JP2013087807A - Spool control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate (re)adjustment of a load of a return spring 4 and to allow an adjusting screw 5 to be surely fixed to a mounting hole (a female screw hole) of a housing hole 2 of a valve body 1 in a set load adjusting device of an electromagnetic hydraulic control valve.SOLUTION: The screw-in position of the adjusting screw 5 with respect to the female screw hole of the housing hole 2 of the valve body 1 is adjusted to adjust output pressure of the electromagnetic hydraulic control valve, that is, a spring load of the return spring 4. After the adjustment of the output pressure of the electromagnetic hydraulic control valve, that is, after the end of the adjustment of the spring load of the return spring 4, a press-fitting part of a stopper 6 is press-fitted and fixed to the mounting hole 44 of the housing hole 2 of the valve body 1, thereby regulating the axial position of the adjusting screw 5 with respect to the female screw hole of the housing hole 2 of the valve body 1. As a result, the adjusting screw 5 is positioned and fixed to the female screw hole of the housing hole 2 of the valve body 1.

Description

  The present invention relates to a spool control valve, and more particularly to a support structure for an adjustment screw of a valve spring.

[Conventional technology]
Conventionally, for example, an electromagnetic hydraulic control valve (electromagnetic valve) is used for hydraulic control of an automatic transmission (AT), a continuously variable transmission (CVT), or the like (see, for example, Patent Document 1).
The electromagnetic valve includes a spool control valve that is accommodated in an accommodation hole formed in the valve body, and an electromagnetic actuator that moves a valve spool that is a valve body of the spool control valve to the opening side of the spool accommodation hole. .
The spool control valve is a cylindrical sleeve fitted in the accommodation hole, a valve spool that is supported so as to be slidable in the spool accommodation hole formed in the sleeve, and biases the valve spool toward the actuator. A compression coil spring and an adjusting screw for closing the opening of the spool housing hole are provided.

In the sleeve, a plurality of ports extending in the radial direction perpendicular to the axial direction of the spool accommodation hole are formed so as to communicate the inside and the outside of the sleeve. The plurality of ports includes a supply port to which oil is supplied, an output port from which oil is output, a feedback port that feeds back a valve spool, and a discharge port from which oil is discharged.
The valve spool slides directly on the hole wall surface of the sleeve. The valve spool has a plurality of lands that control the communication state between the supply port and the output port.
Here, one end of the compression coil spring housed in the spool housing hole (spring housing chamber) on the opening side of the valve spool is engaged with the end surface of the valve spool, and the other end is engaged with the end surface of the adjustment screw. It has been stopped.

A male screw that can be screwed with a female screw of a spool accommodation hole (screw mounting hole) is formed on the outer periphery of the adjustment screw. The part of the sleeve located on the outer periphery of the male screw is formed with two through holes that communicate with the spring accommodating chamber and open on the outer peripheral surface of the sleeve.
A caulking pin is inserted into the through hole of the sleeve, and the screw thread of the adjusting screw is crushed by the inserted caulking pin. Thereby, the adjustment screw is fixed to the sleeve.
That is, the output pressure of the oil is adjusted by changing the mounting load of the compression coil spring by rotating the adjustment screw and moving it in the axial direction. Thereafter, the adjustment screw is fixed at an arbitrary position in the sleeve by crushing the thread of the adjustment screw with a caulking pin.

Further, a valve body support hole formed coaxially with the output rod of the linear solenoid, a valve body having a plurality of ports, a spool valve body slidably disposed in the valve body support hole, and the spool valve A linear solenoid valve including a valve body spring that urges the body toward the linear solenoid and a bottomed thin cylindrical pressure regulating cap having a cylindrical press-fit cylinder portion is known (for example, see Patent Document 2). .
A pressure adjusting cap mounting hole is formed in the valve body. The pressure adjusting cap mounting hole has an inner diameter smaller than the outer diameter of the press-fitting cylinder portion and is opened at the end surface of the valve body so that the press-fitting cylinder portion of the pressure adjustment cap is press-fitted and fixed.
The set load of the valve body spring is adjusted by adjusting the press-fitting depth of the pressure adjusting cap into the pressure adjusting cap mounting hole.

[Conventional technical problems]
However, in the electromagnetic valve described in Patent Document 1, a working space for crushing the screw thread of the adjusting screw is required from the outside in the radial direction of the adjusting screw.
As a result, if the valve spool slides directly on the hole wall of the valve body and an oil passage is provided near the wall of the valve body at the outer periphery of the male screw of the adjustment screw, the screw of the adjustment screw By crushing the mountain with the caulking pin, there is a problem that a structure for fixing the adjusting screw at an arbitrary position in the sleeve cannot be used.

Moreover, in the linear solenoid valve described in Patent Document 2, the set load of the valve body spring is adjusted by adjusting the press-fitting depth of the pressure-control cap into the pressure-control cap mounting hole.
In this way, when the pressure adjusting cap is press-fitted into the pressure adjusting cap mounting hole of the valve body, it is very difficult to readjust the set load of the valve body spring when the target pressure is removed. For example, there is a problem that it is difficult to pull back the pressure adjusting cap that is press-fitted into the pressure adjusting cap mounting hole of the valve body to the opening side and fix it to the pressure adjusting cap mounting hole.

JP 09-166238 A Japanese Patent Laid-Open No. 10-311454

  An object of the present invention is to provide a spool control valve in which the spring load of a spring can be easily (re-) adjusted and the load adjusting member can be securely fixed to the accommodating hole of the valve body.

The invention according to claim 1 (spool control valve) is housed in a housing hole formed in the valve body and regulates the fluid pressure, and is housed in a housing hole of the valve body. A spring for applying a load in the axial direction of the housing hole of the body; a load adjusting member for adjusting the load of the spring; and a position restricting member for regulating the axial position of the load adjusting member with respect to the housing hole of the valve body. Yes.
The load adjusting member is fixed to the hole wall surface of the valve body by being screwed into the accommodation hole of the valve body.
The position restricting member is fixed to the hole wall surface of the valve body by being press-fitted into the accommodating hole of the valve body.

According to the first aspect of the present invention, the load of the spring is adjusted by adjusting the screwing amount of the load adjusting member with respect to the accommodating hole of the valve body.
After the load adjustment of the spring is completed, the position regulating member is press-fitted and fixed in the accommodation hole of the valve body, thereby regulating the position of the load adjustment member in the axial direction with respect to the accommodation hole of the valve body.
Therefore, since the load adjusting member is not press-fitted into the accommodating hole of the valve body, the (re) adjustment of the spring load is facilitated even when the target is deviated.
In addition, the position of the load adjusting member in the axial direction of the valve body housing hole can be regulated by the position regulating member that is press-fitted into the valve body housing hole after the load adjusting member is screwed into the valve body housing hole. The load adjusting member can be reliably fixed to the accommodating hole of the valve body.

According to invention of Claim 2, the internal thread for fixing by screwing a load adjustment member in the (accommodation) hole wall surface of a valve body is formed. Moreover, the external thread which can be fastened to the accommodation hole (female thread) of a valve body is formed in the outer peripheral surface of a load adjustment member.
Accordingly, the load adjusting member is fixed at an arbitrary position in the accommodating hole of the valve body by inserting the load adjusting member into the accommodating hole while rotating.
At this time, when the load of the spring is different from the target value, it is possible to easily return the load adjusting member to the opening side (loosen) or further to the back side. In other words, the (re) adjustment of the spring load becomes easy.

According to a third aspect of the present invention (spool control valve), a valve spool that is accommodated in an accommodation hole formed in the valve body and regulates fluid pressure, and is accommodated in an accommodation hole of the valve body. A spring for applying a load in the axial direction of the housing hole of the body, a load adjusting member for adjusting the load of the spring, a position regulating member for regulating the axial position of the load adjusting member with respect to the housing hole of the valve body, and a valve body And a positional deviation absorbing member that absorbs an axial positional deviation of the load adjusting member with respect to the receiving hole.
The load adjusting member is fixed to the hole wall surface of the valve body by being screwed into the accommodation hole of the valve body.
The position restricting member is fixed to the hole wall surface of the valve body by being press-fitted into the accommodating hole of the valve body.

According to the third aspect of the present invention, by providing the position shift absorbing member that absorbs the position shift in the axial direction of the load adjusting member with respect to the valve body receiving hole, the position regulating member is press-fitted into the valve body receiving hole. Since the load can be managed with a constant dimension, the press-fitting work of the position regulating member is facilitated.
Further, the positional deviation in the axial direction of the load adjusting member can be absorbed by the positional deviation absorbing member. As a result, the relative rotation and looseness of the load adjusting member with respect to the valve body can be absorbed, so that it is not necessary to readjust the spring load after adjusting the spring load.
According to the fourth aspect of the present invention, the misalignment absorbing member is installed between the position regulating member and the load adjusting member.
When the position deviation absorbing member is composed of a spring member such as a coil spring, wave washer, or plate spring, one end is locked (held) by the position regulating member, and the other end is locked by the load adjusting member. (Held).

According to the fifth aspect of the present invention, the valve spool is supported on the (housing) hole wall surface of the valve body so as to be slidable back and forth.
According to the sixth aspect of the present invention, the valve spool slides directly with the (housing) hole wall surface of the valve body.
According to the invention described in claim 7, the load adjusting member is provided with the first spring seat for receiving the spring load, and the valve spool is provided with the second spring seat for receiving the spring load. A spring is installed between the first spring seat of the load adjusting member and the second spring seat of the valve spool.

According to the invention described in claim 8, the accommodating hole of the valve body opens at least at one end surface in the axial direction, and extends in the axial direction (straight) from the opening side to the back side.
Note that the housing hole of the valve body may be opened at both end faces in the axial direction, and may be extended (straight) in the axial direction from one opening side to the other opening side.
According to the ninth aspect of the present invention, the actuator for driving the valve spool, which is the valve body of the spool control valve, toward the opening side in the axial direction of the accommodation hole of the valve body (the full lift side of the valve spool) is provided. .
According to the invention described in claim 10, the spring is provided to bias the valve spool toward the back side in the axial direction of the valve body housing hole (the initial position side of the valve spool).
Further, the spring is housed on the opening side of the housing hole in the axial direction with respect to the valve spool.

According to the eleventh aspect of the present invention, the sliding hole for directly sliding the valve spool is provided in a part of the accommodating hole of the valve body.
According to the twelfth aspect of the present invention, the mounting hole (screw hole) for fixing the load adjusting member is provided in a part of the accommodating hole of the valve body.
Further, the load adjusting member is accommodated on the opening side in the axial direction of the accommodation hole with respect to the spring.
According to the thirteenth aspect of the present invention, the mounting hole (press-fit hole) for fixing the position regulating member is provided in a part of the accommodating hole of the valve body.
Further, the position regulating member is accommodated on the opening side in the axial direction of the accommodation hole with respect to the load adjusting member.

(A) is the side view which showed the valve body which the some accommodation hole opened at one end surface, (b) is sectional drawing which showed the electrohydraulic control valve accommodated in the accommodation hole of a valve body (Example) 1). It is sectional drawing which showed the set load adjustment apparatus of the electromagnetic hydraulic control valve (Example 1). (A) is the side view which showed the valve body which the some accommodation hole opened at the end surface, (b) is sectional drawing which showed the electromagnetic hydraulic control valve accommodated in the accommodation hole of a valve body (Example 2) ). (Example 2) which was sectional drawing which showed the set load adjusting device of the electrohydraulic control valve.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
An object of the present invention is to facilitate (re) adjustment of a load of a valve spring that applies a load in the axial direction of a valve body housing hole to a valve spool, and to reliably fix a load adjusting member to the valve body housing hole. After the load adjusting member is screwed into the valve body housing hole, the position regulating member is press-fitted into the valve body housing hole to regulate the position of the load adjusting member in the axial direction relative to the valve body housing hole. It was realized.

[Configuration of Example 1]
1 and 2 show a first embodiment of the present invention. FIG. 1 (a) is a view showing a valve body having a plurality of receiving holes opened at one end surface, and FIG. 1 (b) is a view showing the valve body. FIG. 2 is a view showing a set load adjusting device of the electromagnetic hydraulic control valve.

The hydraulic control apparatus according to this embodiment is used for hydraulic control of an automatic transmission (AT), a continuously variable transmission (CVT), and the like mounted on an automobile.
The hydraulic control device includes a valve body 1 having a plurality of oil passages L1 to L6 and the like, and a valve spool 3, a return spring 4, an adjustment screw 5 and a stopper 6 in each accommodation hole 2 formed in the valve body 1. A plurality of electromagnetic hydraulic control valves that are accommodated, and a transmission control unit (electronic control unit: TCU) that controls the plurality of electromagnetic hydraulic control valves so as to realize a shift state requested by a driver or the like.

The TCU is mounted on the outer surface of the valve body 1 and controls the energization of a plurality of linear solenoids to drive the valve spools 3 of the plurality of electromagnetic hydraulic control valves, thereby performing a shift control of the automatic transmission and the like. Do.
The valve body 1 is installed in an oil pan attached to the lower part of the transmission case.
The valve body 1 is a spool support member that is formed in a flat plate shape by a metal material such as an aluminum alloy, for example, and supports the valve spool 3 so as to be slidable back and forth.

The valve body 1 is a valve holding member that holds a plurality of electrohydraulic control valves, and includes a plurality of accommodation holes 2, a plurality of oil passages L1 to L6, a plurality of first to fourth communication passages 11 to 14, and a plurality of A drain port 15 and a plurality of first and second openings 16 and 17 are provided.
In the valve body 1, as a plurality of oil passages through which hydraulic oil (oil) flows in and out, oil pressure is supplied from an oil pump as a hydraulic pressure generating means via an oil passage (not shown), a switching valve (not shown), and the like. The output pressure regulated by the valve spool 3 and the first communication path (IN port) 11 that communicates the supplied oil path (supply oil path, inlet (IN) oil path) L1 and the accommodation hole 2 is output. A second communication path (OUT port) 12 that communicates the oil path (output oil path, outlet (OUT) oil path) L2 and the accommodation hole 2, and an oil path that communicates with the oil path L2 (feedback (FB) oil path) A third communication path (FB port) 13 that communicates L3 and the accommodation hole 2 is formed.

The valve body 1 includes a fourth communication passage 14 that communicates an oil passage (exhaust (EX) oil passage) L4 connected to the low pressure side (oil pan oil reservoir and the like) and the accommodation hole 2, and a low pressure side (oil A drain port 15 that communicates the oil storage portion of the bread and the accommodation hole 2 is formed.
The first to fourth communication passages 11 to 14 and the drain port 15 communicate the inside and the outside of the accommodation hole 2 in a radius (radiation) direction perpendicular to the axial direction of the accommodation hole 2.
The first and second communication passages 11 and 12 are opened at positions separated from each other by a predetermined distance in the axial direction of the accommodation hole 2. Further, the first and third communication passages 11 and 13 are opened at positions spaced apart from each other in the axial direction of the accommodation hole 2.

The valve body 1 opens at one end face and the other end face (both end faces) in the axial direction, and from the first opening (insertion opening) 16 on one end side in the axial direction to the second opening 17 on the other end side (back side). The housing hole 2 extends straight up to the end. A plurality of the accommodation holes 2 are provided in parallel.
Each first opening 16 of the plurality of receiving holes 2 communicates the inside and the outside of the valve body 1 in the axial direction of the receiving hole 2. The first opening 16 also serves as a drain port (EX port) that communicates the low-pressure side (such as an oil storage part of an oil pan) and the accommodation hole 2.
A cylindrical extension portion (cylindrical portion) 18 extends from the end surface of the valve body 1 on the solenoid side (second opening portion 17 side) to the other side in the axial direction. An annular flange 19 that is coupled to the linear solenoid is integrally formed at the end of the cylindrical portion 18.

Next, details of the electromagnetic hydraulic control valve of the present embodiment will be described with reference to FIGS.
At least one of the plurality of electromagnetic hydraulic control valves adjusts the hydraulic pressure (line pressure) generated by an oil pump (not shown) that is hydraulic pressure generating means driven by the internal combustion engine (engine). And a solenoid valve for sending to a friction engagement element (clutch or brake) incorporated in the automatic transmission.
The electromagnetic hydraulic control valve constitutes an electromagnetic spool control valve that inputs line hydraulic pressure into the accommodation hole 2 and regulates and outputs the line hydraulic pressure input into the accommodation hole 2.
The valve body 1 is equipped with an electromagnetic actuator (linear solenoid) that drives the valve spool 3 of the electromagnetic hydraulic control valve toward the opening side (full lift side) in the axial direction of the accommodation hole 2.

  Here, the linear solenoid is energized with a non-magnetic shaft 21 connected to the valve spool 3 so as to be integrally movable, and a magnetic plunger 22 connected so as to be integrally movable with the valve spool 3 and the shaft 21. A coil 23 that generates magnetic flux around it, an external connection connector 24 for connecting the coil 23 to an external circuit (external power supply or external control circuit: TCU), and a magnetic path on the inner peripheral side of the coil 23 Coil inner peripheral side fixed core (stator cores 25, 26, magnetoresistive portion 27, ring-shaped magnetic component 28) and coil outer peripheral side fixed core (bottomed cylindrical shape) forming a magnetic path on the outer peripheral side of the coil 23 Yoke 29).

The plunger 22 is made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 23 is energized.
The plunger 22 is a magnetic moving body that constitutes a part of a magnetic circuit formed by energization of the coil 23, and is a movable core (moving core) that can reciprocate in the axial direction in the stator core 26. is there. The plunger 22 is urged toward the bottom surface side of the yoke 29 together with the valve spool 3 and the shaft 21 by the urging force of the return spring 4 transmitted to the valve spool 3. Further, the plunger 22 is provided with a breathing hole 30 in the axial direction that communicates with both end faces of the plunger in order to ensure the flow of oil in the space before and after the plunger due to the displacement in the stator core 26.

The coil 23 is magnetic flux generating means (magnetic force generating means) that generates a magnetic force that draws the plunger 22 toward the magnetic attracting portion 31 of the stator core 25 when supplied with electric power (when a current is applied or energized). When the coil 23 is energized, a magnetic circuit is formed in which magnetic flux concentrates through the plunger 22, the stator cores 25 and 26, the magnetoresistive portion 27, and the yoke 29.
The coil 23 drives the valve spool 3, the shaft 21, and the plunger 22 to one side (front side) in the axial direction of the valve body 1 and the valve spool 3 by magnetic force. The coil 23 is a solenoid coil obtained by winding a conductive wire with an insulating coating around a bobbin 32 made of synthetic resin having insulation properties a plurality of times.

The coil 23 has a coil portion wound around the bobbin 32 and a pair of coil terminal leads drawn from the coil portion.
The pair of coil terminal leads are connected to an external circuit (external power supply or external control circuit: TCU) via a terminal (external connection terminal) 33 of the external connection connector 24. The outer periphery of the coil 23 and the conductive joint between the coil 23 and the terminal 33 are covered and protected by an insulating mold resin material.
The outer periphery of the mold resin material forms a housing for the external connection connector 24 that exposes and accommodates the tip of the terminal 33.

A magnetic stator composed of a coil inner peripheral fixed core and a coil outer peripheral fixed core is a magnetic fixed member made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 23 is energized. .
The coil inner peripheral fixed core includes stator cores 25 and 26 that slidably fit and support the shaft 21 and the plunger 22 in the axial direction thereof, and a magnetoresistive portion 27 that reduces the flow of magnetic flux between the stator cores 25 and 26. The ring-shaped magnetic component 28 is integrally provided with a magnetic material.
The stator core 25 and the stator core 26 may be connected with a nonmagnetic material interposed therebetween.

The magnetic resistance portion 27 is constituted by a thin portion that connects the stator cores 25 and 26.
The magnetic component 28 is configured as a separate component with respect to the bobbin 32 and the stator cores 25 and 26 of the coil 23.
The yoke 29 is an integral part in which a concave portion extending from the open end side to the far side is integrally provided with a magnetic material.

Here, in the electrohydraulic control valve of the present embodiment, the valve spool 3, the shaft 21 and the plunger 22 with respect to the initial position increase as the supply power such as the applied voltage value or supply current value to the coil 23 of the linear solenoid increases. The stroke amount (lift amount, movement amount) is configured to be large.
Further, in the electromagnetic hydraulic control valve, the outer diameters of the flange 19 of the valve body 1 and the flange 34 of the stator core 25 are matched, and the flanges 19 and 34 are accommodated in the inner peripheral surface of the thin portion 35 on the opening end side of the yoke 29. Later, the thin-walled portion 35 is bent inward to fix the flanges 19 and 34 by caulking.

In the linear solenoid configured as described above, when the coil 23 is energized through the terminal 33, the magnetic flux is circulated around the coil 23 in the order of the yoke 29, the stator core 25, the plunger 22, the stator core 26, and the yoke 29. Is formed. Thereby, a magnetic attraction force acts between the magnetic attraction portion 31 of the stator core 25 and the plunger 22 to attract the plunger 22.
Here, since the shaft 21 slidable in the axial direction through the sliding hole of the bearing portion of the stator core 25 is in contact with the distal end surface of the plunger 22, the shaft 21 moves in the axial direction as the plunger 22 is sucked. It is pushed forward (left direction in the figure). As a result, the valve spool 3 of the electromagnetic hydraulic control valve is driven by the linear solenoid.

Next, details of the set load adjusting device for the electromagnetic hydraulic control valve of this embodiment will be described with reference to FIGS.
The electromagnetic hydraulic control valve includes a set load adjusting device (a load adjusting device for the electromagnetic spool control valve) that adjusts the set load (spring load) of the return spring 4 according to the screwing position of the adjusting screw 5.
The set load adjusting device for the electrohydraulic control valve includes a valve spool 3 supported so as to be reciprocally movable (slidable) in the accommodation hole 2 of the valve body 1, and a load in the axial direction of the accommodation hole 2 ( A return spring 4 that applies a spring load), an adjustment screw 5 that adjusts the spring load of the return spring 4, and a stopper 6 that regulates the axial position of the adjustment screw 5.

Here, the electrohydraulic control valve of this embodiment is a spool control valve in which a valve spool 3, a return spring 4, an adjustment screw 5 and a stopper 6 are accommodated in an accommodation hole 2 formed in the valve body 1.
Here, the accommodation hole 2 has a plurality of sliding holes 41 that support the valve spool 3 so as to be slidable back and forth. The housing hole 2 closer to the first opening 16 than the plurality of sliding holes 41 is provided with a spring housing chamber 42 having a circular cross section for accommodating the return spring 4 in an extendable manner.
The accommodation hole 2 on the first opening 16 side of the spring accommodation chamber 42 is provided with a mounting hole (female screw hole) having a circular cross section for fixing the adjusting screw 5. A female screw 43 into which the adjusting screw 5 is screwed is formed on the hole wall surface of the female screw hole of the valve body 1.

In addition, the housing hole 2 closer to the first opening 16 than the female screw hole is provided with a mounting hole (press-fit hole) 44 having a circular cross section for fixing the stopper 6.
The accommodation hole 2 has an opening diameter (hole diameter) that decreases in the order of an attachment hole (press-fit hole) 44, an attachment hole (female screw hole), and a plurality of sliding holes 41. Further, the opening diameter (hole diameter) of the first opening 16 and the attachment hole (press-fit hole) 44 may be different. For example, the opening diameter (hole diameter) from the first opening 16 to the end of the mounting hole 44 (immediately before the female screw 43) may be gradually reduced. Or you may make it small in steps.

The oil passage L1 formed in the valve body 1 includes a first communication passage 11 through which oil flows from the outside of the electromagnetic hydraulic control valve toward the inside (communication chamber (cylindrical communication portion 45) of the accommodation hole 2), and The first communication passage 11 communicates with the accommodation hole 2 side, and has an annular first concave groove (input groove) 46 opened at the hole wall surface of the accommodation hole 2 of the valve body 1. The first concave groove 46 extends in the circumferential direction on the hole wall surface of the accommodation hole 2 of the valve body 1. Further, the first concave groove 46 is recessed outward from the hole wall surface of the valve body 1 in the radial direction.
The oil passage L2 formed in the valve body 1 has a second communication passage 12 through which oil flows out from the inside of the electromagnetic hydraulic control valve (the communication chamber 45 of the housing hole 2).

The oil passage L3 formed in the valve body 1 includes a third communication passage 13 through which oil flows from the oil passage L2 toward the inside (the communication chamber 45 of the accommodation hole 2), and the third communication passage 13 and the accommodation hole 2. The ring-shaped third concave groove 47 opened at the hole wall surface of the accommodating hole 2 of the valve body 1 is provided. The third concave groove 47 extends in the circumferential direction on the hole wall surface of the accommodating hole 2 of the valve body 1. The third concave groove 47 is recessed outward from the hole wall surface of the valve body 1 in the radial direction.
The oil passage L4 formed in the valve body 1 has a fourth communication passage 14 through which oil flows out from the inside (communication chamber 45 of the accommodation hole 2) of the electromagnetic hydraulic control valve toward the outside (oil storage portion of the oil pan). In addition, the fourth communication passage 14 communicates with the accommodation hole 2 side, and has an annular fourth concave groove 48 opened at the hole wall surface of the accommodation hole 2 of the valve body 1. The fourth concave groove 48 extends in the circumferential direction on the hole wall surface of the accommodation hole 2 of the valve body 1. Further, the fourth concave groove 48 is recessed outward from the hole wall surface of the valve body 1 in the radial direction.

The valve spool 3 constitutes a valve body of an electrohydraulic control valve, and is inserted into the accommodation hole 2 of the valve body 1 so as to be reciprocally movable. The valve spool 3 is inserted from the first opening 16 of the valve body 1 and is accommodated in the accommodation hole 2. The valve spool 3 is supported on the hole wall surface of the accommodation hole 2 of the valve body 1 so as to be slidable back and forth. Further, the valve spool 3 has a plurality of lands 51 to 53 for controlling the communication state between the plurality of oil passages L1 to L4.
The outer peripheral surfaces of the lands 51 to 53 are sliding portions (sliding surfaces) that slide directly with the hole wall surface of the housing hole 2 of the valve body 1. A sliding clearance for enabling the valve spool 3 to reciprocate is formed between the sliding surfaces of the lands 51 to 53 and the hole wall surface of the receiving hole 2 of the valve body 1. .

The land 51 of the valve spool 3 has a step perpendicular to the axial direction of the valve spool 3 between the land 51 and the spool shaft portion having a smaller diameter than the land 51.
Further, a plurality of (two) notches 54 are formed on the edge of the land 51 by cutting out from the vertical surface of the step, that is, from the end surface on the communication chamber 45 side (spool shaft side) to the outer peripheral surface of the land 51. Is formed.
The plurality of notches 54 are formed in the circumferential direction of the land 51 at a predetermined interval (for example, an angular interval of 180 °). The plurality of notches 54 control the flow rate of oil flowing from the oil passage L <b> 1 to the communication chamber 45 with the first concave groove 46 of the valve body 1. As a result, a spool control valve having a characteristic (stroke-opening area characteristic) in which the opening area of the first communication passage 11 of the oil passage L1 gradually changes with respect to the stroke change (movement amount) of the valve spool 3 can be configured. .
The land 51 of the valve spool 3 has a function of changing the opening area of the oil passage L <b> 1 according to the amount of movement with respect to the valve body 1.

Since the electromagnetic hydraulic control valve of the present embodiment is a normally open type electromagnetic valve, the valve body 1 is provided with a plurality of notches 54 at the initial position of the valve spool 3 (the lift amount and the movement amount are zero). A communication chamber 45 formed between the hole wall surface of the accommodation hole 2 and the outer periphery of the spool shaft portion of the valve spool 3 communicates with the oil passage L1.
Further, a communication chamber 45 formed between the hole wall surface of the accommodating hole 2 of the valve body 1 and the outer periphery of the spool shaft portion communicates with the oil passage L2.

The electrohydraulic control valve displaces (moves) the valve spool 3 in the axial direction by the operation of the linear solenoid, so that the communication area between the oil path L1 and the oil path L2 and the communication area between the oil path L2 and the oil path L4 Changes. Thereby, the hydraulic pressure generated in the oil passage L2 is regulated.
In the present embodiment, the opening area of the oil passage L1 gradually decreases as the valve spool 3 moves to the left side (the first opening 16 side) in the figure.
Here, the adjustment screw 5 and the valve spool 3 are provided with a spring seat (first spring seat) 55 and a spring seat (second spring seat) 56 that receive the spring load of the return spring 4.

The return spring 4 generates a urging force (spring load, spring force) that urges the valve spool 3 toward the back side in the axial direction of the housing hole 2 (the other end side, the initial position side, the solenoid side). Is configured. The return spring 4 is accommodated in the accommodation hole 2 closer to the first opening 16 in the axial direction of the accommodation hole 2 than the valve spool 3 so as to be extendable and contractible.
The return spring 4 has a coil wound in a spiral between the spring seat portion 55 of the adjustment screw 5 and the spring seat portion 56 of the valve spool 3. An annular first coil end portion that contacts the spring seat portion 55 of the adjustment screw 5 is provided on one end side (first opening portion 16 side) in the axial direction of the coil of the return spring 4.
An annular second coil end portion that contacts the spring seat portion 56 of the valve spool 3 is provided on the other end side (second opening portion 17 side, spool side) of the coil of the return spring 4 in the axial direction. .

The adjustment screw 5 is formed in a cylindrical shape from a metal material such as an aluminum alloy, for example, and is accommodated in the accommodation hole 2 on the first opening 16 side in the axial direction of the accommodation hole 2 relative to the return spring 4. The adjusting screw 5 is fixed to the hole wall surface of the mounting hole of the valve body 1 by being screwed into the female screw 43 of the accommodating hole 2 of the valve body 1. The adjusting screw 5 is a load adjusting member that adjusts the spring load of the return spring 4 according to the amount of screwing (screwing amount) of the housing hole 2 of the valve body 1 into the female screw 43.
The adjustment screw 5 has a concave spring seat portion (concave portion) 55 that receives the spring load of the return spring 4.

The adjustment screw 5 has first to third cylindrical portions 61 to 63.
The first cylindrical portion 61 is the maximum outer diameter portion of the adjusting screw 5 and is provided so as to surround the spring seat portion 55 and the second cylindrical portion 62 in the circumferential direction. On the outer peripheral surface of the first cylindrical portion 61, a male screw 64 that is screwed with the female screw 43 of the accommodation hole 2 of the valve body 1 is formed.
An annular contact surface 65 with which the stopper 6 contacts is provided on one end surface (annular end surface) in the axial direction of the second cylindrical portion 62. In addition, an engagement portion (cross groove or hexagonal groove) 66 with which a tool for twisting the adjustment screw 5 is engaged is provided inside the second cylindrical portion 62. The spring load of the return spring 4 applied to the valve spool 3 is adjusted by fitting a tool into the engaging portion 66 and adjusting the screwing amount of the adjusting screw 5.
The third cylindrical portion 63 is provided with a facing surface 67 facing the valve spool 3 with a predetermined axial distance. The third cylindrical portion 63 is provided on the inner side in the radial direction than the spring seat portion 55.
The adjusting screw 5 has a breathing hole 68 that communicates with both end faces of the adjusting screw in order to ensure the flow of oil in the front and rear space of the screw accompanying the displacement of the valve spool 3 in the housing hole 2 of the valve body 1. In the direction.

The stopper 6 is formed in a predetermined shape from a metal material such as an aluminum alloy, for example, and is accommodated in the accommodation hole 2 on the first opening 16 side in the axial direction of the accommodation hole 2 relative to the adjustment screw 5. The stopper 6 is a position restricting member that restricts the position of the adjusting screw 5 in the axial direction with respect to the female screw 43 of the accommodating hole 2 of the valve body 1.
The stopper 6 includes a cylindrical portion 71 that locks the second cylindrical portion 62 of the adjustment screw 5, and an annular flange (annular portion) 72 provided at one end of the cylindrical portion 71 in the axial direction. Yes.
A contact surface 73 that contacts the contact surface 65 of the second cylindrical portion 62 is provided on the other end surface of the cylindrical portion 71 in the axial direction.

A press-fit portion 74 that is press-fitted and fitted into the mounting hole 44 of the housing hole 2 of the valve body 1 is provided on the outer circumferential portion of the flange 72 in the entire circumferential direction (entire circumference). The press-fit portion 74 has an outer diameter that is slightly larger than the inner diameter of the mounting hole 44 of the accommodation hole 2 of the valve body 1. Accordingly, the stopper 6 is fixed to the hole wall surface of the mounting hole 44 of the valve body 1 by press-fitting the press-fitting portion 74 of the flange 72 into the mounting hole 44 of the accommodating hole 2 of the valve body 1.
The stopper 6 has a breathing hole 75 communicating with both end faces of the stopper in the axial direction in order to ensure the flow of oil in the space before and after the stopper due to the displacement of the valve spool 3 in the accommodation hole 2 of the valve body 1. Is provided.

Here, as a procedure for assembling the electrohydraulic control valve of this embodiment, a linear solenoid is caulked and fixed to the flange 19 of the cylindrical portion 18 of the valve body 1, whereby the second opening 17 of the accommodation hole 2 of the valve body 1. Block the side.
Then, the valve spool 3 and the return spring 4 are sequentially inserted from the first opening 16 side (opening side) of the housing hole 2 of the valve body 1 toward the back side (shaft 21 side) of the housing hole 2.
Then, the adjusting screw 5 is inserted into the mounting hole (female screw hole) of the accommodating hole 2 from the opening side of the accommodating hole 2 of the valve body 1, and the return spring 4 is compressed by the adjusting screw 5 while the spring of the return spring 4 is compressed. The adjustment screw 5 is screwed into the mounting hole (female screw hole) of the accommodation hole 2 of the valve body 1 until the load reaches an appropriate value (target value).
After adjusting the spring load of the return spring 4, the stopper 6 is inserted into the mounting hole 44 of the accommodation hole 2 from the opening side of the accommodation hole 2 of the valve body 1, and the stopper 6 comes into contact with the adjustment screw 5. The stopper 6 is press-fitted into the mounting hole 44 of the receiving hole 2 of the valve body 1 up to the position.
As a result, the adjustment screw 5 is prevented from being fixed (fixed) to the female screw 43 of the accommodation hole 2 of the valve body 1.

[Operation of Example 1]
Next, the operation of an electromagnetic hydraulic control valve used for hydraulic control of an automatic transmission (AT), a continuously variable transmission (CVT), etc. will be briefly described with reference to FIGS.

When electric power is not supplied to the coil 23, the valve spool 3, the shaft 21 and the plunger 23 are stopped at the initial position on the solenoid side by the urging force of the return spring 4 (state of FIG. 1).
That is, when the valve spool 3 is in the rightmost position (initial position) in FIG. 1 in the accommodation hole 2 of the valve body 1, the spool shaft portion of the valve spool 3 is connected via the first concave groove 46 and the notch 54. The communication chamber 45 provided so as to surround the periphery in the circumferential direction communicates with the first communication passage 11 of the oil passage L1, and the oil passage L1 is opened (fully opened).
Accordingly, the first communication passage 11 and the first groove 46 of the oil passage L1 and the second communication passage 12 of the oil passage L2 communicate with each other through the communication chamber 45.

Accordingly, the oil flowing from the oil pump through the oil passage L1 of the valve body 1 into the first communication passage 11 passes through the first concave groove 46 and the notch 54 to the inside of the electromagnetic hydraulic control valve (communication chamber 45). Flow into. Further, oil is output from the inside of the electromagnetic hydraulic control valve (communication chamber 45) to the oil passage L2 through the second communication passage 12, and the hydraulic pressure acting on the clutch (or brake) is maximized.
Thus, the electromagnetic hydraulic control valve of this embodiment functions as a normally open type solenoid valve because the oil passage L1 and the oil passage L2 communicate with each other when power is not supplied to the coil 23. To do.

  On the other hand, when electric power is supplied to the coil 23 (current application), the plunger 22 is attracted to the magnetic attraction portion 31 of the stator core 25 by a magnetic attraction force corresponding to the magnitude of the current flowing through the coil 23. Along with this, the shaft 21 having the valve spool 3 connected to the tip is pushed forward in the axial direction, whereby the valve spool 3 moves to the first opening 16 side of the accommodation hole 2 of the valve body 1.

Here, when the valve spool 3 moves from the initial position toward the first opening 16 side in the axial direction of the housing hole 2 by a predetermined stroke amount, the valve spool 3 moves to the sliding hole 41 of the housing hole 2 of the valve body 1. A portion of the notch 54 overlaps and the notch 54 is partially blocked.
At this time, the valve spool 3 acts on the valve spool 3 by the thrust (magnetic attractive force) of the plunger 22, the spring load of the return spring 4, and the oil pressure (feedback oil pressure) input from the oil passage L 2 to the oil passage L 3. Stopping at a position where the feedback force (axial force) is balanced, and the opening area of the first communication passage 11 and the first groove 46 of the oil passage L1 is reduced as the valve spool 3 moves to the first opening 16 side. .

Accordingly, the oil flowing into the first communication path 11 from the oil pump through the oil path L1 flows into the interior (communication chamber 45) of the accommodation hole 2 of the valve body 1 through the first concave groove 46 and the notch 54. To do. Furthermore, oil is output from the communication chamber 45 to the oil passage L2 via the second communication passage 12, and the hydraulic pressure acting on the clutch (or brake) is lowered.
Further, when the stroke amount of the valve spool 3 becomes larger, the opening areas of the first communication passage 11 and the first concave groove 46 of the oil passage L1 become smaller as the stroke amount of the valve spool 3 increases. Along with this, oil is output from the second communication passage 12 to the oil passage L2, and the hydraulic pressure acting on the clutch (or brake) decreases. That is, the hydraulic pressure (output pressure) output to the clutch (or brake) is adjusted according to the overlap amount in which part of the land 51 of the valve spool 3 and the oil passage L1 overlap.

[Effect of Example 1]
As described above, in the set load adjusting device for the electrohydraulic control valve according to the present embodiment, the valve spool 3 that regulates the output pressure output to the clutch (or brake) in the accommodation hole 2 formed in the valve body 1. And a return spring 4 for applying a load on the second opening 17 side (back side) in the axial direction of the receiving hole 2 to the valve spool 3, and a hole wall surface of the sliding hole 41 of the receiving hole 2 of the valve body 1 Further, the lands 51 to 53 of the valve spool 3 are configured to slide directly.
Further, the adjustment of the output pressure of the electromagnetic hydraulic control valve, that is, the adjustment of the spring load of the return spring 4 is performed by changing the screwing position of the first cylindrical portion 61 of the adjusting screw 5 with respect to the female screw 43 of the accommodating hole 2 of the valve body 1. Made by adjusting.

Then, after the adjustment of the output pressure of the electromagnetic hydraulic control valve, that is, the adjustment of the spring load of the return spring 4 is completed, the stopper 6 is press-fitted and fixed in the mounting hole 44 of the accommodation hole 2 of the valve body 1, whereby the valve body 1. The position of the adjusting screw 5 in the axial direction relative to the female screw 43 of the receiving hole 2 is restricted. That is, the adjusting screw 5 is positioned and fixed in the mounting hole (female screw hole) of the accommodation hole 2 of the valve body 1.
Therefore, since a load adjusting member such as an adjusting screw is not press-fitted into the accommodating hole 2 of the valve body 1, even if the output pressure deviates from the target value (target pressure), the press-fitted portion of the flange 72 of the stopper 6 Before press-fitting 74, the (re) adjustment of the output pressure of the electromagnetic hydraulic control valve, that is, the (re) adjustment of the spring load of the return spring 4 is facilitated.

  Further, after the male screw 64 of the first cylindrical portion 61 of the adjusting screw 5 is screwed into the female screw 43 of the housing hole 2 of the valve body 1, a stopper that is press-fitted into the mounting hole 44 of the housing hole 2 of the valve body 1. 6 can regulate the axial position of the adjusting screw 5 with respect to the female screw 43 of the receiving hole 2 of the valve body 1. As a result, the adjustment screw 5 can be reliably fixed to the female screw 43 of the housing hole 2 of the valve body 1. That is, it is possible to prevent the adjustment screw 5 from rotating (including locking) against the female screw 43 of the accommodation hole 2 of the valve body 1.

  3 and 4 show a second embodiment of the present invention. FIG. 3 (a) is a view showing a valve body having a plurality of receiving holes opened at the end face, and FIG. 3 (b) is a view of the valve body. FIG. 4 is a view showing an electromagnetic hydraulic control valve accommodated in the accommodation hole, and FIG. 4 is a view showing a set load adjusting device of the electromagnetic hydraulic control valve.

  The set load adjusting device for the electrohydraulic control valve according to the present embodiment includes a valve spool 3 supported so as to be reciprocally slidable in the accommodating hole 2 of the valve body 1, and 2 Return spring 4 biased toward the opening 17 side (initial position side), an adjustment screw 5 for adjusting the spring load of the return spring 4, and a stopper 6 for regulating the axial position of the adjustment screw 5 The absorber spring 7 that is a position shift absorbing member that absorbs the position shift in the axial direction of the adjusting screw 5 with respect to the housing hole 2 of the valve body 1 and the valve spool 3 on the first opening 16 side in the axial direction of the housing hole 2 ( And a linear solenoid that drives toward the full lift side.

Here, the accommodating hole 2 of the valve body 1 includes a plurality of sliding holes 41 that support the valve spool 3 so as to be reciprocally slidable, a spring accommodating chamber 42 having a circular cross section that accommodates the return spring 4 in an extendable manner, and an adjustment. A mounting hole (female screw hole) having a circular cross section for fixing the screw 5 is provided. On the wall surface of the female screw hole of the valve body 1, a female screw 43 that is screwed with the male screw 64 of the first cylindrical portion 61 of the adjusting screw 5 is formed.
The housing hole 2 on the first opening 16 side of the female screw hole is provided with a spring housing chamber 49 having a circular cross section that accommodates the absorber spring 7 in an extendable manner. In addition, the accommodation hole 2 closer to the first opening 16 than the spring accommodation chamber 49 is provided with a mounting hole (press-fit hole) 50 having a circular cross section for fixing the stopper 6.
Here, the stopper 6 and the adjustment screw 5 are provided with a spring seat (first spring seat) 81 and a spring seat (second spring seat) 82 that receive the spring load of the absorber spring 7.

The stopper 6 is formed in an annular plate shape by a metal material such as an aluminum alloy, and is accommodated in the accommodation hole 2 on the first opening 16 side in the axial direction of the accommodation hole 2 with respect to the adjustment screw 5. . The stopper 6 is a position restricting member that restricts the position of the adjusting screw 5 in the axial direction with respect to the female screw 43 of the accommodating hole 2 of the valve body 1.
Further, the stopper 6 has an annular portion 83 that is disposed with a predetermined axial distance between the stopper 6 and the adjusting screw 5.
The annular portion 83 is provided with a facing surface facing the adjustment screw 5 with a predetermined axial distance therebetween. The spring seat portion 81 is provided on the opposing surface of the annular portion 83.

A press-fit portion 84 that is press-fitted into the mounting hole 44 of the housing hole 2 of the valve body 1 is provided on the entire circumference direction (entire circumference) of the annular portion 83. The press-fit portion 84 has an outer diameter that is slightly larger than the inner diameter of the mounting hole 44 of the accommodation hole 2 of the valve body 1. Accordingly, the stopper 6 is fixed to the hole wall surface of the mounting hole 44 of the valve body 1 by press-fitting the press-fitting portion 84 of the annular portion 83 into the mounting hole 44 of the accommodation hole 2 of the valve body 1.
The stopper 6 is provided with a breathing hole 85 in the axial direction communicating with both end faces of the stopper in order to ensure the oil flow in the space before and after the stopper in accordance with the displacement of the valve spool 3 in the accommodating hole 2 of the valve body 1. ing.

The absorber spring 7 is a screw spring that generates an urging force (spring load, spring force) that urges the adjustment screw 5 toward the back side (the other end side, the initial position side, the solenoid side) of the housing hole 2 in the axial direction. Is configured. The absorber spring 7 is accommodated in the accommodation hole 2 on the first opening 16 side in the axial direction of the accommodation hole 2 so as to be extendable and retractable from the adjustment screw 5.
The absorber spring 7 has a coil wound in a spiral between the spring seat portion 81 of the stopper 6 and the spring seat portion 82 of the adjustment screw 5.
An annular first coil end portion that contacts the spring seat portion 81 of the stopper 6 is provided on one end side (first opening portion 16 side) in the axial direction of the absorber spring 7.
On the other end side in the axial direction of the absorber spring 7 (second opening 17 side, spool side), an annular second coil end portion that contacts the spring seat portion 82 of the adjusting screw 5 is provided.

Here, in the electromagnetic hydraulic control valve of the first embodiment, it is necessary to manage the press-fitting load and the press-fitting allowance when the stopper 6 is press-fitted. In particular, if an excessive load is applied and the stopper 6 is excessively press-fitted, the female screw 43 of the accommodation hole 2 of the valve body 1 that is screwed with the male screw 64 of the adjusting screw 5 may be damaged.
Accordingly, by providing an absorber spring 7 between the adjusting screw 5 and the stopper 6 for absorbing the displacement of the adjusting screw 5 in the axial direction with respect to the receiving hole 2 of the valve body 1, the mounting hole 2 of the valve body 1 can be attached. Since the press-fitting load of the stopper 6 with respect to the hole 44 can be managed with a fixed dimension, the press-fitting work of the stopper 6 becomes easy. Further, the displacement of the adjusting screw 5 can be absorbed by elastic deformation of the absorber spring 7. That is, it is possible to reliably prevent the adjustment screw 5 from rotating around the female screw 43 of the accommodation hole 2 of the valve body 1 (including a loosening prevention).

[Modification]
In this embodiment, the spool control valve of the present invention is applied to an electromagnetic hydraulic control valve incorporated in a hydraulic control device that performs hydraulic control of an automatic transmission of an automobile. You may apply to a control valve, a fluid flow control valve, and a flow-path switching control valve.
Further, as a spool control valve, not only hydraulic oil (ATF) used in an automatic transmission, but also fuel supplied to an internal combustion engine (engine), and supply to a sliding portion of the internal combustion engine (engine) and the automatic transmission You may apply to the fluid pressure control valve which controls flow volume and pressure, such as cooling water circulated and supplied to high temperature parts, such as lubricating oil and an internal combustion engine (engine).

In this embodiment, the actuator that drives the valve spool 3 of the spool control valve of the present invention toward the first opening 16 side is constituted by a linear solenoid that is an electromagnetic actuator. The actuator that drives the valve spool toward the opening side may be an electric actuator that uses an electric motor as a drive source, or a negative pressure actuated actuator that includes an electromagnetic or electric negative pressure control valve.
Further, the spool control valve of the present invention may be changed from a normally open type to a normally closed type.

DESCRIPTION OF SYMBOLS 1 Valve body 2 Valve body accommodation hole 3 Valve spool 4 Return spring 5 Adjustment screw (load adjustment member)
6 Stopper (position restriction member)
7 Absorber spring (position displacement absorbing member)
DESCRIPTION OF SYMBOLS 16 1st opening part of accommodation hole 17 2nd opening part of accommodation hole 41 Sliding hole of valve body 42 Spring accommodation chamber of valve body 43 Female screw of valve body attachment hole (female screw hole) 44 Valve body attachment hole (Press-fit hole)
45 Communication chamber 55 Adjust screw spring seat (first spring seat)
56 Spring seat of the valve spool (second spring seat)
61 1st cylinder part 62 2nd cylinder part 63 3rd cylinder part 64 Male screw of adjustment screw

Claims (13)

(A) a valve spool that is accommodated in an accommodation hole formed in the valve body and regulates fluid pressure;
(B) a spring that is accommodated in the accommodation hole and applies a load in the axial direction of the accommodation hole to the valve spool;
(C) a load adjusting member that is fixed to the hole wall surface of the valve body by being screwed into the accommodation hole, and that adjusts the load of the spring according to the amount of screwing into the accommodation hole;
(D) A spool control valve provided with a position restricting member that is fixed to the hole wall surface of the valve body by being press-fitted into the accommodating hole and restricts the position of the load adjusting member in the axial direction relative to the accommodating hole. The spool control valve according to claim 1,
On the hole wall surface of the valve body, a female screw is formed,
2. A spool control valve according to claim 1, wherein a male screw threadedly engaged with the female screw is formed on an outer peripheral surface of the load adjusting member. The spool control valve according to claim 1 or 2,
A spool control valve comprising a positional deviation absorbing member that absorbs an axial positional deviation of the load adjusting member with respect to the accommodation hole. The spool control valve according to claim 3,
The spool control valve, wherein the position deviation absorbing member is installed between the position regulating member and the load adjusting member. In the spool control valve according to any one of claims 1 to 4,
The spool control valve, wherein the valve spool is slidably supported on a hole wall surface of the valve body. In the spool control valve according to any one of claims 1 to 5,
The spool control valve, wherein the valve spool slides directly with a hole wall surface of the valve body. The spool control valve according to any one of claims 1 to 6,
The load adjusting member has a first spring seat that receives the load of the spring,
The valve spool has a second spring seat for receiving the load of the spring,
The spool control valve, wherein the spring is installed between the first spring seat and the second spring seat. The spool control valve according to any one of claims 1 to 7,
The spool control valve is characterized in that the accommodation hole opens at least at one end surface in the axial direction and extends in the axial direction from the opening side to the back side. The spool control valve according to claim 8,
A spool control valve comprising an actuator that drives the valve spool toward an opening side in the axial direction of the accommodation hole. In the spool control valve according to claim 8 or 9,
The spool control valve according to claim 1, wherein the spring biases the valve spool toward an inner side in the axial direction of the accommodation hole. The spool control valve according to any one of claims 1 to 10,
The spool control valve, wherein the accommodation hole has a sliding hole through which the valve spool slides directly. The spool control valve according to any one of claims 1 to 11,
The spool control valve, wherein the accommodation hole has a mounting hole for fixing the load adjusting member. The spool control valve according to any one of claims 1 to 12,
The spool control valve, wherein the accommodation hole has an attachment hole for fixing the position regulating member.

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