JP6187316B2 - solenoid valve - Google Patents

Description

  The present invention relates to an electromagnetic valve for controlling the pressure of a fluid, and more particularly to a linear solenoid type electromagnetic valve suitable for hydraulic control of an automatic transmission for an automobile.

[Conventional technology]
Conventionally, linear solenoid type solenoid valves having various configurations have been put to practical use. As a typical example, for example, a linear solenoid type solenoid valve described in Patent Document 1 is known.

  This solenoid valve includes, as a basic configuration, a sleeve having an inlet port, an outlet port, and a discharge port, and a spool (valve element) that is driven by a linear solenoid and slides in the sleeve in the axial direction. Electromagnetic force by the solenoid (hereinafter also referred to as electromagnetic attractive force) and urging force (hereinafter also referred to as a mounting load) by urging means (such as a spring, which is an elastic body such as a spring, hereinafter collectively referred to as a spring). A structure is employed in which the pressure of the target fluid to be controlled is adjusted by balancing these acting forces. Thereby, the supply pressure of the fluid supplied to the inlet port is adjusted to an output pressure corresponding to the electric signal input to the electromagnet part (linear solenoid) when the fluid flows out from the outlet port.

Then, the adjustment of the amount of movement of the spool relative to the supply pressure is performed by moving an adjustment member, which is engaged with one end of the spring that biases the spool in the direction opposite to the direction in which the electromagnetic force is applied by the linear solenoid, in the axial direction. This is done by adjusting the spring load. Specifically, a screw adjustment mechanism is used.
The screw adjusting mechanism is provided with a female screw portion on the inner periphery on one end side of the sleeve, and a male screw portion on the outer periphery of a screw adjust (hereinafter simply referred to as a stopper) that forms an adjusting member. In addition to screwing together, one end of the spring is locked to one end of the receptacle, and the spring load can be adjusted by moving the receptacle in the axial direction while rotating the receptacle itself.

  Further, it is necessary to fix the receptacle to the sleeve so as to determine the position of the receptacle so that the adjustment position does not fluctuate after adjusting the mounting load of the spring. As the fixing means, (A) a structure in which the stopper is fixed to the sleeve using a fitting pin that engages the stopper and the sleeve, or (B) a sleeve surrounding the stopper is partially A structure is adopted in which the stopper is fixed to the sleeve by caulking (deforming).

  Both the above-mentioned fixing means have advantages and disadvantages. The former fixing means (A) has a spring mounting load because the engagement position between the stopper and the sleeve, that is, the fitting pin position is limited to a plurality of positions. The latter fixing means (B) is exclusively used because it has problems such as that it cannot be adjusted steplessly or the number of parts is increased by using the fitting pin.

  By the way, in a device that plays a central role in vehicle control, such as an automatic transmission for automobiles, there is a demand for further miniaturization and higher performance year by year including its components. Therefore, on the component side, in particular, miniaturization and high performance of the solenoid valve that constitutes the main part are urgently needed, and how to improve them is a common proposition for those skilled in the art.

[Problems of the prior art]
The present inventor has conducted numerous experiments and research aiming at further improvement of the miniaturization and high performance of the solenoid valve, but this time the stopper is used in the fixing means (B) that has been used award. After scrutinizing the fixed state, the following problems were identified.

(1) According to the fixing means (B), more specifically, a two-sided width portion is formed on the outer periphery of the sleeve, and the screw portion is plastically deformed by caulking the two-sided width portion from above and below. Since the stopper and the sleeve are fixed (collapsed), it is considered that the stopper and the sleeve are firmly fixed, and the stopper is accurately fixed at a predetermined position.
However, since there is a clearance such as backlash between the male screw part and the female screw part, it is known that the receiving plug moves in the axial direction by this clearance during caulking, resulting in a difference in the spring load. It was.

(2) However, in addition to the above-mentioned axial movement phenomenon, there was an unexpected phenomenon in which the stopper was inclined. As a result, the spring that is locked to the stopper is inclined, and the lateral force as the spring is increased. As a result, the slidability of the spool deteriorates, and the control accuracy may vary (variation). did.

(3) Then, when the cause of the inclination of the above-mentioned stopper is investigated, if the caulking deformation state of each of the male screw portion and the female screw portion is examined closely, for example, in the portion located on the upper side, it is plastically deformed at the crest portion of the screw. (Crushing), an abnormal deformation phenomenon that is plastic deformation (crushing) at the valley of the screw at the lower part, and as a result, the axis of the receptacle is tilted, and abnormal It has been found that the deformation phenomenon is largely caused by the fact that the caulking position is at the same axial position in the vertical direction.

JP-A-2-129484

  The present invention has been made in view of the above circumstances, and an object of the present invention is to make maximum use of an adjustment function capable of stepless adjustment of a mounting load (biasing force) of a spring (biasing means). An object of the present invention is to provide an electromagnetic valve capable of improving control accuracy by accurately fixing a stopper (adjusting member) at a predetermined position.

[Means of Claim 1]
The invention according to claim 1 (solenoid valve) restricts the amount of movement of the spool by a balance action of a spool driven by electromagnetic force, a sleeve for reciprocating the spool in the axial direction, and electromagnetic force. And a receiving member (adjusting member) that is movable in the axial direction through the screw adjusting mechanism and adjusts the mounting load of the spring. The screw adjusting mechanism is a female member of the sleeve. The basic configuration is that it is composed of a screw portion and a male screw portion of the receptacle.

The solenoid valve according to the present invention is a fixing means for fixing the stopper to the sleeve after adjusting the mounting load of the spring by moving the stopper in the axial direction, at a position shifted by a half pitch in the axial direction. In addition, a fixing means for determining the position of the stopper is provided by deforming from the opposing position across the axial line in the axial direction toward the radially inner side .

According to the above configuration, since the screw adjustment mechanism is composed of the female screw portion of the sleeve and the male screw portion of the receptacle, the screw adjustment mechanism is used in the axial direction by skillfully utilizing the characteristics (screw pitch) peculiar to the screw. Therefore, the screw threads of the screw adjusting mechanism can be reliably crushed at the facing position, and the receiving plug can be positioned and fixed to the sleeve.
Therefore, since the stopper is not inclined and the inclination of the spring is not caused, good slidability of the spool can be ensured and the control accuracy of the solenoid valve can be improved.

  In addition, the fixing means for fixing the stopper to the sleeve is based on the basic structure of deforming the screw adjustment mechanism at the opposite position in the axial direction, and the spring mounting load, which is the original characteristic of the screw adjustment mechanism, is stepless. Therefore, it is possible to further contribute to the provision of a solenoid valve with excellent control accuracy.

It is a longitudinal cross-sectional view of the solenoid valve for hydraulic control which shows the example of application of the solenoid valve of this invention (Example 1). FIG. 2 is a front view of the hydraulic control solenoid valve, as viewed from the direction of arrow A in FIG. 1 (Example 1). It is a schematic block diagram of the hydraulic system to which the solenoid valve for hydraulic control is applied. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic cross-sectional view of a main part showing a fixing process of a plug (screw adjust), which is used for explaining a first embodiment of a screw adjusting mechanism in a solenoid valve of the present invention. Example 1). For comparison with the present invention, (a) and (b) are schematic cross-sectional views of a portion corresponding to FIG. 4 in the adjusting screw mechanism (reference example).

  Hereinafter, the best mode for carrying out the present invention will be described in detail according to embodiments shown in the drawings.

[Example 1]
In this embodiment, a hydraulic control electromagnetic valve applied to a hydraulic system for an automatic transmission for automobiles is shown, and the positioning of the electromagnetic valve in the automatic transmission will be outlined with reference to FIG.

As shown in FIG. 3, the hydraulic system 100 in the automatic transmission includes an oil pump 101, a manual valve 102, a hydraulic control electromagnetic valve 103, a clutch mechanism 104, a hydraulic pipe 105, and the like. The oil pump 101 supplies hydraulic oil from the discharge port to the manual valve 102 via the hydraulic pipe 105. The manual valve 102 selects a P (parking), R (reverse), N (neutral), or D (drive) mode by operating a select lever (not shown).
The hydraulic control solenoid valve 103 opens or closes the oil supply passage for oil to the clutch mechanism 104 when the D mode is selected, and adjusts the oil supply pressure. The electromagnetic valve 103 includes a linear solenoid 2 as an actuator for driving the spool valve 1, and is installed so that the axis is horizontal in an oil tank (oil pan) of the engine.

[Basic configuration of solenoid valve 103 for hydraulic control]
Next, a specific structure of the hydraulic control electromagnetic valve (hereinafter abbreviated as electromagnetic valve) 103 will be described in sequence with reference to FIG. In FIG. 1, the upper and lower parts of the figure correspond to the sky direction and the earth direction at the time of installation.
First, the electromagnetic valve 103 includes the spool valve 1 and the linear solenoid 2 that drives the spool valve 1 as described above.

  The spool valve 1 includes a sleeve 3, a spool 4, a spring 5, and a receptacle 10 as a basic configuration.

  The sleeve 3 constitutes a substantially cylindrical valve housing, and is formed of a nonmagnetic metal material such as an aluminum alloy. The sleeve 3 has an insertion hole 6 that penetrates in the axial direction, and a plurality of oil ports 7 that penetrate the outer wall of the sleeve 3 from the hole 6 along the insertion hole 6. The plurality of oil ports 7 include an exhaust port 7 c and a breathing port 7 d in addition to an inlet port 7 a communicating with the manual valve 102 and an outlet port 7 b communicating with the clutch mechanism 104.

  The spool 4 constitutes a valve body that cooperates with the valve housing, and is slidably received in the insertion hole 6 of the sleeve 3. The spool 4 has a land 8 (8a, 8b, 8c) that fits into the insertion hole 6 with high accuracy and defines a plurality of oil ports 7, and a small-diameter portion 9 positioned between the land 8b and the land 8c. Is provided. The spool 4 changes the opening area of the oil port 7 depending on the relative position with the sleeve 3. Further, the spool 4 switches between the communication state and the shut-off state of the oil port 7 according to the relative position with the sleeve 3.

  The spring 5 constitutes an urging means for urging the spool 4 toward the linear solenoid 2, and is represented by a compression coil spring. One end of the spring 5 is in contact with the end surface of the spool 4 opposite to the linear solenoid 2, and the other end is in contact with the receptacle 10.

The receptacle 10 is an adjustment member that is also referred to as a screw adjuster, and is attached to the end of the sleeve 3 via a screw adjustment mechanism 11. By changing the screwing amount of the screw adjusting mechanism 11, the axial position of the stopper 10 with respect to the sleeve 3 can be changed, and the urging force (mounting load) of the spring 5 can be adjusted steplessly. In addition, after such adjustment, the receptacle 10 is fixed so that it cannot move in the axial direction with respect to the sleeve 3 by the fixing means 12 applied to the screw adjustment mechanism 11.
Details of the screw adjusting mechanism 11 and the fixing means 12 will be described later.

  Next, the structure of the linear solenoid 2 will be described. As a basic configuration, the linear solenoid 2 includes a solenoid coil 13, a stator core 14, a plunger 15, a shaft 16, a yoke 17, a connector 18, a ring core 19, and an axial biasing member 20.

  When energized, the solenoid coil 13 generates a magnetic force to form a magnetic circuit that passes through the stator core 14, the yoke 17, and the plunger 15. The solenoid coil 13 is configured by winding an insulating coating wire around a resin bobbin 13a.

  The stator core 14 is made of a magnetic metal material such as iron. The stator core 14 includes a magnetic attraction core 14a, a magnetic blocking portion 14b, and a guide core 14c that are integrally formed in the axial direction, and has a substantially cylindrical shape as a whole.

  The plunger 15 is formed in a substantially cylindrical shape with a magnetic metal material such as iron. The plunger 15 can reciprocate in the axial direction on the inner peripheral surface of the guide core 14c, and has a breathing hole 15a penetrating in the axial direction.

  The shaft 16 is slidably supported by the magnetic attraction core 14 a and is interposed between the spool 4 and the plunger 15. The spring 5 biases the spool 4 toward the shaft 16, so that one end of the shaft 16 abuts on the end surface of the spool 4 and the other end of the shaft 16 abuts on the end surface of the plunger 15.

  The yoke 17 is made of a magnetic metal material such as iron, and has a substantially cup shape including a cylindrical portion 17a and a bottom portion 17b. The cylindrical portion 17 a accommodates the solenoid coil 13, the stator core 14, and the ring core 19. The cylindrical portion 17a is fixed to the sleeve 3 by crimping the opening end side of the sleeve 3 to the sleeve 3, and the stator core 14 (magnetic suction core 14a side) and the yoke 7 are magnetically connected to each other. Are connected.

  The connector 18 is a connection means for making an electrical connection via a connection line with an electronic control device (not shown) that controls the electromagnetic valve 103. Inside the connector 18, terminals 18 a connected to both ends of the coil 13 are provided. The connector 18 is provided on the ground side of the cylindrical portion 17 a of the yoke 17.

The ring core 19 is formed in a ring shape from a magnetic metal material such as iron, and assists magnetic coupling between the stator core 14 and the yoke 17. The ring core 19 is pressed against the bottom 17b of the yoke 17 by the biasing force of the axial biasing member 20 interposed between the bobbin 13a of the solenoid coil 13. The axial urging member 20 is made of an elastic body such as rubber, a disc spring, or a wave washer.
The guide core 14c of the stator core 14 is fitted to the ring core 19, and the magnetic flux is transferred between the guide core 14c and the ring core 19. The end surface of the ring core 19 abuts on the bottom 17a of the yoke 17, and the magnetic flux is transferred between the ring core 19 and the yoke 17. As a result, the guide core 14 c and the yoke 17 are magnetically coupled via the ring core 19.

[Basic operation of solenoid valve 103]
Next, the basic operation of the electromagnetic valve 103 having the above configuration will be described.
When the solenoid coil 13 is not energized, no electromagnetic attractive force (electromagnetic force) is generated in the magnetic attractive core 14a of the stator core 14. Accordingly, the spool 4, the shaft 16, and the plunger 15 are pressed to the right in FIG. 1 by the urging force of the spring 5. The end surface of the plunger 15 is in contact with the bottom 17 b of the yoke 17.
In this state, the oil flowing in from the inlet port 7a flows out to the discharge port 7c through the gap between the land 8b and the land 8c. Therefore, the clutch mechanism 104 is not driven.

When the solenoid coil 13 is energized, an electromagnetic attracting force is generated in the magnetic attracting core 14a of the stator core 14, and the plunger 15 is attracted. Then, the plunger 15 drives the spool 4 in the left direction in FIG. At this time, as the plunger 15 moves, oil on the shaft 16 side of the plunger 15 flows out to the rear side of the plunger 15 through the breathing hole 15a, so that pressure fluctuations on both sides of the plunger 15 are prevented.
In this state, since the land 8c blocks the discharge port 7c, the oil flowing in from the inlet port 7a flows out from the gap between the land 8b and the land 8c to the outlet port 7b, and drives the clutch mechanism 104. Further, part of the oil flowing out from the outlet port 7b is returned to the breathing port 7d.
The non-energized (off) state and the energized (on) state are repeated by duty control of the electronic control unit.

[Load adjustment of spring 5]
Thus, a suction force by the linear solenoid 2 and an urging force (attachment load) by the spring 5 act on the spool 4 that slides in the sleeve 3 in the axial direction. Thereby, the supply pressure of the oil supplied to the inlet port 7a is adjusted to an output pressure corresponding to the input electric signal to the linear solenoid 2 when the oil flows out from the outlet port 7b. Adjustment of the moving amount of the spool 4 with respect to the supply pressure is performed by adjusting the mounting load of the spring 5 by the screw adjusting mechanism 11.

  Here, a configuration for adjusting the mounting load of the spring 5 by the above-described screw adjusting mechanism 11 will be described in detail with reference to FIGS. 1 and 2.

The sleeve 3 has a spring chamber 31 that houses the spring 5 inside the linear solenoid 2. The spring chamber 31 communicates in the axial direction with the insertion hole 6 that accommodates the spool 4 on one end side, and one end of the spring 5 is in contact with the end surface of the spool 4.
The sleeve 3 has a small-diameter cylindrical portion 32 at the end opposite to the linear solenoid 2. The small-diameter cylindrical portion 32 is formed in a two-surface width portion 32a in which a part of the outer peripheral surface faces vertically, and has an internal thread portion 32b on the inner peripheral surface.

  The receptacle 10 is a solid body and is attached to the small diameter cylindrical portion 32 of the sleeve 3 to close the other end side of the spring chamber 31. The receptacle 10 has a cross groove 10a for rotating the receptacle 10 itself on the outer end surface, and a male screw portion 10b on the outer peripheral surface. The other end of the spring 5 is in contact with the inner end face of the receptacle 10.

  The screw adjusting mechanism 11 is constituted by a female screw portion 32 b of the sleeve 3 and a male screw portion 10 b of the receptacle 10. Via this screw adjusting mechanism 11, the stopper 10 and the end portion (small-diameter cylindrical portion 32) of the sleeve 3 are in a threaded state, and the stopper 10 can move in the sleeve 3 in the axial direction while rotating. it can.

  Therefore, in order to adjust the mounting load of the spring 5, a tool such as a Phillips screwdriver is fitted in the cross groove 10 a of the receptacle 10 and the receptacle 10 is rotated so that the position of the receptacle 10 with respect to the sleeve 3 is pivoted. It is possible to adjust the urging force (mounting load) of the spring 5 by moving in the direction and increasing or decreasing the compression length of the spring 5.

  Thus, after the attachment load of the spring 5 is adjusted to a predetermined value, it is necessary to fix (rotate) the stopper 10 so as not to move with respect to the sleeve 3, and the fixing means 12 for preventing the rotation is screwed. The adjustment mechanism 11 is applied. Specifically, in the small-diameter cylindrical portion 32 of the sleeve 3, the screw adjusting mechanism 11 (the female screw portion 32b and the male screw portion 10b) is plastically deformed (collapsed) by caulking the two-surface width portion 32a from above and below. Thus, the stopper 10 is prevented from moving (rotating) with respect to the sleeve 3.

[Features of Example 1]
In particular, the gist of the present invention resides in the fixing means 12 applied to the screw adjusting mechanism 11, and a specific example thereof will be described in detail with reference to FIGS. 4 and 5.

First, a reference example to which the present invention is not applied will be described with reference to FIG.
FIG. 5A shows a screwed state of the screw adjusting mechanism 11 immediately after adjusting the mounting load of the spring 5 to a predetermined value.
The fixing means 12 is applied to the screw adjusting mechanism 11 in such a state. Specifically, in the small-diameter cylindrical portion 32 of the sleeve 3, the two-surface width portion 32a is indicated by an arrow by a pair of caulking punches X (X1, X2). Crush from above and below.
Then, for example, the upper caulking punch X1 presses and deforms the peak portion (thick portion) of the female screw portion 32b, and the lower caulking punch X2 presses and deforms the valley portion (thin portion) of the female screw portion 32b. become.
As a result, as shown in FIG. 5B, there is a clearance S between the female screw portion 32b and the male screw portion 10b. When a balanced pressing load is applied and the male screw portion 10b receives a bending moment as indicated by an arrow Y, an event occurs in which the central axis O of the stopper 10 is inclined with respect to the reference line (the central axis of the sleeve 3) Z. As a result of the inclination of the stopper 10, the spring 5 in contact with the end face of the stopper 10 is also inclined. As a result, the lateral force as the spring 5 is increased and the slidability of the spool 4 is deteriorated. .

On the other hand, the fixing means 12 of the present invention according to the first embodiment has been created to solve the above problem, and will be described with reference to FIG.
FIG. 4A shows a screwed state of the screw adjusting mechanism 11 immediately after adjusting the mounting load of the spring 5 to a predetermined value. In the present invention, a pair of upper and lower caulking punches X (X1, X2) are used. Although it is caulking, it is characterized in that the axial position to be caulking is devised.
That is, since the screw adjustment mechanism 11 is a combination of the female screw portion 32b and the male screw portion 10b, paying attention to the screw pitch (interval between peaks or valleys) P, the upper caulking punch X1 and the lower caulking punch X2 Is shifted by a half pitch (P / 2).
Accordingly, the fixing means 12 can be constructed by pressing and deforming the crest portions (thick portions) of the female screw portion 32b together with the upper caulking punch X1 and the lower caulking punch X2.
As a result, as shown in FIG. 4B, a pressing load is evenly applied to the male screw portion 10 b of the receptacle 10, and the central axis O of the receptacle 10 can be held on the reference line Z.
Thus, the fixing means 12 can be provided by plastically deforming (crushing) the screw adjusting mechanism 11 without tilting the receiving plug 10, and the fixing means 12 fixes the receiving position of the receiving plug 10 with respect to the sleeve 3 to a predetermined position. It can be defined uniquely.

[Effect of Example 1]
According to the fixing means 12 of the present invention according to the first embodiment, the following operational effects can be obtained.

(1) By deforming the screw adjusting mechanism 11 in the radial direction from a position that is shifted by a half pitch (P / 2) in the axial direction and sandwiching the axial line in the axial direction , the stopper 10 is moved. Since it is fixed to the sleeve 3, the stopper 10 can be positioned and fixed to the sleeve 3 by reliably crushing the threads of the screw adjusting mechanism 11.
Therefore, the shaft center of the stopper 10 is not inclined, and the inclination of the spring 5 is not caused. Therefore, good slidability of the spool 4 can be ensured and the control accuracy of the electromagnetic valve 103 can be reliably improved.
In addition, as shown in FIG.4 (b), the accompanying effect which can equalize the clearance S by equalization of a pressing load can also be anticipated.

(2) The screw adjustment mechanism 11 is effectively used as it is, which is composed of the female screw portion 32b of the sleeve 3 and the male screw portion 10b of the receptacle 10. P / 2) Because it is only shifted, it does not require any special processing or parts to prevent the shaft center of the stopper 10 from tilting, and contributes to miniaturization of the solenoid valve 103 and reduction of manufacturing costs. is there.

(3) The basic configuration for fixing the stopper 10 to the sleeve 3 is to deform the screw adjusting mechanism 11 at the axially opposed position, and there is no mounting load of the spring 5 which is an inherent characteristic of the screw adjusting mechanism 11. Since no adjustment function that can be adjusted in stages is lost, it is possible to further contribute to the improvement of the control accuracy of the solenoid valve 103.

(4) The sleeve 3 is provided with a small-diameter cylindrical portion 32 to construct the screw adjustment mechanism 11 here, and the small-diameter cylindrical portion 32 is provided with a two-surface width portion 32a, where the deformation position of the screw adjustment mechanism 11 is defined. It is set. Therefore, since the deformation position is a flat surface, an accurate shift setting of half pitch (P / 2) can be easily performed, and since the deformation position is thin in addition to the flat surface, a pair of caulking punches X (X1, X2) Thus, a stable pressing deformation effect can be obtained.

[Other Embodiments; Modifications]
Although one embodiment of the present invention has been described in detail, various modifications can be made without departing from the spirit of the present invention, and the modification is illustrated as another embodiment.

(1) In the first embodiment, the deformation position of the screw adjustment mechanism 11 is set so as to crush the crest portions of the female screw portion 32 b of the sleeve 3. Of course, the position may be crushed. That is, in order to prevent the axis of the receptacle 10 from being inclined, it is important to apply a pressing load evenly to the male screw portion 10b, and the female screw portion 32b of the sleeve 3 or the male screw portion 10 of the receptacle 10 is important. This is to plastically deform (crush) the screw threads or screw valleys of the screw portion 10b.

(2) Further, in the first embodiment, the sleeve 3 is provided with the small-diameter cylindrical portion 32 having the two-surface width portion 32a, and the screw adjusting mechanism 11 is constructed here, and the deformation position of the screw adjusting mechanism 11 is set. However, the end portion of the sleeve 3 is left as the large-diameter cylindrical portion without providing the small-diameter cylindrical portion 32 having the two-surface width portion 32a, and the screw adjusting mechanism 11 is constructed here, and the screw adjusting mechanism 11 Of course, it is possible to set the deformation position.
(3) Further, in the first embodiment, a compression coil spring that can easily ensure a long stroke is illustrated as the spring 5, but other elastic bodies such as rubber and a disc spring are used as the biasing means collectively referred to as the spring. Can also be used.

(4) In the above-described embodiment, as an application example of the electromagnetic valve of the present invention, the hydraulic control electromagnetic valve 103 in the hydraulic system 100 of the automobile automatic transmission is illustrated. In addition to this, the electromagnetic valve of the present invention can be useful as an electromagnetic valve in various flow rate control devices, for example, applied to an electromagnetic valve accommodated in an engine head cover as a hydraulic valve for adjusting valve timing.

  The features and advantages of the present invention that have been described in detail above will be summarized as follows according to each means described as a dependent claim (excluding dependent claim 6) in the claims.

(Feature 1 = Means of claim 2)
The electromagnetic valve 103 according to claim 1,
The fixing means 12 is characterized in that the stopper (adjusting member) 10 is positioned and fixed by crushing the thread of the female screw portion 32b or the male screw portion 10b constituting the screw adjusting mechanism 11 (Example 1 and Modification example (1)).
According to the above means, the female screw portion 32b or the male screw portion 10b, which is a component of the screw adjusting mechanism 11, can be effectively used as it is, and the receiving plug 10 can be accurately fixed to a predetermined position of the sleeve 3.

(Feature point 2 = Means of claim 3)
In the solenoid valve 103 according to claim 1 or 2,
The sleeve 3 includes a small-diameter cylindrical portion 32 having a two-surface width portion 32a, the screw adjusting mechanism 11 is constructed in the small-diameter cylindrical portion 32, and the fixing means 12 is provided in the two-surface width portion 32a ( See Example 1).
According to the above means, since the deformation position of the screw adjustment mechanism 11 is a flat surface, an accurate shift setting of half pitch (P / 2) can be easily performed, and the deformation position is thin in addition to the flat surface. A stable press deformation effect can be obtained by the pair of caulking punches X (X1, X2).

(Feature point 3 = Means of claim 4)
In the solenoid valve 103 according to any one of claims 1 to 3,
The spring 5 constituting the urging means is constituted by a compression coil spring (see Example 1).
According to the above means, the compression coil spring can easily ensure a long stroke, and the attachment load can be easily adjusted.

(Feature point 4 = Means of claim 5)
In the solenoid valve 103 according to any one of claims 1 to 4,
The electromagnetic valve 103 is used as the hydraulic control electromagnetic valve 103 in the hydraulic system 100 of the automatic transmission for an automobile (see Example 1).
According to the above-described means, it is possible to contribute to further miniaturization and higher performance in an automatic transmission for automobiles, which are required to be smaller and higher in performance.

DESCRIPTION OF SYMBOLS 1 ... Spool valve, 2 ... Linear solenoid, 3 ... Sleeve, 4 ... Spool, 5 ... Spring (biasing means), 10 ... Receptacle (adjustment member), 10b ... Male screw part (a part of screw adjustment mechanism), DESCRIPTION OF SYMBOLS 11 ... Screw adjustment mechanism, 12 ... Fixing means, 32b ... Female screw part (a part of screw adjustment mechanism), 103 ... Solenoid valve.

Claims (5)

A spool (4) driven by electromagnetic force, a sleeve (3) that accommodates the spool (4) so as to be reciprocally movable in the axial direction, and the amount of movement of the spool (4) by the balance action of the electromagnetic force. An urging means (5) for limiting and an adjusting member (10) that is movable in the axial direction in the sleeve (3) via a screw adjusting mechanism (11) and adjusts the urging force of the urging means (5). ) And
The screw adjustment mechanism (11) is an electromagnetic valve (103) composed of a female screw part (32b) of the sleeve (3) and a male screw part (10b) of the adjustment member (10),
After adjusting the biasing force of the biasing means (5) by moving the adjustment member (10) in the axial direction, the screw adjustment mechanism (11) is pivoted as a means for determining the position of the adjustment member (10). The adjustment member (10) is deformed toward the inner side in the radial direction from the opposed position sandwiching the axial line in the axial direction by a half-pitch (P / 2) in the direction. An electromagnetic valve comprising fixing means (12) for fixing. The solenoid valve (103) according to claim 1,
The electromagnetic valve characterized in that the fixing means (12) positions and fixes the adjusting member (10) by crushing a thread of the female screw portion (32b) or the male screw portion (10b). The solenoid valve (103) according to claim 1 or 2,
The sleeve (3) includes a small diameter cylindrical portion (32) having a two-sided width portion (32a),
The screw adjusting mechanism (11) is constructed in the small diameter cylindrical portion (32),
The electromagnetic valve according to claim 1, wherein the fixing means (12) is provided in the two-surface width portion (32a). In the solenoid valve (103) according to any one of claims 1 to 3,
The solenoid valve according to claim 1, wherein the biasing means (5) comprises a compression coil spring. In the solenoid valve (103) according to any one of claims 1 to 4,
The electromagnetic valve (103) is used as a hydraulic control electromagnetic valve (103) in a hydraulic system (100) of an automobile automatic transmission.

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