JP2003090454A - Proportional solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a proportional solenoid valve surely preventing troubles such as a plunger's being caught by a yoke for improving operating performance by a low cost means, and capable of improving operating performance further and improving sealing performance at low cost. SOLUTION: This device is provided with the plunger 23 formed of a magnetic body and driving a valve by moving, the yoke 24 including a hollow part inside and composed of a magnetic body applying electromagnetic attraction force generated by energizing a coil 25c wound around outer part thereof on the plunger 23, and a cylindrical member 27 arranged in the hollow part of the yoke 24 and composed of non-magnetic body retaining the plunger 23 on an inner circumference slidably in an axial direction.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a proportional solenoid valve.

[0002]

2. Description of the Related Art Conventionally, in a proportional solenoid valve in which a plunger is attracted by an electromagnetic force flowing through a yoke and a valve spool is operated at an arbitrary position, it is attracted so that the electromagnetic force generated as much as possible does not change with the stroke of the plunger. It is considered that the yoke is provided with a recess and the plunger is sucked into the recess. As such conventional technology,
See, for example, Japanese Patent Laid-Open No. 2001-50420.

[0003]

However, in the above-mentioned prior art, when the axial center of the plunger is deviated from the axial center of the recess provided in the yoke, the outer circumference of the plunger is caught on the inner circumference of the yoke. However, since there is a problem that the stroke does not occur any more, it is necessary to provide a ball bearing with less wear, and it is also necessary to improve the positional accuracy of the plunger, the recess, and the ball bearing. For this reason, it must be expensive.

The present invention has been made by paying attention to the above-mentioned conventional problems, and it is possible to inexpensively improve the operation performance by reliably preventing the trouble such as the plunger being caught by the yoke by an inexpensive means. To provide a proportional solenoid valve that can be achieved at a low cost while further improving the operating performance and the sealing performance.

[0005]

In order to achieve the above-mentioned object, the proportional solenoid valve of the present invention is formed of a magnetic material,
A plunger (23) that drives a valve by moving and a hollow part inside, and an electromagnetic attraction force generated by energizing a coil (25c) wound outside is applied to the plunger (23). A yoke (24) made of a magnetic material, and a tubular member (27) made of a non-magnetic material, which is arranged in the hollow portion of the yoke (24) and holds the plunger (23) axially slidably in the inner circumference. )When,
It is a means equipped with.

The invention described in claim 2 is the same as claim 1
In the proportional solenoid valve described in (1), the outer periphery of the plunger and the inner periphery of the tubular member are formed to have a constant diameter, and both are in sliding contact with each other.

According to a third aspect of the present invention, in the proportional solenoid valve according to the first or second aspect, the cylindrical member is provided with a stopper that restricts sliding of the plunger at a predetermined position. The means to do so.

According to a fourth aspect of the present invention, in the proportional solenoid valve according to the third aspect, the stopper is made of a non-magnetic material.

According to a fifth aspect of the present invention, in the proportional solenoid valve according to any of the first to fourth aspects, the tubular member has a shape in which one end has a bottomed tubular shape and is capable of accommodating a plunger. And a flange part is integrally formed on the outer periphery of the other end part, and the flange part fixes the yoke to the yoke fixing part while being sandwiched between the yoke and the yoke fixing part. This means that the data is retained.

According to a sixth aspect of the present invention, in the proportional solenoid valve according to the fifth aspect, a seal member is provided between the flange portion and the yoke fixing portion.

According to a seventh aspect of the present invention, in the proportional solenoid valve according to the fifth or sixth aspect, the bottom portion of the tubular member also serves as a stopper that restricts sliding of the plunger, and the plunger and the surface. The means is characterized in that it is formed in an inclined cross-sectional shape that does not contact.

[0012]

In the proportional solenoid valve of the present invention, since the plunger and the yoke are completely separated by the tubular member made of a non-magnetic material, the relative positional accuracy between them is not increased. However, it is possible to avoid the trouble that the two do not come into contact with each other, that is, the two are caught and do not stroke. Further, since the plunger is inserted into the tubular member, even if the plunger is worn by sliding inside the tubular member, it does not come into contact with the yoke, and an expensive bearing such as a ball bearing is required. Not. As described above, according to the present invention, a tubular member that can be manufactured at a low cost is simply interposed between the yoke and the plunger without using the expensive ball bearing and the high setting of the position accuracy which are conventionally required. With an inexpensive means, it is possible to provide a proportional solenoid valve with high operating performance that can reliably prevent problems such as the plunger getting caught in the yoke.

According to the second aspect of the invention, the outer circumference of the plunger and the inner circumference of the tubular member are always in sliding contact with each other. Therefore, it is difficult for contaminants to enter from between the outer periphery of the plunger and the inner periphery of the tubular member, and thus it is possible to prevent defective operation due to the intrusion of contaminants and improve operating performance.

According to the third aspect of the invention, the stopper for restricting the sliding of the plunger at a predetermined position is provided inside the tubular member. Therefore, it is not necessary to separately attach a stopper member to a portion for accommodating the valve or the plunger, and the assembling workability is excellent.

In the invention according to claim 4, since the stopper is made of a non-magnetic material, when the stopper restricts the sliding of the plunger, the plunger is not attracted to the stopper.

According to the fifth aspect of the invention, the fluid flowing into the tubular member from the valve side is blocked by the bottomed portion of the tubular member to prevent the fluid from flowing out to the outside such as the coil portion. In this way, it is possible to prevent fluid leakage without separately providing a seal member, and it is possible to prevent fluid leakage at low cost.

According to the sixth aspect of the invention, since the seal member is provided between the flange portion formed on the tubular member and the yoke fixing portion, the fluid flowing from the valve side is prevented from leaking from the front and rear of the plunger. It can be surely prevented by one sealing member. Therefore, it is possible to prevent fluid leakage at low cost.

In the invention described in claim 7, the plunger is brought into contact with the bottom portion of the cylindrical member and its sliding is regulated.
At this time, even if the plunger end is not specially processed, the outer peripheral portion of the plunger end and the bottom of the tubular member are not in surface contact but in line contact. Therefore, when restarting after stopping the plunger for a long time, the plunger can be easily started.

[0019]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

(Embodiment) FIG. 1 is a sectional view showing a valve timing adjusting device to which the proportional solenoid valve of the embodiment is applied. In FIG. 1, reference numeral 1 denotes a sprocket, which is driven by a chain, a belt, or the like (not shown) from a crankshaft serving as an engine drive shaft (not shown) to rotate in synchronization with the crankshaft.

In the figure, reference numeral 2 is a cam shaft. The cam shaft 2 receives a driving force from the sprocket 1 and opens / closes at least one of an intake valve and an exhaust valve (not shown).

The camshaft 2 and the sprocket 1
And are coaxially provided so as to be rotatable relative to each other. That is, the sprocket 1 is coaxially and integrally fixed to the shoe housing 4 and the front plate 5 by the bolt 3. On the other hand, the vane member 6 is fastened and fixed to the left end portion of the camshaft 2 in the figure by the bolt 7. Furthermore, inside the shoe housing 4,
Although not shown, a substantially fan-shaped space portion is formed when viewed from the left side in the drawing, and a vane (not shown) provided in the vane member 6 is accommodated in the space portion. An advance hydraulic chamber and a retard hydraulic chamber (not shown) are formed on both sides. Therefore, when hydraulic fluid is supplied to the advance hydraulic chamber (not shown), the vane member 6 relatively rotates in the advance direction with respect to the shoe housing 4, whereby the camshaft 2 moves relative to the sprocket 1. Rotate relatively in the advance direction. On the other hand, when hydraulic fluid is supplied to the retard hydraulic chamber (not shown), the vane member 6 relatively rotates in the retard direction with respect to the shoe housing 4, whereby the camshaft 2 retards relative to the sprocket 1. Rotate relatively in the angular direction.

The configuration and operation of the valve timing adjusting device described above are well known and not the subject matter of the present invention. Therefore, detailed description thereof will be omitted, and the proportional solenoid valve 20 of the embodiment will be described below. Will be described.

The proportional solenoid valve 20 of this embodiment supplies and discharges the hydraulic fluid to and from the advance hydraulic chamber and the retard hydraulic chamber. The proportional solenoid valve 20 includes a valve sleeve 21 and a valve spool. 22, a plunger 23, a yoke 24, a mold coil 25, and a tubular member 27.

The valve sleeve 21 is formed of a non-magnetic metal such as aluminum or a resin in a substantially cylindrical shape, and a flange 21f is formed at a base end portion thereof so as to be drilled from one end surface of the valve body 30. The flange 21f is fitted and fixed in a state where the flange 21f is brought into contact with one end surface of the valve body 30 by being inserted into the provided valve housing hole 31 from the front end side. A seal member 21g is provided between the outer circumference of the base end portion of the valve sleeve 21 and the inner circumference of the valve accommodating hole 31.
Is provided to prevent leakage of hydraulic oil.

Further, the valve sleeve 21 is provided between the valve body 30 and the advance side hydraulic pressure supply port 21a, the retard side hydraulic pressure supply port 21b, and the advance side hydraulic pressure discharge port 2.
1c, retard side hydraulic discharge port 21d, and hydraulic pressure supply port 2
1e are formed. The advance side hydraulic pressure supply port 2
1a is connected to the advance side hydraulic circuit 32 which is connected to the advance angle hydraulic chamber (not shown). The retard side hydraulic pressure supply port 21b is connected to a retard side hydraulic circuit 33 connected to a retard angle hydraulic chamber (not shown). The advance side hydraulic pressure discharge port 21c and the retard side hydraulic pressure discharge port 21d are connected to a drain tank (not shown), and hydraulic pressure discharge circuits 34 and 35 are provided.
It is connected to the. The hydraulic pressure supply port 21e is connected to a hydraulic pressure supply circuit 36 connected to a hydraulic pump (not shown).

The valve spool 22 is slidably inserted in the inner circumference of the valve sleeve 21 in the axial direction, and is made of a non-magnetic metal such as aluminum, as shown in the enlarged sectional view of FIG. As described above, the first land 221, the second land 222, and the third land 223 each having a large diameter are formed in order from the tip end side in the axial direction, and the flange 22f is formed on the outer periphery of the base end portion. A return spring 28 made of, for example, spring steel is provided between the flange 21f and the step portion 21h formed on the inner circumference of the valve sleeve 21, and the valve spool 22 is provided by the return spring 28. It is biased to the right in FIG. A plurality of axial grooves 224 are formed on the outer circumference of the second land 222 along the entire length of the outer circumference.

Next, the ports 21a to 21d of the valve sleeve 21 and the lands 221 of the valve spool 22.
The positional relationship with respect to ~ 223 will be described. At the position where the valve spool 22 slides to the right in the figure by the return spring 28 shown in FIG. 2 (this position is called the OFF position), the first land 221 closes the retard side hydraulic discharge port 21d and advances. The angle side hydraulic pressure discharge port 21c and the retard angle side hydraulic pressure discharge port 21d are shut off, and the second land 222 is closed.
However, the hydraulic pressure supply port 21e and the retard side hydraulic pressure supply port 21
b, and the third land 223 communicates the advance side hydraulic pressure supply port 21a and the advance side hydraulic pressure discharge port 21c. Therefore, at the OFF position, the hydraulic oil is supplied to the retarded hydraulic pressure chamber (not shown) through the retarded hydraulic pressure supply port 21b, while the advanced hydraulic pressure (not shown) is supplied through the advanced hydraulic pressure supply port 21a. Hydraulic oil discharge port 2 for advancing hydraulic oil in the room
It is discharged via 1c. In this case, the camshaft 2 rotates to the retard side.

Next, in the state where the valve spool 22 is arranged at the position shown in FIG. 3 (this is called the neutral position), the first land 221 has the retard side hydraulic discharge port 21d.
Is closed to block between the advance side hydraulic pressure discharge port 21c and the retard side hydraulic pressure discharge port 21d, and the second land 222 closes the hydraulic pressure supply port 21e, and the hydraulic pressure supply port 21e and the advance side hydraulic pressure supply port. 21a and the retard side hydraulic pressure supply port 21b are cut off, and the third land 223 closes the advance side hydraulic pressure discharge port 21c to close the advance side hydraulic pressure supply port 2
The connection between 1a and the advance side hydraulic pressure discharge port 21c is cut off.
Therefore, at this neutral position, both the advance side hydraulic pressure supply port 21a and the retard side hydraulic pressure supply port 21b are closed, and hydraulic fluid is not supplied to both the advance angle hydraulic chamber and the retard angle hydraulic chamber (not shown). The camshaft 2 is held in position by being trapped. The advance side hydraulic pressure supply port 21a and the retard side hydraulic pressure supply port 21b are provided on the first land 221 and the third side for the respective hydraulic pressure discharge ports 21c and 21d.
The land 223 is surely shut off to maintain the neutral position, but the advance side hydraulic pressure supply port 21a and the retard side hydraulic supply port 21b are not connected to each other.
It is not completely blocked from 1e, but is slightly communicated with the hydraulic pressure supply port 21e by the groove 224 formed on the outer periphery of the land 222, and in the advance hydraulic chamber and the retard hydraulic chamber (not shown). A small amount of oil corresponding to the leakage is supplied to each chamber.

Next, at the position shown in FIG. 4 in which the valve spool 22 is slid to the left with respect to the neutral position (this position is referred to as the ON position), the first land 221 discharges the retard side hydraulic pressure. The port 21d communicates with the retard side hydraulic pressure supply port 21b, and the second land 222 is connected to the hydraulic pressure supply port 21e.
And the advance side hydraulic pressure supply port 21a are communicated with each other, and the third land 223 closes the advance side hydraulic pressure discharge port 21c to block between the advance side hydraulic pressure supply port 21a and the advance side hydraulic pressure discharge port 21c. Therefore, at this ON position, the hydraulic oil in the retard hydraulic pressure chamber (not shown) is discharged through the retard hydraulic pressure supply port 21b and the retard hydraulic pressure discharge port 21d, while the advance hydraulic pressure supply port is discharged. The hydraulic oil is supplied to an advance hydraulic chamber (not shown) via 21a. In this case, the camshaft 2 rotates to the advance side.

It is the plunger 2 that the above-mentioned valve spool 22 slides against the biasing force of the return spring 28.
It is formed by being pushed in the axial direction by 3. The plunger 23 includes a small-diameter columnar shaft portion 23a and the shaft portion 2
The large diameter cylindrical armature portion 23b is provided on the outer periphery of the base end portion of 3a. In the present embodiment, the non-magnetic stainless steel shaft portion 23a is press-fitted into the center of the iron armature portion 23b, but both may be integrally formed of a magnetic material such as iron. In addition, a plurality of grooves 23 for fluid circulation are provided on the outer periphery of the amateur part 23b.
c is formed over the entire length in the axial direction.

The plunger 23 is slidably supported by a tubular member 27. The tubular member 27 is formed of, for example, a non-magnetic metal such as stainless steel or a hard resin, and is provided coaxially with the valve spool 22 and the plunger 23. As shown in the drawing, the armature of the plunger 23 is provided. A tubular portion 27a having a constant diameter dimension in which the outer periphery of the portion 23b is in sliding contact with the inner periphery thereof, and the tubular portion 27
a bottom portion 27b integrally formed at one end of a with a curved surface shape
And a flange portion 27f extending in the outer diameter direction at the other end of the tubular portion 27a.

Further, a stopper 271 is provided inside the tubular member 27. The stopper 271 has a cylindrical shape and is made of a non-magnetic material such as stainless steel or resin. Further, the stopper 271 is
The position of the one end face is provided so as to match the opening end face of the tubular portion 27a (end face of the flange portion 27f).
The other end of 1 is arranged so as to regulate the movement of the plunger 23 in the left direction in the figure at a predetermined position, that is, a position corresponding to the ON position of the valve spool 22, and is tightly fitted or not shown. It is fixed by fixing screws. The movement of the plunger 23 to the right in the figure is restricted by using the bottom portion 27b of the tubular member 27 as a stopper, and the restricted position is O of the valve spool 22.
This corresponds to the FF position.

The yoke 24 is formed of a magnetic material such as iron and has a flange member 24a having a flange 24f.
And a case member 24b having a case 24c are divided into two substantially cylindrical members in the front-rear direction in the axial direction. The hollow member inside accommodates the cylindrical member 27 and the plunger 23, and the mold coil 25 is mounted between the two members 24a and 24b. The yoke 24, the mold coil 25, and the valve sleeve 21 are integrally fixed by crimping the outer periphery of the tip of the case 24c to the flange 21f of the valve sleeve 21. Due to this caulking, the flange portion 27f of the tubular member 27 is replaced with the flange 21f of the valve sleeve 21.
And a flange 24f of the yoke 24, and a sealing member 29 is provided between the flange 24f and the flange 21f to prevent hydraulic oil leakage. In addition, the case member 24b of the yoke 24
A bracket 24g is fixed to the outer periphery of the bracket by welding or the like, and the bracket 24g is fixed to the valve body 30 with bolts or the like.

The mold coil 25 includes a bobbin 25b composed of two resin inner and outer members, and the bobbin 2
And a coil 25c housed inside 5b, and
A connector 25d is formed integrally with the bobbin 25b. The connector 25d has the coil 25
A terminal 25t connected to c and energized is provided.

Next, the assembly procedure of the embodiment will be described. At the time of assembling, as shown in FIG. 5, the valve spool 22 having the return spring 28 assembled therein is inserted into the valve sleeve 21, and further the seal member 29 is assembled. Further, the seal member 21g is mounted on the outer side of the valve sleeve 21, and the filter member 40 whose description is omitted is mounted.

On the other hand, the plunger 23 and the stopper 27
1 is attached to the tubular member 27, and these are further attached to the yoke 24.
Is inserted inside the flange member 24a. Next, the flange member 24a of the yoke 24 to which the above-mentioned tubular member 27 and the like are attached from the front and rear of the mold coil 25 and the case member 2
4b, and the flange portion 27f of the tubular member 27 is sandwiched between the flange 21f of the valve sleeve 21 and the flange 24f of the flange member 24a of the yoke 24. In this state, the outer periphery of the case member 24b of the yoke 24 is The flange 21f of the valve sleeve 21 is crimped and integrally assembled. The valve sleeve 21 of the proportional solenoid valve 20 in this assembled state is inserted into the valve accommodating hole 31 of the valve body 30, and the bracket 24g fixed to the case member 24b of the yoke 24 by welding or the like is attached to the valve body by a bolt or the like (not shown). Fix to 30 and finish the assembly work.

Next, the operation of the embodiment will be described. B) When the coil 25c is not energized when it is off, the valve spool 22 is moved to the right in FIG. 2 by the urging force of the return spring 28, and the armature part 23b of the plunger 23 strikes the bottom part 27b of the tubular member 27. This movement is restricted by the position. At this time, the position of the valve spool 22 is the OFF position described above, and this OF
At the F o'clock position, as described above, the hydraulic pressure supply port 21e
And the retard side hydraulic pressure supply port 21b are communicated with each other to supply hydraulic oil to the retard angle hydraulic chamber, while the advance side hydraulic pressure supply port 21a and the advance side hydraulic pressure discharge port 21c are communicated with each other.
The hydraulic oil in the advance hydraulic chamber outside the drawing is the advance side hydraulic discharge port 2
It is discharged via 1c. This allows the camshaft 2
Is arranged at the most retarded position.

(B) When the coil 25c is energized when it is ON, the duty is output to the coil 25c to adjust the generated suction force.
When the generated suction force exceeds the urging force of the return spring 28, the plunger 23 slides leftward in the figure. The movement of the plunger 23 is restricted by the end face of the armature portion 23b of the plunger 23 abutting the end face of the stopper 271. At this time, the valve spool 22 is in the ON position shown in FIG. 4, and in this ON position, the retard hydraulic chamber (not shown) is located in the retard hydraulic supply port 21 as described above.
The hydraulic oil in the retard hydraulic chamber is discharged by communicating with the retard hydraulic discharge port 21d via b, while the hydraulic oil in the retard hydraulic chamber (not shown) is operated via the advance hydraulic supply port 21a. Oil is supplied, and the camshaft 2 rotates to the advance side.

C) Neutral position After the camshaft 2 has been rotated by the desired amount from the most retarded position as described above, the position of the camshaft 2 is maintained at the desired position. In this case, the attraction force (duty ratio) generated by energizing the coil 25c is adjusted to balance with the urging force of the return spring 28 and the plunger 23
It also holds the valve spool 22 in the neutral position shown in FIG. As a result, as described above, the hydraulic oil is confined in both the advance hydraulic chamber and the retard hydraulic chamber (not shown), and the position of the camshaft 2 is maintained.

Next, the effect of the embodiment will be described. In performing the above-described operation, in the proportional solenoid valve 20 according to the present embodiment, the plunger 23 and the yoke 24 are completely separated by the tubular member 27 made of a non-magnetic material, so that the relative positions of the two. Even if the accuracy is not increased, it is possible to avoid the problem that the two are caught and do not stroke. For example, when the axes of the plunger 23 and the yoke 24 are deviated from each other, in the related art, the edge 24t of the flange member 24a of the yoke 24 and the outer periphery of the armature portion 23b of the plunger 23 are caught and actuated. Although there is a possibility that a defect may occur, this can be reliably avoided in the present embodiment. Moreover, even if the plunger 23 slides and the tubular member 27 wears, the plunger 23 does not contact the yoke 24, and the avoidance of the above-mentioned catching can be maintained. In order to avoid such a malfunction, in the present embodiment, the outer circumference of the plunger 23 is supported by the tubular member 27 made of stainless steel that can be manufactured at low cost, and thus the expensive cost that was conventionally required. There is an effect that it can be achieved by an inexpensive means without using various ball bearings or setting of high positional accuracy.

Further, in this embodiment, the armature portion 23b of the plunger 23 is formed to have a constant outer diameter dimension, while the tubular portion 27a of the tubular member 27 is formed to have a constant inner diameter dimension. The outer circumference of 23b and the inner circumference of the tubular portion 27a are slidably contacted with each other so that the slidable contact state between the two is always maintained even when the plunger 23 slides, so that it is difficult for contamination to enter between the two. It is possible to prevent the problem that the slidability of the plunger 23 deteriorates due to the invasion of the contaminants, and the operating performance can be improved.

Further, in the present embodiment, the cylindrical member 27 is used as a stopper for restricting the position for disposing the valve spool 22 at the ON position and the OFF position.
The stopper 271 and the bottom portion 27b provided inside the are used. For this reason, conventionally, for example, it is provided so as to regulate the sliding of the valve spool 22 at the back of the valve housing hole 31, the opening end portion, or the like, but the assembling workability is superior to that. Further, the stopper 271 is arranged such that if the position of one end of the stopper 271 coincides with the position of the tubular portion 27a of the tubular member 27, the other end is placed at a position that restricts the movement of the plunger 23 at the ON position. Also excellent in workability in assembly. In addition, since the stopper 271 is formed of a non-magnetic material, the plunger 23 does not stick when the movement of the plunger 23 is restricted. Furthermore, when a magnetic material is used as the material of the stopper 271 provided at this position, when the coil 25c is energized, a part of the magnetic flux around the yoke 24 passes through this stopper 271 and the attractive force increases. As a result, the operating efficiency can be improved. In this case, in order to prevent the stopper 271 from sticking the plunger 23 when the movement of the plunger 23 is restricted, the side of the stopper 271 close to the plunger 23 is made of a non-magnetic material, and the opposite side is made of a magnetic material. To form. The length of the non-magnetic material portion is set so that the attraction force generated in the magnetic material portion does not act on the plunger 23.

The cylindrical member 2 serving as the other stopper
Since the bottom part 27b of 7 is formed in a curved shape, the armature part 23b of the plunger 23 comes into line contact with the bottom part, and when the plunger 23 is restarted after being stopped for a long time, the armature part 23b. 23b does not stick to the bottom portion 27b, the plunger 23 can be easily moved, and the operability is excellent. The bottom 27
The shape of b is not limited to the curved shape shown in the figure, and similar effects can be obtained with other shapes such as a conical shape.
The same effect can be obtained even if the bottom portion 27b has a planar shape and a plurality of protrusions are provided thereon.

Further, in the present embodiment, leakage of hydraulic oil from the inner peripheral side of the valve sleeve 21 to the outside is caused between the flange portion 27f of the tubular member 27 and the flange 21f of the valve sleeve 21. It is regulated by the seal member 29 provided. That is, the hydraulic oil that has flowed into the tubular member 27 is blocked by the bottom portion 27b of the tubular member 27, and a seal member is not necessary to prevent leakage from the inside of the tubular member 27. There is. Therefore, it is possible to reduce the number of necessary seal members and prevent the leakage of hydraulic oil at a low cost as compared with the related art. Further, in adopting this structure, the tubular member 27 is provided with the flange portion 27f, and the flange portion 27f is caulked and fixed between the yoke 24 and the valve sleeve 21 as the yoke fixing member. Therefore, the tubular member 27 is simultaneously fixed at a desired position only by performing the conventional work of fixing the yoke. Therefore, the workability of assembling is excellent.

The embodiment of the present invention has been described in detail above with reference to the drawings. However, the specific configuration is not limited to this embodiment, and design changes and the like within the scope not departing from the gist of the present invention. Even if it exists, it is included in the present invention. For example, in the embodiment, the example in which the proportional solenoid valve is applied to the valve timing adjusting device has been shown, but the proportional solenoid valve of the present invention can also be applied to other vehicle-mounted equipment and other industrial equipment.

In the embodiment, the bottomed cylindrical member 27 is shown. However, even if the cylindrical member 27 is formed to have no bottom, the plunger 23 and the yoke 24 are prevented from being caught. The effect of can be obtained. Further, in the embodiment, the example in which the stopper 271 and the bottom portion 27b are provided as the stopper inside the tubular member 27 is shown, but the initial effect can be obtained without providing these stoppers. Further, in the embodiment, the flange portion 27f is provided on the tubular member 27 to improve the assembling workability and ensure the sealing performance at low cost. The flange portion 27f is not essential to obtain the effect.

[Brief description of drawings]

FIG. 1 is a sectional view showing a valve timing adjusting device to which a proportional solenoid valve according to an embodiment of the present invention is applied.

FIG. 2 is a cross-sectional view showing an off state of the proportional solenoid valve according to the embodiment.

FIG. 3 is a cross-sectional view showing a neutral state of the proportional solenoid valve according to the embodiment.

FIG. 4 is a cross-sectional view showing when the proportional solenoid valve according to the embodiment is turned on.

FIG. 5 is an exploded perspective view illustrating a procedure for assembling the proportional solenoid valve according to the embodiment.

[Explanation of symbols]

1 sprocket 2 camshaft 3 bolts 4 shoe housing 5 Front plate 6 vane members 7 volts 20 proportional solenoid valve 21 Valve sleeve 21e Hydraulic supply port 21a Advance side hydraulic pressure supply port 21b Retardation side hydraulic pressure supply port 21c Advance side hydraulic discharge port 21d Retardation side hydraulic discharge port 21f flange 21g seal member 21h step 22 valve spool 22f flange 221 First Land 222 Second Land 223 Third Land 23 Plunger 23a Shaft 23b Amateur club 23c groove 24 York 24a Flange member 24b case member 24c case 24f flange 24g bracket 24t edge 25 Mold coil 25b bobbin 25c coil 25d connector 25t terminal 27 Cylindrical member 27a barrel 27b bottom 27f Flange part 271 stopper 28 Return spring 29 Seal member 30 valve body 31 Valve accommodation hole 32 Advance side hydraulic circuit 33 Delay angle hydraulic circuit 34, 35 hydraulic discharge circuit 36 Hydraulic supply circuit 40 Filter member

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 3H106 DA02 DA23 DB02 DB12 DB23                       DB32 DC09 DC20 DD09 EE04                       EE07 GA11 GA15 GA23 GC04                       KK02 KK17                 5E048 AB02 AC08 AD03

Claims (7)

[Claims] 1. An electromagnetic wave generated by energizing a plunger (23), which is formed of a magnetic material and drives a valve by moving, and a coil (25c) which has a hollow portion inside and is wound outside. A yoke (24) made of a magnetic material that exerts a suction force on the plunger (23), and is arranged in the hollow portion of the yoke (24) and holds the plunger (23) axially slidably in the inner circumference. And a cylindrical member (27) made of a non-magnetic material, the proportional solenoid valve. 2. The proportional solenoid valve according to claim 1, wherein the outer circumference of the plunger and the inner circumference of the tubular member are formed to have constant diameters and are in sliding contact with each other. . 3. The proportional solenoid valve according to claim 1 or 2, wherein the tubular member is provided with a stopper that restricts sliding of the plunger at a predetermined position. 4. The proportional solenoid valve according to claim 3, wherein the stopper is made of a non-magnetic material. 5. The proportional solenoid valve according to any one of claims 1 to 4, wherein the tubular member is formed in a shape such that one end thereof has a bottomed tubular shape and is capable of accommodating a plunger. A flange portion is integrally formed on the outer circumference of the other end portion, and the flange portion is held by fixing the yoke to the yoke fixing portion while being sandwiched between the yoke and the yoke fixing portion. Proportional solenoid valve. 6. The proportional solenoid valve according to claim 5, wherein a seal member is provided between the flange portion and the yoke fixing portion. 7. The proportional solenoid valve according to claim 5, wherein the bottom portion of the tubular member also functions as a stopper that restricts sliding of the plunger, and is formed in an inclined cross-sectional shape that does not make surface contact with the plunger. Proportional solenoid valve characterized by being.