JP2003120847A - Solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a solenoid valve having a structure capable of increasing attraction force without being enlarged, and preventing the generation of excessive pressure of the fluid flowing in and out in accordance with the movement of a movable element. SOLUTION: This solenoid valve is provided with a valve part B having a valve member 3 for opening and closing a fluid channel, and a housing 2 accommodating the valve member 3 and provided with an opening part 2a for operating the valve member 3, and an electromagnetic driving part S having an electromagnetic coil 4 and a stationary element 6, the valve member 3 comprises a large cylindrical part 3a for opening and closing the fluid channel and a small cylindrical part 3b abutting on the movable element 6. The movable element 6 is provided with an escape passage 61 communicated to spaces G6a, G6b positioned at both sides in the reciprocating direction of the movable element 6, on a shaft or near the shaft. The escape passage 61 is communicated to the reciprocation spaces G3a, G3b formed by the large cylindrical part 3a and the housing 2 through the small cylindrical part 3b.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetic valve, and more particularly to a structure of a stator of an electromagnetic drive unit, a mover, and a valve member of a valve unit that reciprocates in cooperation with the mover.

[0002]

2. Description of the Related Art As an electromagnetic valve, a valve member is reciprocally moved in the axial direction together with a movable element of an electromagnetic drive unit, or the axial position of the valve member is made variable to open / close a fluid passage or a fluid flowing in the fluid passage. It is known to increase or decrease the flow rate (Japanese Patent Laid-Open No. 61-244984, DE 195041).
85A1 German patent publication).

In this type of solenoid valve, since the fluid passage is blocked and communicated with each other, an excessive differential pressure is generated at both axial end portions of the mover housed in the cylindrical portion of the stator, and the magnetic force of the electromagnetic drive portion is generated. A relief passage communicating with the movable element is provided so as not to hinder the axial movement of the mover driven by.

Japanese Patent Laid-Open No. 61-244948 discloses a spiral groove provided on the outer periphery of a mover as the escape passage, and in DE 19504185A1 German Patent Publication, the escape passage has an outer periphery inside the mover. A communication hole provided near the side is disclosed. As a result, it is possible to breathe between the both ends of the mover through the escape passage without generating an excessive fluid pressure in the fluid flowing in and out according to the movement of the mover.

[0005]

In any of the conventional configurations, since the escape passage is provided in the outer periphery of the mover or in the vicinity of the outer periphery side, the magnetic resistance flowing in the mover forming the magnetic circuit increases, that is, the magnetic transmission. There is a problem that efficiency is reduced. For this reason, sufficient consideration has not been given to preventing the occurrence of over-fluid pressure of the fluid flowing in and out according to the movement of the mover while improving the suction force.

The present invention has been made in consideration of such circumstances, and an object thereof is to increase the suction force without increasing the size and to prevent the fluid flowing in and out depending on the movement of the mover. An object of the present invention is to provide a solenoid valve having a structure for preventing generation of fluid pressure.

[0007]

According to a first aspect of the present invention, a valve having a valve member for opening and closing a fluid passage, and a housing for accommodating the valve member and having an opening for operating the valve member is formed. A solenoid valve having an electromagnetic coil, a stator, and a mover, and moving the valve member according to the movement of the mover, the valve member has a fluid passage formed in the housing. It has a large-diameter cylindrical part that opens and closes, and a small-diameter cylindrical part that contacts the mover.The mover has a relief passage on the shaft or near the shaft that communicates with the spaces located on both sides of the mover in the reciprocating direction. While being provided, the escape passage communicates with the reciprocating space formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner, via the small-diameter cylindrical portion.

Generally, it has a valve member that opens and closes a fluid passage by reciprocating in the axial direction, a mover that enables the valve member to move in the axial direction, and an electromagnetic coil that generates an electromagnetic force to attract the mover. In a solenoid valve equipped with an electromagnetic drive unit, a liquid-tight closed space is formed on both ends of the mover in the axial direction to prevent fluid from entering the electromagnetic coil. At times, excessive differential pressure is likely to occur in both closed spaces on the axial end side of the mover. If this overpressure occurs, it may hinder the axial movement of the mover driven by the electromagnetic force of the electromagnetic coil.Therefore, an escape passage is provided on the outer periphery of the mover so that both ends of the mover communicate with each other. There is. However, when the escape passage is provided in the cross section of the mover, in the magnetic circuit formed by the stator and the mover, the magnetic resistance when the magnetic flux flows through the mover increases, and the attractive force decreases.

On the other hand, in the solenoid valve according to the present invention, the mover has the escape passages communicating with the spaces located on both sides of the mover in the reciprocating direction on the axis or in the vicinity of the axis, that is, in the central portion or the inner side. The magnetic circuit formed by the stator that houses the mover and the mover prevents or suppresses a decrease in the magnetic transmission efficiency of the mover in which the magnetic flux concentrates on the outer peripheral side compared to the inside. be able to.

Further, the escape passage communicates with the reciprocating space formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner via the small-diameter cylindrical portion. There is. That is, the escape passage does not simply communicate with the fluid space for moving the mover on both ends of the mover, but the reciprocating movement formed by the valve member that constitutes the valve portion and the housing that houses the valve member. Since it communicates with the space, it is possible to reduce the throttling diameter of the relief passage necessary for preventing the occurrence of excess pressure difference, that is, excess fluid pressure. As a result, the amount of reduction in the cross-sectional area of the mover, which is reduced by providing the escape passage in the mover, can be reduced, so that the magnetic transmission efficiency of the mover can be improved.

Therefore, it is possible to both increase the suction force without increasing the size and prevent the occurrence of over-fluid pressure of the fluid flowing out in accordance with the movement of the mover.

It is said that the escape passage communicates with a reciprocating space formed by a large-diameter cylindrical portion and a housing accommodating the large-diameter cylindrical portion in a reciprocating manner via a small-diameter cylindrical portion. As described in claim 2 of the present invention, the small-diameter cylindrical portion has a communication passage penetrating in the axial direction, and the reciprocating space is in the communication passage provided in the radial direction or the axial direction of the large-diameter cylindrical portion. It is connected and both connecting passages communicate with the escape passage.

That is, the small-diameter cylindrical portion that contacts the mover is provided with a communication passage that penetrates in the axial direction, and the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner are provided. Since the communication passage is provided in the radial direction or the axial direction of the large-diameter cylindrical portion so as to be connected to the formed reciprocating space, both communicating passages can communicate with the escape passage, and thus the escape passage communicates with the reciprocating space. it can.

The escape passage communicates with the reciprocating space formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner via the small-diameter cylindrical portion. As described in claim 3 of the present invention, an outer peripheral communication passage is formed between the small-diameter cylindrical portion and a stator that is slidably supported outside the small-diameter cylindrical portion in the radial direction. A radial slit that connects the relief passage and the outer peripheral communication passage is provided at the end of the relief portion on the relief passage side, and the relief passage communicates with the reciprocating space through the outer communication passage. is there.

That is, an outer peripheral communication passage is provided between the small-diameter cylindrical portion and the stator that slidably accommodates the small-diameter cylindrical portion of the valve member, and the small-diameter cylindrical portion on the side contacting the mover is provided. A radial slit is provided at the end so that the escape passage provided on or near the axis of the mover and the outer peripheral communication passage formed on the outer periphery of the mover are communicated with each other. Can communicate with the reciprocating space.

According to the fourth aspect of the present invention, the opening is covered with a cup-shaped member formed of a thin non-magnetic member, and the cup-shaped member is connected to the housing in a liquid-tight manner. And a cylindrical portion that supports the mover so as to be movable in the axial direction.

As a result, it becomes easy to assemble the tubular portion of the cup-shaped member between the stator housing the mover and the mover, that is, on the inner circumference of the stator without misalignment. It is possible to prevent misalignment between the circumference and the mover. Furthermore, since the cup-shaped member is formed of a thin non-magnetic member, the inner diameter of the stator can be made as small as possible in accordance with the outer diameter of the mover.
With this, the electromagnetic drive unit without reducing the suction force,
That is, it is possible to reduce the size of the solenoid valve in the radial direction.

Therefore, the cup-shaped member has a connecting portion which is liquid-tightly connected to the housing and covers the opening of the housing to prevent the fluid in the housing from leaking to the outside of the cup-shaped member and to suck the fluid. The solenoid valve can be miniaturized in the radial direction without reducing the force.

According to a fifth aspect of the present invention, the housing has a flange portion that extends radially around the opening,
The coupling portion of the cup-shaped member is a flange portion that expands in the radial direction, and includes a fastening unit that fastens both flange portions in the axial direction.

Thus, if the seal member is interposed between both flange portions, the housing and the cup-shaped member can be easily sealed by the fastening means for fastening both flange portions in the axial direction.

According to the sixth aspect of the present invention, the valve member is formed of a magnetic member, and a cylindrical portion formed of a non-magnetic member is fixed to an end of the small diameter cylindrical portion on the side of the escape passage.

When the valve member is a magnetic member, by fixing the tubular portion formed of a non-magnetic member to the end portion of the valve member that abuts the mover, that is, the end portion on the escape passage side of the small diameter cylindrical portion. Since the non-magnetic material can be sandwiched between the mover and the valve member, the valve member can block the magnetism generated in the electromagnetic drive unit, particularly the mover, without being directly magnetized. is there.

In this case, regarding the stator forming the magnetic circuit with the mover, as described in claim 7 of the present invention, the first stator portion facing the mover radially outside the mover is provided. A second stator portion located in the axial direction of the mover, the first stator portion being arranged outside the cup-shaped member, and the second stator being arranged inside the cup-shaped member. In addition, the second stator portion is capable of contacting the valve member and includes a nonmagnetic contact portion.

This makes it easy to assemble the tubular portion of the cup-shaped member between the stator housing the mover and the mover, that is, on the inner circumference of the stator without misalignment, and at the same time to contact the valve member. Since the second stator portion in contact, that is, the contact portion of the stator is formed of a non-magnetic material, the valve member can block the magnetism generated in the electromagnetic drive portion without being directly magnetized. is there.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention, in which the electromagnetic communication of the present invention is applied to a hydraulic control valve of a valve timing adjusting device of an internal combustion engine, will be described with reference to the drawings.

FIG. 1 is a sectional view showing the structure of a solenoid valve according to an embodiment of the present invention. FIG. 2 is a cross-sectional view showing a valve member which is a main part according to the present embodiment in FIG.

The hydraulic control valve 1 of the present embodiment is an intake valve (provided in a cylinder head of a 4-cycle reciprocating engine (internal combustion engine), for example, a DOHC (double overhead camshaft) engine (hereinafter referred to as an engine). The retarded hydraulic chamber 100 (see FIG. 1) or the advanced hydraulic chamber 20 of the variable valve timing adjusting device that continuously changes the opening / closing timing (valve timing) of not shown).
0 (see Fig. 2) can selectively switch the oil supply to the solenoid valve (oil control valve: OC
V).

First, the variable valve timing adjusting apparatus to which the present embodiment is applied includes a timing rotor (not shown) as a housing member which is rotationally driven by a crankshaft (driving shaft) of an engine, and the timing rotor. With respect to the variable valve timing mechanism having a built-in intake side camshaft (not shown) as a driven shaft provided so as to be relatively rotatable, and the retarded hydraulic chamber 100 and the advanced hydraulic chamber 200 of the variable valve timing mechanism. It is composed of a hydraulic system circuit for selectively supplying and discharging hydraulic pressure, and an engine control device (hereinafter referred to as ECU) for controlling the hydraulic control valve 1 provided in the hydraulic system circuit.

The hydraulic system circuit includes a retard hydraulic chamber 100.
A first oil supply passage (oil passage on the retard angle hydraulic chamber side) 101 (see FIG. 1) for supplying and discharging hydraulic pressure to and from the advance hydraulic chamber 2
A first oil supply passage (oil passage on the advancing hydraulic chamber side) 201 (see FIG. 1) for supplying and discharging the hydraulic pressure is provided in 00. The first and second oil supply passages 101 and 201 are formed in the cylinder head of the engine, and the retard angle hydraulic chamber 100 is provided.
It is also a drain oil passage for draining oil from the inside or the advance hydraulic chamber 200.

Further, the first and second oil supply paths 101, 2
In 01, an oil pressure feed passage (oil passage on the oil pressure source side) 301 (see FIG. 1) on the oil pump 300 side and an oil discharge passage (oil passage on the drain side) 302 (see FIG. 1) are respectively controlled for hydraulic pressure. It is connected through the oil passage of the valve 1.

Here, in the oil pressure feed passage 301, an oil pump (for pumping up oil in an oil pan (drain) for temporarily storing engine oil as working fluid and discharging the oil to various parts of the engine ( Hydraulic pressure source) 3
00 (see FIG. 1) is provided, and the outlet end of the oil discharge passage 92 communicates with the oil pan. The oil pump 300 is rotationally driven in synchronism with the crankshaft of the engine, and pumps oil having a discharge amount proportional to the engine speed to each part of the engine.

Next, the solenoid valve 1 as the hydraulic control valve of the present invention will be described below with reference to FIGS. 1 and 2.

In the solenoid valve 1, the spool 3 as a valve member reciprocates in the sleeve 2 as a housing, so that the oil pressure of the oil pump 300 with respect to the retarded hydraulic chamber 100 and the advanced hydraulic chamber 200 of the variable valve timing mechanism is changed. Spool control valve for supplying / discharging (hereinafter referred to as valve section) B
And an electromagnetic drive unit S that generates a magnetic attraction force by supplying an electric current. The solenoid valve 1 can relatively control switching between the first oil supply passage 101, the second oil supply passage 201, the oil pressure feed passage 301, and the oil discharge passage 302 according to the drive current from the ECU. Is configured.

The valve portion B is provided with the first and second oil supply passages 10.
1, 201, oil pressure feed passage 301 and oil discharge passage 3
02, and a cylindrical sleeve 2 and a spool 3 slidably accommodated in the sleeve 2.

The sleeve 2 is provided with a plunger 6 as a movable element, which will be described later, on the spool 3 (more specifically, on the electromagnetic drive S side).
An opening 2a is formed for operating the spool 3 by abutting the small diameter cylindrical portion 3b) and applying a driving force to the spool 3.

As shown in FIG. 1, a plurality of openings 21, 22, 23, 24 are formed at predetermined wall positions of the sleeve 2 as fluid passages for allowing the working fluid to pass therethrough. Specifically, in the center of the wall surface of the sleeve 2, an input port (supply port) 22 connected to the oil pressure feed passage 301 on the oil pump 300 side, and on the right side surface in FIG. The retard oil port 23 connected to the first oil supply passage 101 on the angular hydraulic chamber 100 side, and the left side surface in FIG. An advance port 21 is formed to connect to the. In the present embodiment, the retard port 23, the advance port 21, and the input port 22 are respectively provided to the first oil supply passage 101 and the second oil supply passage irrespective of the mounting direction of the solenoid valve 1. 201, and the annular groove 23 on the wall surface so as to communicate with the oil pressure feeding path 301.
a, 21a, 22a are formed. Further, a drain port 24 connected to the oil discharge path 302 is formed on the wall surface of the axial end portion of the sleeve 2.

The spool 3 comprises a large-diameter cylindrical portion 3a for opening and closing the openings 21, 22, 23 formed in the sleeve 2 and a small-diameter cylindrical portion 3b for abutting the plunger 6 of the electromagnetic drive section S. The cylindrical portion 3a is supported by the inner peripheral wall of the sleeve 2 so as to be capable of reciprocating in the axial direction. The large-diameter cylindrical portion 3a is composed of large-diameter portions 31, 32, 33, 34, which are lands having a diameter substantially equal to the inner diameter of the sleeve 2, and groove portions 35, 36, 37 connecting these large-diameter portions. It is configured. More specifically, a concave first oil passage 35 is provided around the outer circumference of the spool 3 (between the first and second land portions 31 and 32), and the outer circumference of the spool 3 (the second and third land portions 3).
A concave second oil passage 36 is provided around (between 2 and 33), and the outer circumference (third and fourth land portions 33 and 34) of the spool 3 is provided.
A third oil passage 37 having a concave shape is provided around the space.

The second oil passage 36 is always in communication with the oil pressure feed passage via the input port 22 and is selectively connected to the retard port 23 and the advance port 21 depending on the axial movement position of the spool 3. Is switched to. Further, the first oil passage 35 and the third oil passage 37 communicate with the advance port 21 and the retard port 23, respectively, depending on the axial movement position of the spool 3. The first oil passage 35 and the third oil passage 37 are drain passages (hereinafter referred to as first drain passages) 38a in which the inside of the large-diameter cylindrical portion 3a is opened in the axial direction.
Is connected to.

The sleeve 2, more specifically, the large-diameter cylindrical portion 3a and the small-diameter cylindrical portion 3b are provided on the same axis as the plunger 6.

Between the shaft end of the spool 3 and the sleeve 2, a spring 8 as a mover urging means for urging the spool 3 in the right direction in FIG. 1 (electromagnetic drive section S side). Is arranged, and when the electromagnetic drive S is not energized,
The axial maximum movement amount L of the spool 3 is determined by the large-diameter cylindrical portion 3a of the spool 3 coming into contact with the contact portion 59 of the stator 5, which will be described later.

The details of the spool 3 according to the present invention will be described later.

The electromagnetic drive section S includes an electromagnetic coil 4, a stator 5, a plunger 6 as a mover, and a cup-shaped member 7.
It is configured to include and.

The electromagnetic coil 4 includes a bobbin 41 and a bobbin 4
1 and a coil 42 wound around the outer periphery of the coil 1. The end portion of the coil 42 is configured so that current can be supplied from the outside.
It is electrically connected to the terminal 43. The terminal 42 is resin-molded together with the bobbin 41 or the yoke 5.

The stator 5 is formed of a magnetic member together with the plunger 6, and constitutes a magnetic circuit. The stator 5 is composed of a yoke 51 as a first stator portion and a stator core 52 as a second stator portion.

The yoke 51 has an inner peripheral cylinder portion 51a and an outer peripheral cylinder portion 51b, and an inner peripheral cylinder portion 51a and an outer peripheral cylinder portion 51b.
The bobbin 41 and the coil 42 are housed between the and.
The inner peripheral cylinder portion 51a as an inner cylinder covers the outer periphery of the plunger 6 and faces the plunger 6 on the radially outer side of the plunger 6. The outer peripheral cylinder portion 51b serving as the outer cylinder includes the coil 4
It is connected to the stator core 52 via the outside of 2.
A caulking portion 51c as a connecting means is formed at the end of the outer peripheral tubular portion 51b. Inner peripheral cylindrical portion 5 of the yoke 51
1a and the suction portion 52a of the stator core 52 face each other with a gap Mg having a predetermined length formed in the reciprocating direction of the plunger 6. An end portion 52 of the suction portion 52a on the inner peripheral tubular portion 51a side
The radial thickness of at decreases as it approaches the plunger 6.

The plunger 6 is a substantially cylindrical body, and is reciprocally accommodated in the inner cylindrical portion 51a of the stator 5 via a cup-shaped member 7 formed of a non-magnetic member described later.

The details of the plunger 6 will be described later in relation to the spool 3 that reciprocates in cooperation with each other.

The cup-shaped member 7 is formed of a non-magnetic member such as stainless steel, and has a bottomed cylindrical portion 7a as a cylindrical portion.
And has a flange portion 7b as a connecting portion and is formed in a cup shape.

The cup-shaped member 7 is arranged inside the inner cylindrical portion 51a of the yoke 51, in other words, the yoke 51 is arranged outside the cup-shaped member 7. Further, the stator core 52 is arranged inside the cup-shaped member 7.

The flange portion 7b of the cup-shaped member 7
Is the flange portion 52b of the stator core 52 and the sleeve 2
By caulking the flange portion 2b of the yoke 51 with the caulking portion 51c of the yoke 51, the stator core 52 and the sleeve 2 are fluid-tightly coupled with each other with the O-ring 58 interposed.

Here, the plunger 6 according to the present invention and the structure that reciprocates in cooperation with the plunger 6, increase the suction force without increasing the size, and the working fluid that flows out in accordance with the movement of the plunger 6. A structure that is compatible with preventing the occurrence of overfluid pressure will be described below with reference to FIGS. 1 and 2.

Generally, a spool 3 that opens and closes a fluid passage by reciprocating in the axial direction, a plunger 6 that enables the axial movement of the spool 3 and an electromagnetic coil 4 that generates an electromagnetic force that attracts the plunger 6 are provided. In the solenoid valve having the electromagnetic drive section S, the liquid tight closed spaces G6a and G6b are formed on both end sides where the plunger 6 moves in the axial direction so that the fluid does not enter the electromagnetic coil 4. Therefore, when the plunger 6 moves, this double closed space G
Excessive pressure tends to occur between 6a and G6b. If this excess pressure is generated, there is a risk that the axial movement of the plunger 6 driven by the electromagnetic force of the electromagnetic coil 42 may be hindered. Therefore, the outer periphery of the plunger 6 or the like is provided with a relief passage for communicating both ends. However, if an escape passage is provided in the cross section of the plunger 6 as described above, in the magnetic circuit formed by the stator 5 (specifically, the yoke 51, the stator core 52) and the planarer 6, the magnetic resistance when the magnetic flux flows through the plunger 6 is provided. Increase and the suction force decreases.

On the other hand, in the solenoid valve 1 of the present invention, as shown in FIG. 1, the relief passage 61 communicating with the working fluid spaces G6a and G6b located at both ends of the plunger 6 in the reciprocating direction is provided with the escape passage 61 of the plunger 6. It is formed on the shaft or in the vicinity of the shaft, that is, on the central portion or the inner side of the plunger 6.

As a result, the stator 5 forming the magnetic circuit
In the plunger 6 and the plunger 6, the magnetic flux flowing in the plunger 6 is concentrated on the outer peripheral side as compared with the inside due to the structure in which the plunger 6 is reciprocally housed in the stator 5, and the escape passage 61 Is formed in the central portion or the inner side of the plunger 6, it is possible to prevent or suppress the decrease in the magnetic transmission efficiency of the plunger 6.

Further, the escape passage 61 is provided with a small-diameter cylindrical portion 3b of the spool 3 which is in contact with the plunger 6 (specifically,
A working fluid space (hereinafter referred to as a reciprocating movement space) which is formed by the large-diameter cylindrical portion 3a and the sleeve 2 via the slit 3b1) and is located at both ends in the reciprocating movement direction of the large-diameter cylindrical portion 3a.
It has a feature of communicating with G3a and G3b. That is, the escape passage 6 does not simply communicate with the working fluid spaces G6a and G6b located at both ends in the reciprocating direction of the plunger 6, but rather the large-diameter cylindrical portion 3a of the spool 3 of the valve portion B.
The reciprocating space G3a located at both ends in the reciprocating direction of
It communicates with G3b.

As a result, the working fluid space for accommodating the working fluid flowing out in accordance with the expansion and contraction of the working fluid spaces G6a and G6b due to the reciprocating movement of the plunger 6 can be expanded. Therefore, both spaces G6a, G6 due to the reciprocating movement of the plunger 6
It is possible to reduce the throttling diameter of the escape passage 61 necessary for preventing the occurrence of excess pressure difference between b, that is, excess fluid pressure.

Therefore, since the cross-sectional area of the plunger 6 which is reduced by providing the escape passage 61 can be reduced, the magnetic transmission efficiency of the plunger 6 can be improved.

The escape passage 61 has a small-diameter cylindrical portion 3b.
(Specifically, the large diameter cylindrical portion 3a via the slit 3b1)
Working fluid space (hereinafter,
Details of the structure communicating with G3a and G3b (referred to as a reciprocating space) will be described below with reference to FIGS. 1 and 2. As shown in FIG. 2, in the spool 6 that abuts on the plunger 6, the outer circumference of the small-diameter cylindrical portion 3b and the stator 5 that slidably accommodates the small-diameter cylindrical portion 3b (specifically, the radially outer side of the small-diameter cylindrical portion 3b). Suction part 52 of the second stator part 52 arranged in the
An outer peripheral communication passage 39a is formed between the inner periphery and the inner periphery of a), and a radial slit 39b is formed at the end of the cylindrical small diameter portion 3b that abuts on the plunger 6. As a result, when the plunger 6 moves, the working fluid flowing out through the relief passage 61 has a slit 39b formed in the end portion and the outer periphery of the small diameter cylindrical portion 3b and an outer peripheral communication passage 39a.
Through the reciprocating space G3a.

As shown in FIG. 1, the opening 2a of the sleeve 2 is covered with a cup-shaped member 7. The cup-shaped member 7 is formed of a thin non-magnetic member and has a flange as a connecting portion. It has a portion 7b and a bottomed cylindrical portion 7a as a tubular portion that supports the plunger 6 movably in the axial direction.

This makes it easy to assemble the cylindrical portion 7a of the cup-shaped member 7 between the stator 5 accommodating the plunger 6 and the plunger 6, that is, on the inner periphery of the stator 5 without misalignment. It is possible to prevent misalignment between the inner circumference of the stator 5 and the plunger 6. Furthermore, since the cup-shaped member 7 is formed of a thin non-magnetic member, the inner diameter of the stator 5 can be made as small as possible in accordance with the outer diameter of the plunger 6. As a result, the electromagnetic drive unit S, that is, the electromagnetic valve 1 can be downsized in the radial direction without reducing the suction force.

A second drain passage 38b is formed in the reciprocating space G3a so as to pass through the large-diameter cylindrical portion 3a in the radial direction, and an excess in the reciprocating space G3a is provided through the first drain passage 38a. Drain port 2
4 to return to the oil discharge path 302, the working fluid space G6 due to the reciprocating movement of the plunger 6
a, G6b fluid pressure, drain port 24
A constant low pressure can be maintained in the oil discharge path 302 connected to.

Further, the spool 3 is attached to the contact portion 59 of the stator 5.
Since the maximum movement amount L of the spool 3 in the axial direction is determined by the abutment of the large-diameter cylindrical portion 3a, the cup shape that accommodates the plunger 6 freely in the axial direction when the electromagnetic drive unit is not energized. The biasing force of the spring 8 is not applied to the end of the bottomed cylindrical portion 7a of the member 7.

Therefore, the wall thickness of the cup-shaped member 7 can be made thin so as not to be damaged by the low pressure of the oil discharge passage 302, so that the electromagnetic drive portion S, that is, the electromagnetic valve 1 is not reduced. Further downsizing in the radial direction is possible.

Next, the operation of the solenoid valve 1 will be described below with reference to FIGS.

FIG. 5 is a sectional view showing the operating state of the solenoid valve in the most retarded angle mode, and FIG. 6 is a sectional view showing the operating state of the solenoid valve in the most advanced angle mode. It should be noted that FIG. 1 showing the configuration of the solenoid valve 1 of the present invention shows the state in the most retarded angle mode.

(1) Most retarded angle mode FIG. 5 shows a state in which no current is supplied to the coil 42, the magnetic attraction force is not acting on the plunger 6, and the spool 3 and the plunger 6 are provided with the spring 8 It is in the position shown in FIG. At this time, the valve section B
The input port 22 and the retard port 23 of the sleeve 2 of
The oil pressure feed passage 301 and the first oil oil passage 101 are connected to each other through the second oil passage 36 of the spool 3 and the input port 22 and the advance port 21 are blocked, so that the input port 22 and the retard angle are delayed. Connected via port 23. That is, oil is supplied from the oil pump 300 to the retard hydraulic chamber 100. At the same time, the advance port 21 is connected to the first oil passage 3
5, the oil in the advance hydraulic chamber 200 is returned to the oil pan via the oil discharge path 302. That is, the position L of the spool 3 is L
= L.

(2) Maximum advance mode When a control current is supplied from the ECU to the coil 42, an electromagnetic force is generated in the electromagnetic coil 4 according to the control current. When this electromagnetic force is generated in the electromagnetic coil 4, a magnetic flux corresponding to the electromagnetic force flows through the stator 5 and the plunger 6 as a magnetic circuit, and the plunger 6 is directed toward the suction portion 52a of the stator 5 in the left side in FIG. Is sucked in the direction.

At this time, the input port 22 and the advance port 21 of the sleeve 2 of the valve portion B are connected to the second oil passage 3 of the spool 3.
The oil pressure feed passage 301 and the second oil oil passage 201 are connected to each other via the input port 22 and the advance angle port 21 by communicating with each other via 6 and disconnecting the input port 22 and the retard angle port 23. That is, oil is supplied from the oil pump 300 to the advance hydraulic chamber 200. At the same time, since the retard port 23 communicates with the drain port 24 via the third oil passage 37, the oil in the retard hydraulic chamber 100 is returned to the oil pan via the oil discharge passage 302. That is, the position L of the spool 3 decreases.

Here, when the control current reaches a predetermined value (for example, the maximum value as the drive current, or an intermediate value between the minimum value and the maximum value controlled by the ECU), the solenoid valve 1 moves to the maximum advance angle shown in FIG. It becomes the state of the mode. That is, the position L of the spool 3 becomes L = L.

(Modification) As a first modification, a reciprocating space in which the escape passage 61 described in the above embodiment is located on both ends in the reciprocating direction of the large-diameter cylindrical portion 3a via the small-diameter cylindrical portion 3b. In the structure communicating with G3a and G3b, the structure of the spool 3 is replaced with the structure shown in FIG. FIG. 3 is a cross-sectional view showing a valve member which is a main part according to the first modification.

As shown in FIG. 3, the small-diameter cylindrical portion 3b of the spool 3 is formed with a communication passage 3b1 penetrating in the axial direction. Therefore, when the plunger 6 moves, the escape passage 61 is formed.
The working fluid flowing out through the slit 39b formed in the end portion and the outer periphery of the small-diameter cylindrical portion 3b and the outer peripheral communication passage 3
It can be led out to the reciprocating space G3a via 9a.

As a result, the first modification can similarly obtain the effects of the above-described embodiment.

As a second modification, a spool 3 having different magnetic characteristics shown in FIG. 4 is provided in place of the spool formed of the non-magnetic member described in the first modification and the like.

As shown in FIG. 4, the spool 3 is formed of a magnetic member, and a cylindrical portion 3b2 formed of a non-magnetic member is fixed to the end portion that abuts on the plunger 6.

That is, in the plunger 6 and the spool 3 formed of a magnetic member, the plunger 6 and the spool 3 are
With a structure in which a non-magnetic member formed of a non-magnetic member is sandwiched between the spool and the magnetic member, the spool 3 formed of a magnetic member (specifically, the portion of the spool 3 excluding the cylindrical portion that is the end) is The magnetism of the plunger 6 magnetized by the electromagnetic force of the coil 4 can be blocked without being directly magnetized.

The contact portion 59 of the stator 5 for controlling the maximum reciprocating amount L of the spool 3 is made of a non-magnetic member. As a result, the spool 3 is attached to the plunger 6
With respect to the magnetism, it can be surely cut off without being directly magnetized.

[Brief description of drawings]

FIG. 1 is a sectional view showing a configuration of a solenoid valve according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view showing a valve member that is a main part according to the present embodiment in FIG.

FIG. 3 is a cross-sectional view showing a valve member which is a main part according to a first modification.

FIG. 4 is a cross-sectional view showing a valve member and a mover, which are essential parts according to a second modification.

FIG. 5 is a sectional view showing an operating state of the solenoid valve in the most retarded angle mode.

FIG. 6 is a cross-sectional view showing an operating state of the solenoid valve in the most advanced angle mode.

[Explanation of symbols]

1 Solenoid Valve (Hydraulic Control Valve) 2 Sleeve (Housing) 2a Opening 2b Flange 21, 22, 23 Advance Port, Input Port, Delay Port (Fluid Passage) 3 Spool (Valve Member) 3a Large Diameter Cylindrical Section 3b Small-diameter cylindrical portion 3b1 (passing through in the axial direction) communication passage 3b2 (formed of a non-magnetic member) tubular portion 38a First drain passage (communication passage provided in the large-diameter cylindrical portion 3a in the axial direction) 38b First drain Passage (communication passage provided in radial direction of large-diameter cylindrical portion 3a) 39a Outer peripheral communication passage 39b Slit 4 Electromagnetic coil 42 Coil 5 Stator 51 Yoke (first stator portion) 52 Stator core (second stator portion) 59 Contact part (contact part of stator 5 with which large-diameter cylindrical part 3a of spool 3 contacts) 6 Plunger (mover) 61 Escape passage 7 Cup-shaped members 7a, 7b Bottomed cylindrical part (tube) Part), flange part (connecting part) 8 spring 100 retarding hydraulic chamber 200 advancing hydraulic chamber 300 oil pump B valve part S electromagnetic drive parts G3a, G3b working fluids located on both ends in the reciprocating direction of the large diameter cylindrical part 3a Space (reciprocating space) G6a, G6b Working fluid space located on both ends in the reciprocating direction of the plunger 6.

Continued front page    F-term (reference) 3H106 DA03 DA23 DB02 DB12 DB22                       DB32 DC09 DC18 DD05 EE07                       EE16 KK02 KK17

Claims (7)

[Claims] 1. A valve member for opening and closing a fluid passage, and a valve portion having a housing for accommodating the valve member and having an opening for operating the valve member, an electromagnetic coil, a stator, and a mover. And a solenoid drive unit that moves the valve member according to the movement of the mover, wherein the valve member has a large-diameter cylindrical shape that opens and closes the fluid passage formed in the housing. And a small-diameter cylindrical portion that abuts against the mover, the mover is provided with an escape passage communicating with spaces located on both sides in the reciprocating direction of the mover on or near the axis. The escape passage communicates with the reciprocating space formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner, via the small-diameter cylindrical portion. Is characterized by solenoid valve. 2. A reciprocating space in which the escape passage is formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner via the small-diameter cylindrical portion. The small-diameter cylindrical portion has a communication passage that penetrates in the axial direction, and the reciprocating space is connected to the communication passage provided in the radial direction or the axial direction of the large-diameter cylindrical portion. The solenoid valve according to claim 1, wherein the communication passages are in communication with the escape passages. 3. A reciprocating space in which the escape passage is formed by the large-diameter cylindrical portion and the housing that accommodates the large-diameter cylindrical portion in a reciprocating manner via the small-diameter cylindrical portion. To communicate with the small-diameter cylindrical portion, and an outer peripheral communication passage is formed between the small-diameter cylindrical portion and the stator that is slidably supported outside the small-diameter cylindrical portion in the radial direction. A radial slit that connects the escape passage and the outer peripheral communication passage is provided at an end portion of the shape portion on the escape passage side, and the escape passage is provided in the reciprocating space via the outer peripheral communication passage. The solenoid valve according to claim 1, wherein the solenoid valve is in communication. 4. The opening is covered with a cup-shaped member formed of a thin non-magnetic member, and the cup-shaped member includes a connecting portion liquid-tightly connected to the housing and the mover. The solenoid valve according to any one of claims 1 to 3, further comprising: a cylindrical portion movably supported in the axial direction. 5. The housing has a flange portion that expands in the radial direction around the opening, and the coupling portion of the cup-shaped member is a flange portion that expands in the radial direction. The solenoid valve according to claim 4, further comprising fastening means for fastening in a direction. 6. The valve member is formed of a magnetic member, and a cylindrical portion formed of a non-magnetic member is fixed to an end of the small-diameter cylindrical portion on the side of the escape passage. The solenoid valve according to claim 2 or claim 3. 7. The stator has a first stator portion that faces the mover radially outside the mover and a second stator portion that is located in the axial direction of the mover. And the first
The stator part is arranged outside the cup-shaped member, the second stator is arranged inside the cup-shaped member, and the second stator part can abut the valve member. 7. The solenoid valve according to claim 6, further comprising a nonmagnetic contact portion.