JP4613907B2 - solenoid valve - Google Patents

Description

  The present invention relates to an electromagnetic valve, and more particularly to an electromagnetic valve suitable as a hydraulic control valve used in a hydraulic circuit such as a brake device.

  2. Description of the Related Art Conventionally, there has been known a brake device that applies a braking force to a wheel by generating a hydraulic pressure in a hydraulic circuit according to an operation force of a brake pedal and supplying the hydraulic pressure to a wheel cylinder. Such a brake device is provided with an electromagnetic valve such as a pressure increasing valve or a pressure reducing valve in front of the wheel cylinder. By controlling the opening and closing of these electromagnetic valves, the amount of hydraulic fluid supplied to and discharged from the wheel cylinder can be reduced. The hydraulic pressure is controlled by adjusting, and an appropriate braking force is applied to each wheel.

  Such a solenoid valve is configured by integrally assembling a body incorporating a valve portion and a solenoid. A valve seat is provided in a passage through which hydraulic fluid is introduced and led out inside the body, and a valve body that can be attached to and detached from the valve seat to open and close the valve portion is disposed. The valve body is supported by a plunger constituting a solenoid so as to be able to operate integrally.

  For example, in the case of a normally closed solenoid valve, when the solenoid is energized, a suction force (hereinafter also referred to as “solenoid force”) is generated between the fixed iron core of the solenoid and the plunger, and the valve element is the valve. Operates in the valve opening direction away from the seat. Between the plunger and the fixed iron core, a spring that biases the plunger and thus the valve body against the solenoid force in the valve closing direction to be separated from the fixed iron core is interposed. For this reason, when the energization to the solenoid is interrupted, the valve body is seated on the valve seat and maintains the valve closed state. During control in which the solenoid is energized, the valve opening is adjusted so that the force due to the differential pressure applied to the valve body, the solenoid force, and the load due to the spring are balanced.

  By the way, such a solenoid valve generally has a problem of self-excited vibration due to fluctuations in the differential pressure between the front and rear due to operation of a brake pedal or the like. For example, when attempting to start from a state where the vehicle is stopped with the brake applied, when the operation of the brake pedal is loosened, the hydraulic fluid flows from the brake cylinder into the reservoir by opening control of the pressure reducing valve. In this case, if the differential pressure before and after the pressure reducing valve is large, the flow rate of the working fluid flowing through the pressure reducing valve per unit time increases, so that stable pressure reduction is difficult to be performed at a constant rate, and the pressure reducing valve vibrates by itself. There is a case. Also in other solenoid valves such as a pressure booster valve, the problem of self-excited vibration can similarly occur due to the large fluctuation in the differential pressure across the valve. This self-excited vibration is promoted by bubbles precipitated from the working fluid.

  That is, when the solenoid is energized and the valve element is separated from the valve seat along with the operation of the plunger, the hydraulic fluid flows from the high pressure primary pressure side to the low pressure secondary pressure side through the valve portion. At this time, the hydraulic fluid introduced from the valve portion into the valve chamber passes through the communication passage formed in the plunger and flows into the spring chamber on the opposite side of the valve chamber so that the pressure before and after the plunger is eventually balanced. Works. However, when the hydraulic fluid is thus released from the high pressure side to the low pressure side via the valve portion, the gas dissolved under high pressure in the hydraulic fluid may precipitate and become bubbles. When the bubbles are introduced into the spring chamber together with the hydraulic fluid, the oil amount rigidity on the spring chamber side of the plunger is lowered, and a differential pressure acts on the plunger, so that self-excited vibration is likely to occur.

  On the other hand, for example, a technique has been proposed in which a member that covers the communication path of the plunger is provided to suppress intrusion of bubbles (for example, see Patent Document 1).

This solenoid valve is provided with a cap that covers the communication path at the tip of the plunger. A ball constituting the valve body is held at the distal end portion of the cap, and a flange portion that extends outward in the radial direction and covers the communication path is formed on the proximal end portion side. A part of the hydraulic fluid introduced into the valve chamber flows into the communication path through a notch formed between the flange portion and the tip end surface of the plunger, but the inflow of bubbles is prevented as much as possible. ing.
JP 2006-194324 A

  However, since such a solenoid valve does not positively discharge the generated bubbles to the outside, the effect of preventing the introduction of bubbles to the spring chamber side is limited to some extent. Further, since the generated bubbles may stay around the cap, the bubbles may hinder the introduction of the working fluid to the spring chamber side.

  The present invention has been made in view of such problems, and an object thereof is to provide an electromagnetic valve capable of effectively suppressing self-excited vibration with a relatively simple configuration.

  In order to solve the above problems, an electromagnetic valve according to an aspect of the present invention includes a valve portion that is controlled to be opened and closed by a solenoid. This solenoid valve is provided with a valve part inside, and can be attached to and detached from a body formed with an internal / external communication hole for leading the hydraulic fluid that has passed through the valve part to the outside, and a valve seat provided inside the body. The valve body is arranged to open and close the valve part, and the inside of the body is divided into a valve chamber on the valve part side and a back pressure chamber on the opposite side of the valve part. A predetermined communication passage that communicates with the chamber is formed, and the valve body is supported on the valve chamber side, while the back pressure chamber side is opposed to the solenoid fixed iron core, and the plunger is arranged in the valve closing direction. Energizing means for energizing, and a passage forming portion that is disposed in the valve chamber so as to be rotatable about the axis of the plunger and guides the working fluid that has passed through the valve portion to a predetermined region in the rotation direction to the inner and outer communication holes And a guide member provided.

  The guide member is arranged so as to cover the communication passage from the valve chamber side, and has a center of gravity at a position shifted from the rotation center thereof, and is positioned in the rotation direction by the gravity, so that the passage forming portion is It is hold | maintained so that a part and an internal / external communication hole may be connected.

  Here, the “valve portion” means a portion that is configured by a valve body and a valve seat and opens and closes a passage through which hydraulic fluid flows. Further, the “guide member” may be provided separately from the plunger and displaced relative to the plunger, or may be provided integrally with the plunger and operate together with the plunger. However, the former is preferable in that the guide member itself can be made small, so that positioning in the rotational direction due to gravity imbalance can be achieved quickly. Furthermore, the “communication path” may be a through hole provided in the plunger, for example, or may be a path formed between the outer surface of the plunger and the inner surface of the body. However, the former is preferable in realizing the configuration covered from the valve chamber side by the guide member.

  In this aspect, the flow rate of the hydraulic fluid introduced from the upstream side is adjusted at the valve portion, and is led out to the outside through the inner and outer communication holes. At that time, the hydraulic fluid is positively guided to the internal / external communication passage along the passage formation portion provided in the guide member. Part of the hydraulic fluid that has flowed into the valve chamber is introduced into the back pressure chamber via the communication path, thereby balancing the pressure before and after the plunger.

  According to this aspect, the guide member is configured to be rotatable around the axis of the plunger, while its center of gravity is deviated from the rotation center, so that the weight distribution differs in the rotation direction. In this case, this center of gravity deviation (eccentricity) is used, and when the guide member is held at a predetermined position in the rotation direction by gravity, the passage forming portion has a positional relationship that allows the valve portion and the inner and outer communication holes to communicate with each other. ing. That is, the guide member can rotate around the axis of the plunger in the body, but moves autonomously by its gravity, and the position in the rotation direction settles at a predetermined position that satisfies the above positional relationship. On the other hand, the guide member has a shape that covers the communication path from the valve chamber side. For this reason, even if bubbles are generated from the hydraulic fluid that has passed through the valve portion, the bubbles are positively guided along with the hydraulic fluid along the guide member to the inner and outer communication holes. Therefore, introduction of bubbles into the back pressure chamber can be prevented or effectively suppressed. This guide member can be realized by a simple configuration in which the weight distribution in the rotation direction is biased.

  Specifically, the guide member may be extrapolated rotatably on a valve body extending from the plunger. In this aspect, the guide member can rotate the valve element supported by the plunger like a bearing, and the configuration is simplified.

  Moreover, the guide member may be provided with an eccentric member for shifting the center of gravity inside thereof. By using a material that is heavier than the material of the main body of the guide member as the eccentric member, the effect of shifting the center of gravity of the guide member can be increased, and the guide member can be held in place more quickly.

  The electromagnetic valve as described above is configured in a horizontal installation type so that the axis of the plunger is substantially horizontal, and the effect is obtained when the inner and outer communication holes are formed to open upward at the side of the body. Can be exhibited more remarkably. Since the bubbles are lighter than the working fluid and tend to move upward, the bubbles can be efficiently discharged by providing an opening in the upper part.

  According to the solenoid valve of the present invention, self-excited vibration can be effectively suppressed with a relatively simple configuration.

  The best mode for carrying out the present invention will be described below in detail with reference to the drawings.

[First Embodiment]
FIG. 1 is an explanatory diagram showing a hydraulic circuit of a brake device to which the solenoid valve according to the first embodiment of the present invention is applied.
The brake device 10 constitutes an electronically controlled brake system for a vehicle, and controls the four-wheel brakes of the vehicle independently and optimally based on the amount of operation of the brake pedal 12 by the driver.

  The brake pedal 12 is connected to a master cylinder 14 that sends out brake fluid as hydraulic fluid in response to a depression operation by the driver. The brake pedal 12 is provided with a stroke sensor 46 for detecting the depression stroke. One output port of the master cylinder 14 is connected to a stroke simulator 24 that creates a reaction force according to the operating force of the brake pedal 12 by the driver. A simulator cut valve 23 is provided in the flow path connecting the master cylinder 14 and the stroke simulator 24. The master cylinder 14 is connected to a reservoir tank 26 for storing brake fluid.

  A brake hydraulic pressure control pipe 16 for the right front wheel is connected to one output port of the master cylinder 14. The brake hydraulic pressure control pipe 16 is connected to a wheel cylinder 20FR for the right front wheel. A brake hydraulic pressure control pipe 18 for the left front wheel is connected to the other output port of the master cylinder 14. The brake hydraulic pressure control pipe 18 is connected to a wheel cylinder 20FL for the left front wheel. The brake hydraulic control pipe 16 for the right front wheel is provided with a right electromagnetic open / close valve 22FR, and the brake hydraulic control pipe 18 for the left front wheel is provided with a left electromagnetic open / close valve 22FL. These right solenoid on-off valve 22FR and left electromagnetic on-off valve 22FL are normally open solenoid valves that are open when not energized and switched to closed when energized.

  The brake hydraulic control pipe 16 for the right front wheel is provided with a right master pressure sensor 48FR that detects the master cylinder pressure on the right front wheel side, and the brake hydraulic control pipe 18 for the left front wheel has a left front wheel side. A left master pressure sensor 48FL for measuring the master cylinder pressure is provided.

  On the other hand, one end of a hydraulic supply / discharge pipe 28 is connected to the reservoir tank 26. A suction port of an oil pump 34 driven by a motor 32 is connected to the other end of the hydraulic supply / discharge pipe 28. The discharge port of the oil pump 34 is connected to the high pressure pipe 30. An accumulator 50 and a relief valve 53 are connected to the high pressure pipe 30.

  The accumulator 50 stores the brake fluid boosted by the oil pump 34. When the pressure of the brake fluid in the accumulator 50 increases abnormally, the relief valve 53 is opened, and the high-pressure brake fluid is returned to the hydraulic supply / discharge pipe 28. Further, the high-pressure pipe 30 is provided with an accumulator pressure sensor 51 that detects the outlet pressure of the accumulator 50.

  The high pressure pipe 30 is connected to the right front wheel wheel cylinder 20FR, the left front wheel wheel cylinder 20FL, the right rear wheel wheel cylinder 20RR, and the left rear wheel through the pressure increasing valves 40FR, 40FL, 40RR, 40RL. It is connected to the cylinder 20RL. Hereinafter, the wheel cylinders 20FR to 20RL will be collectively referred to as “wheel cylinders 20”, and the pressure increase valves 40FR to 40RL will be appropriately collectively referred to as “pressure increase valves 40”. The pressure increasing valve 40 is a normally closed electromagnetic flow control valve (linear valve) that is closed when not energized and is used for pressure increasing of the wheel cylinder 20 as necessary.

  Further, the wheel cylinder 20FR for the right front wheel and the wheel cylinder 20FL for the left front wheel are connected to the hydraulic supply / discharge pipe 28 via the pressure reducing valve 42FR or 42FL, respectively. The pressure reducing valves 42FR and 42FL are normally closed electromagnetic flow control valves (linear valves) used for pressure reduction of the wheel cylinders 20FR and 20FL as necessary. On the other hand, the wheel cylinder 20RR for the right rear wheel and the wheel cylinder 20RL for the left rear wheel are connected to the hydraulic supply / discharge pipe 28 via a pressure reducing valve 42RR or 42RL which is a normally open electromagnetic flow control valve. . Hereinafter, the pressure reducing valves 42FR to 42RL are collectively referred to as “pressure reducing valve 42” as appropriate.

  Wheel cylinders for detecting the wheel cylinder pressure, which is the pressure of the brake fluid acting on the corresponding wheel cylinder 20, in the vicinity of the wheel cylinders 20FR to 20RL for the right front wheel, the left front wheel, the right rear wheel, and the left rear wheel Pressure sensors 44FR, 44FL, 44RR and 44RL are provided.

  The right electromagnetic on-off valve 22FR and the left electromagnetic on-off valve 22FL, the pressure increasing valves 40FR to 40RL, the pressure reducing valves 42FR to 42RL, the oil pump 34, the accumulator 50, and the like constitute the hydraulic actuator 80 of the brake device 10. The hydraulic actuator 80 is controlled by the ECU 200.

  In the brake device 10, the ECU 200 calculates the target deceleration of the vehicle from the pedal stroke indicating the depression amount of the brake pedal 12 and the master cylinder pressure, and the target of the wheel cylinder pressure of each wheel according to the calculated target deceleration. The target hydraulic pressure, that is, the target wheel cylinder pressure, is obtained. Then, the ECU 200 controls the pressure increasing valve 40 and the pressure reducing valve 42 so that the wheel cylinder pressure of each wheel becomes the target wheel cylinder pressure.

  When the accumulator pressure is less than the lower limit value of the preset control range, the oil pump 34 is driven by the ECU 200 to increase the accumulator pressure. When the accumulator pressure enters the control range, the drive of the oil pump 34 is stopped. Is done.

  Next, a specific configuration of the hydraulic control valve used as the pressure increasing valve 40 and the pressure reducing valve 42 will be described. FIG. 2 is a cross-sectional view illustrating the configuration of the hydraulic control valve according to the first embodiment. In the following description, the positional relationship of each component may be expressed on the basis of the illustrated state for convenience.

  The hydraulic control valve 101 is configured as an electromagnetic valve in which a body 102 provided with a valve portion therein and a solenoid 103 for controlling the opening degree of the valve portion are provided integrally.

  The body 102 has a stepped cylindrical shape, and is provided with an introduction port 104 for introducing brake fluid from the upstream side (primary pressure side) at the upper end opening, and downstream of the brake fluid at the side near the center in the longitudinal direction. A pair of lead-out ports 105 (corresponding to “internal / external communication holes”) leading to the side (secondary pressure side) are provided. A bottomed cylindrical valve seat member 106 is press-fitted into a passage communicating between the introduction port 104 and the outlet port 105, and a valve hole penetrating in the axial direction is provided at the center of the bottom of the valve seat member 106. 107 is provided. The opening on the outlet port 105 side of the valve hole 107 is formed in a tapered shape, and the valve seat 108 is formed by the tapered surface.

  A valve body 109 is disposed below the valve seat 108 in the body 102. The valve body 109 is composed of one end of a stepped columnar rod member 110 and is detachably disposed on the valve seat 108 from the outlet port 105 side. In the present embodiment, the rod member 110 itself can be regarded as a valve body.

  In addition, a filter 112 is attached to the upper end portion of the valve seat member 106 so as to cover the introduction port 104, thereby preventing foreign matter from entering the body 102. Similarly, a filter 113 is attached to the side portion of the body 102 so as to cover the outlet port 105.

  On the other hand, the solenoid 103 includes a cylindrical fixed iron core 121 joined to the lower end portion of the body 102, a columnar plunger 122 disposed in a space surrounded by the body 102 and the fixed iron core 121, and a fixed iron core 121. An electromagnetic coil 123 that is externally attached to the electromagnetic coil 123 and a case 124 that accommodates the electromagnetic coil 123 therein are provided. The case 124 has an upper end fixed to the lower end of the body 102 and a lower end fixed to the lower end of the fixed iron core 121. In the present embodiment, the combination of the body 102 and the fixed iron core 121 can be regarded as the body of the hydraulic control valve 101 as a whole. The plunger 122 divides the inside of the body into a valve chamber 141 on the valve portion side and a back pressure chamber 142 on the opposite side to the valve portion.

  The plunger 122 is provided with a connecting hole 126 at the center of the upper end surface. The valve body 109 is integrally fixed to the plunger 122 by press-fitting the end of the rod member 110 opposite to the valve body 109 into the connecting hole 126. The rod member 110 has a flange portion 111 slightly extending outward at the center thereof, and the press-fitting amount is regulated by the flange portion 111 abutting against the end surface of the plunger 122. In addition, a plurality of communication holes 127 (corresponding to “communication passages”) penetrating the plunger 122 in the axial direction are formed in the peripheral portion of the plunger 122, and the hydraulic fluid that has flowed into the valve chamber 141 communicates therewith. It is also introduced into the back pressure chamber 142 through the hole 127. The plunger 122 is disposed to face the fixed iron core 121 on the back pressure chamber 142 side.

  An air block (corresponding to a “guide member”) 130 having a cylindrical main body is inserted into the rod member 110. The air block 130 is formed by molding an iron core 136 inside a resin main body. Details of the structure will be described later.

  The fixed iron core 121 has a bottomed cylindrical shape, and its inner diameter is gradually reduced toward the bottom. Between the bottom of the spring accommodating portion 128 formed on the fixed iron core 121 and the plunger 122, a spring 129 as an urging means for urging the plunger 122 in the upward valve closing direction is interposed.

FIG. 3 is a perspective view showing the configuration of the air block. For convenience of the following description, the air block 130 in the same figure is shown in a state inclined 90 degrees from the state shown in FIG.
The air block 130 has a stepped cylindrical main body 131 made of a resin material. One end side (plunger 122 side) of the main body 131 is an enlarged diameter portion 132 having an enlarged inner diameter, and is extrapolated to the flange portion 111 of the rod member 110 with a predetermined clearance. The end surface of the flange portion 111 can come into contact with the base end surface 133 of the enlarged diameter portion 132, and when the end surface of the flange portion 111 abuts, the air block 130 moves integrally with the plunger 122. On the other hand, the other end side of the main body 131 is formed with an insertion portion 134 that passes through the tip end portion of the rod member 110 along the axis L, and the circumferential half portion (the upper half portion in the figure) is formed. A cutout portion 135 is formed. As will be described later, the notch 135 constitutes a passage forming part that actively guides the hydraulic fluid that has passed through the valve part to one of the outlet ports 105. Furthermore, an iron core 136 as an eccentric member made of stainless steel square material is molded on the peripheral edge of the main body 131 opposite to the notch 135. In other words, the air block 130 is held at a predetermined position (shown) when the air block 130 rotates about the axis L due to a shift (eccentricity) of the center of gravity due to the notch 135 and the iron core 136 provided in the main body 131. It is comprised so that.

  Returning to FIG. 2, the air block 130 configured as described above can be rotated around the axis of the plunger 122 and advanced and retracted in the axial direction by being inserted through the rod member 110.

Next, the configuration and operation of the main part of the hydraulic control valve according to the present embodiment will be described. FIG. 4 is a conceptual diagram showing the operation of the hydraulic control valve of FIG. The figure shows a valve open state.
The hydraulic control valve 101 according to the present embodiment is configured as a horizontally installed type so that the axis L of the plunger 122 is substantially horizontal. Therefore, as shown in the figure, the hydraulic control valve 101 is installed in a state inclined about 90 degrees from the state shown in FIG. At this time, one of the pair of outlet ports 105 opens upward, and the other opens downward.

  The air block 130 is pressed against the plunger 122 by the differential pressure between the valve chamber 141 and the back pressure chamber 142 immediately after opening. At this time, the surface on one end side of the air block 130 is disposed so as to cover the communication hole 127 from the valve chamber 141 side. On the other hand, the air block 130 is rotatable around the axis L, but is settled so that the portion on the iron core 136 side is lowered due to the shift of the center of gravity due to the notch 135 and the iron core 136 described above. At this time, as illustrated, a lead-out passage 161 that smoothly connects the valve portion and the upper lead-out port 105 is formed along the notch 135 of the air block 130. For this reason, as indicated by the arrows in the figure, the hydraulic fluid that has passed through the valve portion is guided to the derivation port 105 along the derivation passage 161 and is external to the hydraulic pressure control valve 101 (on the secondary pressure side of the hydraulic circuit). Discharged into the piping). On the other hand, since the lower part of the air block 130 substantially closes the lower outlet port 105 at this time, the flow of the hydraulic fluid is naturally directed to the outlet passage 161 side. As a result, even if bubbles are generated from the hydraulic fluid that has passed through the valve section, the bubbles are guided to the upper outlet port 105 and discharged together with the hydraulic fluid. In this case, since the lead-out portion is on the upper side, it is possible to suppress the bubbles from staying in the body 102.

  Since there are appropriate clearances between the air block 130 and the rod member 110, between the air block 130 and the plunger 122, and between the air block 130 and the inner peripheral surface of the body 102, the hydraulic fluid Since itself is introduced to the back pressure chamber 142 side through the clearance and the communication hole 127, the differential pressure between the valve chamber 141 and the back pressure chamber 142 is gradually eliminated, and the operation of the plunger 122 is stabilized.

  When the energization of the solenoid 103 is stopped, the plunger 122 moves in the valve closing direction and the valve body 109 is seated on the valve seat 108. At this time, since a sufficient space is provided between the valve seat member 106 and the plunger 122, the air block 130 is not sandwiched between the two to prevent the transition to the valve closed state. On the other hand, since the distance between the valve seat member 106 and the plunger 122 is defined to some extent, even if the air block 130 is separated from the plunger 122 and displaced toward the valve portion, the air block 130 moves toward the valve seat member 106. The amount of displacement is regulated by hitting. Further, even when the air block 130 is displaced to the limit position where it abuts against the valve seat member 106 in this way, the formation state of the lead-out passage 161 is maintained, so the air block 130 is displaced in the axial direction. Even then, the bubbles can pass through the outlet port 105.

  As described above, in the hydraulic control valve 101 of the present embodiment, the air block 130 is disposed so as to cover the communication hole 127 of the plunger 122 from the valve chamber 141 side. On the other hand, the center of gravity of the air block 130 is shifted from the center of rotation due to the shape of the air block 130 and the iron core 136 being embedded, so that the rotational position is always settled at the same position. The light-weight cutout portion 135 always forms a lead-out passage 161 between the lead-out port 105 opened upward and the valve portion. For this reason, even if bubbles are generated from the hydraulic fluid that has passed through the valve portion, the bubbles are positively guided along the outlet passage 161 to the outlet port 105 and discharged together with the hydraulic fluid. Therefore, introduction of bubbles into the back pressure chamber 142 can be prevented or effectively suppressed, and the occurrence of self-excited vibration can be prevented or suppressed.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The hydraulic control valve according to the present embodiment is different from the hydraulic control valve according to the first embodiment in the structure for discharging bubbles to the outside. However, the configuration of the hydraulic brake device to be applied and the approximate configuration of the hydraulic control valve are the same. For this reason, about the component similar to the said 1st Embodiment, the same code | symbol is attached | subjected as needed, and the description is abbreviate | omitted suitably.

FIG. 5 is a cross-sectional view illustrating a configuration of a hydraulic control valve according to the second embodiment.
The hydraulic control valve 201 is provided with an air guard 230 for directing the flow of bubbles instead of the air block 130 as shown in FIG.

  The air guard 230 has a bottomed cylindrical main body 231 made of stainless steel, and is press-fitted in the vicinity of the rod member 110 in the body 102. The main body 231 has an inner diameter larger than the outer diameter of the flange portion 111 of the rod member 110, and an insertion hole 232 through which the tip end portion of the rod member 110 is inserted is formed in the upper bottom portion. Further, the valve portion side surface of the main body 231 has a tapered outer edge portion so as to be smoothly connected to the outlet port 105. The air guard 230 is disposed at a position so as not to interfere with the plunger 122 and the rod member 110 when the valve portion is opened and closed.

  Note that the installation mode of the hydraulic pressure control valve 201 according to the present embodiment is not limited to the state shown in FIG. 5, and may be an upside down installation mode as illustrated, or as in the first embodiment. It may be installed horizontally.

  In the hydraulic pressure control valve 201 of the present embodiment, part of the hydraulic fluid that has passed through the valve portion is introduced to the back pressure chamber 142 side through the clearance between the insertion hole 232 and the tip portion of the rod member 110. Is done. However, since the clearance is formed on the inner side, the clearance area of the clearance is very small, so even if bubbles are generated from the hydraulic fluid that has passed through the valve, Introduction to the 142 side is prevented. The bubbles are guided to the outlet port 105 along the surface of the air block 130 together with the hydraulic fluid and discharged.

[Third Embodiment]
Next, a third embodiment of the present invention will be described. The hydraulic control valve according to the present embodiment is also different from the hydraulic control valve according to the first embodiment in the structure for discharging bubbles to the outside. However, the configuration of the hydraulic brake device to be applied and the approximate configuration of the hydraulic control valve are the same. For this reason, about the component substantially the same as the said 1st Embodiment, the same code | symbol is attached | subjected as needed, and the description is abbreviate | omitted suitably.

FIG. 6 is a cross-sectional view illustrating a configuration of a hydraulic control valve according to the third embodiment.
The hydraulic control valve 301 has a function of directing the flow of bubbles by the shape of the rod member 310 instead of the air block 130 as shown in FIG.

  The rod member 310 has a flange portion 311 extending to the vicinity of the inner surface of the body 102, and an outer edge portion of the rod member 310 is raised to the valve portion side so that the valve portion side is smoothly connected to the outlet port. A surface 312 is formed.

  Note that the installation mode of the hydraulic pressure control valve 301 according to the present embodiment is not limited to the state shown in FIG. 6, and may be an upside down installation mode as illustrated, or as in the first embodiment. It may be installed horizontally.

  In the hydraulic pressure control valve 301 according to the present embodiment, a part of the hydraulic fluid that has passed through the valve portion passes through the clearance between the flange portion 311 of the rod member 310 and the inner surface of the body 102 and is on the back pressure chamber 142 side. To be introduced. However, since the guide surface 312 is formed on the rod member 310, even if bubbles are generated from the hydraulic fluid that has passed through the valve portion, the bubbles together with the hydraulic fluid travel along the guide surface 312 to the outlet port 105. Guided and discharged.

  The present invention is not limited to the above-described embodiments, and various modifications such as design changes can be added to the embodiments based on the knowledge of those skilled in the art. Embodiments to which is added can also be included in the scope of the present invention.

  For example, in the first embodiment, an example is shown in which the main body 131 of the air block 130 is made of a resin material and a stainless steel core 136 is embedded as an eccentric member. However, at least one of them is made of a different material. May be. At this time, a material having a weight density larger than that of the main body 131 is used as the eccentric member.

  In the first embodiment, the shape of the notch 135 of the air block 130 is a shape in which a half of the circumferential direction is notched. However, the lead-out passage 161 can function in the holding state of the air block 130. If possible, a smaller notch or hole may be used. Moreover, if a sufficient eccentric state is obtained by the shape of the main body 131 of the air block 130, the eccentric member does not have to be embedded therein.

It is explanatory drawing showing the hydraulic circuit of the brake device with which the solenoid valve which concerns on the 1st Embodiment of this invention is applied. It is sectional drawing showing the structure of the hydraulic control valve which concerns on 1st Embodiment. It is a perspective view showing the structure of an air block. It is a conceptual diagram showing operation | movement of the hydraulic-pressure control valve of FIG. It is sectional drawing showing the structure of the hydraulic control valve concerning 2nd Embodiment. It is sectional drawing showing the structure of the hydraulic control valve concerning 3rd Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Brake device, 20 Wheel cylinder, 40 Pressure increase valve, 42 Pressure reduction valve, 80 Hydraulic actuator, 101 Fluid pressure control valve, 102 Body, 103 Solenoid, 104 Introduction port, 105 Outlet port, 106 Valve seat member, 107 Valve hole, 108 Valve seat, 109 Valve body, 110 Rod member, 111 Flange part, 121 Fixed iron core, 122 Plunger, 127 Communication hole, 129 Spring, 130 Air block, 135 Notch part, 136 Iron core, 141 Valve chamber, 142 Back pressure chamber, 161 Guide passage, 200 ECU, 201 hydraulic control valve, 230 air guard, 301 hydraulic control valve, 310 rod member, 311 flange portion, 312 guide surface.

Claims (4)

An electromagnetic valve having a valve portion that is controlled to open and close by a solenoid,
A body in which the valve portion is provided, and an internal / external communication hole for leading the hydraulic fluid that has passed through the valve portion to the outside;
A valve body that is detachably disposed on a valve seat provided in the body and capable of opening and closing the valve portion;
A predetermined chamber which is disposed in the body and divides the body into a valve chamber on the valve portion side and a back pressure chamber on the opposite side of the valve portion, and communicates the valve chamber with the back pressure chamber. A plunger that forms a communication path and supports the valve element on the valve chamber side, and is arranged to face the fixed iron core of the solenoid on the back pressure chamber side;
Biasing means for biasing the plunger in the valve closing direction of the valve body;
The valve chamber is disposed so as to be rotatable around the axis of the plunger, and a passage forming portion is provided in a predetermined region in the rotation direction for guiding the working fluid that has passed through the valve portion to the inner and outer communication holes. A guide member;
With
The guide member is disposed so as to cover the communication path from the valve chamber side, and has a center of gravity at a position deviated from the rotation center thereof, and is positioned in the rotation direction by the gravity. An electromagnetic valve, wherein the forming portion is held so as to communicate the valve portion with the inner and outer communication holes.   The electromagnetic valve according to claim 1, wherein the guide member is rotatably inserted into a valve body extending from the plunger.   The electromagnetic valve according to claim 1, wherein the guide member includes an eccentric member for shifting the center of gravity inside the guide member. It is configured in a horizontal installation type so that the axis of the plunger is substantially horizontal,
The solenoid valve according to any one of claims 1 to 3, wherein the inner and outer communication holes are formed so as to open upward at a side portion of the body.

Images