JP2014037874A - Solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem in which a conventional solenoid valve causes sliding failure of a cup guide or plunger due to shortage of lubrication oil supplied to a lubrication portion of the solenoid.SOLUTION: There is provided a lubrication oil supply flow passage (a plurality of sleeve grooves 8, a plurality of spool grooves 9, etc.) which, when a spool moving position is at a full stroke position (full stroke time), communicates a retard drain port 15 with an inside of guide hole 47 of a cup guide 46, and supplies drain oil drained from a retard output port 14 to the retard drain port 15 through inside a spool hole 4, to a lubrication section 7 of the solenoid as lubrication oil. Thus, the lubrication oil can be supplied to the lubrication section 7 of the solenoid. Consequently, even in an OCV where an angle of the mounting posture of the OCV is 60 degrees or more with respect to a vertical direction of the vehicle or the like (gravity direction), the occurrence of shortage of the lubrication oil in the lubrication section 7 of the solenoid is prevented.

Description

  The present invention relates to a solenoid valve provided with a bottomed cylindrical cup guide that supports a movable core in a reciprocating manner inside a solenoid that drives a spool of a spool valve in an axial direction.

[Conventional technology]
2. Description of the Related Art Conventionally, for example, in an internal combustion engine (engine) mounted on a vehicle such as an automobile, the opening / closing timing (valve timing) of an intake or exhaust valve is adjusted by the pressure of hydraulic oil (hereinafter referred to as oil) in accordance with the operating state of the engine. A variable valve timing mechanism (hereinafter referred to as VVT) is mounted.
The VVT includes a shoe housing in which a recess is formed on the inner peripheral side, and a vane rotor having a vane that divides the recess of the shoe housing into two first and second pressure chambers (advance chamber and retard chamber). In the state where the shoe housing is connected to the crankshaft via a timing belt and the vane rotor is connected to the camshaft, the oil pressure (hereinafter referred to as oil pressure) supplied to the advance chamber and retard chamber is controlled by an oil control valve (electromagnetic) This is a mechanism for shifting the opening / closing timing (valve timing) of the intake or exhaust valve continuously or stepwise by shifting the rotational phase of the crankshaft and the camshaft.

The solenoid valve is a spool valve that controls switching of an oil passage for hydraulic control to an advance chamber and a retard chamber provided in the VVT, and an electromagnetic actuator (hereinafter, solenoid) that drives the spool of the spool valve in the axial direction. Is an electromagnetic hydraulic control valve that is coupled in the axial direction.
The spool valve includes a cylindrical sleeve that extends in the axial direction from the base end side to the tip end side that is coupled to the solenoid, and a spool that is supported so as to be slidable back and forth within the spool hole of the sleeve.
The spool valve is an advance drain port that discharges oil from the inside of the spool hole in order from the front end side to the base end side of the sleeve, and an advance output port that outputs oil from the inside of the spool hole to the advance chamber. , An input port through which oil is supplied from the oil pump to the inside of the spool hole, a retarding output port that outputs the working fluid from the inside of the spool hole to the retarding chamber, and a retarded drain that discharges oil from the inside of the spool hole The port is formed with an opening at a predetermined distance in the axial direction of the sleeve.

The solenoid is a fixed core (cylindrical yoke, cylindrical stator core) that is fixed to the proximal end side of the sleeve, a plunger that is installed on the inner peripheral side of the stator core and is movably connected to the spool, and electric power The coil that generates a magnetic force that magnetizes the fixed core and the plunger.
The solenoid is configured to drive the spool in the axial direction from the initial position on the proximal end side of the sleeve toward the spool moving position on the distal end side by attracting the plunger to the magnetic attraction portion of the stator core by the magnetic force generated by the coil. ing.
By the way, when the solenoid is operated, it is necessary to change the volume of the space at both ends in the axial direction of the plunger. However, the solenoid is arranged in a state of being exposed to the outside such as a cylinder head of the engine. For this reason, in order to prevent oil leakage from the solenoid to the outside of the engine, the spaces at both ends of the plunger cannot be communicated to the outside (atmosphere).

Therefore, a bottomed cylindrical cup guide is disposed inside the solenoid, in particular, between the inner periphery of the stator core and the outer periphery of the plunger to partition the interior and the exterior of the solenoid in a liquid-tight manner, and the spaces at both ends of the plunger. By connecting the space after the plunger = the first volume changing portion and the space before the plunger = the second volume changing portion to the inside of the spool hole, the volume of the space at both ends of the plunger can be changed.
Here, since the plunger is supported in the guide hole of the cup guide so as to be slidable back and forth, it is necessary to supply oil as a lubricating oil to the sliding clearance between the cup guide and the plunger.
Therefore, a sub-drain port is provided on the base end side of the sleeve, and oil is sucked up by the volume variation (breathing action) of the space of one end of the plunger communicating with the sub-drain port, so that the sliding clearance between the cup guide and the plunger is increased. An electromagnetic valve that supplies lubricating oil is known (see, for example, Patent Document 1).

[Conventional technical problems]
However, in the solenoid valve described in Patent Document 1, the oil is sucked up by the breathing action of the sub drain port and the lubricating oil is supplied to the sliding portion between the cup guide and the plunger. Intrusion of foreign matter increases with oil. And when a foreign material penetrate | invaded into the sliding part of a cup guide and a plunger, there existed a subject of causing the sliding defect and sliding wear of a cup guide or a plunger.
Thus, a solenoid valve is known that eliminates the above problem by eliminating the sub-drain port and reducing the amount of foreign matter intrusion (see, for example, Patent Document 2).
However, in the solenoid valve described in Patent Document 2, when the angle of the mounting posture (the direction of the solenoid yoke top surface is 90 ° with respect to the horizontal) becomes 60 ° or more with respect to the direction of gravity, the spool inner shaft hole The oil does not suck up from the solenoid to the solenoid side, and it becomes difficult to reach the lubrication part of the solenoid provided in the cup guide. As a result, there is a problem that the lubricating oil supplied to the lubrication part of the solenoid is insufficient, causing the cup guide or the plunger to slide poorly.

Japanese Patent No. 4618133 Japanese Patent Laid-Open No. 2008-051203

  An object of the present invention is to provide an electromagnetic valve capable of suppressing foreign matter from entering a sliding portion between a cup guide and a movable core and preventing insufficient lubrication of a lubricating portion in a solenoid. Another object of the present invention is to provide an electromagnetic valve that can suppress sliding failure of the movable core with respect to the cup guide and can suppress sliding wear between the cup guide and the movable core.

According to the first aspect of the present invention (solenoid valve), when the spool movement position is at a predetermined stroke position, the drain port of the sleeve and the inside of the guide hole of the cup guide are communicated to each other from the output port to the spool hole. The spool valve is provided with lubricating oil supply means for supplying hydraulic oil discharged to the drain port through the interior of the solenoid as lubricating oil to a lubricating part (for example, a sliding part between the movable core and the cup guide) in the solenoid. .
As a result, the lubricating oil in the solenoid can be supplied to the lubricating portion. Therefore, even in the solenoid valve when the mounting posture angle is 60 ° or more with respect to the direction of gravity, there is insufficient lubricating oil in the lubricating portion in the solenoid. It is possible to prevent the occurrence of malfunctions. Thereby, there exists an effect which can improve the slidability of the movable core with respect to a cup guide.
In addition, since the hydraulic oil is supplied as the lubricating oil to the lubrication part of the solenoid without providing the sub-drain port on the sleeve, it is possible to suppress the entry of foreign matter into the sliding part between the cup guide and the movable core. . Thereby, there exists an effect which improves the sliding failure and sliding wear of a cup guide or a movable core.

(Example 1) which was the explanatory view which showed the flow of the oil at the time of the full stroke of a solenoid valve. FIG. 2 is a cross-sectional view illustrating details of FIG. 1 (Example 1). It is explanatory drawing which showed the flow of the oil at the time of default of a solenoid valve (Example 1). FIG. 4 is a sectional view showing details of FIG. 3 (Example 1). (A) is sectional drawing which showed the sleeve, (b) is the top view which showed the sleeve end face side end face (Example 1). (A)-(c) is explanatory drawing which showed the amount of lap | wrapping of the retardation drain port and a spool groove | channel at the time of a full stroke (Example 1).

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

[Configuration of Example 1]
1 to 6 show an electromagnetic valve (Embodiment 1) used as an oil control valve in a variable valve timing control device to which the present invention is applied.

  The valve timing control device of this embodiment is attached to a camshaft (for intake valve, exhaust valve, intake / exhaust combined camshaft) of an internal combustion engine (engine), and valve opening / closing timing is continuously variable. A variable valve timing mechanism (hereinafter referred to as VVT), a hydraulic circuit that hydraulically controls the operation of the VVT, and an engine control unit (electronic control unit) that electrically controls an oil control valve (hereinafter referred to as OCV) provided in the hydraulic circuit : ECU below).

The VVT includes a shoe housing that is driven to rotate in synchronization with the crankshaft of the engine, and a vane rotor that is provided so as to be relatively rotatable with respect to the shoe housing and is connected to the camshaft so as to be integrally rotatable. The vane rotor is driven to rotate relative to the shoe housing by the hydraulic actuator configured as described above to change the camshaft to the advance side or the retard side.
The shoe housing is coupled to a sprocket that is rotationally driven by a crank belt of the engine via a timing belt, a timing chain, or the like by a bolt or the like, and is coupled to the sprocket so as to be integrally rotatable. A plurality of fan-shaped recesses are formed in the shoe housing. Note that the shoe housing rotates clockwise, for example, and this rotation direction is an advance direction.

On the other hand, the vane rotor is positioned at the end of the camshaft by a positioning pin or the like, and is fixed to the end of the camshaft by a bolt or the like. The vane rotor rotates integrally with the camshaft.
The camshaft rotates in a fixed direction in synchronization with the engine crankshaft. This camshaft is rotatably installed in the cylinder head of the engine and is drivingly connected to the crankshaft so that it rotates once when the crankshaft of the engine rotates twice. In addition, the camshaft has an intake valve that opens and closes the intake port opening at the end of the combustion chamber or an intake valve provided with a cam crest that determines the opening and closing timing (valve timing) of the exhaust valve that opens and closes the exhaust port opening. Or an exhaust camshaft.

The vane rotor includes a vane that divides a recess (fluid chamber) of the shoe housing into two first and second pressure chambers (an advance chamber 1 and a retard chamber 2 in this example). The vane rotor is provided so as to be reciprocally movable (rotatable) in the rotational direction within a predetermined angle with respect to the shoe housing.
The advance chamber 1 is an advance hydraulic chamber (first fluid chamber) for driving the vane to the advance side by hydraulic pressure, and is formed in a recess on the side opposite to the rotation direction of the vane.
The retard chamber 2 is a retard hydraulic chamber (second fluid chamber) for driving the vane to the retard side by hydraulic pressure, and is formed in a recess on the vane rotation direction side.

The hydraulic circuit supplies and discharges oil from the advance chamber 1 and the retard chamber 2 provided in the VVT to generate a hydraulic pressure difference (pressure difference) between the advance chamber 1 and the retard chamber 2 to A system for rotating relative to a shoe housing.
The hydraulic circuit includes an oil pump P driven by an engine crankshaft and the like, a first oil passage for supplying and discharging oil to the advance chamber 1, and a second for supplying and discharging oil to the retard chamber 2. An oil passage and an OCV that selectively supplies the pressure (hydraulic pressure) of the oil pumped by the oil pump P to the advance chamber 1 or the retard chamber 2 are provided.

The oil pump P is rotationally driven by an engine crankshaft (or electric motor), and oil in an oil pan (or an oil tank) T that is a storage tank in which engine oil for lubricating each part of the engine is stored. This is a hydraulic pressure generating means for sucking in and pumping. An oil supply passage (oil passage) L2 is connected to the discharge side of the oil pump P, and an OCV that is an electromagnetic spool control valve is installed at the downstream end of the oil supply passage L2.
The OCV is an electromagnetic hydraulic control valve that includes a spool valve and a solenoid (electromagnetic actuator), in which a base end portion in the axial direction of the spool valve and a tip end portion in the axial direction of the solenoid are coupled and integrated in the axial direction.

The spool valve includes a cylindrical sleeve 3 fitted and disposed in a receiving hole opened on a side surface of the cylinder head of the engine, and a spool valve (hereinafter referred to as reciprocatingly slidable within the spool hole 4 of the sleeve 3). Spool) 5, a return spring 6 that generates a biasing force (elastic force) that biases the spool 5 toward the base end side (default side, solenoid side) of the sleeve 3, and the retard chamber 2 to the inside of the spool hole 4. And a lubricating oil supply mechanism that supplies drain oil discharged through the oil pan T to the lubricating portion 7 of the solenoid as lubricating oil.
The lubricating oil supply mechanism includes a lubricating oil supply channel (a slit-shaped sleeve groove 8 formed on the inner peripheral surface of the sleeve 3 and a slit-shaped spool groove 9 formed on the outer peripheral surface (sliding surface) of the spool 5. Etc.).

The sleeve 3 is a cylindrical valve case extending in the axial direction (hereinafter referred to as the axial direction) from the base end side (solenoid side) to the front end side (spring side). The sleeve 3 has a plurality of oil supply / discharge ports (11 to 15) through which oil used in the VVT flows in and out of the sleeve 3 with respect to the axial direction of the spool hole 4 (hereinafter referred to as the axial direction). It communicates in the vertical radius (radiation) direction.
A spool hole 4 extending in the axial direction (hereinafter referred to as the axial direction) is formed inside the sleeve 3. The spool hole 4 is a sliding hole in which the spool 5 is slidably supported in the axial direction (hereinafter referred to as an axial direction) and the spool 5 directly slides.

  A plurality of oil supply / discharge ports (11 to 15) for supplying and discharging oil to the advance chamber 1 and the retard chamber 2 open in a radius (radiation) direction substantially perpendicular to the axial direction of the spool hole 4. In addition, an opening is formed with a predetermined distance in the axial direction of the spool hole 4. These oil supply / discharge ports output a first oil discharge port (hereinafter referred to as an advance drain port) 11 that discharges oil from the inside of the spool hole 4 to the oil pan T, and outputs oil from the inside of the spool hole 4 to the advance chamber 1. Leading angle output port 12, an input port (hereinafter referred to as oil supply port) 13 through which oil is supplied from the oil pump P to the inside of the spool hole 4, and retard angle output for outputting oil from the inside of the spool hole 4 to the retard chamber 2. The port 14 includes a second oil discharge port (hereinafter referred to as a retarded drain port) 15 that discharges oil from the inside of the spool hole 4 to the oil pan T.

The advance drain port 11 communicates with the oil pan T via an advance (first) drain passage (oil passage) L1.
The advance output port 12 communicates with the advance chamber 1 via an advance (first) oil passage.
The oil supply port 13 communicates with the oil discharge port of the oil pump P via an oil supply channel (oil channel) L2.
The retardation output port 14 communicates with the retardation chamber 2 via a retardation (second) oil passage.
The retarded drain port 15 communicates with the oil pan T via a retarded (second) drain channel (oil channel) L3.

The advance angle drain port 11, the advance angle output port 12, the oil supply port 13, the retard angle output port 14, and the retard angle drain port 15 are holes opened on the outer peripheral surface (side surface) of the sleeve 3. From the proximal end side of the sleeve 3 (the right side in FIG. 1 and FIG. 3, the solenoid side) from the left side in FIG. 1 and FIG. An opening is formed in the order of the output port 12, the oil supply port 13, the retard output port 14, and the retard drain port 15.
An opening end on the proximal end side of the sleeve 3 is provided with a coupling end surface coupled to the linear solenoid and an annular flange 16 extending to the outer peripheral side of the coupling end surface.

The spool 5 has an outer diameter that substantially matches the inner diameter of the sleeve 3 (hole diameter of the spool hole 4), and a plurality of large-diameter shaft portions that control the communication state of the plurality of oil supply / discharge ports (11 to 15). (Hereinafter referred to as first to fourth lands) 21 to 24 are provided. The outer peripheral surfaces of these first to fourth lands 21 to 24 are sliding surfaces that slide directly with the hole wall surface of the spool hole 4.
The spool 5 has a small-diameter shaft portion 25 that connects the first and second lands 21 and 22 so as to be interlocked, a small-diameter shaft portion 26 that interlocks the second and third lands 22 and 23, and a third shaft. A small-diameter shaft portion 27 that connects the fourth lands 23 and 24 so as to be interlocked is integrally formed.

Here, between the inner surface of the sleeve 3 (hole wall surface of the spool hole 4) and the outer surface (outer peripheral surface) of the small-diameter shaft portion 25 of the spool 5, the advance drain port 11 and the advance output port when the spool 5 is defaulted. An advance angle drain communication portion (first oil discharge chamber: cylindrical advance angle drain communication chamber 31) is formed.
Further, between the inner surface of the sleeve 3 (hole wall surface of the spool hole 4) and the outer surface (outer peripheral surface) of the small-diameter shaft portion 26 of the spool 5, the advance output port 12 and the oil supply port 13 during the full stroke of the spool 5. A central communication portion (first oil supply chamber: cylindrical central communication chamber 32) is formed.

Further, between the inner surface of the sleeve 3 (hole wall surface of the spool hole 4) and the outer surface (outer peripheral surface) of the small diameter shaft portion 26 of the spool 5, an oil supply port 13 and a retarded output port 14 are provided at the time of default of the spool 5. A central communication portion (second oil supply chamber: cylindrical central communication chamber 32) is formed.
Further, between the inner surface of the sleeve 3 (hole wall surface of the spool hole 4) and the outer surface (outer peripheral surface) of the small-diameter shaft portion 27 of the spool 5, the retard output port 14 and the retard drain port during the full stroke of the spool 5. 15 is formed as a retarded drain communicating portion (second oil discharge chamber: cylindrical retarded drain communicating chamber 33).

The return spring 6 is a compression coil spring that generates an elastic force that biases the spool 5 toward the right side in FIG. The return spring 6 is located between the left wall surface (spring seat) of the sleeve 3 and the front end surface (spring seat) of the spool 5 shown in the left side of the sleeve 3 in FIG. It is arranged in a compressed state in the axial direction.
The details of the spool valve of this embodiment, particularly the sleeve 3, the spool 5, and the lubricating oil supply mechanism will be described later.

  The electromagnetic actuator includes a coil 41 that generates a magnetic flux when energized, an external connection connector 42 for connecting a pair of coil lead wires drawn from the coil 41 and an external circuit, A magnetic coil outer peripheral fixed core (such as a yoke 43) that forms a magnetic path on the outer peripheral side, and a magnetic coil inner peripheral fixed core (a stator core 44, which forms a magnetic path on the inner peripheral side of the coil 41) 45), a non-magnetic cup guide 46 disposed on the inner peripheral side of the stator cores 44, 45, and a magnetic plunger supported in the guide hole 47 of the cup guide 46 so as to be slidable back and forth. 48 and a non-magnetic shaft 49 that connects the spool 5 and the plunger 48 so as to be movable together.

The coil 41 is a magnetic flux generating means (magnetic force generating means) that generates a magnetic force that draws the plunger 48 toward the magnetic attraction portion 51 of the stator core 45 when supplied with electric power (when a current is applied or energized). The coil 41 is a solenoid coil in which a conductive wire with an insulating coating is wound a plurality of times between a pair of hook-shaped portions of a coil bobbin 52 made of synthetic resin having insulating properties and on the outer periphery of a cylindrical portion.
When the coil 41 is energized, a magnetic circuit in which magnetic flux concentrates through the yoke 43, the stator cores 44 and 45, and the plunger 48 is formed.

The coil 41 drives the spool 5, the shaft 49, and the plunger 48 to the front end side (one side, the left side in the drawing) in the solenoid axis direction by magnetic force.
In this embodiment, when the coil 41 is energized (ON), the spool 5, the shaft 49, and the plunger 48 make a full stroke from the default position to one side in the solenoid axis direction. When energization of the coil 41 is stopped (OFF), the spool 5, the shaft 49, and the plunger 48 are returned to the default positions by the urging force of the return spring 6.

The coil 41 has a coil part wound around the coil bobbin 52 and a pair of coil lead wires drawn out from the coil part.
The pair of coil lead wires are electrically connected to an external circuit (external power source or external control circuit: ECU) via a terminal (external connection terminal) 53 of the external connection connector 42. The outer peripheral portion of the coil 41 is covered with a synthetic resin molding resin material 54 having insulating properties. Further, the conductive joint between the coil 41 and the terminal 53 and the base end of the terminal 53 are covered with a bottomed cylindrical mold resin material 55.
The other end portion (the base end portion of the solenoid) of the mold resin material 55 forms a housing (insulating synthetic resin connector case) 56 of the external connection connector 42 that exposes and accommodates the distal end side of the terminal 53. doing.

The coil outer peripheral fixed core is constituted by a yoke 43 made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 41 is energized.
The yoke 43 has a cylindrical portion that covers the outer peripheral side of the coil 41. A claw portion 57 that is caulked and fixed to the flange 16 of the sleeve 3 is provided on the opening end side (the tip end side in the solenoid axial direction) of the yoke 43.
The coil inner peripheral side fixed core covers the outer periphery of the cylindrical core portion of the stator core 44 and the cup guide 46 that has a cylindrical magnetic attraction portion 51 that attracts the plunger 48 toward the distal end side in the solenoid axial direction. And a stator core 45 for delivering the above.

The stator cores 44 and 45 are made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 41 is energized.
The stator core 44 is sandwiched between the sleeve 3 and the flanged portion of the coil bobbin 52 that accommodates the coil 41 (in this example, the annular portion 62 of the bracket 61 for fastening and fixing the OCV to the housing, the valve body, etc.). An annular flange 63 is provided.
The magnetic attraction portion 51 of the stator core 44 is a cylindrical magnetic path that guides the magnetic flux passing through the flange 63 to the vicinity of the plunger 48. The magnetic attraction portion 51 is provided so as to be able to intersect the front end portion of the plunger 48 in the solenoid axis direction.

In addition, a frustoconical tapered surface whose outer diameter is gradually reduced toward the rear end side (stator core 45 side) of the magnetic attraction unit 51 is formed on the outer periphery of the magnetic attraction unit 51. Thereby, the magnetic attraction unit 51 has a characteristic that the magnetic attraction force does not change with respect to the stroke amount of the plunger 48.
The stator core 45 covers the outer periphery of the plunger 48 via the cylindrical portion of the cup guide 46, and is inserted and arranged on the inner peripheral side of the coil 41, and radially outward from the rear end portion of the cylindrical portion. The flange 64 is formed to face and is magnetically coupled to the yoke 43 disposed on the outer peripheral side.
The radial gap between the cylindrical portion of the stator core 45 and the plunger 48 is a magnetic flux delivery gap (side gap).

The cup guide 46 is made of a nonmagnetic metal such as thin stainless steel. The cup guide 46 has a cylindrical portion installed between the cylindrical portions of the stator cores 44 and 45 and the plunger 48. The cup guide 46 prevents oil leakage from the inside of the solenoid to the outside, particularly from the plunger 48 side to the stator cores 44 and 45 side.
The cup guide 46 is formed with an opening (expanded) so that the proximal end side of the sleeve 3 (one end side of the cylindrical portion, the distal end side of the solenoid) faces the inside of the spool hole 4, and the other end side of the cylindrical portion. The bottom end of the solenoid is formed in a bottomed cylindrical shape closed by a bottom wall portion 65.

In addition, a guide hole (sliding hole) 47 having a cross-sectional shape in which the plunger 48 slides directly is formed inside the cylindrical portion of the cup guide 46.
In addition, an annular flange 66 disposed integrally with the front surface side of the flange 63 of the stator core 44 is integrally formed outside the peripheral edge of the cylindrical opening of the cup guide 46 in the radial direction.
The flange 66 is sandwiched and held between the flange 63 of the stator core 44 and the coupling end surface on the proximal end side of the sleeve 3 together with the sealing O-ring 67.

The plunger 48 is slidable back and forth in the solenoid shaft direction on the inner peripheral side of the stator cores 44 and 45 (specifically, the inner peripheral side of the oil seal cup guide 46 inserted and arranged on the inner peripheral side of the stator cores 44 and 45). It is fitted and arranged to move freely.
The plunger 48 is made of a magnetic metal (for example, a ferromagnetic material such as iron) that is excited (magnetized) when the coil 41 is energized.
The plunger 48 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 41. The plunger 48 is urged to the bottom wall 65 side of the cup guide 46 (the bottom wall side of the mold resin material 55) together with the spool 5 and the shaft 49 by the urging force of the return spring 6 transmitted to the spool 5.
The plunger 48 has both end faces (front and rear end faces in the axial direction) of the plunger 48 in order to ensure the oil flow in the rear plunger space (first volume changing portion) due to the displacement in the stator core 45 and the cup guide 46. ) Communicated with the plunger breathing hole (stepped axial hole) 68 is provided in the solenoid axial direction.

The shaft 49 transmits the driving force of the plunger 48 to one side in the solenoid axis direction to the spool 5 and transmits the urging force of the return spring 6 applied to the spool 5 to the plunger 48.
The shaft 49 is a hollow part obtained by processing a non-magnetic metal plate (for example, a stainless steel plate) into a cup shape (bottomed cylindrical shape) that is open at one end and closed at the other end.
A hollow portion 71 that is a space is formed inside the shaft 49. The hollow portion 71 includes a spool breathing hole (axial hole) 72 penetrating the central portion of the spool 5 in the axial direction through a cup opening formed on one end side (opening side) of the shaft 49 in the axial direction. Communicate.

The hollow portion 71 communicates with a plunger breathing hole 68 that penetrates the central portion of the plunger 48 in the axial direction through a communication hole 74 formed on the other end side (bottom side) of the shaft 49 in the axial direction. ing.
Thereby, the plunger rear space (first volume changing portion) closer to the bottom wall portion 65 of the cup guide 46 than the plunger 48 is connected to the spool 5 via the plunger breathing hole 68 → the hollow portion 71 → the spool breathing hole 72. The tip end wall 75 forming the spring accommodating chamber 34 is communicated with an oil discharge hole 76 penetrating in the axial direction. The oil discharge hole 76 is an opening for discharging oil to the outside of the OCV.

In addition, an oil discharge hole 77 is formed on the side surface of the shaft 49 to communicate the inside and outside. The oil discharge hole 77 is a communication hole that communicates the hollow portion 71 of the shaft 49 with the outer peripheral side of the shaft 49.
Thus, the plunger front space (second volume changing portion) between the spool 5 and the plunger 48 communicates with the oil discharge hole 76 via the oil discharge hole 77 → the hollow portion 71 → the spool breathing hole 72. The hollow portion 71, the spool breathing hole 72, and the oil discharge hole 77 constitute drain means that communicates the volume changing portion between the spool 5 and the plunger 48 to the oil discharge hole 76.

  Here, in the OCV, when the coil 41 is energized (ON) by the ECU, the spool moving position is set (set) to the full stroke position (OCV advance angle control mode) by the magnetic force generated by the coil 41. In this advance angle control mode (during the full stroke of the spool 5), the oil supply path from the oil pump P, the OCV (the oil supply port 13 → the central communication chamber 32 → the advance angle output port 12), and the first oil path are connected. After that, oil is supplied into the advance chamber 1 and from the retard chamber 2 through the second oil passage, the OCV (retard output port 14 → retard drain communication chamber 33 → retard drain port 15), and the drain passage. Oil is returned to the oil pan T.

  Further, in the OCV, when energization from the ECU to the coil 41 is stopped (OFF), the generated magnetic force of the coil 41 is demagnetized. For this reason, the spool movement position is set (set) to the default position (OCV retardation control mode) by the urging force of the return spring 6. In this retard control mode (when the spool 5 is the default), the oil supply path from the oil pump P, the OCV (the oil supply port 13 → the central communication chamber 32 → the retard output port 14), and the second oil path. Oil is supplied into the retard chamber 2 and the oil is passed from the advance chamber 1 through the first oil passage, the OCV (advance output port 12 → advanced drain communication chamber 31 → advanced drain port 11), and the drain passage. Oil is returned to pan T.

[Features of Example 1]
Next, details of the spool valve of this embodiment, in particular, the sleeve 3, the spool 5 and the lubricating oil supply mechanism will be briefly described with reference to FIGS.

  The spool 5 shuts off the advance drain port 11 and the advance output port 12 when the spool movement position is a predetermined stroke position (full stroke position in this example), and advances the advance output port 12 and the oil supply port 13. The second and third valve portions (second and third lands 22 and 23, small diameter shaft portion 26) communicating with each other, the oil supply port 13 and the retard output port 14 are shut off, and the retard output port 14 And the retarded drain port 15 have third and fourth valve portions (third and fourth lands 23 and 24, small-diameter shaft portion 27).

  The spool 5 communicates with the advance drain port 11 and the advance output port 12 when the spool movement position is the initial position (the default position in this example) closer to the proximal end of the sleeve 3 than the predetermined stroke position. In addition, the first and second valve portions (first and second lands 21 and 22 and the small diameter shaft portion 25) that shut off the advance angle output port 12 and the oil supply port 13, and the oil supply port 13 and the retard angle output port. 14 and the second and third valve portions (second and third lands 22 and 23, small-diameter shaft portion 26) that block the retard output port 14 and the retard drain port 15 from each other. .

Here, the outer peripheral surfaces of the first to fourth lands 21 to 24 of the spool 5 are, as described above, sliding surfaces that slide directly with the hole wall surface of the spool hole 4 (the first to fourth lands 21 to 24). Sliding surface). The plurality of first to fourth lands 21 to 24 have a sliding clearance for enabling the spool 5 to reciprocate between the hole wall surface of the spool hole 4 (inner peripheral surface of the sleeve 3). Have.
On the other hand, the plunger 48 can reciprocate between the outer peripheral surface of the solenoid plunger 48 (the outer peripheral surface of the cylindrical portion, the cylindrical surface) and the hole wall surface of the guide hole 47 (the inner peripheral surface of the cup guide 46). To have a sliding clearance.
In the OCV of this embodiment, the sliding portion between the inner peripheral surface of the cup guide 46 and the outer peripheral surface of the plunger 48 constitutes the lubrication portion 7 of the solenoid.

The advance drain port 11 is a part of the annular first circumferential wall (downward in the drawing) that surrounds the circumference of the spool 5 in the circumferential direction so that the inside and outside of the spool 5 communicate with each other. It is the 1st communicating hole penetrated in the radial direction.
The advance drain port 11 is provided in a partial annular shape on the inner peripheral side of the first peripheral wall of the spool 5, and has a circumferential groove 81 that opens at the hole wall surface of the spool hole 4. This circumferential groove 81 is connected to the advance drain port 11 at the spool hole side end of the advance drain port 11 so that oil can flow.

The advance output port 12 is a part of the annular second circumferential wall (upward in the drawing) that surrounds the periphery of the spool 5 in the circumferential direction (upward in the drawing) so that the inside of the spool 5 communicates with the outside. This is a second communication hole penetrating in the radial direction.
The advance output port 12 is provided in a partial annular shape on the inner peripheral side of the second peripheral wall of the spool 5, and has a circumferential groove 82 that opens at the hole wall surface of the spool hole 4. The circumferential concave groove 82 is connected to the advance angle output port 12 at the spool hole side end of the advance angle output port 12 so that oil can flow therethrough.

The oil supply port 13 is a part of the annular third peripheral wall that surrounds the circumference of the spool 5 in the circumferential direction (downward in the drawing), and communicates the inside and outside of the spool 5 with each other. This is a third communication hole penetrating in the radial direction.
The oil supply port 13 is provided in a partial annular shape on the inner peripheral side of the third peripheral wall of the spool 5, and has a circumferential groove 83 that opens at the hole wall surface of the spool hole 4. The circumferential groove 83 is connected to the oil supply port 13 at the spool hole side end of the oil supply port 13 so that oil can flow.

The retardation output port 14 is a part of the annular fourth circumferential wall (upward in the drawing) that surrounds the periphery of the spool 5 in the circumferential direction (upward in the drawing) so that the inside and outside of the spool 5 communicate with each other. This is a fourth communication hole penetrating in the radial direction.
The retard output port 14 is provided in a partial annular shape on the inner peripheral side of the fourth peripheral wall of the spool 5, and has a circumferential groove 84 that opens at the hole wall surface of the spool hole 4. The circumferential groove 84 is connected to the retarded output port 14 so that oil can flow at the spool hole side end of the retarded output port 14.

The retard drain port 15 is a part of the annular fifth circumferential wall (downward in the drawing) that surrounds the circumference of the spool 5 in the circumferential direction so that the inside and outside of the spool 5 communicate with each other. It is the 5th communicating hole penetrated in the radial direction.
The retard drain port 15 is provided in a partial annular shape on the inner peripheral side of the fifth peripheral wall of the spool 5, and has a circumferential groove 85 that opens at the hole wall surface of the spool hole 4. The circumferential groove 85 is connected to the retarded drain port 15 at the spool hole side end of the retarded drain port 15 so that oil can flow.
Further, the spool hole side end portions of the advance angle output port 12, the retard angle output port 14, and the retard angle drain port 15 can communicate with the circumferential grooves 82, 84, 85, and the hole wall surface of the spool hole 4 Annular recess grooves 86 to 88 are provided which open at.

  The lubricating oil supply mechanism of the present embodiment has a retarded drain constituted by the fifth communication hole, the circumferential groove 85, and the recess groove 88 when the spool movement position is a predetermined stroke position (full stroke position in this example). The port 15 communicates with the inside of the guide hole 47 of the cup guide 46, and the volume of the space (first and second volume changing portions) at both ends in the axial direction of the plunger 48 due to movement of the plunger 48 in the axial direction front end side is expanded and contracted. By increasing the volume of the space behind the plunger and reducing the volume of the space before the plunger, the retard drain port 15 passes from the retard output port 14 through the inside of the spool hole 4 (retard drain communication chamber 33). Lubricating oil supply passage (sleeve groove for solenoid lubricating port) for supplying oil (drain oil) discharged (drained) to the lubricating portion 7 of the solenoid as lubricating oil , And a spool channel 9, etc.) of the solenoid lubrication ports.

  As shown in FIGS. 1 to 5, the sleeve groove 8 opens on the inner peripheral surface of the sleeve 3, that is, the hole wall surface of the spool hole 4, and is a slit-like axial groove (extending in the axial direction of the spool hole 4). Groove). The sleeve groove 8 is always in communication with the inside of the guide hole 47. A plurality of sleeve grooves 8 are provided at predetermined intervals (equal intervals: 90 ° intervals) in the circumferential direction of the inner peripheral surface of the sleeve 3.

As shown in FIGS. 1 to 4, the spool groove 9 is a slit-shaped axial groove (concave groove) that opens at the sliding surface of the fourth land 24 of the spool 5 and extends in the axial direction of the spool 5. is there. The spool groove 9 is provided so that the circumferential groove 85 or the recess groove 88 of the retard drain port 15 communicates with the sleeve groove 8 when the spool movement position is the full stroke position.
The spool groove 9 is provided so as to block the communication state between the sleeve groove 8 and the circumferential groove 85 or the recess groove 88 of the retard drain port 15 when the spool movement position is the default position.

Here, in the OCV of this embodiment, as shown in FIG. 6, when the spool movement position is at the full stroke position, the retarded drain port 15 including the circumferential groove 85 and the recess groove 88, the spool groove 9 and Is set within a range of −0.5 mm or more and +0.5 mm or less.
In the OCV, when the spool movement position is the full stroke position, the wrap amount between the sleeve groove 8 and the spool groove 9 is set within a range of −0.5 mm or more and +0.5 mm or less.

First, as shown in FIG. 6A, when the wrap amount between the retard drain port 15 and the spool groove 9 or the wrap amount between the sleeve groove 8 and the spool groove 9 is set to +0.5 mm, Lubricating oil can be sufficiently supplied to the cup guide 46 and the plunger 48 which are the lubricating portions 7 in the solenoid, and the amount of foreign matter entering with the lubricating oil can be reduced.
On the other hand, when the amount of wrap between the retarded drain port 15 and the spool groove 9 or the amount of wrap between the sleeve groove 8 and the spool groove 9 is larger than +0.5 mm, the lubricating oil for the lubricating portion 7 in the solenoid Although it is possible to eliminate the deficiency, there is an increased possibility that foreign matter enters with the lubricating oil.

  Next, as shown in FIG. 6B, when the wrap amount between the retard drain port 15 and the spool groove 9 or the wrap amount between the sleeve groove 8 and the spool groove 9 is set to 0 mm, the solenoid It is possible to supply more lubricating oil to the lubricating part 7 than in the case of −0.5 mm, and it is possible to reduce the amount of foreign matter intruding together with the lubricating oil than in the case of +0.5 mm.

Next, as shown in FIG. 6C, when the wrap amount between the retard drain port 15 and the spool groove 9 or the wrap amount between the sleeve groove 8 and the spool groove 9 is set to -0.5 mm. Can supply the minimum necessary amount of lubricating oil to the lubricating portion 7 in the solenoid, and can further reduce the amount of foreign matter that enters along with the lubricating oil than when it is 0 mm.
On the other hand, when the amount of wrap between the retarded drain port 15 and the spool groove 9 or the amount of wrap between the sleeve groove 8 and the spool groove 9 is reduced to less than −0.5 mm, foreign matter enters with the lubricating oil. Although the possibility becomes low, there is a high possibility that the lubricating oil 7 is insufficient for the lubrication portion 7 in the solenoid, and the sliding failure of the plunger 48 with respect to the cup guide 46 is caused.

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

When the ECU advances the camshaft according to the driving state of a vehicle such as an automobile, the ECU supplies power to the solenoid coil 41 (for example, energization with a large current: ON).
When electric power is supplied to the coil 41 (current application), the plunger 48 is attracted to the magnetic attracting part 51 of the stator core 45 by a magnetic attraction force corresponding to the magnitude of the current flowing through the coil 41. Along with this, the shaft 49 connected to the spool 5 at the tip is pushed toward the tip in the solenoid axial direction, so that the spool 5 moves to the tip in the axial direction of the spool hole 4 of the sleeve 3.

Here, in the OCV of the present embodiment, since the magnitude of the current flowing through the coil 41 is the maximum value, the full stroke amount (about 2.3 mm in this example) from the default position where the spool 5 is the initial position. The spool moves to the full stroke position by moving to the front side (advance side) in the axial direction.
Then, the communication between the advance angle drain port 11 and the advance angle output port 12 is blocked, and the advance angle output port 12 and the oil supply port 13 are communicated. Further, the communication between the oil supply port 13 and the retard output port 14 is blocked, and the retard output port 14 and the retard drain port 15 communicate.

As a result, since the oil discharged from the discharge port of the oil pump P is supplied to the advance chamber 1 via the OCV, the oil pressure (hydraulic pressure) in the advance chamber 1 increases. Further, since the oil flowing out from the retarding chamber 2 is discharged (drained) to the oil pan T via the OCV, the oil pressure (hydraulic pressure) in the retarding chamber 2 decreases.
Therefore, in the VVT, the vane rotor is displaced to the advance side relative to the shoe housing, so that the camshaft is changed to the advance side.

When the ECU retards the camshaft according to the driving condition of a vehicle such as an automobile, the ECU supplies power to the coil 41 of the solenoid (for example, energizes with a small current smaller than a large current: ON). Alternatively, power supply to the coil 41 is stopped (energization is stopped: OFF).
When the energization current to the coil 41 is reduced or the power supply to the coil 41 is stopped, the magnetic force generated in the coil 41 is reduced or demagnetized, and the urging force of the return spring 6 causes the spool 5, the shaft 49, and the plunger. When the spool 48 is pushed back to the proximal end side (rear side) in the solenoid shaft direction, the spool 5 moves to the proximal end side (rear side) in the axial direction of the spool hole 4 of the sleeve 3.
Then, the advance angle drain port 11 and the advance angle output port 12 communicate with each other, and the communication between the advance angle output port 12 and the oil supply port 13 is blocked. Further, the oil supply port 13 and the retard output port 14 communicate with each other, and the communication between the retard output port 14 and the retard drain port 15 is blocked.

As a result, the oil discharged from the discharge port of the oil pump P is supplied to the retard chamber 2 via the OCV, so that the oil pressure (hydraulic pressure) in the retard chamber 2 increases. Further, since the oil flowing out from the advance chamber 1 is discharged (drained) to the oil pan T via the OCV, the oil pressure (hydraulic pressure) in the advance chamber 1 decreases.
Therefore, in VVT, the vane rotor is displaced to the retard side relative to the shoe housing, so that the camshaft is changed to the retard side.

[Effect of Example 1]
As described above, in the OCV of this embodiment, when the spool movement position is the full stroke position (at the time of the full stroke), the retard drain port 15 and the inside of the guide hole 47 of the cup guide 46 are communicated with each other. Lubricating oil supply mechanism for supplying drain oil drained from the retarded output port 14 to the retarded drain port 15 through the inside of the spool hole 4 (retarded drain communication chamber 33) as the lubricated oil 7 in the solenoid. It has.
The lubricating oil supply mechanism includes a plurality of sleeve grooves 8 extending in the axial direction on the inner peripheral surface of the base end side of the sleeve 3, a plurality of spool grooves 9 extending in the axial direction on the outer peripheral surface of the fourth land 24 of the spool 5, and the like. It is comprised by the lubricating oil supply flow path comprised by these.

When the spool movement position is at the full stroke position (full stroke), the lubricating oil supply mechanism communicates with the sleeve groove 8 and the spool groove 9, and the retard drain port 15 and the spool groove 9 communicate with each other. The volume of the first and second volume change portions fluctuates due to the movement of the distal end side of 48 in the axial direction (the volume of the space on the proximal end side in the axial direction of the plunger 48 (the space after the plunger) increases, and the distal end of the plunger 48 in the axial direction The structure is such that the drain oil drained from the retard chamber 2 is introduced (sucked) into the guide hole 47 of the cup guide 46 by reducing the volume of the side space (pre-plunger space).
Further, in the lubricating oil supply mechanism, when the spool movement position is the default position (default time), the sleeve groove 8 and the spool groove 9 do not communicate with each other, and the retard drain port 15 and the spool groove 9 do not communicate with each other. Thus, the drain oil does not enter the guide hole 47 of the cup guide 46.

As a result, it becomes possible to supply the lubricating oil to the lubrication unit 7 in the solenoid. Therefore, even in the OCV in which the angle of the mounting posture of the OCV is 60 ° or more with respect to the vehicle vertical direction (gravity direction) of an automobile or the like. In addition, it is possible to prevent the occurrence of a problem that the lubricating oil is insufficient in the lubricating portion 7 of the solenoid. Thereby, there is an effect that the slidability of the plunger 48 with respect to the cup guide 46 can be secured or improved.
Further, since the hydraulic oil is supplied as the lubricating oil to the lubricating portion 7 in the solenoid without providing the sub-drain port in the sleeve 3 as in the conventional solenoid valve, the sliding portion between the cup guide 46 and the plunger 48 ( Intrusion of foreign matter into (sliding clearance) can be suppressed. Thereby, there exists an effect which improves the sliding failure of the cup guide 46 or the plunger 48, and sliding wear.

[Modification]
In this embodiment, the electromagnetic valve (electromagnetic spool control valve) of the present invention is applied to an OCV incorporated in a hydraulic circuit that hydraulically controls the operation of the VVT, but the electromagnetic valve (electromagnetic spool control valve) of the present invention is applied. The present invention may be applied to an electromagnetic hydraulic control valve incorporated in a hydraulic control device that performs hydraulic control of an automatic transmission of an automobile.
Further, the electromagnetic valve (electromagnetic spool control valve) of the present invention may be applied to a hydraulic oil flow control valve, a hydraulic oil flow control valve, and a hydraulic oil pressure control valve.
In addition, as the operating oil, the fuel supplied to the internal combustion engine (engine), the lubricating oil supplied to each part of the internal combustion engine (engine) and the sliding portion of the automatic transmission, and the operating oil (ATF) used in the automatic transmission are used. You may do it.

In this embodiment, when the spool movement position is a predetermined stroke position (full stroke position in this example), the retard drain port 15 and the spool groove 9 which is a part of the lubricating flow path of the lubricating oil supply means are directly or The connection is made through the sliding clearance, but when the spool movement position is a predetermined stroke position (full stroke position in this example), the advance drain port 11 and the lubricating flow path of the lubricating oil supply means You may comprise so that the spool groove | channel 9 which is a part may connect directly or through a sliding clearance.
Further, the circumferential drain groove 81 may not be provided in the advance drain port 11. Further, it is not necessary to provide the circumferential recessed groove 82 or the recessed groove 86 in the advance angle output port 12. Further, the circumferential groove 83 may not be provided in the oil supply port 13. Further, it is not necessary to provide the circumferential concave groove 84 or the recess groove 87 in the retard output port 14. Further, the circumferential drain groove 85 or the recess groove 88 may not be provided in the retarded drain port 15.

  In this embodiment, a plurality of oil supply / discharge ports for supplying and discharging oil to the advance chamber 1 and the retard chamber 2 are provided from the distal end side of the sleeve 3 (opposite to the solenoid side) to the proximal end of the sleeve 3. The advance angle drain port 11, the advance angle output port 12, the oil supply port 13, the retard angle output port 14, and the retard angle drain port 15 are formed in this order toward the side (solenoid side). And the retard chamber 2 are switched, and a plurality of oil supply / discharge ports are retarded from the distal end side of the sleeve 3 (opposite to the solenoid side) toward the proximal end side of the sleeve 3 (solenoid side). An opening may be formed in the order of the drain port, the retard output port, the oil supply port, the advance output port, and the advance drain port.

Further, a plurality of oil supply / discharge ports for supplying and discharging oil to the advance chamber 1 or the retard chamber 2 are provided from the distal end side of the sleeve 3 (opposite to the solenoid side) to the proximal end side of the sleeve 3 (solenoid). The drain port, the output port, and the oil supply port may be formed in this order. Alternatively, the drain port, the oil supply port, and the output port may be formed in this order from the distal end side of the sleeve 3 (opposite to the solenoid side) toward the proximal end side of the sleeve 3 (solenoid side).
In this case, an electromagnetic hydraulic control valve (first electromagnetic valve) that controls the supply and discharge of oil to the advance chamber 1 and a separate component from this electromagnetic hydraulic control valve, the oil is supplied to the retard chamber 2. An electromagnetic hydraulic control valve (second electromagnetic valve) for controlling supply and discharge is provided.

1 Advance chamber (advance hydraulic chamber, first fluid chamber)
2 Retarded chamber (retarded hydraulic chamber, second fluid chamber)
3 Sleeve 4 Spool hole 5 Spool 7 Lubricating part in solenoid 8 Sleeve groove (lubricating oil supply means)
9 Spool groove (lubricating oil supply means)
46 Cup guide 48 Plunger (movable core)

Claims (14)

A spool having a cylindrical sleeve (3) extending in the axial direction from the proximal end side to the distal end side, and a spool (5) supported so as to be reciprocally slidable in a spool hole (4) of the sleeve (3) A valve,
A cylindrical fixed core (43 to 45) fixed to the base end side of the sleeve (3), installed on the inner peripheral side of the fixed core (43 to 45), and the base end side of the sleeve (3) is A bottomed cylindrical cup guide (46) formed so as to face the inside of the spool hole (4), supported in a guide hole (47) of the cup guide (46) so as to be reciprocally slidable, A movable core (48) coupled to the spool (5) so as to move integrally, and a coil that generates a magnetic force to magnetize the fixed core (43 to 45) and the movable core (48) when supplied with electric power ( 41)
By pulling the movable core (48) to the fixed core (43 to 45) by the magnetic force generated by the coil (41), the initial position on the proximal end side of the sleeve (3) is moved to the spool moving position on the distal end side. And a solenoid for driving the spool (5).
The sleeve (3) includes an input port (13) through which hydraulic oil is supplied to the inside of the spool hole (4), an output port (12, 14) that outputs hydraulic oil from the inside of the spool hole (4), And drain ports (11, 15) for discharging hydraulic oil from the inside of the spool hole (4),
The spool (5) shuts off the input port (13) and the output port (12, 14) when the spool movement position is a predetermined stroke position, and the output port (12, 14) and the drain. A valve portion communicating with the ports (11, 15);
The spool valve communicates between the drain port (11, 15) and the inside of the guide hole (47) from the output port (12, 14) when the spool movement position is the predetermined stroke position. Lubricating oil supply means (8, 9) for supplying hydraulic oil discharged to the drain ports (11, 15) through the inside of the spool hole (4) as lubricating oil in the solenoid (7) of the solenoid A solenoid valve characterized by comprising: The solenoid valve according to claim 1,
The valve portion communicates the input port (13) and the output port (12, 14) when the spool movement position is closer to the base end side of the sleeve (3) than the predetermined stroke position, and The solenoid valve characterized in that the output port (12, 14) and the drain port (11, 15) are shut off. The solenoid valve according to claim 1 or 2,
The lubricating oil supply means (8, 9) has a sleeve groove (8) that opens at the hole wall surface of the spool hole (4) and extends in the axial direction of the spool hole (4),
The solenoid valve characterized in that the sleeve groove (8) is always in communication with the inside of the guide hole (47). The solenoid valve according to claim 3,
The spool (5) has a sliding surface that slides directly on the hole wall surface of the spool hole (4), and the lubricating oil supply means (8, 9) opens on the sliding surface, and the spool A spool groove (9) extending in the axial direction of (5),
The solenoid valve characterized in that the spool groove (9) communicates the drain port (11, 15) and the sleeve groove (8) when the spool movement position is the predetermined stroke position. The solenoid valve according to claim 4,
The spool groove (9) is blocked from the drain ports (11, 15) when the spool moving position is at the initial position provided on the proximal end side of the sleeve (3) with respect to the predetermined stroke position. A solenoid valve characterized by that. In the solenoid valve according to claim 4 or claim 5,
The solenoid valve according to claim 1, wherein the sleeve groove (8) is a slit-like concave groove (8) opened at a hole wall surface of the spool hole (4). The solenoid valve according to any one of claims 4 to 6,
The solenoid valve (OCV) has a lap amount between the drain port (11, 15) and the spool groove (9) of −0.5 mm or more when the spool movement position is the predetermined stroke position, and A solenoid valve set within a range of +0.5 mm or less. The solenoid valve according to any one of claims 4 to 7,
The solenoid valve is configured such that when the spool movement position is the predetermined stroke position,
The electromagnetic valve according to claim 1, wherein a lap amount between the spool groove (9) and the sleeve groove (8) is set in a range of -0.5 mm or more and +0.5 mm or less. The electromagnetic valve according to any one of claims 1 to 8,
A solenoid clearance is provided between the hole wall surface of the spool hole (4) and the spool (5) to enable the spool (5) to reciprocate. valve. The electromagnetic valve according to any one of claims 1 to 9,
A sliding clearance is provided between the hole wall surface of the guide hole (47) and the movable core (48) to enable the movable core (48) to slide back and forth. Solenoid valve. In the solenoid valve according to any one of claims 1 to 10,
At least one of the input port (13), the output port (12, 14), and the drain port (11, 15) has a radius substantially perpendicular to the axial direction of the spool hole (4) ( An electromagnetic valve having an opening formed in the (radiation) direction. The solenoid valve according to any one of claims 1 to 11,
A solenoid groove characterized in that a recess groove (88) that opens at the hole wall surface of the spool hole (4) is provided at the end of the drain port (11, 15) on the spool hole (4) side. The electromagnetic valve according to any one of claims 1 to 12,
The drain port (11, 15) is provided with a circumferential groove (81, 85) opened at the hole wall surface of the spool hole (4) at the end of the spool hole (4) side. Solenoid valve. The solenoid valve according to any one of claims 1 to 13,
In order from the distal end side to the proximal end side of the sleeve (3),
A first drain port (11) for discharging hydraulic oil;
A first output port (12) for outputting hydraulic oil from the inside of the spool hole (4) toward the first fluid chamber (1);
The input port (13),
A second output port (14) that constitutes the output port and outputs hydraulic oil from the inside of the spool hole (4) toward a second fluid chamber (2) different from the first fluid chamber (1);
And a second drain port (15) that constitutes the drain port and discharges hydraulic oil from the inside of the spool hole (4),
An electromagnetic valve having an opening formed at a predetermined distance in the axial direction of the sleeve (3).

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