeve 1, the spring passes through the DRAIN port 26 from the sixth oil passage. Oil flows into the storage chamber 28.

The plunger sliding portion is provided between the sliding surface (outer peripheral surface) of the plunger 9 and the hole wall surfaces (inner peripheral surface) of the second guide holes of the stator cores 11 and 12 and the magnetic resistance portion 13.
A shaft sliding portion (sliding clearance) is provided between the sliding surface (outer peripheral surface) of the shaft 8 and the hole wall surface (inner peripheral surface) of the first guide hole of the stator core 11.
Further, on the inner periphery of the outer peripheral wall 19 of the sleeve 1, large-diameter inner holes 31 and 32 extending in the axial direction of the sleeve 1, small-diameter inner holes 33 extending in the axial direction of the sleeve 1, large-diameter inner holes 32 and small-diameter inner holes. An annular inner circumferential groove 34 formed between the cylinder 33 and a cylindrical feedback oil chamber (hereinafter referred to as F / B chamber) 35 communicating with the F / B port 24 is formed.

The large-diameter inner hole 32 has a slightly smaller hole diameter (inner diameter) than the large-diameter inner hole 31. The small diameter inner hole 33 has a smaller hole diameter (inner diameter) than the large diameter inner holes 31 and 32. These large diameter inner holes 31 and 32 and the small diameter inner hole 33 constitute the guide hole 2 of the sleeve 1.
The F / B chamber 35 is formed between the outer periphery of the spool 5 and the bottom surface of the inner circumferential groove 34. The F / B chamber 35 is installed on the left side of the DRAIN port 23 in the figure.
Details of the sleeve 1 of this embodiment will be described later.

The two strainers 3 and 4 are integrally formed of, for example, a metal such as stainless steel or copper, and are wound around and attached to the bottom surfaces of all the circumferential grooves (described later) of the outer peripheral wall 19 of the sleeve 1. Yes. These strainers 3 and 4 are thin plate-like oil filters that prevent foreign matter from flowing into the guide hole 2 of the sleeve 1 (communication chamber 46).
The two strainers 3 and 4 penetrate in the plate thickness direction, and communicate with the inside and the outside of the first and second peripheral walls of the outer peripheral wall 19 through the IN and OUT ports 21 and 22. It is formed of a metal porous sheet having a rectangular shape (a rectangular metal thin plate in the developed state).
Details of the strainers 3 and 4 of this embodiment will be described later.

The spool 5 constitutes a valve body (valve body) of the spool control valve. The spool 5 has an outer diameter that substantially matches the inner diameter of the outer peripheral wall 19 of the sleeve 1 (large inner diameter and small inner diameter of the guide hole 2), and a plurality of oil supply / discharge ports (21 to 26). Are provided with a plurality of lands (41 to 43) for controlling the communication state.
The plurality of lands (41 to 43) include a large-diameter portion (hereinafter referred to as a large-diameter land) 41 having an outer diameter larger than the spool outer diameter, and a plurality of small-diameter portions having an outer diameter substantially matching the spool outer diameter ( (Hereinafter referred to as small-diameter land) 42, 43.

The outer peripheral surface of the large-diameter land 41 is a sliding surface that slides directly on the hole wall surfaces of the large-diameter inner holes 31 and 32 of the guide hole 2. Here, between the hole wall surface of the large-diameter inner holes 31 and 32 of the guide hole 2 and the sliding surface of the plurality of large-diameter lands 41, a spool sliding portion for enabling the spool 5 to reciprocate. (Sliding clearance) is formed.
The outer peripheral surfaces of the small-diameter lands 42 and 43 are sliding surfaces that slide directly on the hole wall surface of the small-diameter inner hole 33 of the guide hole 2. Further, the small-diameter lands 42 and 43 have a smaller outer diameter than the large-diameter land 41.
Here, between the hole wall surface of the small-diameter inner hole 33 of the guide hole 2 and the sliding surfaces of the plurality of small-diameter lands 42, 43, a spool sliding portion (slider) for enabling the spool 5 to reciprocate. Dynamic clearance) is formed.

An annular constricted portion 44 is formed between two adjacent large-diameter lands 41 and small-diameter lands 42. The constricted portion 44 is provided on the outer periphery of the spool 5 so as to be positioned in the F / B chamber 35 even when the spool 5 reciprocates in the axial direction thereof, that is, even when the spool 5 is fully lifted from zero lift.
A cylindrical small-diameter shaft portion 45 that connects the small-diameter lands 42 and 43 so as to be interlocked is formed between two adjacent small-diameter lands 42 and 43. An oil chamber (hereinafter referred to as a communication chamber) 46 that communicates the IN port 21 with the OUT port 22 or the DRAIN port 23 is formed on the outer periphery of the small-diameter shaft portion 45.

  In addition, on the right end (solenoid side) end surface of the small-diameter land 43, an axial convex portion (axial projection) 47 that abuts against the plunger 9 of the linear solenoid S is integrally formed through a nonmagnetic shaft 8. Is formed. Accordingly, the spool control valve is configured to drive the spool 5 in the axial direction via the shaft 8 when the plunger 9 moves in the axial direction. Further, an oil chamber (hereinafter referred to as a communication chamber) that communicates the interior of the linear solenoid S (shaft sliding portion, plunger chamber, plunger sliding portion) and the DRAIN port 25 is provided on the distal end side of the shaft 8 and the outer periphery of the axial projection 47. 48) is formed.

The return spring 6 is a compression coil spring that generates an elastic force (biasing force) that urges the spool 5 toward the proximal end side (solenoid side) of the sleeve 1 in the guide hole 2. The return spring 6 is axially arranged between the wall surface (spring seat) of the adjusting screw 7 and the wall surface (spring seat) of the large-diameter land 41 of the spool 5 in the spring accommodating chamber 28 on the distal end side of the guide hole 2. Arranged in a compressed state.
The adjustment screw 7 is a load adjusting member that adjusts the spring load of the return spring 6 in accordance with the screwing amount (screwing amount) of the distal end side cylindrical portion 50 of the sleeve 1 with respect to the female screw. It also has a function as a plug (end plug) or an end cap that closes the opening.

The linear solenoid S is an electromagnetic actuator that drives the spool 5 to one side (tip side) in the axial direction via a nonmagnetic shaft 8. The linear solenoid S includes a plunger 9, a coil 10, a coil inner peripheral side fixed core (11-13), a coil outer peripheral side fixed core (14), an external connection connector 15, and the like.
The shaft 8 is installed on the central axis of the outer peripheral wall 19 of the sleeve 1 of the linear solenoid valve. The shaft 8 transmits a driving force to one side in the axial direction (solenoid axis direction) by the plunger 9 to the spool 5 and transmits a biasing force of the return spring 6 applied to the spool 5 to the plunger 9. The shaft 8 is a connecting portion that contacts the axial projection 47 of the spool 5 and contacts one end surface of the plunger 9 in the axial direction to connect the spool 5 and the plunger 9.

The plunger 9 is fitted and arranged on the inner peripheral side of the coil inner peripheral side fixed core (11-13) so as to be reciprocally slidable in the solenoid axis direction. The plunger 9 is made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 10 is energized.
The plunger 9 is a movable core (moving core) that is magnetically attracted toward one side in the solenoid axis direction by the magnetic force of the coil 10. The plunger 9 is urged to the bottom plate of the bottomed cylindrical yoke 14 together with the spool 5 and the shaft 8 by the urging force of the return spring 6 transmitted to the spool 5.

The plunger 9 is accommodated in the inside (plunger chamber) of the coil inner peripheral side fixed core (11-13) so as to be reciprocally slidable. The plunger chamber includes plunger front and rear spaces 51 and 52 formed on both sides of the plunger 9 in the solenoid axial direction.
The plunger front and rear spaces 51 and 52 are first and second volume changing portions whose volumes change when the linear solenoid S is operated. These plunger front and rear spaces 51 and 52 communicate with each other through a plunger breathing hole 53 that penetrates the plunger 9 in the axial direction thereof.
The plunger 9 has a plunger breathing hole 53 that communicates with both end faces (front and rear end faces in the axial direction) of the plunger 9 in order to ensure oil flow in the plunger front and rear spaces 51 and 52 due to displacement in the plunger chamber. It is provided straight in the direction.
Further, on the outer peripheral surface of the plunger 9, a sliding surface is formed that slides directly on the inner peripheral surfaces of the stator cores 11, 12 and the magnetic resistance portion 13.

When the coil 10 is supplied with electric power (when a current is applied or energized), magnetic flux generating means (magnetic force) that generates a magnetic force that attracts the plunger 9 to the magnetic attraction portions (annular step surfaces) 54 of the stator cores 11 and 12. Generating means). The coil 10 is a solenoid coil in which a conductive wire with an insulating coating is wound around the outer periphery of a cylindrical portion of a synthetic resin coil bobbin (hereinafter referred to as a bobbin) 55 a plurality of times.
In the linear solenoid S, when the coil 10 is energized, a magnetic circuit in which magnetic flux concentrates through the plunger 9, the stator cores 11 and 12, and the yoke 14 is formed.

The coil 10 drives the spool 5, the shaft 8, and the plunger 9 to one side (the front end side, the front side, and the full lift side) of the outer peripheral wall 19 of the sleeve 1 and the axial direction of the spool 5 by magnetic force.
Here, in this embodiment, when the coil 10 is energized (ON), the spool 5, the shaft 8 and the plunger 9 are stroked from the initial position (default position) to one side (front end side) in the solenoid axis direction. When energization of the coil 10 is stopped (OFF), the spool 5, the shaft 8 and the plunger 9 are returned to the default positions by the urging force of the return spring 6.

The coil 10 includes a coil portion wound around a bobbin 55 made of an insulating synthetic resin (mold resin material), and a pair of coils drawn outside the winding start end and winding end end of the coil portion. Has lead wires.
The pair of coil lead wires are conductors (conductors) that form the bobbin 55, that is, the coil 10 wound between the pair of hook-shaped portions and the outer periphery of the cylindrical portion, and each terminal 56 of the connector 15 for external connection. It is electrically connected to the external circuit via
Further, the outer peripheral portion of the coil 10 and the conductive joint portion between each coil lead wire of the coil 10 and each terminal 56 are covered and protected by a solenoid case 57 made of an insulating synthetic resin (molded resin material). Yes. The solenoid case 57 includes a cylindrical portion that surrounds the coil 10 and the bobbin 55 in the circumferential direction, and a connector case that exposes and accommodates the ends of the pair of terminals 56.

The coil inner peripheral fixed core includes a stator core 11 that attracts the plunger 9 toward the distal end side in the axial direction of the solenoid, a stator core 12 that transfers magnetism around the plunger 9, and a flow of magnetic flux between the two stator cores 11 and 12. The magnetic resistance part 13 to reduce is provided. The stator cores 11 and 12 and the magnetoresistive portion 13 are configured as an integral part or a separate part.
Stator cores 11 and 12 and magnetoresistive portion 13 are made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when coil 10 is energized. The stator cores 11 and 12 constitute a magnetic circuit together with the coil 10, the plunger 9 and the yoke 14.

An annular washer 58 is attached to the end surface of the stator core 11 on the plunger side so as to surround the shaft 8 in the circumferential direction.
In addition, the stator core 11 includes an annular flange 62 that is interposed between the flange 18 of the sleeve 1 and the annular portion 61 of the solenoid case 57.
The stator cores 11 and 12 and the magnetoresistive portion 13 include first to third cylindrical portions disposed on the inner peripheral side of the coil 10.

A first guide hole having a circular cross section in which the outer peripheral surface (sliding surface) of the shaft 8 slides directly is formed inside (inner periphery) of the first cylindrical portion of the stator core 11. A shaft sliding portion is provided between the sliding surface of the shaft 8 and the hole wall surface (inner peripheral surface) of the first guide hole of the stator core 11.
The outer peripheral surface (sliding surface) of the plunger 9 is inside (inner periphery) the first cylindrical portion of the stator core 11, the second cylindrical portion of the stator core 12, and the third cylindrical portion (thin cylindrical portion) of the magnetoresistive portion 13. A second guide hole having a circular cross section that directly slides is formed. And the plunger sliding part is provided between the sliding surface of the plunger 9, and the hole wall surface (inner peripheral surface) of the 2nd guide hole of each 1st-3rd cylindrical part.
The magnetoresistive portion 13 is configured by a thin portion that connects the two stator cores 11 and 12.

The coil outer peripheral fixed core is composed of a yoke 14 made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 10 is energized. The yoke 14 is formed in a bottomed cylindrical shape.
The yoke 14 constitutes a magnetic circuit together with the plunger 9, the coil 10, and the stator cores 11 and 12.
The yoke 14 has a cylindrical portion that covers the outer peripheral side of the coil 10. The yoke 14 is open at one end side (spool control valve side) of the cylindrical portion, and is closed at the other end side of the cylindrical portion by a disk-shaped bottom plate.

The bottom plate of the yoke 14 is provided with a stopper that protrudes toward the plunger chamber and that the rear end surface of the plunger 9 comes into contact with and is locked. The stopper is an axial protrusion that is installed on the central axis of the linear solenoid S.
A cylindrical opening on one end side of the cylindrical portion of the yoke 14 is provided with a step for locking the outer peripheral portion of the flange 62 of the stator core 11 and a flange 62 of the stator core 11 between the flange 18 of the sleeve 1 and the step of the yoke 14. A claw portion 65 that is caulked and fixed to the outer peripheral portion of the flange 18 of the sleeve 1 while being sandwiched is provided. As a result, the spool control valve and the linear solenoid S are assembled together.

  Here, the linear solenoid valve of the present embodiment communicates the IN port 21 and the OUT port 22 when the supply of power to the coil 10 is stopped, and shuts off the OUT port 22 and the DRAIN port 23, as well as to the coil 10. As the power supply increases, the communication area between the IN port 21 and the OUT port 22 decreases stepwise or continuously, and the communication area between the OUT port 22 and the DRAIN port 23 increases stepwise or continuously. This is an open (N / O) type electromagnetic spool control valve.

Next, details of the sleeve 1 of this embodiment will be briefly described with reference to FIGS.
The sleeve 1 includes a guide hole 2 extending in the axial direction thereof, a cylindrical outer peripheral wall 19 that surrounds the periphery of the guide hole 2 in the circumferential direction, an inside of the outer peripheral wall 19 (guide hole 2), and the outer peripheral wall 19 A plurality of internal and external communication holes (at least four oil supply / discharge ports 21 to 24 among the plurality of oil supply / discharge ports 21 to 26) communicating with an external oil passage are provided.

In the outer peripheral wall 19 of the sleeve 1, two first and second outer peripheral groove grooves (recessed) formed (concave) over the entire circumference of the outer peripheral wall 19 at a predetermined distance in the axial direction. Hereinafter, all-round concave grooves) 67 and 68 are formed. These all-round concave grooves 67 and 68 are formed so as to be recessed (dig down or recessed) by a predetermined depth inward in the radial direction from the outer peripheral surfaces of the first and second peripheral walls of the outer peripheral wall 19. These are the first and second circumferential grooves.
Further, an axial concave groove 69 extending along a direction parallel to the axial direction of the sleeve 1 is formed on the outer peripheral surface of the outer peripheral wall 19. The axial groove 69 is formed so as to be recessed (notched, dug, or recessed) by a predetermined depth from the outer peripheral surface of the second to fourth peripheral walls of the outer peripheral wall 19 inward in the radial direction. )

The plurality of oil supply / discharge ports (21 to 26) are connected to the downstream end of the oil supply passage (first oil passage L1) and have a radius (radiation) substantially perpendicular to the axial direction of the guide hole 2 of the sleeve 1. ) In the axial direction of the guide hole 2 of the sleeve 1 and a predetermined distance in the axial direction.
The IN port 21 is a part of the first peripheral wall in the circumferential direction of the cylindrical outer peripheral wall 19 that surrounds the circumference of the spool 5 in the circumferential direction, and the first peripheral wall communicates with the inside of the first peripheral wall and the outside. The first inner and outer communication holes are formed through in the radial direction.

  The IN port 21 has a first opening 71 that opens in a partial annular shape (arc shape) in the circumferential direction of the first peripheral wall at the bottom surface of the entire circumferential concave groove 67 of the first peripheral wall. This is a first flow path hole (valve hole) through which oil is supplied to the inside of the guide hole 2 (communication chamber 46) via the path L1. When the linear solenoid S is operated, the guide hole side end of the IN port 21 is connected to the inside of the guide hole 2 (communication chamber 46) so that oil can flow.

The first opening 71 opens on the radially outer side of the IN port 21. The width of the first opening 71 is smaller than the groove width of the entire circumferential groove 67 of the first peripheral wall. For this reason, on both sides in the width direction of the first opening 71, opening peripheral portions (angular annular sheet portion A: see FIG. 7) where a curved surface portion (described later) of the strainer 3 can come into curved contact are formed.
In addition, a first opening that is opened by a hole wall surface of the guide hole 2 is formed on the radially inner side of the IN port 21.

The OUT port 22 is a part of the circumferential direction of the second circumferential wall of the cylindrical outer circumferential wall 19 that surrounds the circumference of the spool 5 in the circumferential direction, and the second circumferential wall communicates the inside and the outside of the second circumferential wall. The second inner and outer communication holes are formed penetrating in the radial direction.
The OUT port 22 includes a second opening 72 that is opened in a partial annular shape (arc shape) in the circumferential direction of the second peripheral wall at the bottom surface of the entire circumferential concave groove 68 of the second peripheral wall. This is a second passage hole through which oil is supplied from the communication chamber 46) to the hydraulic servo of the clutch (or brake) via the second oil passage L2.
The guide hole side end of the OUT port 22 is connected to the inside of the guide hole 2 (communication chamber 46) so that oil can flow when the linear solenoid S operates.

The second opening 71 opens on the outer side in the radial direction of the OUT port 22. The width of the second opening 72 is smaller than the groove width of the entire circumferential concave groove 68 of the second peripheral wall. For this reason, on both sides in the width direction of the second opening 72, opening peripheral portions (angular annular sheet portion B: refer to FIG. 7) where the curved surface portions (described later) of the strainer 3 can come into curved contact are formed.
Further, a second opening that is opened at the hole wall surface of the guide hole 2 is formed on the radially inner side of the OUT port 22.

The DRAIN port 23 is a part of the third peripheral wall in the circumferential direction of the cylindrical outer peripheral wall 19 that surrounds the circumference of the spool 5 in the circumferential direction, and communicates the inside and the outside of the third peripheral wall. 3rd inside-and-outside communication hole penetrated in the radial direction.
The DRAIN port 23 has a third opening 73 opened in a partial annular shape (arc shape) in the circumferential direction of the third peripheral wall on the outer peripheral surface of the third peripheral wall, and from the inside of the guide hole 2 (communication chamber 46). This is a third flow path hole (valve hole) through which oil is supplied to the oil pan via the third oil path L3.
When the linear solenoid S is operated, the guide hole side end of the DRAIN port 23 is connected to the inside of the guide hole 2 (communication chamber 46) so that oil can flow.

The F / B port 24 is a fourth through hole formed in the radial direction of the fourth peripheral wall so as to communicate the inside and the outside of the fourth peripheral wall of the cylindrical outer peripheral wall 19 that surrounds the periphery of the spool 5 in the circumferential direction. Internal and external communication holes.
The F / B port 24 has a circular fourth opening 74 opened at the bottom surface of the axial groove 69 of the third and fourth peripheral walls of the outer peripheral wall 19, and extends from the entire peripheral groove 68 of the OUT port 22. This is a fourth flow path hole through which oil is supplied to the inside of the guide hole 2 (F / B chamber 35) via the F / B oil path L4.

The guide hole side end of the F / B port 24 is connected to the inside of the guide hole 2 (F / B chamber 35) so that oil can flow when the linear solenoid S operates. The F / B chamber 35 is formed between the bottom surface of the inner circumferential groove 34 in the fourth circumferential wall of the outer circumferential wall 19 of the sleeve 1 and the outer circumference of the constricted portion 44 of the spool 5.
The first opening 71, the second opening 72, the third opening 73, and the fourth opening 74 are formed with a predetermined distance in the axial direction of the sleeve 1.

Further, the F / B port 24 is formed with an orifice hole for reducing the pressure fluctuation accompanying the pumping operation of the oil pump.
The orifice hole is formed by reducing the hole diameter of the F / B port 24 by a predetermined restriction amount. The orifice hole is formed in the entire F / B port 24 from the port opening portion on the radially inner side of the F / B port 24 to the port opening portion (fourth opening portion) on the radially outer side.

  Note that the entire circumferential concave groove 68 of the OUT port 22 is between the bottom surface of the axial concave groove 69 formed on the outer circumferential surface of the outer circumferential wall 19 of the sleeve 1 and the inner surface of the valve insertion groove (concave portion) of the valve body. And an F / B oil passage L4, which is a feedback flow path communicating with the F / B port 24, is formed. The F / B oil passage L4 is formed across or avoiding the third opening 73 of the DRAIN port 23.

Next, the details of the strainers 3 and 4 of this embodiment will be briefly described with reference to FIGS.
The two strainers 3 and 4 are bent so as to have a C-shape, and are wound around the entire circumferential direction (entire circumference) of the entire circumferential concave grooves 67 and 68, and are attached by welding means such as laser welding. Are provided with first and second connection portions 81 and 82 for joining (connecting) both end portions of the strainers 3 and 4 in the circumferential direction.

The large number of filter holes are small circular holes that are smaller than the particle size of the foreign matter contained in the oil and through which the oil can flow. These filter holes are formed by etching or pressing.
The formation range of the many filter holes is longer than the circumferential width of the first and second openings 71 and 72 of the IN and OUT ports 21 and 22 in the longitudinal direction (circumferential direction) of the strainers 3 and 4. It ’s fine.

The strainer 3 is an oil filter (first strainer) for an input port that covers a first opening 71 provided on the radially outer side of the IN port 21, and the bottom surface of the entire circumferential concave groove 67 of the outer peripheral wall 19 is a partial cylinder. It is mounted (fitted) so as to surround the shape.
The strainer 4 is an oil filter (second strainer) for an output port that covers a second opening 72 provided on the radially outer side of the OUT port 22, and the bottom surface of the entire circumferential concave groove 68 of the outer peripheral wall 19. It is mounted (fitted) so as to surround a partial cylinder.

Here, the widths of the two strainers 3 and 4 are slightly smaller than the widths of the entire circumferential grooves 67 and 68. As a result, the two strainers 3 and 4 can be easily fitted into the entire circumferential concave grooves 67 and 68.
The widths of the two strainers 3 and 4 are larger than the width of the first opening 71 of the IN port 21 and the width of the second opening 72 of the OUT port 22. Around the filter hole forming portions of the strainers 3 and 4, there are opening peripheral portions (sheet portions A and B) of the first and second opening portions 71 and 72 of the IN and OUT ports 21 and 22, and respective concave portions on the entire circumference. A rectangular ring-shaped seal portion is formed on the bottom surface of the grooves 67 and 68 so as to make a curved contact with the curved surface.

  The two strainers 3 and 4 have a plate thickness (for example, about 0.3 mm) thinner than the depths of the entire circumferential concave grooves 67 and 68, and from the outer peripheral surfaces of the first and second peripheral walls of the outer peripheral wall 19. The outer circumferential wall 19 is accommodated in the entire circumferential concave grooves 67 and 68 without protruding outward in the radial direction of the first and second circumferential walls. The two strainers 3 and 4 are accommodated in the circumferential grooves 67 and 68 without protruding from the circumferential ends of the circumferential grooves 67 and 68 to the outer sides in the circumferential direction of the circumferential grooves 67 and 68. Has been.

The two strainers 3, 4 have arcuate curved surface portions 83, 84 corresponding to the bottom shape of the entire circumferential concave grooves 67, 68. In the strainers 3 and 4, the inner diameters of the curved surface portions 83 and 84 are elastically deformed in the expanding direction so as to be in close contact with the bottom surfaces of the entire circumferential grooves 67 and 68, and the outer circumferences of the first and second peripheral walls of the outer peripheral wall 19. It is installed.
A number of filter holes are formed by etching or pressing. The curved surface portions 83 and 84 are formed by pressing.

[Assembly method of Example 1]
Next, an assembling procedure of the strainers 3 and 4 with respect to the first and second peripheral walls of the outer peripheral wall 19 of the sleeve 1 of the present embodiment will be described.
Here, the procedure for assembling the strainer 3 with respect to the first peripheral wall of the outer peripheral wall 19 of the sleeve 1 and the procedure for assembling the strainer 4 with respect to the second peripheral wall of the outer peripheral wall 19 of the sleeve 1 are the same. Only the description will be given, and the assembly procedure of the strainer 4 will be omitted.

  First, in FIG. 2, the strainer 3 is moved along the strainer mounting direction from the radially outer side of the first peripheral wall of the outer peripheral wall 19 of the sleeve 1 (above the center line passing through the center of the IN port 21, the upper side in the drawing). Sliding into the bottom surface of the entire circumferential concave groove 67 of the outer peripheral wall 19, and so that both ends in the circumferential direction of the strainer 3 partially overlap so as to surround the periphery of the bottom surface of the total circumferential concave groove 67 of the outer peripheral wall 19. Wrap. That is, the coil is wound around the bottom surface of the entire circumferential concave groove 67 of the outer peripheral wall 19 of the sleeve 1 such that the other end in the circumferential direction of the strainer 3 overlaps with one end in the circumferential direction of the strainer 3 by a predetermined overlap. At this time, the curved inner surface of the curved surface portion 83 of the strainer 3 is wound around the bottom surface of the entire circumferential concave groove 67 of the outer peripheral wall 19 so that the curved inner surface closely contacts the bottom surface of the entire circumferential concave groove 67 of the outer peripheral wall 19.

  And after winding so that the curved surface part 83 of the strainer 3 closely_contact | adheres to the bottom face of the all-around concave groove 67 of the outer peripheral wall 19 (curved surface contact), the overlapping part (1st connection part 81) of the circumferential direction both ends of the strainer 3 Are joined (connected) by laser welding. Specifically, for example, the circumferential end of the strainer 3 and the other circumferential end of the strainer 3 are overlapped on the circumferential end of the strainer 3 by a predetermined overlapping amount. Laser welding. Alternatively, the circumferential one end and the other circumferential end of the strainer 3 may be laser welded in a state where the circumferential one end of the strainer 3 and the other circumferential end of the strainer 3 face each other.

With the above assembly procedure, the strainer 3 is mounted (locked and fixed) in a state where it is wound around the entire circumferential concave groove 67 of the outer peripheral wall 19, so that the strainer 3 is assembled to the first peripheral wall of the outer peripheral wall 19 of the sleeve 1. Is completed. Further, the strainer 4 is mounted (locked and fixed) in a state where the strainer 4 is wound around the entire circumferential concave groove 68 of the outer peripheral wall 19 by the same assembling procedure, whereby the strainer 4 with respect to the second peripheral wall of the outer peripheral wall 19 of the sleeve 1. Assembling is completed.
In addition, when the strainers 3 and 4 are assembled in the entire circumferential grooves 67 and 68 of the first and second peripheral walls of the outer peripheral wall 19 of the sleeve 1, the inside of the first and second peripheral walls of the outer peripheral wall 19 of the sleeve 1 (guide) The spool 3 may not be inserted in the hole 2).

[Operation of Example 1]
Next, the operation of the linear solenoid valve of this embodiment will be briefly described with reference to FIGS.

  The linear solenoid valve drives oil pressure control (hydraulic control) used in the automatic transmission to the front end side in the axial direction of the sleeve 1 so that the spool 5 can be reciprocated in the guide hole 2 of the sleeve 1. The magnetic attraction force of the coil 10 of the linear solenoid S, the urging force of the return spring 6 that urges the spool 5 toward the other axial side of the sleeve 1 (the base end side of the sleeve 1), and the F / B chamber 35 are supplied. Thus, the spool 5 is held at a predetermined axial position (stroke position) by the pressure balance with the feedback hydraulic pressure (part of the output pressure of the oil output from the OUT port 22) acting on the constricted portion 44 of the spool 5. The

Incidentally, as shown in FIG. 3, the feedback force (feedback hydraulic pressure) is generated by the pressure receiving area difference between the outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5 and the outer diameter (main diameter) of the small-diameter land 42. produce.
However, the volume change with respect to the stroke of the spool 5 is small because it is a pressure receiving area difference, and since the effect as a damper is small, it is easily affected by oil vibration (oil pulse) that is a pressure fluctuation accompanying the pumping operation of the oil pump. .
Therefore, the linear solenoid valve changes the communication area between the IN port 21 and the OUT port 22 and the communication area between the OUT port 22 and the DRAIN port 23 by controlling the stroke position of the spool 5. Thereby, the output pressure of the oil output from the OUT port 22 is regulated.

When electric power is not supplied to the coil 10 of the linear solenoid S, the spool 5 is stopped at the default position on the solenoid side by the urging force of the return spring 6.
At this time, since the small-diameter land 43 of the spool 5 opens the IN port 21, the communication chamber 46 formed on the outer periphery of the small-diameter shaft portion 45 between the small-diameter lands 42 and 43 connects the IN port 21 and the OUT port 22. Communicate. Further, the small-diameter land 42 of the spool 5 closes (fully closes) the DRAIN port 23.

  At this time, the oil discharged from the oil pump and passing through each filter hole of the strainer 3 reaches the spool hole side end of the IN port 21 from the first opening 71. The oil reaching the spool hole side end of the IN port 21 has the small-diameter land 43 opening the IN port 21. Then, oil pressure is applied to the outer peripheral surface (convex curved surface) of the curved surface portion 83 of the strainer 3 from the radially outer side to the inner side of the curved surface portion 83, and the inner peripheral surface of the curved surface portion 83 of the strainer 3 is Since it is liquid-tightly adhered (curved surface contact) to the sheet portion A of the entire circumferential groove 67, the inside of the guide hole 2 for foreign matters such as metal powder contained in the oil pressure-fed and supplied from the oil pump to the IN port 21 ( Inflow into the communication chamber 46) is prevented.

The oil flowing into the guide hole 2 (communication chamber 46) is output from the OUT port 22, and the pressure (hydraulic pressure) of the oil acting on the hydraulic servo of the clutch (or brake) increases. That is, the oil pressure (hydraulic pressure) output from the OUT port 22 to the hydraulic servo of the clutch (or brake) is adjusted according to the overlap amount between the small-diameter land 43 of the spool 5 and the IN port 21.
Thus, the solenoid valve of this embodiment functions as a normally open type linear solenoid valve because the IN port 21 and the OUT port 22 communicate with each other when power is not supplied to the coil 10.

On the other hand, when electric power is supplied to the coil 10 of the linear solenoid S, the plunger 9 is attracted to the magnetic attracting portions 54 of the stator cores 11 and 12 with a magnetic attracting force corresponding to the magnitude of the current flowing through the coil 10. Along with this, the shaft 8 having the spool 5 connected to the tip is pushed out to one side in the axial direction, whereby the spool 5 moves toward the tip of the sleeve 1.
At this time, the spool 5 has the F / B chamber 35 via the thrust (magnetic attractive force) of the plunger 9, the urging force of the return spring 6, the F / B oil passage L 4 and the F / B port 24 from the OUT port 22. Stops at a position where the feedback force (axial force: hereinafter referred to as F / B force) acting on the large-diameter land 41 and the small-diameter land 42 of the spool 5 is balanced by the oil pressure (feedback hydraulic pressure) input to the spool 5, and the spool 5 is in the sleeve The opening area of the IN port 21 is narrowed and the opening area of the DRAIN port 23 is expanded as it moves to the tip end side.

When the OUT (control) pressure, which is the output pressure of the oil output from the OUT port 22, is increased, that is, at the time of apply evaluation, the F / B chamber 35 flows from the IN (supply) pressure having a large oil pulse. However, the F / B chamber 35 passes through the first oil passage L1 → IN port 21 → the inside of the guide hole 2 (communication chamber 46) → OUT port 22 → F / B oil passage L4 → F / B port 24 from the oil pump. Since the oil flowing into the gas passes through the two porous oil filters including the strainer 3 covering the first opening 71 of the IN port 21 and the strainer 4 covering the second opening 72 of the OUT port 22, the F / B chamber The oil pulse input to 35 can be sufficiently suppressed, and stable characteristics can be obtained.
That is, the follow-up performance from the rise of the output pressure of the oil output from the OUT port 22 to the target value of the feedback hydraulic pressure (a value capable of reducing the pressure fluctuation of the output pressure of the oil output from the OUT port 22). Can be improved.

  Here, the oil discharged from the oil pump and passing through each filter hole of the strainer 3 flows into the IN port 21 from the first opening 71. At this time, oil pressure is applied to the outer peripheral surface (convex curved surface) of the curved surface portion 83 of the strainer 3 from the radially outer side to the inner side of the curved surface portion 83, and the inner peripheral surface of the curved surface portion 83 of the strainer 3 is Since the liquid-tight contact (curved surface contact) is made with the sheet portion A of the entire circumferential groove 67, the inside of the guide hole 2 for foreign matter such as metal powder contained in the oil pressure-fed and supplied from the oil pump to the IN port 21 Inflow to (communication chamber 46) is prevented.

  When the opening area of the IN port 21 decreases as the stroke amount of the spool 5 increases, the oil pressure (hydraulic pressure) that is output from the OUT port 22 and acts on the hydraulic servo of the clutch (or brake) increases. That is, the oil pressure (hydraulic pressure) output from the OUT port 22 to the hydraulic servo of the clutch (or brake) is adjusted according to the overlap amount between the small-diameter land 43 of the spool 5 and the IN port 21.

When the stroke amount of the spool 5 exceeds a predetermined value, the small-diameter land 43 of the spool 5 closes the IN port 21 (fully closes). A communication chamber 46 formed on the outer periphery of the small-diameter shaft portion 45 between the small-diameter lands 42 and 43 communicates the OUT port 22 and the DRAIN port 23.
At this time, the oil discharged from the oil pump reaches the guide hole side end of the IN port 21 from the first oil passage L1. The oil reaching the end portion on the guide hole side of the IN port 21 is prevented from flowing into the guide hole 2 of the sleeve 1 because the small-diameter land 43 blocks the IN port 21.

The oil discharged (drained) from the hydraulic servo of the clutch (or brake) and passed through the filter holes of the strainer 4 flows into the OUT port 22 from the second opening 72.
At this time, oil pressure is applied to the outer peripheral surface (convex curved surface) of the curved surface portion 84 of the strainer 4 from the radially outer side to the inner side of the curved surface portion 84, and the inner peripheral surface of the curved surface portion 84 of the strainer 4 is Since it is in liquid-tight contact (curved surface contact) with the sheet portion B of the entire circumferential groove 68, a guide for foreign matters such as metal powder contained in the oil returned from the hydraulic servo of the clutch (or brake) to the OUT port 22 is provided. Inflow to the inside of the hole 2 (communication chamber 46) is prevented.

The oil that has passed through the filter holes of the strainer 4 and returned to the OUT port 22 flows out from the DRAIN port 23 to the outside of the third peripheral wall of the outer peripheral wall 19 of the sleeve 1 through the communication chamber 46 in the sleeve 1. To do. Since the oil that has flowed out of the third peripheral wall of the outer peripheral wall 19 of the sleeve 1 is discharged to the oil pan through the third oil passage L3, the oil acting on the hydraulic servo of the clutch (or brake) Pressure (hydraulic pressure) drops.
When the OUT (control) pressure, which is the output pressure of the oil output from the OUT port 22, falls, that is, during drain evaluation, the OUT pressure decreases, so the F / B port 24 → F / B Oil flows from the oil passage L4 to the OUT port 22 (there is no influence of the oil pulse).

[Effect of Example 1]
As described above, in the linear solenoid valve of the present embodiment, the IN port 21 that communicates the first oil passage L1 provided outside the outer peripheral wall 19 of the sleeve 1 and the inside of the guide hole 2 (communication chamber 46). An annular belt-like strainer 3 is wound around and attached to the bottom surface of the entire circumferential groove 67 of the outer peripheral wall 19 so as to cover the first opening 71 and is provided outside the outer peripheral wall 19 of the sleeve 1. An annular belt-shaped strainer is formed on the bottom surface of the entire circumferential groove 68 of the outer peripheral wall 19 so as to cover the second opening 72 of the OUT port 22 that communicates the second oil passage L2 and the inside of the guide hole 2 (communication chamber 46). 4 is wound around and installed in the circumferential direction, so that foreign matter can be reliably prevented from entering the inside of the guide hole 2 (communication chamber 46) of the sleeve 1, so that the IN port 21 and the OUT port 22 are resistant to damage. Improve foreign matter Rukoto can.

In addition, the processing cost of the spool 5 can be reduced by eliminating the need for drilling such as a slanted hole in the small-diameter land 42 of the spool 5. As a result, the manufacturing cost of the spool 5, and thus the linear solenoid valve, can be reduced.
Further, the followability from the rise of the output pressure of the oil output from the OUT port 22 to the target value of the feedback hydraulic pressure (a value capable of reducing the pressure fluctuation of the output pressure of the oil output from the OUT port 22) ( Characteristic) can be improved.

In addition, since the first and second connecting portions 81 and 82 at the circumferential ends of the two strainers 3 and 4 are joined by welding with a high holding force, the linear solenoid valve can be handled during production or linearly. Due to vibrations or the like when the solenoid valve is mounted on a valve body arranged in an oil pan of an automatic transmission of a vehicle such as an automobile, the entire circumferential groove 67 or the circumferential groove 68 of the outer peripheral wall 19 of the sleeve 1 is removed. There is no fear that the strainer 3 or the strainer 4 may fall off or the strainer 3 or the strainer 4 may be detached or displaced with respect to the first opening 71 of the IN port 21 of the sleeve 1 or the second opening 72 of the OUT port 22 of the sleeve 1. .
Accordingly, foreign matter can be reliably prevented from entering the guide hole 2 of the sleeve 1 (communication chamber 46), so that the foreign matter resistance of the IN port 21 and the OUT port 22 can be further improved.

The diameter of the spool disposed in the F / B chamber 35 is set such that the outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5> the outer diameter (main diameter) of the small-diameter land 42.
The F / B chamber 35 is installed on the left side of the DRAIN port 23 in the figure.
Further, the F / B oil passage L4 communicating the OUT port 22 and the F / B chamber 35 extends over the third opening 73 of the DRAIN port 23 opened at the outer peripheral surface of the outer peripheral wall 19 of the sleeve 1, or It is formed to avoid.

By the way, it is preferable that the pressure pulsation (oil pulsation) of oil when flowing into the F / B chamber 35 from the OUT port 22 is small, and the oil pressure pulsation (oil pulsation) is input from the IN port 21 to the inside of the guide hole 2. The pulsation (oil pulsation) of the input pressure of the oil is the main factor.
Further, the F / B oil passage L4 flowing from the OUT port 22 to the F / B chamber 35 at the time of rising of the output pressure of the oil output from the OUT port 22 (apply evaluation) is outside the outer peripheral wall 19 of the sleeve 1 (first 1 oil passage L1) → IN port 21 → inside guide hole 2 (communication chamber 46) → OUT port 22 → F / B chamber 35 in this order, and is affected by oil pressure pulsation (oil pulse). Since the oil reaches the F / B chamber 35 via 3 and 4, the pressure pulsation amount (oil pulse amount) of the oil can be greatly reduced. Thereby, delicate hydraulic control can be performed.

Further, the diameter of the spool disposed in the F / B chamber 35 of the sleeve 1 is such that the outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5> the outer diameter (main diameter) of the small-diameter land 42 of the spool 5. Is set. Then, as shown in FIG. 1, F / B force is generated by the pressure receiving area difference between the outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5 and the outer diameter (main diameter) of the small-diameter land 42. The F / B force is a feedback hydraulic pressure acting on the large-diameter land 41 and the small-diameter land 42 of the spool 5, and is based on a pressure receiving area difference between the large-diameter land 41 and the small-diameter land 42 of the spool 5. It acts as an urging force toward one side (in the direction of the arrow in FIG. 4) in the axial direction.
However, the volume change amount with respect to the stroke of the spool 5 in the axial direction is small because the pressure receiving area difference between the large-diameter land 41 and the small-diameter land 42 is small, and the effect as a damper is small. It is easy to be influenced by the oil vibration (oil pulse).

By providing the sleeve 1 with the F / B oil passage L4, it is necessary to secure a complicated F / B oil passage in the valve body immersed in the oil in the oil pan of the automatic transmission of a vehicle such as an automobile. Therefore, the valve body can be downsized.
Further, at the time of drainage evaluation, the F / B chamber 35 to the F / B port 24, the F / B oil passage L4, and the OUT port 22 do not pass through at least one porous oil filter of the two strainers 3 and 4. Then, it flows into the DRAIN port 23 through the inside of the guide hole 2 (communication chamber 46). Then, the oil flowing into the DRAIN port 23 is sent to the low pressure side oil pan via the third oil passage L3.

[Configuration of Example 2]
5 to 7 show a linear solenoid valve (Embodiment 2) to which the spool control valve of the present invention is applied.
Here, the same reference numerals as those in the first embodiment indicate the same configuration or function, and the description thereof is omitted.

The linear solenoid valve (electromagnetic spool control valve, solenoid valve) of this embodiment includes a spool valve and a linear solenoid S. The spool valve includes a sleeve 1, a strainer 3, 4, a spool 5, a return spring 6, and an adjustment screw 7.
A plurality of oil supply / discharge ports (21 to 26) through which oil flows in and out of the outer peripheral wall 19 of the sleeve 1 are substantially perpendicular to the axial direction of the guide hole 2 between the inside and the outside of the outer peripheral wall 19. It communicates in the radial (radiating) direction.

Further, the plurality of oil supply / discharge ports (21 to 26) are arranged from the proximal end side to the distal end side of the outer peripheral wall 19 of the sleeve 1, from the DRAIN port 25, the DRAIN port 23, the OUT port 22, the IN port 21, and the DRAIN port. In order of 26, openings are formed in the axial direction of the guide hole 2 of the sleeve 1 with a predetermined distance therebetween.
Large diameter inner holes 31, 32, small diameter inner holes 33, inner peripheral concave grooves 34, and F / B chambers 35 are formed on the inner periphery of the outer peripheral wall 19 of the sleeve 1.

The F / B chamber 35 communicates with the F / B port 24 and is formed between the outer periphery of the constricted portion 44 of the spool 5 and the bottom surface of the inner peripheral groove 34. The F / B chamber 35 is installed on the right side of the DRAIN port 23 in the figure.
Further, the entire circumferential concave groove 68 of the OUT port 22 is disposed between the bottom surface of the axial concave groove 69 formed on the outer circumferential surface of the outer circumferential wall 19 of the sleeve 1 and the inner surface of the valve insertion groove (concave portion) of the valve body. And an F / B oil passage L4 communicating with the F / B port 24 is formed. The F / B oil passage L4 is formed across or avoiding the third opening 73 of the DRAIN port 23.

The spool 5 includes a large-diameter land 41 and small-diameter lands 42 and 43 that control the communication state of the plurality of oil supply / discharge ports (21 to 26). Further, a constricted portion 44 is formed between two adjacent large-diameter lands 41 and small-diameter lands 42. The constricted portion 44 is formed between the large-diameter land 41 and the small-diameter land 42 of the spool 5 so that the spool 5 is positioned in the F / B chamber 35 even when the spool 5 reciprocates in the axial direction, that is, even when the spool 5 is fully lifted from zero lift. It is provided on the outer periphery.
A small-diameter shaft portion 45 is formed between the two adjacent small-diameter lands 42 and 43. A communication chamber 46 for communicating the IN port 21 with the OUT port 22 or the DRAIN port 23 is formed on the outer periphery of the small diameter shaft portion 45.

The two strainers 3 and 4 are respectively wound around and attached to the bottom surface of the entire circumferential concave groove (described later) of the outer peripheral wall 19 of the sleeve 1. These strainers 3 and 4 are thin plate-like oil filters that prevent foreign matter from flowing into the guide hole 2 of the sleeve 1 (communication chamber 46).
The two strainers 3 and 4 have first and second connection portions 81 and 82 for joining (connecting) the circumferential ends of the strainers 3 and 4 by laser welding, and bottom shapes of the all-round concave grooves 67 and 68. Arc-shaped curved surface portions 83 and 84 corresponding to the above.

  The linear solenoid valve of this embodiment shuts off the IN port 21 and the OUT port 22 when the supply of power to the coil 10 is stopped, and communicates the OUT port 22 and the DRAIN port 23 and supplies power to the coil 10. As the communication area increases, the communication area between the IN port 21 and the OUT port 22 increases stepwise or continuously, and the communication area between the OUT port 22 and the DRAIN port 23 decreases stepwise or continuously. / C) type electromagnetic spool control valve.

[Operation of Example 2]
Next, the operation of the linear solenoid valve of the present embodiment will be briefly described with reference to FIGS.

When electric power is not supplied to the coil 10 of the linear solenoid S, the spool 5 is stopped at the default position on the solenoid side by the urging force of the return spring 6.
At this time, the small-diameter land 43 of the spool 5 closes the IN port 21 (fully closes). A communication chamber 46 formed on the outer periphery of the small-diameter shaft portion 45 between the small-diameter lands 42 and 43 communicates the OUT port 22 and the DRAIN port 23.
At this time, the oil discharged from the oil pump and passed through the filter holes of the strainer 3 reaches the guide hole side end of the IN port 21 from the first opening 71. The oil reaching the end portion on the guide hole side of the IN port 21 is prevented from flowing into the guide hole 2 of the sleeve 1 because the small-diameter land 43 blocks the IN port 21.

  The oil discharged (drained) from the hydraulic servo of the clutch (or brake) and passed through the filter holes of the strainer 4 flows into the OUT port 22 from the second opening 72. At this time, oil pressure is applied to the outer peripheral surface (convex curved surface) of the curved surface portion 84 of the strainer 4 from the radially outer side to the inner side of the curved surface portion 84, and the inner peripheral surface of the curved surface portion 84 of the strainer 4 is Since it is in liquid-tight contact (curved surface contact) with the sheet portion B of the entire circumferential groove 68, a guide for foreign matters such as metal powder contained in the oil returned from the hydraulic servo of the clutch (or brake) to the OUT port 22 is provided. Inflow to the inside of the hole 2 (communication chamber 46) is prevented.

The oil that has passed through the filter holes of the strainer 4 and returned to the OUT port 22 flows out from the DRAIN port 23 to the outside of the outer peripheral wall 19 of the sleeve 1 through the communication chamber 46 inside the sleeve 1. The oil flowing out of the outer peripheral wall 19 of the sleeve 1 is discharged to the oil pan through the third oil passage L3, and the pressure (hydraulic pressure) of the oil acting on the hydraulic servo of the clutch (or brake) is increased. Descend.
As described above, the linear solenoid valve of this embodiment is normally closed (N / C) type because the communication between the IN port 21 and the OUT port 22 is cut off when power is not supplied to the coil 10. It functions as a linear solenoid valve.

On the other hand, when electric power is supplied to the coil 10 of the linear solenoid S, the plunger 9 is attracted to the magnetic attracting portions 54 of the stator cores 11 and 12 with a magnetic attracting force corresponding to the magnitude of the current flowing through the coil 10. Along with this, the shaft 8 having the spool 5 connected to the tip is pushed out to one side in the axial direction, whereby the spool 5 moves toward the tip of the sleeve 1.
At this time, the spool 5 is configured such that the thrust of the plunger 9 (magnetic attractive force), the urging force of the return spring 6, and the pressure of oil input to the F / B chamber 35 via the F / B port 24 (feedback hydraulic pressure). Is stopped at a position where the feedback force (axial force: hereinafter referred to as F / B force) acting on the large-diameter land 41 and the small-diameter land 42 of the spool 5 is balanced, and the IN port increases as the spool 5 moves toward the distal end side of the sleeve 1. The opening area of 21 is expanded and the opening area of the DRAIN port 23 is narrowed.

  Here, the oil discharged from the oil pump and passing through each filter hole of the strainer 3 flows into the IN port 21 from the first opening 71. At this time, oil pressure is applied to the outer peripheral surface (convex curved surface) of the curved surface portion 83 of the strainer 3 from the radially outer side to the inner side of the curved surface portion 83, and the inner peripheral surface of the curved surface portion 83 of the strainer 3 is Since the liquid-tight contact (curved surface contact) is made with the sheet portion A of the entire circumferential groove 67, the inside of the guide hole 2 for foreign matter such as metal powder contained in the oil pressure-fed and supplied from the oil pump to the IN port 21 Inflow to (communication chamber 46) is prevented.

  When the opening area of the IN port 21 increases as the stroke amount of the spool 5 increases, the oil pressure (hydraulic pressure) output from the OUT port 22 and acting on the hydraulic servo of the clutch (or brake) increases. That is, the oil pressure (hydraulic pressure) output from the OUT port 22 to the hydraulic servo of the clutch (or brake) is adjusted according to the overlap amount between the small-diameter land 43 of the spool 5 and the IN port 21.

Further, the spool diameter disposed in the F / B chamber 35 of the sleeve 1 is the same as in the first embodiment. The outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5> the small-diameter land 42 of the spool 5. The outer diameter (main diameter) is set. Then, F / B force is generated by the pressure receiving area difference between the outer diameter (F / B diameter) of the large-diameter land 41 of the spool 5 and the outer diameter (main diameter) of the small-diameter land 42.
The F / B force is a feedback hydraulic pressure acting on the large-diameter land 41 and the small-diameter land 42 of the spool 5, and is based on a pressure receiving area difference between the large-diameter land 41 and the small-diameter land 42 of the spool 5. It acts as an urging force to the other side (base end side) in the axial direction.
As described above, the linear solenoid valve of this embodiment has the same effect as that of the first embodiment.

[Modification]
In this embodiment, the spool control valve of the present invention is applied to an electromagnetic spool control valve (electromagnetic valve) incorporated in a hydraulic circuit of a hydraulic control device that performs hydraulic control of an automatic transmission of an automobile. The present invention may be applied to an electromagnetic spool control valve (electromagnetic oil path switching valve) incorporated in a hydraulic circuit of a variable valve timing device (VVT) that changes the opening / closing timing of an intake valve or exhaust valve of an engine.
The spool control valve of the present invention may be applied to a spool control valve used for fluid pressure control, flow rate control, and flow path switching control.

  In this embodiment, as an actuator for reciprocatingly driving the spool 5 of the spool control valve in its axial direction, a coil (10) that generates magnetic force when supplied with electric power, and an axial direction by the generated magnetic force of this coil (10). A linear solenoid S (electromagnetic actuator) having a movable core (9) that moves to one side or the other side is adopted, but a negative pressure control valve is used as an actuator that reciprocates the spool 5 of the spool control valve in its axial direction. A negative pressure actuated actuator that is driven by a negative pressure from an electric vacuum pump may be employed.

  In addition, as an actuator, a motor that generates rotational power (torque) when supplied with electric power, a reduction mechanism that decelerates the rotation of the output shaft of the motor, and a rotary motion of the output portion of the reduction mechanism is converted into a reciprocating linear motion. An electric actuator provided with a conversion mechanism that performs this may be employed. In this embodiment, a large number of filter holes are circular small holes, but a large number of filter holes may be elliptical, oval or polygonal small holes.

1 Sleeve 2 Guide hole (Inner hole)
3 Strainer (1st strainer)
4 Strainer (second strainer)
21 IN port (input port)
22 OUT port (output port)
23 DRAIN port (discharge port)
24 F / B port (feedback port)
67 Groove on all circumference (first groove on outer circumference)
68 Groove on all circumference (second groove on outer circumference)

Claims (12)

(A) a cylindrical sleeve (1) having an inner hole (2) for accommodating the valve (5) so as to be reciprocally slidable in its axial direction;
(B) In a spool control valve provided with a strainer (3, 4) that is wound around the outer periphery of the sleeve (1) and prevents the inflow of foreign matter into the inner hole (2).
The sleeve (1)
An input port (21) for inputting an input pressure of fluid into the inner hole (2);
An output port (22) for adjusting the input pressure of the fluid to a predetermined output pressure and outputting from the inside of the inner hole (2);
A discharge port (23) for discharging the fluid flowing into the inner hole (2) from the input port (21) or the output port (22) to the low pressure side;
A feedback port (24) for feeding back the output pressure of the fluid output from the output port (22) to the valve (5);
The sleeve (1) has two first and second outer circumferential grooves (67, 68) formed at a predetermined distance in the axial direction and over the entire circumference of the sleeve (1). Have
The input port (21) has a first opening (71) opened at the bottom surface of the first outer circumferential groove (67),
The output port (22) has a second opening (72) opened at the bottom surface of the second outer circumferential groove (68),
The strainer (3, 4) is a belt-shaped first strainer (3) mounted around the first outer circumferential groove (67) so as to cover the first opening (71), and the second opening. A belt-shaped second strainer (4) mounted around the second outer circumferential groove (68) so as to cover the portion (72) ,
The output port (22) exists between the input port (21) and the feedback port (24) in the axial direction,
The second outer circumferential groove (68) and the feedback port (24) communicate with each other by an axial groove (69) formed in the outer circumferential wall (19) of the sleeve (1). Spool control valve to do. The spool control valve according to claim 1,
The first strainer (3) is attached by being wound around the entire circumferential direction of the first outer circumferential groove (67) and joining both circumferential ends of the first strainer (3) by welding. (81) The spool control valve characterized by the above-mentioned. The spool control valve according to claim 1 or 2,
The second strainer (4) is attached by being wound around the entire circumferential direction of the second outer circumferential groove (68) and joining both ends in the circumferential direction of the second strainer (4) by welding. (82) The spool control valve characterized by the above-mentioned. In the spool control valve according to any one of claims 1 to 3,
The sleeve (1) has a large-diameter inner hole (32) extending in the axial direction, a small-diameter inner hole (33) extending in the axial direction, having a smaller hole diameter than the large-diameter inner hole (32), and the large-diameter inner hole. (32) and the annular inner circumferential groove (34) formed between the small-diameter inner hole (33), and between the outer periphery of the valve (5) and the bottom surface of the inner circumferential groove (34). A cylindrical feedback chamber (35) communicating with the feedback port (24),
The spool control valve, wherein the large-diameter inner hole (32) and the small-diameter inner hole (33) constitute the inner hole (2). The spool control valve according to claim 4,
The valve (5) has a large-diameter portion (41) that slides directly on the wall surface of the large-diameter inner hole of the sleeve (1), and has a smaller outer diameter than the large-diameter portion (41). A small-diameter portion (42, 43) that slides directly on the wall surface of the small-diameter inner hole, and an annular constricted portion (44) formed between the large-diameter portion (41) and the small-diameter portion (42). ,
The spool control valve, wherein the constricted portion (44) is provided so as to be positioned in the feedback chamber (35) even when the valve (5) reciprocates in the axial direction thereof. The spool control valve according to claim 5,
The feedback pressure acting on the valve (5) is one side in the axial direction of the valve (5) (the tip side or the tip side) due to the pressure receiving area difference between the large diameter part (41) and the small diameter part (42). A spool control valve characterized by acting as an urging force to the base end side). The spool control valve according to claim 5 or 6,
The valve (5) has an outer diameter in the feedback chamber (35),
The spool control valve is set so that the outer diameter of the large-diameter portion (41)> the outer diameter of the small-diameter portion (42). The spool control valve according to any one of claims 5 to 7,
The spool control valve, wherein the feedback chamber (35) is installed next to the discharge port (23). The spool control valve according to any one of claims 5 to 8,
The sleeve is a cylindrical valve sleeve (1) fitted and disposed in a recess of a valve body of a hydraulic control device used for shift control of an automatic transmission,
The valve sleeve (1) forms a feedback flow path (L4) that communicates the output port (22) and the feedback port (24) by the axial groove (69) and the inner surface of the recess. A spool control valve characterized by that. The spool control valve according to claim 9,
The discharge port (23) has a third opening (73) opened at the outer peripheral surface of the valve sleeve (1),
The spool control valve, wherein the feedback flow path (L4) is formed across or avoiding the third opening (73). The spool control valve according to any one of claims 1 to 10,
The spool control valve, wherein the feedback port (24) has a fourth opening (74) opened at the bottom surface of the axial groove (69) . The spool control valve according to any one of claims 1 to 11,
The feedback port (24) has an orifice hole (24) for reducing fluctuations in the output pressure of the fluid discharged from the output port (22) by reducing the diameter of the hole. Spool control valve to do.