JP6640637B2 - Solenoid valve, vehicle brake fluid pressure control device, and method of manufacturing electromagnetic valve - Google Patents

Description

  The present invention relates to a solenoid valve, a vehicle brake fluid pressure control device, and a method for manufacturing a solenoid valve.

  As the electromagnetic valve used in the vehicle brake fluid pressure control device, the first valve seat member and the second valve seat member fixed in a fixed core, between the first valve seat member and the second valve seat member There is a so-called two-position three-way valve including a spherical valve body member arranged (for example, see Patent Document 1).

  In the above-described conventional solenoid valve, the valve body member is held by the retainer covering the end of the first valve seat member, and a spring member (coil spring) is interposed between the retainer and the second valve seat member. Have been. Then, the retainer is pressed against the first valve seat member by the urging force of the spring member, and the valve body member is seated on the valve seat surface of the first valve seat member.

  In the above-described conventional solenoid valve, the movable core is moved by the electromagnetic force, and the retainer is pushed out by the movable core, whereby the valve body member is separated from the valve seat surface of the first valve seat member, and the valve body member is moved to the second position. It is configured to be seated on the valve seat surface of the valve seat member.

International Publication No. WO 2015/046308

  When manufacturing the above-described conventional solenoid valve, the opening of the fixed core is arranged on the upper side, and the first valve seat member, the valve body member, the retainer, and the spring member are sequentially assembled in the fixed core. When the above-described components are assembled in the fixed core, the spring member is set upright on the upper surface of the first valve seat member in the fixed core.

  Thereafter, the second valve seat member is pressed into the fixed core, and the lower end of the second valve seat member is inserted into the upper end of the spring member. At this time, the upper end of the spring member is unstable, and the work of assembling the second valve seat member becomes difficult, so that there is a problem that the productivity of the solenoid valve is reduced.

  An object of the present invention is to provide an electromagnetic valve capable of solving the above-described problems and improving the assemblability of parts, a vehicle brake hydraulic pressure control device using the electromagnetic valve, and a method of manufacturing the electromagnetic valve. I do.

In order to solve the above-mentioned problem, the present invention is an electromagnetic valve of a two-position three-way valve , comprising: a fixed core in which a flow path is formed; a movable core movably provided with respect to the fixed core; And a coil for moving the movable core by force. Further, the solenoid valve includes a first valve seat member and a second valve seat member fixed in the fixed core, and a valve body disposed between the first valve seat member and the second valve seat member. A member, and a spring member interposed between the valve body member and the second valve seat member. The valve body member is a main body, formed at one end of the main body, a first valve portion seated on a valve seat surface of the first valve seat member, and protrudingly provided at the other end of the main body, A second valve portion seated on the valve seat surface of the second valve seat member. In the valve body member, the first valve portion is seated on the valve seat surface of the first valve seat member by the urging force of the spring member. When the valve member is pushed out by the movable core, the first valve portion is separated from the first valve seat member, and the second valve portion is seated on the valve seat surface of the second valve seat member. It is configured as follows. The valve body member and the spring member are held by the second valve seat member by a guide member that regulates separation of the valve body member from the second valve seat member. The main body, the second valve, and the spring member are accommodated in the guide member, and the first valve is inserted into an insertion hole formed in a distal end wall of the guide member, and the guide member is Projecting from. A communication hole opened to the inner peripheral surface of the fixed core radially outside of the guide member, and the opening of the first valve seat member, the inner peripheral surface of the fixed core and the outer peripheral surface of the guide member, Communicate through

  In the electromagnetic valve of the present invention, the valve member, the spring member, the guide member, and the second valve seat member are integrally formed. Thereby, when manufacturing the solenoid valve of the present invention, the valve body member, the spring member, the guide member, and the second valve seat member can be assembled in the fixed core as one unit. Therefore, in the solenoid valve according to the present invention, the assemblability of parts can be improved, and the productivity of the solenoid valve can be improved.

  In the above-described solenoid valve, it is preferable that a guide surface on which the valve body member can slide is formed on the guide member. With this configuration, the valve member can be moved stably.

  In the above-described solenoid valve, a spring receiving portion in which an end of the spring member is fitted to the valve body member, a sliding surface slidable on the guide member, and engagement with the guide member. It is preferable that the spring member and the guide member are easily assembled to the valve body member.

  In the above-described solenoid valve, the valve body member includes a first valve portion seated on a valve seat surface of the first valve seat member, and a second valve portion seated on a valve seat surface of the second valve seat member. , Can be formed. In this case, the area where the first valve portion abuts on the valve seat surface of the first valve seat member is such that the second valve portion abuts on the valve seat surface of the second valve seat member. It can be configured to be larger than the area.

  In this configuration, since two valve portions are formed in one valve body member, the area of each of the two valve portions that comes into contact with the valve seat surface of the valve seat member can be set. That is, when the valve portion contacts the valve seat surface of the valve seat member, the area where the valve portion contacts the valve seat surface can be set independently for both valve portions. In the above-described configuration, the sealing performance of the first valve portion with respect to the first valve seat member can be improved while increasing the flow rate of the fluid passing through the first valve seat member.

  In the above-described solenoid valve, when a movable rod that moves in conjunction with the movable core is provided, a flat surface is formed on the first valve portion, and an end surface of the movable rod is brought into contact with the flat surface. Is preferred.

  With this configuration, the movable rod can be stably brought into contact with the first valve portion. In addition, since the movable rod and the first valve portion are in surface contact with each other, the movable rod is less likely to be worn, so that the degree of freedom of the material of the movable rod can be increased.

  In the above-described solenoid valve, the valve body member includes a main body, the first valve formed at one end of the main body, and the second valve protruding from the other end of the main body. When a part of the spherical surface is formed at the tip of the second valve portion, the second valve portion can be stably seated on the valve seat surface of the second valve seat member.

  In the above-described solenoid valve, the guide member is formed in a cylindrical shape, the spring member is accommodated in the guide member, and the flow is formed between an inner peripheral surface of the fixed core and an outer peripheral surface of the guide member. It is preferable to form a part of the road.

In this configuration, since a large amount of fluid can be prevented from hitting the spring member by flowing the liquid through the flow path outside the guide member, the degree of freedom in designing the spring member can be increased.
For example, when the urging force of the spring member is suppressed, the electric power of the coil required to move the movable core against the urging force of the spring member can be reduced.

  The present invention is a vehicular brake fluid pressure control device disposed between a master cylinder and a wheel cylinder, comprising: a slave cylinder that generates brake fluid pressure by driving an electric actuator; and the solenoid valve. I have. The solenoid valve may be configured such that the valve body member is seated on a valve seat surface of the first valve seat member and the master cylinder and the wheel cylinder communicate with each other. , And is configured to switch between a state in which the slave cylinder and the wheel cylinder are in communication with each other.

According to the vehicle brake fluid pressure control device of the present invention, since the above-described solenoid valve of the present invention is used, the productivity of the vehicle brake fluid pressure control device can be improved.
Further, according to the vehicle brake fluid pressure control device of the present invention, the electromagnetic valve can be stably opened and closed, and the flow rate of the brake fluid passing through the electromagnetic valve can be sufficiently ensured. Can be controlled.

The present invention is the method for manufacturing the electromagnetic valve, wherein the step of fixing the first valve seat member in the fixed core, and the step of fixing the valve body member and the spring member to the second valve seat member by the guide member. And fixing the second valve seat member in the fixed core, and seating the valve body member on the valve seat surface of the first valve seat member.
ADVANTAGE OF THE INVENTION According to the manufacturing method of the solenoid valve of this invention, since the valve body member, the spring member, the guide member, and the second valve seat member are assembled as one unit in the fixed core, the productivity of the solenoid valve is improved. be able to.

In the solenoid valve of the present invention, since the valve body member, the spring member, the guide member, and the second valve seat member are integrally formed, the assemblability of parts can be improved, and the productivity of the solenoid valve can be improved. Can be improved.
Further, in the solenoid valve of the present invention, since the degree of freedom of the shape of the valve seat surface and the flow path of the valve seat member can be increased, it is easy to configure the valve seat member according to the specifications of the solenoid valve.
Further, in the vehicle brake fluid pressure control device of the present invention, the productivity of the vehicle brake fluid pressure control device can be improved, and the vehicle brake can be well controlled.
In the method of manufacturing a solenoid valve according to the present invention, since the valve body member, the spring member, the guide member, and the second valve seat member are assembled as a single unit in the fixed core, the productivity of the solenoid valve is improved. be able to.

1 is a schematic diagram illustrating a non-starting state of a vehicle brake hydraulic pressure control device according to an embodiment of the present invention. FIG. 2 is a schematic diagram showing a vehicle brake fluid pressure control device according to an embodiment of the present invention at the time of activation. FIG. 4 is a cross-sectional view illustrating a state where the first switching valve according to the embodiment of the present invention is not energized. FIG. 4 is a cross-sectional view illustrating a state where power is supplied to a first switching valve according to the embodiment of the present invention. 1A and 1B are diagrams showing a valve body unit according to an embodiment of the present invention, wherein FIG. 1A is a cross-sectional view and FIG. 1A and 1B are views showing a first valve seat member, a valve body member, and a second valve seat member according to an embodiment of the present invention, wherein FIG. 1A is an exploded view, and FIG. It is a figure showing a diameter. It is the perspective view which showed the process of assembling the valve body unit in the fixed core in the manufacturing method of the 1st switching valve which concerns on embodiment of this invention.

An embodiment of the present invention will be described in detail with reference to the drawings as appropriate.
As shown in FIG. 1, the vehicle brake fluid pressure control device A of the present embodiment includes a by-wire (By Wire) brake system that operates when a prime mover (engine, electric motor, or the like) is started. And a hydraulic brake system that operates when the prime mover stops.

The vehicle brake hydraulic pressure control device A includes a hydraulic pressure generation device A1 that generates brake hydraulic pressure by depressing force of a brake pedal P (brake operator), and a motor cylinder device A2 that generates brake hydraulic pressure using a motor 70. And a hydraulic pressure control device A3 for assisting stabilization of the vehicle behavior.
The hydraulic pressure generating device A1, the motor cylinder device A2, and the hydraulic pressure control device A3 are configured as separate units, and communicate with each other via external piping.

  The vehicle brake fluid pressure control device A is applicable to a hybrid vehicle using both an engine (internal combustion engine) and a motor, an electric vehicle using only a motor as a power source, a fuel cell vehicle, and a vehicle using only an engine as a power source. Can also be installed.

  The hydraulic pressure generator A1 includes a base 10, a tandem master cylinder 20, a stroke simulator 30, and a reservoir 40. The hydraulic pressure generator A1 includes switching valves 15 and 16 (“electromagnetic valves” in the claims), a normally-closed electromagnetic valve 17, and pressure sensors 18 and 19.

The base 10 is a metal component mounted on a vehicle, and the above-described components are assembled to the base 10.
Inside the base body 10, main hydraulic pressure paths 10a and 10b, connecting hydraulic pressure paths 10c and 10d, and branch hydraulic pressure paths 10e are formed.
A control device 50 is mounted on the outer surface of the base 10. A reservoir 40 is mounted on the upper surface of the base 10.

The master cylinder 20 converts the depression force of the brake pedal P into a brake fluid pressure.
The master cylinder 20 includes a first piston 21 arranged on the bottom side of the first cylinder hole 20a, and a second piston 22 arranged on the opening side of the first cylinder hole 20a. Further, the master cylinder 20 includes a first elastic member 24 housed in a first pressure chamber 20b between the bottom surface of the first cylinder hole 20a and the first piston 21, and a second pressure between the two pistons 21 and 22. A second elastic member 25 housed in the chamber 20c. The two elastic members 24 and 25 of the present embodiment are coil springs.

  The second piston 22 is connected to the brake pedal P via a push rod P1. The pistons 21 and 22 receive the depression force of the brake pedal P and slide in the first cylinder hole 20a to pressurize the brake fluid in the pressure chambers 20b and 20c.

  The stroke simulator 30 generates a pseudo operation reaction force on the brake pedal P. The stroke simulator 30 includes a piston 31 that slides in the second cylinder hole 30a, and two elastic members 32 and 33 that urge the piston 31 toward the bottom surface of the second cylinder hole 30a. A pressure chamber 30b is formed between the bottom surface of the second cylinder hole 30a and the piston 31.

  The pressure chamber 30b of the stroke simulator 30 communicates with a second pressure chamber 20c of the master cylinder 20 via a branch hydraulic pressure passage 10e and a second main hydraulic pressure passage 10b described later. Then, by the brake fluid pressure generated in the second pressure chamber 20c, the piston 31 moves against the urging force of the elastic members 32 and 33, so that a pseudo operation reaction force is applied to the brake pedal P.

The two main hydraulic paths 10a and 10b are hydraulic paths starting from the master cylinder 20. Pipes Ha and Hb leading to the hydraulic pressure control device A3 are connected to output ports 10f and 10g, which are end points of the two main hydraulic pressure paths 10a and 10b, respectively.
The first main hydraulic pressure passage 10a communicates from the first pressure chamber 20b of the master cylinder 20 to one output port 10f. The second main hydraulic pressure passage 10b communicates from the second pressure chamber 20c of the master cylinder 20 to the other output port 10g.

The two communication hydraulic lines 10c and 10d are hydraulic lines from the input ports 10h and 10i to the main hydraulic lines 10a and 10b. Pipes Hc and Hd leading to the motor cylinder device A2 are connected to the two input ports 10h and 10i.
The first communication hydraulic pressure passage 10c communicates from one input port 10h to the first main hydraulic pressure passage 10a. The second communication hydraulic pressure passage 10d communicates from the other input port 10i to the second main hydraulic pressure passage 10b.

  The branch hydraulic pressure path 10e is a hydraulic pressure path that branches from the second main hydraulic pressure path 10b and reaches the pressure chamber 30b of the stroke simulator 30.

In the first main hydraulic pressure passage 10a, a first switching valve 15, which is a three-way valve, is provided at a portion connected to the first communication hydraulic pressure passage 10c.
The first switching valve 15 is an electromagnetic valve, and communicates between the upstream side (the master cylinder 20 side) and the downstream side (the output port 10f side) of the first main hydraulic pressure passage 10a when not energized (initial state). While doing so, the first communication hydraulic passage 10c and the first main hydraulic passage 10a are shut off.
In addition, the first switching valve 15 shuts off the upstream side and the downstream side of the first main hydraulic pressure passage 10a when energized, while the first connection hydraulic pressure passage 10c and the downstream of the first main hydraulic pressure passage 10a. Side (see FIG. 2).

In the second main hydraulic pressure passage 10b, a second switching valve 16, which is a three-way valve, is provided at a portion connected to the second communication hydraulic pressure passage 10d.
The second switching valve 16 is an electromagnetic valve, and communicates between the upstream side (the master cylinder 20 side) and the downstream side (the output port 10g side) of the second main hydraulic pressure passage 10b when power is not supplied (initial state). While doing so, the second communication hydraulic passage 10d and the second main hydraulic passage 10b are shut off.
The second switching valve 16 shuts off the upstream side and the downstream side of the second main hydraulic pressure passage 10b when energized, and connects the second communication hydraulic pressure passage 10d and the downstream of the second main hydraulic pressure passage 10b. Side (see FIG. 2).

A normally closed solenoid valve 17 is provided in the branch hydraulic pressure passage 10e.
When not energized (initial state), the normally closed solenoid valve 17 shuts off the side of the second hydraulic pressure passage 10b of the branch hydraulic pressure passage 10e from the stroke simulator 30 side.
When energized, the normally-closed solenoid valve 17 communicates the branch hydraulic pressure passage 10e with the second main hydraulic pressure passage 10b and the stroke simulator 30 (see FIG. 2).

The pressure sensors 18 and 19 detect the magnitude of the brake fluid pressure, and information acquired by the two pressure sensors 18 and 19 is output to the control device 50.
The first pressure sensor 18 is attached to a sensor attachment hole (not shown) communicating with the first main hydraulic pressure passage 10a. The first pressure sensor 18 is disposed upstream of the first switching valve 15 and detects the magnitude of the brake fluid pressure generated in the master cylinder 20.

  The second pressure sensor 19 is attached to a sensor attachment hole (not shown) communicating with the second main hydraulic pressure passage 10b. The second pressure sensor 19 is arranged downstream of the second switching valve 16. The second pressure sensor 19 detects the brake hydraulic pressure generated in the motor cylinder device A2 when the second switching valve 16 is closed (the upstream and downstream sides of the second main hydraulic pressure passage 10b are shut off). Detect the size of.

The control device 50 has a housing 51 made of resin, and a control board (not shown) is housed in the housing 51.
The control device 50 drives the motor 70 and switches the two switching valves 15 based on information obtained from various sensors such as the pressure sensors 18 and 19 and a stroke sensor (not shown) and a program stored in advance. , 16 and the opening and closing of the normally closed solenoid valve 17 are controlled.

  The motor cylinder device A2 includes a tandem-type slave cylinder 60, a motor 70, a drive transmission unit 80, and a reservoir 90.

The slave cylinder 60 generates a brake fluid pressure corresponding to the brake fluid pressure generated in the master cylinder 20.
The slave cylinder 60 includes a base 61 which is a cylindrical metal part, a first piston 62 arranged on the bottom side of the cylinder hole 61a of the base 61, and a second piston 63 arranged on the opening side of the cylinder hole 61a. , Is provided. The slave cylinder 60 includes a first elastic member 64 housed in a first pressure chamber 61b between the bottom surface of the cylinder hole 61a and the first piston 62, and a second pressure chamber 61c between the pistons 62 and 63. And a second elastic member 65 housed in the second member. The reservoir 90 is mounted on the upper surface of the base 61.

The drive transmitting unit 80 converts the rotational driving force of the output shaft 71 of the motor 70 into a linear axial force, and is attached to an end of the base 61.
The drive transmission unit 80 includes a rod 81, a cylindrical nut member 82 externally fitted to the rod 81, a ball screw mechanism 83 provided between the rod 81 and the nut member 82, and a rotational drive of the motor 70. A gear mechanism 84 for transmitting a force to the nut member 82. The above-described components are housed in a housing 85. The tip of the rod 81 is inserted into the cylinder hole 61 a of the slave cylinder 60, and the tip of the rod 81 contacts the second piston 63.

  The motor 70 is an electric servomotor driven and controlled by the control device 50. The motor 70 is fixed to a motor fixing portion 85 a protruding from the outer peripheral surface of the housing 85. An output shaft 71 protrudes from the motor 70, and the output shaft 71 is inserted into an opening of the motor fixing portion 85a.

When the rotation driving force of the output shaft 71 is input to the nut member 82 via the gear mechanism 84, a linear axial force is applied to the rod 81 by the ball screw mechanism 83, and the rod 81 moves forward and backward in the axial direction. .
When the rod 81 moves to the bottom side of the cylinder hole 61a, the second piston 63 receives the input from the rod 81 and slides in the cylinder hole 61a to apply the brake fluid in both the pressure chambers 61b and 61c. Press.

  The two pressure chambers 61b, 61c of the slave cylinder 60 communicate with the input ports 10h, 10i of the hydraulic pressure generator A1 via pipes Hc, Hd. Then, the brake hydraulic pressure generated in the slave cylinder 60 is input to the hydraulic pressure generator A1 via the pipes Hc and Hd.

The hydraulic pressure control device A3 has a configuration capable of executing various hydraulic pressure controls such as antilock brake control and behavior stabilization control by appropriately controlling the brake hydraulic pressure applied to each wheel cylinder W of the wheel brake. And is connected to each wheel cylinder W via a pipe.
Although not shown, the hydraulic pressure control device A3 includes a hydraulic pressure unit provided with an electromagnetic valve and a pump, a motor for driving the pump, a control device for controlling the electromagnetic valve and the motor, and the like. Have.

  The hydraulic pressure control device A3 communicates with the output ports 10f and 10g of the hydraulic pressure generation device A1 via pipes Ha and Hb, and the brake hydraulic pressure generated in the master cylinder 20 receives the hydraulic pressure via the pipes Ha and Hb. Input to the pressure control device A3.

Next, the operation of the vehicle brake fluid pressure control device A will be schematically described.
In the vehicle brake hydraulic pressure control device A, when the vehicle system is started, as shown in FIG. 2, the first switching valve 15 shuts off the upstream side and the downstream side of the first main hydraulic pressure passage 10a. In addition, the first communication hydraulic passage 10c communicates with the downstream side of the first main hydraulic passage 10a.
Further, the second switching valve 16 communicates the second communication hydraulic pressure path 10d with the downstream side of the second main hydraulic pressure path 10b while shutting off the upstream side and the downstream side of the second main hydraulic pressure path 10b. .
Also, the normally closed solenoid valve 17 is opened, and the side of the second main hydraulic pressure path 10b of the branch hydraulic pressure path 10e communicates with the stroke simulator 30 side.

  In this state, the brake fluid pressure generated in the master cylinder 20 by operating the brake pedal P is transmitted to the stroke simulator 30 without being transmitted to the wheel cylinder W. Then, the brake fluid pressure in the pressure chamber 30b of the stroke simulator 30 increases, and the piston 31 moves against the urging force of the elastic members 32 and 33, whereby the stroke of the brake pedal P is allowed. At this time, a pseudo operation reaction force is applied to the brake pedal P by the piston 31 urged by the elastic members 32 and 33.

When the depression of the brake pedal P is detected by a stroke sensor (not shown), the motor 70 of the motor cylinder device A2 is driven, and the rod 81 moves to the bottom side of the cylinder hole 61a. Thereby, the second piston 63 of the slave cylinder 60 moves to the bottom side of the cylinder hole 61a, and the brake fluid in the pressure chambers 61b and 61c is pressurized.
In this way, the brake fluid pressure generated by the motor cylinder device A2 is transmitted to each wheel cylinder W via the fluid pressure generator A1 and the fluid pressure control device A3, and each wheel cylinder W is actuated. A braking force is applied to the wheels.

In a state where the motor cylinder device A2 does not operate (for example, when power cannot be obtained), as shown in FIG. 1, the first switching valve 15 is connected to the upstream side and the downstream side of the first main hydraulic pressure passage 10a. And the first communication hydraulic passage 10c and the first main hydraulic passage 10a are shut off.
The second switching valve 16 shuts off the second communication hydraulic pressure passage 10d and the second main hydraulic pressure passage 10b while communicating the upstream and downstream sides of the second main hydraulic pressure passage 10b. The normally closed solenoid valve 17 is closed.
In this state, the brake fluid pressure generated in master cylinder 20 is transmitted to each wheel cylinder W.

Next, the configuration of the switching valves 15 and 16 of the present embodiment will be described in detail.
In the present embodiment, as shown in FIG. 1, the first switching valve 15 and the second switching valve 16 have the same structure. Therefore, in the following description, the first switching valve 15 will be described, and the second switching valve 16 will be described. Will not be described.
In the following description, the up, down, left, and right directions are set for convenience in describing the structure of the first switching valve 15, and do not limit the structure and mounting state of the first switching valve 15.

  The first switching valve 15 is an electromagnetic valve, and is a two-position three-port three-way valve. The first switching valve 15 is provided at a portion of the first main hydraulic pressure passage 10a connected to the first communication hydraulic pressure passage 10c.

  The first switching valve 15 is inserted into a mounting hole 11 formed on one surface of the base 10 as shown in FIG. On the bottom surface of the mounting hole 11, an upstream side (the master cylinder 20 side) of the first main hydraulic passage 10a is opened. Further, on the inner peripheral surface of the mounting hole 11, a downstream side (the hydraulic pressure control device A3 side) of the first main hydraulic pressure passage 10a is opened. In addition, on the inner peripheral surface of the mounting hole 11, a first communication hydraulic pressure passage 10c is opened above the opening on the downstream side of the first main hydraulic pressure passage 10a (on the opening side of the mounting hole 11). .

The first switching valve 15 includes a fixed core 110, a movable core 120 provided above the fixed core 110, and a coil 130 externally fitted to the movable core 120 and the fixed core 110.
Inside the fixed core 110, a first valve seat member 140, a second valve seat member 150, a guide member 160, a valve body member 170, and a spring member 180 are accommodated. Further, a cover member 190 is covered on the movable core 120 and the fixed core 110.

  The fixed core 110 is a cylindrical member made of a magnetic material such as iron or an iron alloy. The fixed core 110 has an insertion portion 111 inserted into the mounting hole 11 of the base 10 and a protruding portion 112 protruding from the mounting hole 11. A central hole 113 having a circular cross section penetrates in the axial direction at the center of the insertion portion 111 and the protrusion 112.

  The central hole 113 includes a small-diameter hole 113a formed from the upper end surface of the protruding portion 112 to the upper portion of the insertion portion 111, and a large-diameter hole portion 113b formed from the upper end of the insertion portion 111 to the lower end surface. , Are formed.

A plurality of first communication holes 114 penetrate in the radial direction on the upper side wall of the insertion portion 111. The small-diameter hole portion 113a and the first communication hydraulic path 10c communicate with each other through the first communication hole 114.
On the outer peripheral surface of the insertion portion 111, a cylindrical first filter 114a disposed so as to cover the opening of each of the first series of through holes 114 is fitted externally.

A plurality of second communication holes 115 penetrate in a radial direction in a lower side wall of the insertion portion 111. Through this second communication hole 115, the large-diameter hole portion 113b and the downstream side of the first main hydraulic pressure passage 10a (the hydraulic pressure control device A3 side) communicate with each other.
On the outer peripheral surface of the insertion portion 111, a cylindrical second filter 115a disposed so as to cover the opening of each second communication hole 115 is externally fitted.

On the outer peripheral surface of the insertion portion 111, an annular first seal member 116a is externally fitted at a position above the opening of the first communication hole 114.
On the outer peripheral surface of the insertion portion 111, an annular second seal member 116b is externally fitted at a position between the opening of the first communication hole 114 and the opening of the second communication hole 115.
On the outer peripheral surface of the insertion portion 111, an annular third seal member 116c is externally fitted at a position below the opening of the second communication hole 115.
Each of the seal members 116a, 116b, and 116c seals the space between the outer peripheral surface of the insertion portion 111 and the inner peripheral surface of the mounting hole 11 in a liquid-tight manner.

On the outer peripheral surface of the insertion portion 111, an annular locking member 117 is fitted at a position corresponding to the opening of the mounting hole 11. The locking member 117 is fixed to the opening of the mounting hole 11 by a clip or the like, thereby forming the fixed core 110 to prevent the fixed core 110 from being removed from the mounting hole 11.
Note that the opening edge of the mounting hole 11 may be plastically deformed toward the fixed core 110 to prevent the fixed core 110 from coming off the mounting hole 11.

The first valve seat member 140 is a cylindrical member made of metal. The first valve seat member 140 is press-fitted into the lower end of the small diameter hole 113a (the end on the side of the large diameter hole 113b).
The outer peripheral edge of the upper end surface of the first valve seat member 140 is in contact with the step in the small-diameter hole 113a. The first valve seat member 140 is disposed in the center hole 113 between the opening of the first communication hole 114 and the opening of the second communication hole 115.

As shown in FIG. 6A, a flow path 141 having a circular cross section penetrates the center of the first valve seat member 140 in the axial direction.
On the lower end surface 140a of the first valve seat member 140, a funnel-shaped (tapered) valve seat surface 142 is formed at the opening edge of the flow path 141. The valve seat surface 142 of the first valve seat member 140 is a portion where the first valve portion 172 of the valve body member 170 described later is seated (see FIG. 3).
In the present embodiment, the opening of the flow path 141 and the valve seat surface 142 are formed on substantially the entire lower end surface 140a of the first valve seat member 140.

The second valve seat member 150 is a cylindrical member made of metal. As shown in FIG. 3, the second valve seat member 150 is press-fitted into the lower part of the large-diameter hole 113b. The second valve seat member 150 is disposed below the second communication hole 115 in the center hole 113.
Further, below the second valve seat member 150, a third filter 113d press-fitted into the base end opening 113c of the center hole 113 is provided.

As shown in FIG. 6A, a flow path 151 passes through the center of the second valve seat member 150 in the axial direction. A recess 150c is formed in the center of the lower end surface 150b of the second valve seat member 150. The channel 151 is open at the bottom of the recess 150c.
In the present embodiment, the inner diameter of the flow path 151 of the second valve seat member 150 is formed to be significantly smaller than the inner diameter of the flow path 141 of the first valve seat member 140.

A funnel-shaped (tapered) valve seat surface 152 is formed at the opening edge of the flow path 151 on the upper end surface 150 a of the second valve seat member 150. The valve seat surface 152 of the second valve seat member 150 is a portion where a second valve portion 173 of the valve body member 170 described later is seated (see FIG. 4).
A cylindrical mounting portion 153 protrudes from the upper end surface 150 a of the valve seat member 150 around the valve seat surface 152. A channel 151 is opened at the center of the bottom surface of the mounting portion 153.

The guide member 160 includes a metal cylindrical portion 161 as shown in FIG. An opening 162 is formed at the lower end of the cylindrical portion 161, and a distal end wall 163 is formed at the upper end of the cylindrical portion 161.
As shown in FIG. 5A, the lower end of the cylindrical portion 161 is externally fitted to the mounting portion 153 of the second valve seat member 150.
The guide member 160 is fixed to the upper end surface 150a of the second valve seat member 150. The guide member 160 regulates the separation of the valve member 170 from the second valve seat member 150.

  A plurality of third communication holes 164 penetrate the side wall of the cylindrical portion 161 in the radial direction. As shown in FIG. 3, when the cylindrical portion 161 is attached to the second valve seat member 150, the third communication hole 164 is arranged above the attachment portion 153.

As shown in FIG. 5 (a), a circular insertion hole 165 penetrates in the axial direction at the center of the distal end wall portion 163 of the cylindrical portion 161 (see FIG. 5 (b)). The insertion hole 165 is a portion through which the first valve portion 172 of the valve member 170 described later is inserted.
An inner peripheral surface 161a of the cylindrical portion 161 is a guide surface 161b on which a main body portion 171 of the valve member 170 described later slides.

  As shown in FIG. 3, a cylindrical flow path 119 is formed in a space between the outer peripheral surface of the cylindrical portion 161 of the guide member 160 and the inner peripheral surface of the center hole 113 of the fixed core 110. The third communication hole 164 of the guide member 160 and the second communication hole 115 of the fixed core 110 communicate with each other by the flow path 119.

The valve member 170 is a metal member, and as shown in FIG. 5A, a main body 171 housed in the guide member 160 and a first valve protruding from an upper end surface of the main body 171. And a second valve portion 173 protruding from a lower end surface of the main body portion 171.
The main body portion 171, the first valve portion 172, and the second valve portion 173 of the valve body member 170 are formed in a circular cross section (see FIG. 5B). The main body part 171, the first valve part 172, and the second valve part 173 are formed on the same axis.
The outer diameter of the first valve part 172 is formed smaller than the outer diameter of the main body part 171, and the outer diameter of the second valve part 173 is formed smaller than the outer diameter of the first valve part 172.

  The main body 171 is a part housed in the guide member 160 as shown in FIG. The main body 171 is slidable up and down with respect to the guide member 160. The outer peripheral surface of the main body 171 is a sliding surface 171c that slides on the guide surface 161b in the guide member 160.

As shown in FIG. 6A, the first valve portion 172 is provided so as to protrude at the center of the upper end surface 171a of the main body portion 171.
The distal end surface 172a of the first valve portion 172 is a flat surface (plane) whose normal line is the axis of the valve member 170. In addition, a spherical belt-shaped contact surface 172b is formed on the outer peripheral edge of the distal end surface 172a of the first valve portion 172. The contact surface 172b is a portion that sits on the valve seat surface 142 of the first valve seat member 140.

As shown in FIG. 5A, the first valve portion 172 is inserted through the insertion hole 165 of the guide member 160, and protrudes above the distal end wall portion 163 of the guide member 160 (FIG. 5B). )reference).
The outer peripheral edge of the upper end surface 171a of the main body 171 is an engaging portion 171d that comes into contact with the inner surface of the distal end wall 163 of the guide member 160 when the valve member 170 moves upward.

As shown in FIG. 6A, the second valve portion 173 is provided so as to protrude at the center of the lower end surface 171 b of the main body portion 171.
The second valve portion 173 is reduced in diameter from a base portion (upper end portion) to a distal end portion (lower end portion). The maximum outer diameter of the second valve part 173 is formed smaller than the maximum outer diameter of the first valve part 172.
As shown in FIG. 5A, the base of the second valve portion 173 is a spring receiving portion 173c to which an upper end portion of a spring member 180 described later is fitted.

  A spherical band-shaped contact surface 173b is formed on the outer peripheral edge of the distal end surface 173a of the second valve portion 173. The contact surface 173b is formed by a part of the spherical surface, and in the present embodiment, the annular contact surface 173b is formed by forming the top of the hemisphere flat. The contact surface 173b is a portion that sits on the valve seat surface 152 of the second valve seat member 150 when the valve member 170 is moved downward (see FIG. 4).

  As shown in FIG. 6B, the valve member 170 of the present embodiment is configured such that the seal diameter L1 of the first valve portion 172 is larger than the seal diameter L2 of the second valve portion 173. When the contact surfaces 172b, 173b of the valve portions 172, 173 are seated on the valve seat surfaces 142, 152 of the valve seat members 140, 150, the seal diameters L1, L2 of the valve portions 172, 173 are determined. 173b is the outer diameter of the region in contact with the valve seat surfaces 142, 152.

In the valve body member 170 of the present embodiment, the area of the contact surface 172b that contacts the valve seat surface 142 of the first valve seat member 140 contacts the valve seat surface 152 of the second valve seat member 150. It is larger than the area of the contact surface 173b.
That is, when the first valve portion 172 contacts the valve seat surface 142 of the first valve seat member 140, the pressure receiving area where the first valve portion 172 receives a reaction force from the valve seat surface 142 is reduced. Is larger than the pressure receiving area in which the second valve portion 173 receives a reaction force from the valve seat surface 152 when the valve abuts on the valve seat surface 152 of the second valve seat member 150.

The spring member 180 is a coil spring as shown in FIG. The spring member 180 is provided between the second valve seat member 150 and the valve body member 170 in the guide member 160.
The upper end of the spring member 180 is fitted to the spring receiving portion 173c of the second valve portion 173. The upper end of the spring member 180 contacts the lower end 171b of the main body 171.
The lower end of the spring member 180 is inserted into the mounting portion 153 of the second valve seat member 150, and contacts the bottom surface of the mounting portion 153.

  As shown in FIG. 3, the spring member 180 is interposed between the second valve seat member 150 and the valve member 170 in a compressed state, and the urging force of the spring member 180 pushes the valve member 170 to the fourth position. It pushes up in a direction away from the two-valve seat member 150. Thus, the first valve portion 172 of the valve member 170 is pressed against the valve seat surface 142 of the first valve seat member 140, and the flow path 141 of the first valve seat member 140 is closed.

In the present embodiment, as shown in FIG. 5A, a part of the valve member 170 and the spring member 180 are accommodated in the guide member 160. That is, the valve member 170 and the spring member 180 are held by the second valve seat member 150 by the guide member 160.
Thus, in the present embodiment, the valve member 170, the spring member 180, the guide member 160, and the second valve seat member 150 are integrally formed.
Thereby, when manufacturing the first switching valve 15 (see FIG. 3), the valve member 170, the spring member 180, the guide member 160, and the second valve seat member 150 can be handled as one valve unit U.

  As shown in FIG. 3, the movable core 120 is a magnetic material having a circular cross section, and is disposed above the protrusion 112 of the fixed core 110.

A movable rod 121 having a circular cross section is inserted into the small-diameter hole 113a of the fixed core 110. The movable rod 121 is a member made of resin. The movable rod 121 is vertically slidable with respect to the small diameter hole 113a.
A plurality of grooves (not shown) extending in the axial direction are formed on the outer peripheral surface of the movable rod 121. For example, four grooves may be arranged at equal intervals in the circumferential direction of the movable rod 121.
The upper end of the movable rod 121 projects upward from the center hole 113 of the fixed core 110 and contacts the lower end surface of the movable core 120.

  The lower part 122 of the movable rod 121 has a reduced diameter, and a space is formed between the outer peripheral surface of the lower part 122 and the inner peripheral surface of the center hole 113. This space communicates with the first communication hole 114.

  The lower end of the movable rod 121 is inserted into the flow path 141 of the first valve seat member 140. Further, the lower end surface of the movable rod 121 is in contact with the distal end surface 172a of the first valve portion 172.

A communication groove 123 is formed on the outer peripheral surface of the lower part 122 of the movable rod 121. The communication groove 123 extends in the axial direction of the movable rod 121. A space is formed between the inner surface of the communication groove 123 and the inner peripheral surface of the first valve seat member 140.
As shown in FIG. 4, in a state where the first valve portion 172 is separated from the valve seat surface 142 of the first valve seat member 140, the space above the first valve seat member 140 and the space below the first valve seat member 140 are communicated through the communication groove 123. The space is in communication.

  The cover member 190 is a tubular member whose upper end is closed, is covered on the upper end of the protrusion 112 of the movable core 120 and the fixed core 110, and is welded to the outer peripheral surface of the protrusion 112.

The coil 130 is an electromagnetic coil for moving the movable core 120, and is disposed around the protrusion 112 of the fixed core 110.
The coil 130 generates a magnetic field around the protrusion 112 of the fixed core 110 when energized by the control device 50 (see FIG. 1).

When the first switching valve 15 of the present embodiment is not energized (initial state), the valve body member 170, the movable rod 121, and the movable core 120 are moved upward by the urging force of the spring member 180, as shown in FIG. It has been pushed up.
In this state, the second valve portion 173 is separated from the valve seat surface 152 of the second valve seat member 150, and the flow path 151 of the second valve seat member 150 is open. Further, the first valve portion 172 is seated on the valve seat surface 142 of the first valve seat member 140, and the flow path 141 of the first valve seat member 140 is closed.
As a result, the first switching valve 15 in the non-energized state communicates between the upstream side (the master cylinder 20 side) and the downstream side (the hydraulic pressure control device A3 side) of the first main hydraulic pressure passage 10a while maintaining the first communication. The hydraulic passage 10c and the first main hydraulic passage 10a are shut off (see FIG. 1).

When the first switching valve 15 of the present embodiment is energized, the coil 130 is energized and the coil 130 is excited. Thus, the fixed core 110 is excited, and the movable core 120 is drawn to the fixed core 110 as shown in FIG. Then, the movable core 120, the movable rod 121, and the valve body member 170 move downward against the urging force of the spring member 180.
In this state, the second valve portion 173 is seated on the valve seat surface 152 of the second valve seat member 150, and the flow path 151 of the second valve seat member 150 is closed. Further, the first valve portion 172 is separated from the valve seat surface 142 of the first valve seat member 140, and the flow path 141 of the first valve seat member 140 is opened.
Thereby, the first switching valve 15 at the time of energization shuts off the upstream side and the downstream side of the first main hydraulic pressure passage 10a, while the downstream side of the first communication hydraulic pressure passage 10c and the first main hydraulic pressure passage 10a. (See FIG. 2).

  Next, a process of assembling the valve member 170 and the second valve seat member 150 in the fixed core 110 in the method of manufacturing the first switching valve 15 of the present embodiment will be described.

In the manufacturing method of the present embodiment, as shown in FIG. 7, the fixed core 110 is prepared, and the fixed core 110 is arranged so that the base end opening 113c opens upward. Then, the first valve seat member 140 is pressed into the center hole 113 to fix the first valve seat member 140 at a predetermined position in the fixed core 110.
On the other hand, the valve body member U and the spring member 180 are held by the second valve seat member 150 by the guide member 160 to form the valve body unit U in advance.

After fixing the first valve seat member 140 in the fixed core 110, the valve body unit U is inserted into the center hole 113, and the second valve seat member 150 is pressed into the center hole 113.
At this time, since the valve member 170 is inserted into the center hole 113 from the guide member 160 side, the valve member 170 and the spring member 180 are arranged below the second valve seat member 150. In this state, the engaging portion 171d of the valve member 170 is engaged with the distal end wall portion 163 of the guide member 160, so that the state in which the valve member 170 and the spring member 180 are held in the guide member 160 can be maintained. it can.

  Then, as shown in FIG. 3, by fixing the second valve seat member 150 at a predetermined position in the center hole 113, the valve member 170 can be arranged at a predetermined position in the center hole 113. The first valve portion 172 of the member 170 is seated on the valve seat surface 142 of the first valve seat member 140.

In the first switching valve 15 described above, as shown in FIG. 5A, the valve body member 170, the spring member 180, the guide member 160, and the second valve seat member 150 are integrally formed. Thereby, when manufacturing the first switching valve 15, as shown in FIG. 7, the valve body member 170, the spring member 180, the guide member 160, and the second valve seat member 150 are used as one valve body unit U, and the fixed core 110 can be assembled.
Therefore, in the first switching valve 15 (see FIG. 3) of the present embodiment, the assemblability of parts can be improved, and the productivity of the first switching valve 15 can be improved.

  The valve member 170 includes a spring receiving portion 173c to which the end of the spring member 180 is fitted, a sliding surface 171c slidable on the guide member 160, and an engaging portion 171d engaging with the guide member 160. Are formed, so that each component of the valve body unit U can be easily assembled.

In the first switching valve 15, as shown in FIG. 3, it is not necessary to externally fit the retainer and the spring member on the first valve seat member 140, so that the radial size of the first valve seat member 140 is sufficiently secured. can do.
In the first switching valve 15, since the shapes of the two valve portions 172 and 173 can be formed independently, the shapes of the valve seat members 140 and 150 are not limited by the shape of the valve member 170.
Therefore, in the first switching valve 15, the degree of freedom of the shape of the valve seat surface 142 of the first valve seat member 140 and the shape of the flow path 141 can be increased.

  Then, as in the present embodiment, by making the seal outer diameter L1 of the first valve portion 172 larger than the seal diameter L2 of the second valve portion 173 (see FIG. 6B), the first valve seat member 140 is formed. Of the flow path 141 of the second valve seat member 150 can be larger than the axial cross-sectional area of the flow path 151 of the second valve seat member 150, and the flow rate of the brake fluid passing through the first valve seat member 140 can be increased. it can.

  Also, by increasing the seal diameter L1 of the first valve portion 172 (see FIG. 6B), the area where the first valve portion 172 abuts on the valve seat surface 142 can be reduced, and the second valve portion 173 can reduce the valve seat surface. The area of contact with the first valve seat member 140 can be increased, and the sealing performance of the first valve portion 172 with respect to the first valve seat member 140 can be enhanced while increasing the flow rate of the brake fluid passing through the first valve seat member 140. .

Further, as in the present embodiment, by increasing the seal diameter L1 of the first valve portion 172 (see FIG. 6B), the opening angle of the valve seat surface 142 of the first valve seat member 140 is increased. Accordingly, the first valve portion 172 can be stably seated on the valve seat surface 142 of the first valve seat member 140.
As shown in FIG. 6A, by forming the contact surface 173 b of the second valve portion 173 on a part of the spherical surface, the second valve portion 173 can be connected to the valve seat surface 152 of the second valve seat member 150. Can be stably seated.

  In the first switching valve 15, as shown in FIG. 5A, since the valve member 170 slides on the inner peripheral surface 161a (guide surface 161b) of the guide member 160, the valve member 170 is stably moved. Can be done.

  In the first switching valve 15, as shown in FIG. 3, since the lower end surface of the movable rod 121 that moves in conjunction with the movable core 120 is in contact with the flat distal end surface 172 a of the first valve portion 172, it is movable. The rod 121 can be stably brought into contact with the first valve portion 172. In addition, since the movable rod 121 and the first valve portion 172 are in surface contact with each other, the movable rod 121 is less likely to be worn, so that the degree of freedom of the material of the movable rod 121 can be increased. Cost can be reduced.

In the first switching valve 15, a flow path 119 is formed between the inner peripheral surface of the center hole 113 and the outer peripheral surface of the guide member 160. Therefore, as shown in FIG. 4, when the brake fluid flows from the first communication hole 114 to the second communication hole 115, the brake fluid flows through the flow path 119 outside the guide member 160. The brake fluid can be prevented from hitting the spring member 180.
Thus, the degree of freedom in designing the spring member 180 can be increased. Therefore, it is not necessary to increase the rigidity of the spring member 180 beyond the rigidity required for the spring member 180 in order to support the valve member 170, so that the spring member 180 can be downsized.
In addition, since the urging force of the spring member 180 can be suppressed, the electric power of the coil 130 required to move the movable core 120 against the urging force of the spring member 180 can be reduced.

According to the vehicle brake fluid pressure control device A of the present embodiment, as shown in FIG. 1, since the switching valves 15 and 16 are used, the productivity of the vehicle brake fluid pressure control device A is improved. be able to.
According to the vehicle brake fluid pressure control device A of the present embodiment, the switching valves 15 and 16 can be stably opened and closed, and a sufficient flow rate of the brake fluid passing through the switching valves 15 and 16 can be ensured. Therefore, the brake of the vehicle can be favorably controlled.

  According to the method for manufacturing the first switching valve 15 of the present embodiment, as shown in FIG. 7, the valve member 170, the spring member 180, the guide member 160, and the second valve seat member 150 are formed as one valve unit U. Since it is assembled in the fixed core 110, the productivity of the first switching valve 15 can be improved.

As described above, the embodiments of the present invention have been described, but the present invention is not limited to the above embodiments, and can be appropriately changed without departing from the gist of the present invention.
In the present embodiment, as shown in FIG. 5B, the guide member 160 is formed in a cylindrical shape, but the shape of the guide member 160 is not limited.
For example, a base member attached to the second valve seat member 150, a distal end portion engaged with the valve body member 170, and a connecting member connecting the proximal end portion and the distal end portion constitute a guide member. The valve member 170 and the spring member 180 may be accommodated between the end and the tip.

  In the first switching valve 15 of the present embodiment, as shown in FIG. 3, the first valve seat member 140 and the first valve portion 172 are arranged on the first communication hydraulic pressure passage 10c side, and the first main hydraulic pressure passage 10a The second valve seat member 150 and the second valve portion 173 are disposed on the upstream side of the second valve seat member. However, the second valve seat member 150 and the second valve portion 173 are disposed on the first communication hydraulic pressure passage 10c side, and the first valve seat member 140 and the first valve portion 172 are disposed on the upstream side of the first main hydraulic pressure passage 10a. May be arranged.

  In the first switching valve 15 of the present embodiment, as shown in FIG. 6B, the seal diameter L1 of the first valve portion 172 is set to be larger than the seal diameter L2 of the second valve portion 173. The seal diameter L2 of the second valve portion 173 can be set to be larger than the seal diameter L1 of the one valve portion 172. Thus, the solenoid valve of the present invention is configured such that the seal diameter L1 of the first valve portion 172 and the seal diameter L2 of the second valve portion 173 are different.

  In the first switching valve 15 of the present embodiment, as shown in FIG. 3, the movable core 120 and the movable rod 121 are formed separately, but the movable core 120 and the movable rod 121 are formed integrally. Is also good.

  In the present embodiment, as shown in FIG. 1, a case is described in which the solenoid valve of the present invention is applied to the switching valves 15 and 16 of the vehicle brake fluid pressure control device A. The present invention can be applied to various hydraulic pressure control devices.

Reference Signs List 10 Base 10a First main hydraulic path 10b Second main hydraulic path 10c First connecting hydraulic path 10d Second connecting hydraulic path 10e Branch hydraulic path 11 Mounting hole 15 First switching valve 16 Second switching valve 17 Normal Closed solenoid valve 20 Master cylinder 30 Stroke simulator 50 Control device 60 Slave cylinder 70 Motor 80 Drive transmission section 110 Fixed core 111 Insertion section 112 Projection section 113 Center hole 113a Small diameter hole 113b Large diameter hole 113c Base end opening 114 Serial communication hole 115 Second communication hole 117 Locking member 119 Flow path 120 Movable core 121 Movable rod 123 Communication groove 130 Coil 140 First valve seat member 141 Flow path 142 Valve seat surface 150 Second valve seat member 151 Flow path 152 Valve seat surface 153 Mounting portion 160 Guide member 161 Cylindrical portion 161b Guide surface 16 3 Front wall portion 164 Third communication hole 165 Insertion hole 170 Valve body member 171 Body portion 171c Sliding surface 171d Engaging portion 172 First valve portion 172b Contact surface 173 Second valve portion 173b Contact surface 173c Spring receiving portion 180 Spring member 190 Cover member A Vehicle brake fluid pressure control device A1 Fluid pressure generation device A2 Motor cylinder device A3 Fluid pressure control device P Brake pedal U Valve body unit W Wheel cylinder

Claims (8)

A fixed core in which a flow path is formed,
A movable core provided movably with respect to the fixed core,
A coil for moving the movable core by electromagnetic force,
A first valve seat member and a second valve seat member fixed in the fixed core,
A valve body member disposed between the first valve seat member and the second valve seat member,
A solenoid member of a two-position three-way valve , comprising: a spring member interposed between the valve body member and the second valve seat member ,
The valve body member,
The main body,
A first valve portion formed at one end of the main body portion and seated on a valve seat surface of the first valve seat member;
A second valve portion projected from the other end of the main body portion and seated on a valve seat surface of the second valve seat member,
The valve body member, by the biasing force of the spring member, the first valve portion is seated on the valve seat surface of the first valve seat member,
When the valve member is pushed out by the movable core, the first valve portion is separated from the first valve seat member, and the second valve portion is seated on the valve seat surface of the second valve seat member. It is configured as
The valve body member and the spring member are held by the second valve seat member by a guide member that regulates separation of the valve body member from the second valve seat member ,
The main body, the second valve and the spring member are housed in the guide member,
The first valve portion is inserted through an insertion hole formed in a distal end wall portion of the guide member and projects from the guide member,
A communication hole opened to the inner peripheral surface of the fixed core radially outside of the guide member, and the opening of the first valve seat member, the inner peripheral surface of the fixed core and the outer peripheral surface of the guide member, Solenoid valve characterized in that it communicates through the gap .   The electromagnetic valve according to claim 1, wherein the guide member has a guide surface on which the valve member can slide. The valve body member,
A spring receiving portion to which an end of the spring member is fitted;
A sliding surface slidable on the guide member,
The solenoid valve according to claim 1, further comprising: an engagement portion that engages with the guide member. Area wherein the first valve portion abuts against the front Stories valve seat surface of the first valve seat member, said second valve portion is larger than the area in contact with the valve seat surface of the second valve seat member The solenoid valve according to any one of claims 1 to 3, wherein: Comprising a movable rod that moves in conjunction with the movable core,
A flat surface is formed on the first valve portion,
Solenoid valve according to any one of claims 1 to 4, characterized in that the end face of the movable rod to the flat surface abuts. Solenoid valve according to any one of claims 1 to 5, wherein a part of the spherical surface is formed on the front Stories tip of the second valve part. A vehicle brake fluid pressure control device disposed between a master cylinder and a wheel cylinder,
A slave cylinder that generates brake fluid pressure by driving an electric actuator;
And the solenoid valve according to any one of claims 1 to 6 ,
The solenoid valve,
A state in which the valve body member is seated on a valve seat surface of the first valve seat member, and the master cylinder and the wheel cylinder communicate with each other;
A vehicle brake fluid pressure control device, wherein the valve body member is seated on a valve seat surface of the second valve seat member, and switches between a state in which the slave cylinder is in communication with the wheel cylinder. It is a manufacturing method of the solenoid valve according to any one of claims 1 to 6 ,
Fixing the first valve seat member in the fixed core;
The second valve seat member is fixed in the fixed core with the valve member and the spring member held by the second valve seat member by the guide member, and the valve member is connected to the first valve. Sitting on a valve seat surface of a seat member.

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