JP5760961B2 - Hydraulic control valve device - Google Patents

Description

The present invention relates to a hydraulic control valve device using an electromagnetic linear valve capable of continuously controlling the valve opening amount in accordance with a current supplied to itself.

  The following patent document describes a hydraulic control valve device for controlling the hydraulic pressure of a brake cylinder, which includes an electromagnetic valve capable of continuously controlling the valve opening amount. Further, the hydraulic control valve device described in Patent Document 2 includes a pressure increasing linear valve and a pressure reducing linear valve that can continuously control the valve opening amount by continuously controlling the current supplied to the hydraulic pressure controlling valve device. It consists of The electromagnetic linear valve used for these pressure-increasing linear valves and pressure-decreasing linear valves includes: (a) the interior is divided into a first liquid chamber and a second liquid chamber, and the first liquid chamber and the second liquid chamber; And a housing filled with hydraulic fluid, and (b) movable in the axial direction, and functions as a valve seat along with the movement in the axial direction. There is an electromagnetic linear valve provided with a plunger disposed in the first liquid chamber so that one end portion functioning as a valve element closes the opening of the communication hole to the first liquid chamber. Such an electromagnetic linear valve having a plunger and a housing prohibits the flow of hydraulic fluid from the hydraulic fluid path on the high pressure side to the hydraulic fluid path on the low pressure side when the valve element is blocking the valve seat. In a state where a gap is generated between the valve body and the valve seat, the flow of the hydraulic fluid from the high-pressure side hydraulic fluid passage to the low-pressure side hydraulic fluid passage is permitted. Furthermore, the elastic body that biases the plunger in one of the direction in which the valve body approaches the valve seat and the direction in which the valve body moves away from the valve seat, and the plunger moves in a direction opposite to the direction in which the elastic body biases the plunger. And a coil that forms a magnetic field for controlling the amount of opening of the coil by controlling the amount of current supplied to the coil, in other words, the amount of hydraulic fluid in the hydraulic fluid path on the high-pressure side. Pressure difference (hereinafter sometimes referred to as “high-pressure side hydraulic fluid pressure”) and hydraulic fluid pressure in the low-pressure side hydraulic fluid passage (hereinafter sometimes referred to as “low-pressure side hydraulic fluid pressure”) It is possible to control.

JP 2001-260843 A JP 2005-145136 A

In the electromagnetic linear valve having the above structure, since the plunger is supported by the elastic body in the housing, there is a possibility that self-excited vibration may occur with the opening and closing of the valve. Various factors have been considered as the cause of the self-excited vibration of the plunger. For example, the action of the hydraulic fluid flowing into the housing from the high-pressure side hydraulic fluid path to the plunger is one of the factors causing the self-excited vibration. It is considered as one .

  Further, in many cases, an electromagnetic linear valve having the same structure is used for the pressure increasing linear valve and the pressure reducing linear valve provided in the hydraulic pressure control valve device. However, naturally, in the pressure increasing linear valve and the pressure reducing linear valve, the high-pressure side hydraulic fluid pressure, the low-pressure side hydraulic fluid pressure, and the differential pressure between them are different from each other. That is, each of the pressure-increasing linear valve and the pressure-reducing linear valve included in the fluid pressure control valve device has a high-pressure side hydraulic fluid pressure, a low-pressure side hydraulic fluid pressure, and a gap between them in order to suppress self-excited vibration of the plunger. It is desirable to determine the structure according to the differential pressure. The present invention has been made in view of such circumstances, and provides a hydraulic pressure control valve device including a pressure increasing linear valve and a pressure reducing linear valve that can effectively suppress self-excited vibration of the plunger in each. The task is to do.

The hydraulic pressure control valve device according to the present invention is premised on a first concave portion in which a convex portion projecting toward the core portion is formed at one end portion of the plunger, and one end portion of the plunger faces the end surface of the core portion facing the plunger. And an electromagnetic linear valve in which a second concave portion having a convex portion that faces the bottom surface of the first concave portion is formed.

The hydraulic control valve device according to the present invention includes: (A) a pressure-increasing linear device that is provided between the high-pressure source and the hydraulic fluid supply device and increases the hydraulic pressure of the hydraulic fluid supplied to the hydraulic fluid supply device. Including a valve, and (B) a linear valve for pressure reduction provided between the hydraulic fluid supply device and the low-pressure source and reducing the hydraulic pressure of the hydraulic fluid supplied to the hydraulic fluid supply device. Each of the pressure-increasing linear valve and the pressure-decreasing linear valve is an electromagnetic linear valve configured as described above, and the ratio of the axial dimension of the first concave portion of the core portion to the axial dimension of the convex portion of the plunger. Is defined as a convex-concave ratio, each of the electromagnetic linear valve used as a pressure-reducing linear valve and the electromagnetic linear valve used as a pressure-increasing linear valve is configured to have a different convex-concave ratio. .

In the hydraulic control valve device of the present invention, the convex-concave ratios of the pressure-increasing linear valve and the pressure-decreasing linear valve are different from each other, and even if the supplied current is the same, the core portion And the magnetic force generated between the plunger and the plunger is different. That is, the frictional force between the housing and the plunger is different. The hydraulic control valve device according to the present invention is, for example, in the case where the average magnitude of the current received by each of the pressure increasing linear valve and the pressure reducing linear valve is different from each other, Each of the pressure reducing linear valves can be configured to generate a frictional force having an appropriate magnitude, and the self-excited vibration of the plunger can be effectively suppressed.

Aspects of the Invention

  In the following, some aspects of the invention that can be claimed in the present application (hereinafter sometimes referred to as “claimable invention”) will be exemplified and described. As with the claims, each aspect is divided into sections, each section is numbered, and is described in a form that cites the numbers of other sections as necessary. This is merely for the purpose of facilitating the understanding of the claimable inventions, and is not intended to limit the combinations of the constituent elements constituting those inventions to those described in the following sections. In other words, the claimable invention should be construed in consideration of the description accompanying each section, the description of the embodiments, etc., and as long as the interpretation is followed, another aspect is added to the form of each section. In addition, an aspect in which constituent elements are deleted from the aspect of each item can be an aspect of the claimable invention.

The following items (1) to (7) are not claimable inventions, but are the terms showing the configuration of the electromagnetic linear valve that is the premise of the claimable invention, and the items (1) to (7) A mode in which the technical features described in any of the following items are added to the claimable invention. Of the claimable inventions in various forms, the combination of items (1), (11), and (12) corresponds to claim 1, and the technology described in claim 14 in claim 1 The feature added is equivalent to claim 2 , and the feature added to claim 2 with the technical feature described in (15) is equivalent to claim 3 .

(1) (a) a housing cylinder part formed in a cylindrical shape, (b) a core part formed so as to close one end of the housing cylinder part, and (c) the interior of the housing cylinder part, Partitioning into a first liquid chamber close to the core part and a second liquid chamber on the opposite side of the core part, and a partition part formed with a communication hole for communicating the first liquid chamber and the second liquid chamber; (d) an inflow port that communicates with the second liquid chamber and allows hydraulic fluid to flow into the second liquid chamber; and (e) communicates with the first liquid chamber and draws hydraulic fluid from the first liquid chamber. A housing having an outflow port for flowing out;
One end portion is opposed to the core portion and the other end portion is opposed to the opening of the communication hole, and is disposed in the first liquid chamber and is movable in the axial direction, and the other end portion is the communication hole. A plunger capable of being seated in the opening of
An elastic body that biases the plunger in one of a direction in which the other end thereof approaches the opening of the communication hole and a direction in which the plunger separates from the opening;
An electromagnetic linear valve provided with a coil disposed around the housing and forming a magnetic field for moving the plunger in a direction opposite to a direction in which the plunger is biased by the elastic body.

  As described above, this section is a section showing a configuration that is a premise of the claimable invention. That is, the aspect described in this section is an aspect in which basic components of the electromagnetic linear valve of the claimable invention are listed.

(2) The elastic body is
The electromagnetic linear valve according to item (1), wherein the plunger is urged in a direction in which the other end thereof approaches the opening of the connection hole.

  The electromagnetic linear valve described in this section is limited to a normally closed electromagnetic linear valve. It is known that the frequency of occurrence of self-excited vibration of the plunger is generally higher in the normally closed electromagnetic linear valve than in the normally open electromagnetic linear valve. Therefore, if the structure which suppresses the self-excited vibration of the plunger is added to the electromagnetic linear valve described in this section, the effect of suppressing the self-excited vibration is sufficiently utilized.

(3) The housing tube portion is
(a-1) a ferromagnetic cylinder formed into a cylindrical shape by a ferromagnetic material, and (a-2) a cylindrical shape formed from a non-magnetic material, with the core portion inserted into one end and the strong tube at the other end. A magnetic cylinder is inserted, and includes a non-magnetic cylinder that connects the core part and the ferromagnetic cylinder in a state where a gap is provided between the end face of the core part and the end face of the ferromagnetic cylinder. ,
The plunger is
Item (1) or (2) has a flange portion that protrudes in the radial direction from the outer peripheral surface, and the flange portion is positioned in the interval between the core portion and the ferromagnetic tube. The electromagnetic linear valve as described in the section.

  In the electromagnetic linear valve described in this section, a liquid chamber is formed between the ferromagnetic cylinder in the housing and the core portion, and a flange portion of the plunger is located in the liquid chamber. The liquid chamber between the ferromagnetic cylinder and the core part is partitioned by the flange part into a liquid chamber between the flange part and the ferromagnetic cylinder and a liquid chamber between the flange part and the core part. . That is, as the plunger moves, the flange moves in the liquid chamber, and the working fluid passes through the gap between the non-magnetic cylinder and the flange between the two liquid chambers partitioned by the flange. Circulate. That is, a resistance force is generated by the flow of the hydraulic fluid, and a damping force is applied to the movement of the plunger. Therefore, according to the electromagnetic linear valve described in this section, the self-excited vibration of the plunger can be suppressed by the damping force with respect to the movement of the plunger.

  The “flange” described in this section is not particularly limited in shape and size, and may be formed over the entire outer periphery of the plunger main body. It may be formed in the part. However, as described above, the electromagnetic linear valve described in this section generates a resistance force by causing the working fluid to flow through the gap between the flange portion and the nonmagnetic cylinder. "Is preferably an appropriate shape and size according to the inner shape, cross-sectional area, etc. of the non-magnetic cylinder.

(4) The plunger is
The electromagnetic linear valve according to (3), wherein a part of the flange portion comes into contact with the nonmagnetic cylinder when tilted with respect to the housing.

(5) The plunger is
When tilted with respect to the housing, a part of itself comes into contact with the end of the ferromagnetic cylinder on the core side, and the flange does not come into contact with the nonmagnetic cylinder ( The electromagnetic linear valve as described in the item 3).

  In the aspect described in the above two items, when the plunger is tilted in the housing in the seated state or the seated state, the contact portion between the plunger and the housing is limited. . In other words, it is limited whether or not the flange portion of the plunger contacts the nonmagnetic cylinder of the housing. Specifically, for example, in order to prevent magnetic adhesion between the plunger and the ferromagnetic cylinder, and to ensure smooth movement of the plunger, an annular formed of a non-magnetic material at a portion located inside the ferromagnetic cylinder of the plunger There is a case where the member is configured to be fitted. By adjusting the length of the annular member in the axial direction and the position in the axial direction, the contact portion between the plunger and the housing can be changed.

  Next, consider the case where the plunger is tilted while seated. In that case, the other end portion where the plunger is seated (hereinafter sometimes referred to as the seating portion) and the portion on the one end portion side of the plunger (hereinafter also referred to as the “contact portion”) are contacted with the housing. It will touch and be supported at two points. Since the suction force, which is the force that attracts the plunger by the core portion of the housing, acts not only in the axial direction but also in the radial direction, the frictional force depending on the radial component of the suction force is applied to the plunger contact portion. Arise. This frictional force is a resistance force when the valve is switched from the closed state to the open state, in other words, when the plunger starts to move from the seated state. If the frictional force at this time becomes large, the acceleration when the plunger is separated increases, and the valve opening amount may increase rapidly. This sudden increase in the valve opening amount causes the hydraulic fluid to rapidly flow from the second liquid chamber into the first liquid chamber, which may cause self-excited vibration of the plunger. That is, it is desirable that the frictional force when the plunger is separated is as small as possible.

  As described above, when current is supplied to the coil when the plunger is supported by the housing at the seating portion and the contact portion of the plunger, a suction force acts on one end portion facing the core portion of the plunger. Depending on the radial component of the suction force, a frictional force acts on the contact portion. That is, the radial component of the suction force is input to one end portion of the plunger with the seating portion (the other end portion) of the plunger as a fulcrum, and the contact portion serves as the action point. Since the action point is located between the fulcrum and the force point, the closer the action point is to the force point, the smaller the force acting on the action point. Therefore, the former aspect in which the flange portion and the nonmagnetic cylinder of the housing abut is compared with the latter aspect in which a part of the plunger is in contact with the end portion on the core portion side of the ferromagnetic cylinder. Therefore, the frictional force acting on the contact portion can be reduced.

  On the other hand, in the latter mode, since the flange portion is configured not to contact the non-magnetic cylinder, there is an axial deviation between the ferromagnetic cylinder and the core portion of the housing when the housing is assembled or welded. However, it is possible to avoid the influence.

(6) The plunger is formed with a convex portion protruding toward the core portion at the one end portion,
The core portion is formed with a first concave portion where the one end portion of the plunger enters the end surface facing the plunger, and a second concave portion where the convex portion enters the bottom surface of the first concave portion. The electromagnetic linear valve according to any one of items (1) to (4).

  In the electromagnetic linear valve described in this section, a stepped recess is formed in the core, a stepped protrusion is formed in the plunger, and the protrusion of the plunger enters the recess of the core. It is configured as follows. With such a configuration, the electromagnetic linear valve of this section is between the inner peripheral surface of the first recess and the outer peripheral surface of the plunger body, and between the inner peripheral surface of the second recess and the outer peripheral surface of the convex portion of the plunger. It is possible to configure the magnetic flux to flow in the two locations. In other words, the electromagnetic linear valve of this section shows the increase in the area of the portion where the magnetic flux flows between the plunger and the core portion with respect to the amount of movement of the plunger toward the core portion, It can be made larger than an electromagnetic linear valve. Therefore, the electromagnetic linear valve of this section can make it difficult for magnetic saturation between the plunger and the core portion to occur. Further, the electromagnetic linear valve having such a configuration can increase the magnetic force generated between the core and the plunger as the plunger moves away from the valve seat. That is, according to the electromagnetic linear valve of this section, the frictional force between the housing and the plunger can be increased by increasing the horizontal component of the magnetic force when the plunger is separated from the plunger. The self-excited vibration of the plunger can be effectively suppressed by the generated frictional force.

(7) The first liquid chamber is
A partition-side liquid chamber formed around the other end of the plunger; a first core-side liquid chamber formed between the one end of the plunger and the first recess of the core; The second core portion side liquid chamber formed between the convex portion of the plunger and the second concave portion of the core portion,
The plunger is
One end opened to the partitioning part side liquid chamber, and the other end opened to both the first core part side liquid chamber and the second core part side liquid chamber. The electromagnetic linear valve according to item (6), further including a communication passage that communicates each of the part side liquid chamber and the second core part side liquid chamber with the partitioning part side liquid chamber.

  The aspect described in this section may include at least one “communication path”. According to the aspect described in this section, it is possible to discharge air bubbles that have entered both of the two core-side liquid chambers to the partition-side liquid chamber by the at least one communication path.

(11) A hydraulic pressure control valve device for adjusting the hydraulic pressure of the hydraulic fluid output from the high-pressure source in order to supply the regulated hydraulic fluid to the hydraulic fluid supply device,
(A) a pressure-increasing linear valve provided between the high-pressure source and the hydraulic fluid supply device and increasing the hydraulic pressure of the hydraulic fluid supplied to the hydraulic fluid supply device; and (B) the hydraulic fluid supply device. A pressure reducing linear valve that is provided between the supply device and the low pressure source and reduces the hydraulic pressure of the hydraulic fluid supplied to the hydraulic fluid supply device;
The hydraulic control valve device in which each of the pressure-increasing linear valve and the pressure-decreasing linear valve is the electromagnetic linear valve according to (6) or (7)

  The aspect described in this section is the electromagnetic type having the above-described configuration in which each of the pressure-increasing linear valve and the pressure-reducing linear valve included in the hydraulic control valve device is formed in a stepped shape in each of the plunger and the core portion. A linear valve is used.

(12) When the ratio of the axial dimension of the first concave portion of the core part to the axial dimension of the convex part of the plunger is defined as a convex concave part ratio,
The electromagnetic linear valve that is used as the pressure-reducing linear valve and the electromagnetic linear valve that is used as the pressure-increasing linear valve are configured such that the convex-concave concave ratios are different from each other. Hydraulic control valve device.

  In the hydraulic control valve device described in this section, the convex-concave ratios of the pressure-increasing linear valve and the pressure-decreasing linear valve are different from each other, and the supplied current is the same. The magnetic force generated between the plunger and the core portion is different. That is, the frictional force between the plunger and the housing is different. The fluid pressure control valve device of this section can be used, for example, even when the average magnitude of the current received by each of the pressure-increasing linear valve and the pressure-decreasing linear valve is different from each other. Each of the pressure reducing linear valves can be configured to generate a frictional force having an appropriate magnitude, and the self-excited vibration of the plunger can be effectively suppressed.

  More specifically, by setting the “convex-concave ratio” described in this section, for example, when the plunger is seated, between the inner peripheral surface of the first concave portion and the outer peripheral surface of the plunger body, The area of the portion where the magnetic flux flows in at least one of the inner peripheral surface and the outer peripheral surface of the convex portion of the plunger can be increased. The electromagnetic linear valve having such a convex-concave-concave ratio can increase the frictional force between the plunger and the housing. In addition, a large amount of magnetic flux is allowed to flow between the plunger and the core portion, and it is possible to make it difficult for magnetic saturation between the plunger and the core portion to occur.

  On the other hand, in a state where the plunger is seated, a magnetic flux flows between the inner peripheral surface of the first recess and the outer peripheral surface of the plunger body, and between the inner peripheral surface of the second recess and the outer peripheral surface of the convex portion of the plunger. Instead, after the plunger has moved to the core portion side, the magnetic flux can flow to one of the plungers. According to the electromagnetic linear valve having such a convex-concave-concave ratio, the suction force when the plunger is seated is reduced, and the frictional force between the plunger and the housing during the seating can be reduced. .

(13) Each of the electromagnetic linear valve, which is the linear valve for pressure reduction, and the electromagnetic linear valve, which is the linear valve for pressure increase,
The hydraulic pressure according to (12), wherein a distance from an opening of the communication hole of the partition portion to a bottom surface of the first recess of the core portion and an axial length of the plunger are equal to each other. Control valve device.

  In the aspect described in this section, the structures of the two electromagnetic linear valves are limited. In the electromagnetic linear valve having the above-described structure, in order to vary the convex-concave ratio, the distance to the end surface of the core portion is varied based on the bottom surface of the first concave portion, or the end surface of the convex portion of the plunger is changed. What is necessary is just to vary the distance to the end surface of a plunger main-body part as a reference | standard. In other words, in the aspect of this section, each of the two electromagnetic linear valves has different areas of the portion where the magnetic flux flows between the inner peripheral surface of the first recess and the outer peripheral surface of the plunger body. Yes.

(14) The elastic body included in each of the electromagnetic linear valve that is the linear valve for pressure reduction and the electromagnetic linear valve that is the linear valve for pressure increase,
The plunger is biased in a direction in which the other end thereof approaches the opening of the communication hole,
Each of the electromagnetic linear valve that is the linear valve for pressure reduction and the electromagnetic linear valve that is the linear valve for pressure increase are:
The convex / concave ratio of the electromagnetic linear valve used as the pressure-reducing linear valve is configured to be larger than the convex / concave ratio of the electromagnetic linear valve used as the pressure-increasing linear valve. (13) The hydraulic control valve device according to item (13).

  In the aspect described in this section, each of the two electromagnetic linear valves is configured such that the areas of the portions where the magnetic flux flows between the inner peripheral surface of the first recess and the outer peripheral surface of the plunger body are different from each other. When the convex-concave ratio is increased, the area is increased. In the aspect of this section, the convex-concave ratio of the pressure-reducing linear valve is set larger than the convex-concave ratio of the pressure-increasing linear valve. The area through which the magnetic flux flows is increased.

  In the aspect of this section, the two electromagnetic linear valves are normally closed valves, and a large current is required to reduce the differential pressure between the high-pressure side hydraulic fluid pressure and the low-pressure side hydraulic fluid pressure. For example, in a system such as a hydraulic brake system, the hydraulic pressure of hydraulic fluid supplied to a brake device as a hydraulic fluid ratio supply device is often displaced in a state close to the hydraulic pressure of a low pressure source. When the hydraulic control valve device is mounted, the pressure reducing linear valve requires a larger current than the pressure increasing linear valve. Therefore, in the pressure reducing linear valve, even when a large current is supplied, magnetic saturation is unlikely to occur between the plunger and the core, and in the pressure increasing linear valve, the frictional force at the time of plunger separation is reduced, Each of the pressure-reducing linear valve and the pressure-increasing linear valve has an appropriate configuration.

  (15) The axial dimension of the first recess of the electromagnetic linear valve used as the pressure-reducing linear valve is the same as that of the first recess of the electromagnetic linear valve used as the pressure-increasing linear valve. The hydraulic control valve device according to item (14), which is made larger than the size.

  (16) The dimension in the axial direction of the convex portion of the electromagnetic linear valve that is the linear valve for pressure increase is the dimension in the axial direction of the convex portion of the electromagnetic linear valve that is the linear valve for pressure reduction. The hydraulic control valve device according to item (14), which is made larger by comparison.

  The configuration described in the above two items is embodied in a configuration in which the convex-concave ratio of the pressure reducing valve is larger than the convex-concave ratio of the pressure increasing valve.

It is the schematic of a brake system provided with the hydraulic control valve device which is an example of claimable invention. It is a schematic sectional drawing of the linear valve for pressure reduction which the control valve apparatus of FIG. 1 has. It is a schematic sectional drawing of the linear valve for pressure increase which the control valve apparatus of FIG. 1 has. It is a schematic sectional drawing for comparing the electromagnetic linear valve of a present Example, and the electromagnetic linear valve of a modification. It is an expanded sectional view for comparing the linear valve for pressure increase of FIG. 1 with the linear valve for pressure reduction. It is an expanded sectional view for comparing the pressure-increasing linear valve and pressure-reducing linear valve with which the hydraulic control valve device of a modification is provided.

  Hereinafter, embodiments of the claimable invention and some modifications will be described in detail with reference to the drawings. In addition to the embodiments described below, the present invention can be claimed in various aspects including various modifications and improvements based on the knowledge of those skilled in the art, including the aspects described in the above [Aspect of the Invention] section. Can be implemented.

<Configuration of hydraulic brake system>
FIG. 1 shows a hydraulic brake system including a hydraulic control valve device that is an embodiment of the claimable invention. As shown in FIG. 1, the brake circuit included in the hydraulic brake system includes a brake pedal 10 as a brake operation member and a manual type that pressurizes hydraulic fluid based on the pedaling force applied to the brake pedal 10. A hydraulic pressure source device 12, a powered hydraulic pressure source device 14 that pressurizes hydraulic fluid depending on the force generated by the power source, four hydraulic brake devices 18 provided on the front, rear, left and right wheels 16, respectively. A brake actuator 20 is provided between the two hydraulic pressure source devices 12 and 14 and the brake device 18 and adjusts the hydraulic pressure generated by the power hydraulic pressure source device 14. It should be noted that some components such as “wheel 16” are used as a generic term, but when indicating that they correspond to any of the four wheels, the left front wheel, the right front wheel, the left rear wheel, The subscripts “FL”, “FR”, “RL”, and “RR” are assigned to the right rear wheel, respectively.

  Each of the four brake devices 18 has a brake cylinder 22, which is actuated by the hydraulic pressure of the brake cylinder 22 to apply a braking force to the wheel 16. In the present embodiment, the disk brake is a disk brake that presses a brake pad as a friction material held by a non-rotating body against the disk rotor as a brake rotating body that rotates together with the wheels 18 by the hydraulic pressure of the brake cylinder 22.

  The manual hydraulic pressure source device 12 includes a hydraulic pressure booster 30 and a master cylinder 32. The hydraulic booster 30 is linked to a hydraulic pressure adjusting unit (regulator, indicated as reg in FIG. 1) 34 that generates a hydraulic pressure higher than the hydraulic pressure corresponding to the operating force applied to the brake pedal 10, and the brake pedal 10. And a booster chamber 38 provided behind the power piston 36. The hydraulic pressure adjusting unit 34 includes a spool valve, a pressure adjusting chamber, and the like (not shown), and is connected to the power type hydraulic pressure source device 14 and to a reservoir 40 that is a low pressure source. The movement of the spool valve accompanying the operation of the brake pedal 10 causes the pressure regulating chamber to selectively communicate with the power hydraulic pressure source device 14 or the reservoir 40, and the hydraulic pressure in the pressure regulating chamber becomes a magnitude corresponding to the operating force. Adjusted. By supplying the hydraulic fluid in the pressure adjusting chamber (the hydraulic fluid adjusted by the hydraulic pressure adjusting unit 34) to the booster chamber 38, a forward force is applied to the power piston 36, and the operating force is assisted. .

  The master cylinder 32 includes a pressurizing piston 50 linked to the power piston 36 described above and a pressurizing chamber 52 provided in front of the pressurizing piston 50. As the power piston 36 advances, the pressurizing piston 50 is advanced, and a hydraulic pressure is generated in the pressurizing chamber 52.

  When the brake pedal 10 is depressed, the power piston 36 is advanced, and the pressurizing piston 50 is advanced accordingly. The booster chamber 38 is supplied with the hydraulic pressure adjusted to a magnitude corresponding to the operating force in the hydraulic pressure adjusting unit 34. The pressurizing piston 50 is advanced by a force that combines an operating force and an assisting force (a force corresponding to the hydraulic pressure of the booster chamber 76), and a hydraulic pressure having a magnitude corresponding to the force is applied to the pressurizing chamber 52. Be generated. In the present embodiment, the hydraulic pressure of the hydraulic pressure adjusting unit 34 and the hydraulic pressure of the pressurizing chamber 52 are set to be substantially the same.

  The power type hydraulic pressure source device 14 includes a pump 60 that pumps hydraulic fluid from the reservoir 40, a pump motor 62 as a power source that drives the pump 60, and hydraulic fluid discharged from the pump 60 in a pressurized state. And an accumulator 64 for storing. The pump motor 62 is controlled such that the pressure of the hydraulic fluid stored in the accumulator 64 is within a predetermined range. The power hydraulic pressure source device 14 also has a relief valve 66 that regulates the discharge pressure of the pump 60 to a set value or less, so that the discharge pressure of the pump 60 is prevented from becoming excessive.

  The power-type hydraulic pressure source device 14, the hydraulic pressure adjusting unit 34 of the hydraulic pressure booster 30, and the pressurizing chamber 52 of the master cylinder 32 are connected to the brake actuator 20. More specifically, the power hydraulic pressure source device 14, the hydraulic pressure adjusting unit 34 of the hydraulic booster 30, and the pressurizing chamber 52 of the master cylinder 32 are connected to a control pressure passage 70, a booster passage 72, and a master passage 74, respectively. The control pressure passage 70, the booster passage 72, and the master passage 74 are connected to a common passage 76 that the brake actuator 20 has. The common passage 76 is connected to brake cylinders 22FR, 22FL, 22RR, and 22RL corresponding to the wheels 16FR, 16FL, 16RR, and 16RL via individual passages 78FR, 78FL, 78RR, and 78RL, respectively. Has been. Further, the common passage 76 is connected to the reservoir 40 via the low pressure passage 80.

  The brake actuator 20 has an output hydraulic pressure control valve device 90 that adjusts the pressure of the hydraulic fluid stored in the accumulator 64, that is, the hydraulic pressure output from the power hydraulic pressure source 14. The output hydraulic pressure control valve device 90 connects the pressure increasing linear valve 92 provided in the control pressure passage 70 connecting the power hydraulic pressure source device 14 and the common passage 76, the common passage 76 and the reservoir 40. And a pressure reducing linear valve 94 provided in the low pressure passage 80. The pressure-increasing linear valve 92 can control the flow of hydraulic fluid from the power hydraulic pressure source device 14 to the common passage 76, while the pressure-decreasing linear valve 94 is a reservoir in the common passage 76. It is possible to control the outflow of hydraulic fluid to 40. The pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 have a predetermined fixed relationship between the hydraulic pressure difference between the high-pressure side hydraulic fluid and the low-pressure side hydraulic fluid and the supply current. The valve opening pressure can be changed accordingly. Therefore, the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 can continuously change the supply pressure, which is the hydraulic pressure of the hydraulic fluid supplied to the common passage 76, by controlling the supply current. It is possible to control to an arbitrary height. The present invention is characterized by the structure of the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94. Since the structure will be described in detail later, description thereof is omitted here.

  The brake actuator 20 has an individual hydraulic pressure control valve device 100 for adjusting the hydraulic pressure of each of the four brake cylinders 22FR, 22FL, 22RR, and 22RL. The individual hydraulic pressure control valve device 100 includes four holding valves 102FR, 102FL, 102RR, 102RL provided in each of the individual passages 78FR, 78FL, 78RR, 78RL described above, and each of the four holding valves 112. Four pressure reducing valves 104FR, 104FL, 104RR, 104RL provided between the reservoir 40 and the reservoir 40 are configured. The holding valve 102 is a normally-open electromagnetic control valve that is open when no current is supplied to the solenoid, and is for increasing and holding the hydraulic pressure in the brake cylinder 22. The pressure reducing valve 104 is a normally closed electromagnetic control valve that is in a closed state when no current is supplied to the solenoid, and is for reducing the hydraulic pressure in the brake cylinder 22.

  The common passage 76 is provided with a communication valve 106 between a portion to which the left and right front wheels 16FR and 16FL are connected and a portion to which the left and right rear wheels 16RR and 16RL are connected. That is, the communication valve 106 communicates the brake cylinders 22RR and 22RL corresponding to the left and right rear wheels 16RR and 16RL and the brake cylinders 22FR and 22FL corresponding to the left and right front wheels 16FR and 16FL, and a disconnected state. Are to be switched. The communication valve 106 is a normally closed electromagnetic control valve that is in a closed state when no current is supplied to the solenoid. The communication valve 106 is normally opened, and the hydraulic fluid from the pressure-increasing linear valve 92 described above is not limited to the brake cylinders 22RR and 22RL corresponding to the left and right rear wheels 16RR and 16RL. The brake cylinders 22FR and 22FL corresponding to the front wheels 16FR and 16FL are connected to each other so as to be supplied.

  Furthermore, the brake actuator 20 has a regulator cut valve 110 provided in the booster passage 72 and a master cut valve 112 provided in the master passage 74. The regulator cut valve 110 and the master cut valve 112 are both normally open electromagnetic control valves that are open when no current is supplied to the solenoid. In the middle of the master passage 72, a stroke simulator 114 is connected via a simulator cut valve 116, which is a normally closed electromagnetic control valve.

<Configuration of electromagnetic linear valve>
Next, the structures of the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94, which are electromagnetic linear valves reserved in the above description, will be described in detail with reference to FIG. Since the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 have substantially the same configuration, the pressure-decreasing linear valve 94 will be described first, and the pressure-increasing linear valve 92 described later will be used for pressure-decreasing. Only portions different from the linear valve 94 will be described.

  As shown in FIG. 2, the pressure-reducing linear valve 94 includes a hollow housing 120, a plunger 122 provided in the housing 120 so as to be movable in the axial direction thereof, and a cylinder provided on the outer periphery of the housing 120. The coil 124 is provided. The housing 120 is fitted into a cylindrical core 126 provided at the upper end, a guide cylinder 128 that is generally cylindrical and guides the movement of the plunger in the axial direction, and a lower end of the guide cylinder 128. And a covered cylindrical valve member 130. The core 126 and the guide tube 128 are formed of a ferromagnetic material, and the core 126 and the guide tube 128 are connected by a cylindrical sleeve 132 formed of a nonmagnetic material. Specifically, the core 126 is inserted into the upper end of the sleeve 132, the guide tube 128 is inserted into the lower end of the sleeve 132, and the connection is made with a space provided between the lower end surface of the core 126 and the upper end surface of the guide tube 128. Has been. A housing cylinder portion is formed by the guide cylinder 128 that is a ferromagnetic cylinder and the sleeve 132 that is a non-magnetic cylinder.

  As described above, the valve member 130 is fitted into the lower end of the guide cylinder 128, and the housing 120 is partitioned into the first liquid chamber 140 and the second liquid chamber 142. It functions as a part. The valve member 130 is provided with a communication hole 144 that penetrates in the axial direction and communicates the first liquid chamber 140 and the second liquid chamber 142. An opening 146 on the upper side of the communication hole 144 is formed in a tapered shape.

  In other words, in the valve member 130, the second liquid chamber 142 of the housing 120 is opened downward, and the opening 150 functions as an inflow port. Communicate. On the other hand, the first liquid chamber 140 of the housing 120 is partitioned by the core 126, the guide cylinder 128, and the valve member 130, and the opening 152 provided on the outer wall surface of the guide cylinder 128 functions as an outflow port. The first liquid chamber 140 communicates with a low pressure passage 80 that is a low pressure side hydraulic fluid passage.

  The plunger 122 includes a plunger main body 160 formed of a ferromagnetic material and a rod 162 formed of a nonmagnetic material and fixedly fitted to the lower end of the plunger main body 160. The lower end of the rod 162 is formed in a hemispherical shape so as to face the opening 146 of the communication hole 144 formed in the valve member 130. That is, the lower end of the rod 162 functions as a valve body, the opening 146 of the communication hole 144 functions as a valve seat, and the lower end of the rod 162 is seated on the opening 146, thereby closing the communication hole 144. . The plunger 122 is urged toward the direction away from the core 126 (downward) by a coil spring 164 disposed between the plunger 122 and the core 126. That is, the coil spring 164 as an elastic body urges the lower end of the rod 162 in a direction to approach the opening 146 of the communication hole 144, and closes the communication hole 144 with the plunger 122.

  A convex portion 170 protruding toward the core 126 is provided on the upper end surface of the plunger main body 160, and the upper end of the plunger main body 160 is a stepped convex portion. A portion that continues below the convex portion 170 of the plunger main body 160 is referred to as an upper end portion of the plunger main body 160. On the other hand, the lower end portion of the core 126 has a first recess 172 formed on the lower end surface of the core 126 and a second recess 174 formed on the bottom surface of the first recess 172, thereby forming a stepped recess. It is said that. Then, the convex portion of the plunger 122 enters the concave portion of the core 126. Specifically, the upper end portion of the plunger main body 160 enters the first concave portion 172, and the convex portion 170 enters the second concave portion 174.

  Incidentally, a bottomed hole 176 is formed in the bottom surface of the second recess 174, and the above-described coil spring 164 is disposed inside the bottomed hole 176. That is, the coil spring 164 is disposed between the bottom surface of the bottomed hole 176 (the upper surface shown in the drawing) and the upper surface of the convex portion 170 of the plunger 122. Further, a stopper 178 is arranged inside the coil spring 164 so that the movement of the plunger 122 in the direction approaching the core 126 is restricted.

  Moreover, the plunger main body 160 has a flange portion 180 that protrudes in the radial direction from the upper outer peripheral surface thereof. The flange portion 180 faces the sleeve 132 described above, and is positioned within a space provided between the lower end surface of the core 126 and the upper end surface of the guide tube 128. The flange portion 180 does not come into contact with the lower end surface of the core 126 and the upper end surface of the guide cylinder 128 within the moving range even when the plunger 122 moves in the axial direction.

  Furthermore, the plunger main body 160 has a plurality of communication passages 190 that pass through the plunger main body 160 in the axial direction and communicate between the upper side and the lower side of the plunger main body 160. Specifically, the plunger 122 is disposed in the first liquid chamber 140, and the first liquid chamber 140 includes a partition-side liquid chamber 192 formed around the rod 162 of the plunger 122, and the plunger 122. The first core portion side liquid chamber 194 formed between the upper end portion of the first portion and the first concave portion 172, and the second core portion side liquid chamber formed between the convex portion 170 of the plunger 122 and the second concave portion 174. 196. Each of the plurality of communication passages 190 communicates the partition portion side liquid chamber 192 and the two core portion side liquid chambers 194, 196, and the upper end of each of them communicates with two cores. It opens to both the part side liquid chambers 194 and 196. That is, the communication path 190 allows the bubbles that have entered both the two core-side liquid chambers 194 and 196 to be discharged to the partition-side liquid chamber 192.

  The plunger main body 160 is fitted with a plunger sleeve 200 formed in a cylindrical shape by a nonmagnetic material. When the plunger 122 is seated and tilted in the housing 120, the upper end of the plunger sleeve 200 comes into contact with the inner surface of the guide tube 128. That is, the plunger 122 is supported at two points: the lower end of the plunger sleeve 200 and the lower end of the rod 162. Further, when the plunger 122 is tilted in the housing 120 in a separated state, the upper end and the lower end of the plunger sleeve 200 abuts against the inner surface of the guide cylinder 128, and the plunger 122 is in contact with the upper end and the lower end of the plunger sleeve 200. And is supported at two points.

  The coil 124 is accommodated in a coil case 204 fixed to the upper outer peripheral surface of the housing 120. The coil case 204 is formed of a ferromagnetic material, and has an upper end portion fixed to the core 126 and a lower end portion fixed to the guide tube 128. With such a configuration, a magnetic path is formed.

  Next, the pressure-increasing linear valve 92 will be described with reference to FIG. In addition, since the linear valve 92 for pressure increase is the structure substantially the same as the linear valve 94 for pressure reduction, in the description, it shows that it respond | corresponds using the same code | symbol as the linear valve for pressure reduction. In the following description, when indicating which of the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 corresponds to each of the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94, Subscripts “SLA” and “SLR” are attached.

  The pressure increasing linear valve 92 is different from the pressure reducing linear valve 94 in the shape of the core 126 of the housing 120. Specifically, the core 126SLA of the pressure increasing linear valve 92 is formed such that the depth of the first recess 172SLA is shallower than the first recess 172SLR of the pressure reducing linear valve 94. Note that the plungers 122 of the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 are the same. Further, the housing 120 of each of the pressure increasing linear valve 92 and the pressure reducing linear valve 94 is formed so that the distance from the valve member 130 functioning as a valve seat to the bottom surface of the first recess 172 of the core 126 is equal. .

  Further, the pressure-increasing linear valve 92 is different from the pressure-decreasing linear valve 94 in the length of the plunger sleeve 200 fitted on the plunger 122. The plunger sleeve 200SLA of the pressure-increasing linear valve 92 is shorter than the plunger sleeve 200SLR of the pressure-decreasing linear valve 94. Due to such a difference in configuration, the upper end of the plunger sleeve 200SLR is configured to abut the inner surface of the housing 120 when the pressure reducing linear valve 94 is tilted in the housing 120 with the plunger 122 seated. The pressure increasing linear valve 92 is configured such that the flange portion 180 abuts against the inner surface of the sleeve 132. That is, in the pressure-increasing linear valve 92, the plunger 122 is supported at two points, that is, the flange portion 180 and the lower end of the rod 162 when it is tilted in the seated state. In addition, when the plunger 122 is tilted in the housing 120 in a separated state, the flange portion 180 abuts against the sleeve 182 and the plunger sleeve 200 abuts against the inner surface of the guide cylinder 128, The flange portion 180, the plunger sleeve 200, and the lower end are supported at two points.

  In the pressure-increasing linear valve 92, the second fluid chamber 142SLA of the housing 120 communicates with the control pressure passage 70 that is a high-pressure side working fluid passage. On the other hand, the first liquid chamber 140SLA of the housing 120 communicates with a common passage 76 that is a low-pressure side hydraulic fluid passage.

<Operation of electromagnetic linear valve>
Due to the above-described structure, the pressure increasing linear valve 92 and the pressure reducing linear valve 94, which are electromagnetic linear valves, are supplied from the high-pressure side hydraulic fluid path to the low-pressure side hydraulic fluid path when no current is supplied to the coil 124. The flow of the hydraulic fluid is prohibited, and the current is supplied to the coil 124 to allow the flow of the hydraulic fluid from the hydraulic fluid passage on the high pressure side to the hydraulic fluid passage on the low pressure side. The pressure difference between the internal hydraulic pressure and the hydraulic pressure in the low-pressure side hydraulic fluid passage is controllable.

More specifically, when no current is supplied to the coil 124, the elastic force of the coil spring 164 closes the opening 146 of the communication hole 144 where the tip of the rod 162 of the plunger 122 is connected to the hydraulic fluid path on the high pressure side. Thus, the electromagnetic linear valves 92 and 94 prohibit the flow of hydraulic fluid from the high-pressure side hydraulic fluid passage to the low-pressure side hydraulic fluid passage. At this time, at the tip of the rod 162, the hydraulic pressure in the high-pressure side hydraulic fluid path (hereinafter sometimes referred to as “high-pressure side hydraulic pressure”) and the hydraulic pressure in the low-pressure side hydraulic fluid path (hereinafter “ A force F ₁ based on a difference from “low pressure side hydraulic fluid pressure” may be applied. The force F ₁ based on the pressure difference and the elastic force F ₂ of the coil spring 164 act in opposite directions, but the elastic force F ₂ is made somewhat larger than the force F ₁ based on the pressure difference. The electromagnetic linear valves 92 and 94 do not open when no current is supplied to the coil 124.

On the other hand, when a current is supplied to the coil 124, the magnetic flux passes through the coil case 204, the core 126, the plunger 122, and the guide cylinder 128 as the magnetic field is formed. Then, a magnetic force is generated to move the plunger 122 in a direction in which the tip of the rod 162 is separated from the opening 146 of the communication hole 144 (hereinafter, sometimes referred to as “separation direction”). When a current is supplied to the coil 124 to form a magnetic field, the plunger 122 has a sum of a force F ₁ based on the pressure difference and a force F ₃ that biases the plunger 122 upward by the magnetic force. The elastic force F ₂ of the compression coil spring 164 acts in the opposite direction. At this time, while the sum of the force F ₁ based on the pressure difference and the biasing force F ₃ due to the magnetic force is larger than the elastic force F _2, the opening 146 closed by the tip of the rod portion 162 is opened, and the high pressure side The hydraulic fluid flows from the hydraulic fluid passage to the hydraulic fluid passage 4 on the low pressure side.

Then, when the high-pressure hydraulic fluid flows into the low-pressure hydraulic fluid passage, the low-pressure hydraulic fluid pressure increases and the force F ₁ based on the pressure difference decreases. By the force F ₁ based on the pressure difference is reduced, the sum of the biasing force F ₃ by the force F ₁ and the magnetic force based on the pressure difference, the smaller than the elastic force F _2, the electromagnetic linear valves 92, 94 Is closed, and the flow of the hydraulic fluid from the high-pressure side hydraulic fluid passage to the low-pressure side hydraulic fluid passage is blocked. For this reason, the low-pressure side hydraulic fluid pressure is maintained at the low-pressure side hydraulic fluid pressure when the sum of the force F ₁ based on the pressure difference and the biasing force F ₃ based on the magnetic force becomes smaller than the elastic force F ₂ . That is, by controlling the energization amount to the coil 124, it becomes possible to control the pressure difference between the low-pressure side hydraulic fluid pressure and the high-pressure side hydraulic fluid pressure, up to the target hydraulic fluid pressure. It is possible to increase.

<Characteristics of electromagnetic linear valve>
As described above, the electromagnetic linear valves 92 and 94 are configured such that the stepped convex portion formed at the upper end portion of the plunger 122 faces the stepped concave portion formed at the lower end portion of the core 126. It is said that. The electromagnetic linear valves 92 and 94 are compared with a conventional electromagnetic linear valve 230 in which the lower end portion of the core 222 is not stepped. 4A, when the plunger 220 is seated, the electromagnetic linear valve 230 of the comparative example has a convex portion 240 formed on the upper end of the plunger 220 and a concave portion formed on the core 222. 242 is in a state of entering. That is, in the electromagnetic linear valve 230 of the comparative example, when a current is supplied to the coil, the magnetic flux flowing from the core 222 to the plunger 220 flows only from the concave portion 242 of the core 222 to the convex portion 240 of the plunger 220. On the other hand, in the electromagnetic linear valves 92 and 94, as shown in FIG. 4B, the magnetic flux flowing from the core 126 to the plunger 122 flows from the first recess 172 of the core 126 to the upper end of the plunger main body 160. At the same time, it flows from the second concave portion 174 of the core 126 to the convex portion 170 of the plunger 122. For this reason, when the same amount of magnetic flux flows from the coil to the core, the amount of magnetic flux flowing from the core to the plunger is greater in the electromagnetic linear valves 92 and 94 than in the electromagnetic linear valve 230 of the comparative example. . That is, even if the energization amount to the coil is the same, the suction force that is the force by which the core 126 of the electromagnetic linear valves 92 and 94 sucks the plunger 122 is the same as that of the core 222 of the electromagnetic linear valve 230 of the comparative example. It becomes larger than the suction force.

  In the electromagnetic linear valve, the plunger moves toward the core as the plunger is attracted by the core, and the convex portion of the plunger enters the concave portion of the core. The electromagnetic linear valve 230 of the comparative example is in a state where the convex portion 240 of the plunger 220 faces the concave portion 242 of the core 222, whereas the electromagnetic linear valves 92 and 94 are arranged at the upper end of the plunger main body 160. The portion enters the first concave portion 172 of the core 126, and the convex portion 170 of the plunger 122 enters the second concave portion 174 of the core 126. Speaking flatly, the electromagnetic linear valve 230 of the comparative example only enters one place of the plunger with respect to the core, whereas the electromagnetic linear valves 92 and 94 enter two places. As shown in FIG. 4, the electromagnetic linear valve 230 of the comparative example increases the area of the portion where the convex portion 240 of the plunger 220 and the concave portion 242 of the core 222 overlap in the radial direction. In the linear valves 92 and 94, the area of the portion where the upper end portion of the plunger main body 160 and the first concave portion 172 of the core 126 overlap in the radial direction, and the convex portion 170 of the plunger 122 and the second concave portion 174 of the core 126 have a diameter. Both the area of the overlapping part in the direction increase. That is, the amount of magnetic flux flowing from the core to the plunger increases as the amount of stroke upward of the plunger increases, and the amount of increase in magnetic flux from the core to the plunger relative to the stroke amount is the electromagnetic linear of this embodiment. There are more valves 92 and 94 than the electromagnetic linear valve 230 of a comparative example. Therefore, the electromagnetic linear valves 92 and 94 have a larger component in the radial direction of the suction force than the electromagnetic linear valve 230 of the comparative example. In the electromagnetic linear valves 92 and 94, the frictional force between the plunger 122 and the core 126 generated depending on the radial component of the suction force is increased, and the self-excited vibration of the plunger 122 is caused by the increased frictional force. Can be effectively suppressed.

  In the electromagnetic linear valves 92 and 94, the plunger 122 has a flange portion 180. The flange portion 180 is located in a liquid chamber formed between the core 126 and the guide tube 128. The liquid chamber between the core 126 and the guide tube 128 is partitioned by the flange portion 180 into a liquid chamber between the flange portion 180 and the core 126 and between the flange portion 180 and the guide tube 128. The That is, in the electromagnetic linear valves 92 and 94, when the flange portion 180 moves between the core 126 and the guide cylinder 128, the hydraulic fluid is moved between the two liquid chambers partitioned by the flange portion 180. Then, it flows through the gap between the sleeve 132 and the flange portion 180. A resistance force is generated by the flow of the hydraulic fluid, and a damping force is applied to the movement of the plunger 122. Therefore, according to the electromagnetic linear valves 92 and 94, the self-excited vibration of the plunger 122 can be suppressed by the damping force with respect to the movement of the plunger 122.

<Characteristics regarding difference between linear valve for pressure increase and linear valve for pressure reduction>
The hydraulic pressure control valve device 90 is mounted in the brake system, and controls the supply pressure to the brake cylinder 22 by the pressure increasing linear valve 92 and the pressure reducing linear valve 94. The supply pressure changes at a value closer to the hydraulic pressure of the reservoir 40 than the hydraulic pressure output from the accumulator 64. That is, the pressure difference between the high pressure side hydraulic fluid pressure and the low pressure side hydraulic fluid pressure is greater in the pressure increasing linear valve 92 than in the pressure reducing linear valve 94. Since the electromagnetic linear valves 92 and 94 are normally closed valves, a larger current is required as the differential pressure becomes smaller.

  As shown in the enlarged view of FIG. 5, the pressure increasing linear valve 92 and the pressure reducing linear valve 94 included in the hydraulic pressure control valve device 90 are different in the depth of the first recess 172 of the core 126, and the pressure increasing linear valve 94. The first recess 172SLA of the valve 92 is shallower than the first recess 172SLR of the pressure-reducing linear valve 94. That is, in the state where the plunger 122 is seated, the area of the portion where the upper end portion of the plunger 122 and the first recess 172 of the core 126 overlap in the radial direction is smaller in the pressure-increasing linear valve 92 than in the pressure-decreasing linear valve 94. ing. With such a configuration, in the pressure-reducing linear valve 94, in order to control a small differential pressure, the magnetic flux flowing between the core 126 and the plunger 122 is increased even when a large current is supplied. Magnetic saturation is unlikely to occur between the core 126 and the plunger 122.

  On the other hand, when the magnetic flux flowing between the core and the plunger increases and the radial component of the attractive force increases, the frictional force between the core and the plunger also increases. The frictional force becomes a resistance force when the plunger starts to move from the seated state when the valve is switched from the closed state to the opened state. If the frictional force at this time becomes too large, the acceleration when the plunger is separated increases and the valve opening amount may increase rapidly. This sudden increase in the valve opening amount causes the hydraulic fluid to rapidly flow from the second liquid chamber into the first liquid chamber, which may cause self-excited vibration of the plunger. That is, it is desirable that the frictional force when the plunger is separated is as small as possible.

  The pressure-increasing linear valve 92 has a large differential pressure between the high-pressure side hydraulic fluid pressure and the low-pressure side hydraulic fluid pressure, and can be opened with a relatively small current. The first recess 172SLA of the pressure increasing linear valve 92 is shallower than the first recess 172SLR of the pressure reducing linear valve 94. Therefore, in the pressure-increasing linear valve 92, the magnetic flux flowing between the core 126 and the plunger 122 in a state where the plunger 122 is seated is less than that in the pressure-decreasing linear valve 94. The frictional force at the time is reduced, and the self-excited vibration of the plunger 122 is hardly generated.

  Further, the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 are different from each other in the length of the plunger sleeve 200, and the flange portion 180SLA of the pressure-increasing linear valve 92 contacts the inner surface of the housing 120. In contrast to the configuration, the flange portion 180SLR of the pressure-reducing linear valve 94 is configured not to contact.

  Here, the frictional force when the plunger 122 is seated will be described. When current is supplied to the coil 124 when the tip of the rod 162 of the plunger 122 and the contact portion are supported at two points on the housing 120, a suction force acts on the plunger 122, and the radial direction of the suction force Depending on the component, a frictional force acts on the contact portion. That is, the radial component of the suction force is input to the upper end portion of the plunger 122 with the tip of the rod 162 as a fulcrum, and the contact portion serves as the point of action. Since the action point is located between the fulcrum and the force point, the closer the action point is to the force point, the smaller the force acting on the action point. Therefore, the pressure-increasing linear valve 92 in which the flange portion 180 and the sleeve 132 are in contact with the upper end portion of the plunger 122 serving as a power point is compared with the pressure-reducing linear valve 94 in which the upper end of the plunger sleeve 200 is in contact with the guide tube 128. Since the contact portion is close, the frictional force acting on the contact portion is small.

  The pressure-increasing linear valve 92 has a configuration in which the flange portion 180 abuts, so that the frictional force when the plunger 122 is separated is reduced, and the self-excited vibration of the plunger 122 is hardly generated. Further, as described above, the linear valve 92 for pressure increase can also be obtained by reducing the area of the portion where the upper end portion of the plunger 122 and the first concave portion 172 of the core 126 overlap in the radial direction. The frictional force at the time of separation is reduced, and it is specialized for suppressing the occurrence of self-excited vibration of the plunger 122.

  On the other hand, the pressure reducing linear valve 94 can effectively exhibit the damper function by the flange portion 180 by the configuration in which the flange portion 180 does not contact, and can attenuate the self-excited vibration of the plunger 122. It is. Further, the pressure reducing linear valve 94 has a large area where the upper end portion of the plunger 122 and the first concave portion 172 of the core 126 overlap in the radial direction, and due to a large frictional force when the plunger 122 is separated. In addition, the self-excited vibration of the plunger 122 can be attenuated, and it is specialized for the attenuation of the self-excited vibration of the plunger 122.

  With this configuration, the hydraulic pressure control valve device 90 includes the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 that are optimized according to the magnitude of the supplied current. Even in the electromagnetic linear valve, the self-excited vibration of the plunger 122 can be effectively suppressed.

<Modification>
In the above embodiment, the pressure-increasing linear valve 92 and the pressure-decreasing linear valve 94 have different depths of the first recess 172 of the core 126, but the plunger 122 and the core 126 have different diameters. What is necessary is just the structure from which the area of the part which overlaps with a direction differs mutually. For example, the convex concave portion ratio r (= Lb / La), which is the ratio of the axial dimension Lb of the first concave portion of the core to the axial dimension La of the convex portion of the plunger, is set to the pressure increasing linear valve 92 and the pressure reducing linear valve 92. What is necessary is just to comprise so that it may differ with the linear valve 94. However, as described above, in the electromagnetic linear valves 92 and 94, for example, the coil spring 164 and the stopper 178 are provided between the plunger 122 and the core 126, and parts other than those having different shapes are used for pressure increase. It is desirable that the linear valve 92 and the pressure reducing linear valve 94 be the same.

  In view of the above, for example, in addition to the above-described embodiment, as shown in FIG. 6, the convex-concave ratio r may be different from each other by making the shape of the plunger different. Specifically, in the pressure-increasing linear valve 260 and the pressure-decreasing linear valve 262 of the present modification, the first concave portion 272 of the core 270 has the same depth, and the height La of the convex portion 282 of the plunger 280 is different from each other. To do. However, the total length of the plunger 280, that is, the distance from the tip of the rod to the upper surface of the convex portion 282 is made equal, and the distance La from the upper surface of the convex portion 282 to the upper surface 284 of the plunger main body portion is different from each other. . Also in the hydraulic control valve device of this modification, the area of the portion where the plunger 280 and the core 270 overlap in the radial direction is the direction of the pressure increasing linear valve 260, as in the hydraulic control valve device 90 of the above embodiment. However, it is made small compared with the linear valve 262 for pressure reduction, and the same effect as the hydraulic control valve apparatus 90 of the said Example is acquired.

  10: Brake pedal 14: Power hydraulic device 16: Wheel 18: Hydraulic brake device 40: Reservoir 64: Accumulator 76: Common passage 80: Low pressure passage 90: Output hydraulic pressure control valve device [hydraulic pressure control valve device] 92: Linear valve for pressure increase [electromagnetic linear valve] 94: Linear valve for pressure reduction [electromagnetic linear valve] 120: Housing 122: Plunger 124: Coil 126: Core [core part] 128: Guide cylinder [ferromagnetic cylinder] 130 : Valve member [partition section] 132: Sleeve [non-magnetic cylinder] 140: First liquid chamber 142: Second liquid chamber 144: Communication hole 146: Opening (valve seat) 150: Opening [inlet port] 152: Opening [outlet] 160]: Plunger body 162: Rod 164: Coil spring [elastic body] 70: convex part 172: first concave part 174: second concave part 180: flange part 190: communication path 192: partition part side liquid chamber 194: first core part side liquid chamber 196: second core part side liquid chamber 260: increase Linear valve for pressure 262: Linear valve for pressure reduction 270: Core 272: First recess 280: Plunger 282: Projection

Claims (3)

A hydraulic pressure control valve device for adjusting the hydraulic pressure of hydraulic fluid output from a high-pressure source in order to supply the regulated hydraulic fluid to the hydraulic fluid supply device,
(A) provided between the high-pressure source and the hydraulic fluid supply device, and supplied to the hydraulic fluid supply device
A pressure-increasing linear valve that increases the hydraulic pressure of the hydraulic fluid to be supplied; (B) the hydraulic fluid supply device and a low-pressure source;
And a pressure reducing linear valve for reducing the hydraulic pressure of the hydraulic fluid supplied to the hydraulic fluid supply device.
Each of the pressure increasing linear valve and the pressure reducing linear valve is
(a) a housing cylindrical portion formed in a cylindrical shape, (b) a core portion formed so as to close one end of the housing cylindrical portion, and (c) the interior of the housing cylindrical portion as the core portion. A partition section that is partitioned into a near first liquid chamber and a second liquid chamber opposite to the core section, and in which a communication hole is formed to connect the first liquid chamber and the second liquid chamber; (d) An inflow port for communicating with the second liquid chamber and allowing the working liquid to flow into the second liquid chamber; and (e) for communicating the first liquid chamber with the working liquid flowing out from the first liquid chamber. A housing having an outlet port of
One end portion is opposed to the core portion and the other end portion is opposed to the opening of the communication hole, and is disposed in the first liquid chamber and is movable in the axial direction, and the other end portion is the communication hole. A plunger capable of being seated in the opening of
An elastic body that biases the plunger in one of a direction in which the other end thereof approaches the opening of the communication hole and a direction in which the plunger separates from the opening;
A coil disposed around the housing and forming a magnetic field for moving the plunger in a direction opposite to a direction in which the plunger is biased by the elastic body,
The plunger is formed with a convex portion protruding toward the core portion at the one end portion,
The core portion is formed with a first concave portion where the one end portion of the plunger enters the end surface facing the plunger, and a second concave portion where the convex portion enters the bottom surface of the first concave portion. It is an electromagnetic linear valve ,
When the ratio of the dimension in the axial direction of the first concave portion of the core portion to the dimension in the axial direction of the convex portion of the plunger is defined as the convex concave portion ratio,
A hydraulic pressure control valve device in which each of the pressure-reducing linear valve and the pressure-increasing linear valve is configured so that the convex-concave ratio is different from each other. The elastic body included in each of the electromagnetic linear valve that is the linear valve for pressure reduction and the electromagnetic linear valve that is the linear valve for pressure increase,
The plunger is biased in a direction in which the other end thereof approaches the opening of the communication hole,
Each of the electromagnetic linear valve that is the linear valve for pressure reduction and the electromagnetic linear valve that is the linear valve for pressure increase are:
The convex / concave ratio of the electromagnetic linear valve used as the pressure-reducing linear valve is configured to be larger than the convex / concave ratio of the electromagnetic linear valve used as the pressure-increasing linear valve. The hydraulic control valve device according to claim 1 . The dimension in the axial direction of the first recess of the electromagnetic linear valve used as the pressure reducing linear valve is compared with the dimension in the axial direction of the first recess of the electromagnetic linear valve used as the pressure increasing linear valve. The hydraulic control valve device according to claim 2 , wherein the hydraulic control valve device is enlarged.

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