JP2011226541A - Liquid pressure valve device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a liquid pressure valve device in which a hydraulic fluid flowing between each valve element and valve seat of a booster valve and a pressure reducing valve flows in a valve opening direction.SOLUTION: The liquid pressure valve device includes: (a) a housing having a low-pressure chamber 272, a pressure regulating chamber 254, a high-pressure chamber 256 positioned between the low-pressure chamber and the pressure regulating chamber, a first inter-chamber part which connects the low pressure chamber and high-pressure chamber, and a second inter-chamber part which connects the high-pressure chamber and pressure regulating chamber; (b) a moving member 196, which plugs the first inter-chamber part and is movable in an inserted state into the second inter-chamber part; (c) a communication passage 260, which opens to the low-pressure chamber and formed on the moving member, has a low-pressure chamber side opening which functions as a valve seat of the pressure reducing valve, and communicates the low-pressure chamber with the pressure regulating chamber; and (d) a plunger 192 which functions as a valve element of the pressure reducing valve which can seat on the low-pressure chamber side opening. In this device, the opening to the pressure regulating chamber of the second inter-chamber part is made to function as a valve seat, and a part in the pressure regulating chamber of the moving member as a valve element of the booster valve. This structure enables the hydraulic fluid to flow in the valve opening direction when pressure is boosted and reduced.

Description

  The present invention includes a housing having a high pressure chamber communicating with a high pressure source, a low pressure chamber communicating with a low pressure source, a pressure regulating chamber capable of communicating with the high pressure chamber and the low pressure chamber, and a high pressure chamber and a pressure regulating chamber. A valve mechanism that opens and closes the flow of hydraulic fluid between them, and a valve mechanism that opens and closes the flow of hydraulic fluid between the low-pressure chamber and the pressure regulating chamber, and can regulate the hydraulic pressure of the hydraulic fluid in the pressure regulating chamber The present invention relates to a hydraulic valve device.

  The hydraulic valve device includes: (a) a housing having a high pressure chamber, a low pressure chamber, and a pressure regulating chamber; and (b) a plunger provided movably in the housing and having one end functioning as a first valve body. (C) a first valve seat on which one end of the plunger is seated is formed, and a movable member is provided in the housing so as to be movable. In the state of being seated on the seat, the flow of the hydraulic fluid between the low pressure chamber and the pressure regulating chamber is blocked, and the second valve body that can be seated on the second valve seat formed in the housing is provided. In a state where the second valve body formed on the moving member is seated on the second valve seat, the flow of the hydraulic fluid between the high pressure chamber and the pressure regulating chamber is blocked. There is a thing of the structure. In the hydraulic valve device having such a structure, the first valve body and the first valve seat constitute a valve mechanism for opening and closing the flow of hydraulic fluid between the low pressure chamber and the pressure regulating chamber, and the second The valve body and the second valve seat constitute a valve mechanism that opens and closes the flow of hydraulic fluid between the high pressure chamber and the pressure regulating chamber.

  Furthermore, the first urging member that urges the moving member in a direction in which the second valve body formed on the moving member approaches the second valve seat, and one end of the plunger are separated from the first valve seat. A second urging member that urges the plunger in a direction to move, and a moving force generator that generates a force for moving the plunger in a direction in which one end of the plunger approaches the first valve seat, One end of the plunger is seated on the second valve seat against the urging force of the second urging member by the force generated by the moving force generator, and the moving member is moved together with the plunger in that state. There is a structure in which the second valve body formed on the moving member is separated from the second valve seat against the urging force of the first urging member.

  In the hydraulic valve device having such a structure, the operation of the moving force generator is controlled, and the second valve body formed on the moving member is separated from the second valve seat, thereby adjusting the pressure from the high pressure chamber. It is possible to allow the hydraulic fluid to flow between the chambers and to increase the hydraulic pressure of the hydraulic fluid in the pressure regulating chamber (hereinafter sometimes referred to as “pressure regulating chamber pressure”). On the other hand, by separating one end of the plunger from the first valve seat, it is possible to allow the hydraulic fluid to flow between the low pressure chamber and the pressure regulating chamber and to reduce the pressure regulating chamber pressure. . That is, the pressure regulating chamber pressure can be regulated to a height corresponding to the force generated by the moving force generator. The following patent document describes a technique related to a hydraulic valve device having such a structure.

JP 2008-25712 A JP 2008-47104 A JP 2008-25711 A JP 2008-132966 A

  In the hydraulic valve device having the above structure, the hydraulic fluid flows between the valve body and the valve seat when the pressure regulating chamber pressure is increased and decreased. The space between the valve body and the valve seat is relatively narrow, and the hydraulic fluid flowing between them acts on the valve body vigorously. For this reason, for example, when the hydraulic fluid flowing between the valve body and the valve seat when the pressure regulating chamber pressure is regulated flows in the direction in which the valve body approaches the valve seat, The valve body is biased in the direction in which the valve body approaches the valve seat by the flow. That is, the valve body is biased in the direction in which the valve is closed by the flow of the hydraulic fluid (hereinafter sometimes referred to as “self-closing direction”). On the other hand, when the pressure regulating chamber pressure is regulated, the force generated by the moving force generator is controlled to open the valve by separating the valve body from the valve seat. For this reason, when the hydraulic fluid flows in the self-closing direction, there is a possibility that the pressure regulating chamber pressure cannot be regulated with high accuracy. In addition, when the hydraulic fluid flows in the self-closing direction, the valve element may be seated on the valve seat. May occur frequently, so-called hunting phenomenon, and the pressure regulating chamber pressure may not be regulated accurately. The present invention has been made in view of such circumstances, and provides a hydraulic valve device capable of accurately regulating the pressure regulating chamber pressure when the pressure regulating chamber pressure is increased and reduced. Let it be an issue.

  In order to solve the above problems, a hydraulic valve device of the present invention includes: (a) a low pressure chamber, a pressure regulating chamber, a high pressure chamber provided between the low pressure chamber and the pressure regulating chamber, a low pressure chamber, and a high pressure chamber. A housing having a first inter-chamber portion connecting the first chamber and a second inter-chamber portion connecting the high pressure chamber and the pressure regulating chamber; and (b) closing the first inter-chamber portion and being inserted into the second inter-chamber portion. A moving member disposed in the housing so as to be movable in the axial direction in a state; (c) a low pressure chamber side opening that is formed in the moving member and that opens to the low pressure chamber and functions as the first valve seat; A communication passage formed in one of the moving member and the housing and having a pressure regulating chamber side opening that opens to the pressure regulating chamber, and communicates the low pressure chamber and the pressure regulating chamber; (d) the low pressure chamber A hydraulic valve device having a plunger functioning as the first valve body that can be seated in a side opening, wherein the opening to the pressure regulating chamber in the second chamber is at the top. And it functions as a second valve seat, the portion located regulating the pressure chamber of the moving member is configured to function as the second valve body.

  In the hydraulic valve device according to the present invention, the plunger as the first valve body seated in the low-pressure side opening as the first valve seat is located in the low-pressure chamber, and the pressure-regulating chamber pressure is reduced. The hydraulic fluid flows from the pressure regulating chamber to the low pressure chamber. Therefore, during decompression, the hydraulic fluid flowing between the valve body and the valve seat is the direction in which the valve body is separated from the valve seat, that is, the direction in which the valve opens (hereinafter, sometimes referred to as “self-opening direction”). To flow. In addition, a part of the moving member as the second valve body, which is seated in the opening to the pressure regulating chamber in the portion between the second chambers as the second valve seat, is located in the pressure regulating chamber. When the chamber pressure is increased, the hydraulic fluid flows from the high pressure chamber to the pressure regulating chamber. For this reason, even when the pressure is increased, the hydraulic fluid flowing between the valve body and the valve seat flows in the self-opening direction. Therefore, according to the hydraulic valve device of the present invention, it is possible to make the flow of the hydraulic fluid flowing between the valve body and the valve seat when the pressure regulating chamber pressure is increased and reduced in a self-opening direction, The occurrence of hunting or the like can be suppressed, and the pressure regulating chamber pressure can be regulated with high accuracy.

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.

  In each of the following items, the item (1) corresponds to the item 1, and the technical feature described in the item (2) is added to the item 1, the item 1, the item (3) The technical feature described in item (4) is added to claim 3, and the technical feature described in item (4) is added to any one of claims 1 to 3 in claim 4. Any one of claims 1 to 4 added with the technical feature described in (5) is described in claim 5, and any one of claims 1 to 5 is described in (6). The technical features described in (6) and (8) are added to any one of claims 1 to 6 to which the technical features described in the items (7) and (7) are added. The technical features described in (6) and (9) are added to any one of claims 1 to 6. The to the claim 8, in any one of claims 1 to 8 (10) obtained by adding the technical features described in terms to claim 9, corresponding respectively.

(1) A hydraulic valve device for regulating hydraulic fluid,
A low pressure chamber communicating with the low pressure source, a pressure regulating chamber filled with a regulated hydraulic fluid, a high pressure chamber provided between the low pressure chamber and the pressure regulating chamber and communicating with the high pressure source, and the low pressure chamber And a first chamber connecting the high pressure chamber and a second chamber connecting the high pressure chamber and the pressure regulating chamber, and a housing that divides them so as to be aligned in the axial direction of the chamber.
It is inserted into the first chamber and the second chamber so as to penetrate the high pressure chamber in the axial direction, and one end portion extends into the pressure regulating chamber and is movable in the axial direction. The high pressure chamber and the pressure regulating chamber are disposed in the housing, block the portion between the first chambers, and the one end portion is seated in an opening on the pressure regulating chamber side of the second chamber portion. A moving member that blocks the flow of hydraulic fluid between the
A first biasing member that biases the moving member in a direction in which the one end is seated in the opening;
A low pressure chamber side opening that is formed at the other end of the moving member and opens to the low pressure chamber, and is formed at one of the one end of the moving member and the housing and is open to the pressure regulating chamber. A pressure adjusting chamber side opening that communicates with the low pressure chamber and the pressure adjusting chamber;
A plunger that is disposed in the housing so as to be movable in the axial direction, and that blocks the flow of hydraulic fluid between the pressure regulating chamber and the low pressure chamber by being seated in the low pressure chamber side opening;
A second urging member that urges the plunger in a direction in which the plunger is separated from the low-pressure chamber side opening;
A hydraulic valve device comprising: a moving force generator that generates a force for moving the plunger in a direction in which the plunger is seated on the low-pressure chamber side opening in a magnitude corresponding to the electric power supplied to the plunger.

  The hydraulic valve device opens and closes the flow of hydraulic fluid between the high pressure chamber, the low pressure chamber, a housing having a pressure regulating chamber capable of communicating with the high pressure chamber and the low pressure chamber, and the high pressure chamber and the pressure regulating chamber. And a valve for opening and closing the flow of hydraulic fluid between the low pressure chamber and the pressure regulating chamber (hereinafter also referred to as “pressure reducing valve”), There is a structure capable of adjusting the hydraulic pressure of the hydraulic fluid in the pressure adjusting chamber (hereinafter sometimes referred to as “pressure adjusting chamber pressure”). The pressure increasing valve has a valve body and a valve seat, and the valve body is seated on the valve seat so that the flow of hydraulic fluid between the high pressure chamber and the pressure regulating chamber is blocked. The valve body and the valve seat have a structure in which the flow of the hydraulic fluid between the low pressure chamber and the pressure regulating chamber is blocked by the valve body seated on the valve seat.

  When the pressure regulating chamber pressure is increased and decreased, the hydraulic fluid flows between the valve body and the valve seat. However, since the space between the valve body and the valve seat is relatively narrow, the hydraulic fluid flowing between them is It acts on the valve body vigorously. For this reason, for example, when the pressure regulating chamber pressure is regulated, the working fluid flowing between the valve body and the valve seat is in a direction in which the valve body approaches the valve seat, that is, in a direction in which the valve is closed (hereinafter, “ In the case of flowing in the “self-closing direction”), there is a possibility that control for regulating the pressure regulating chamber pressure by separating the valve body and the valve seat cannot be performed with high accuracy. In addition, when the hydraulic fluid flows in the self-closing direction, the valve body may be seated on the valve seat. In such a case, the valve is closed by the flow of the hydraulic fluid and the valve is opened by the force generated by the moving force generator. May occur frequently, so-called hunting phenomenon, and the pressure regulating chamber pressure may not be regulated accurately.

  In view of the above, the hydraulic valve device described in this section includes: (a) a high pressure chamber, a low pressure chamber, a pressure regulating chamber provided between the high pressure chamber and the low pressure chamber, a high pressure chamber, A housing having a first chamber connecting the pressure regulating chamber and a second chamber connecting the low pressure chamber and the pressure regulating chamber; and (b) closing the first chamber and closing the second chamber. A moving member disposed in the housing so as to be movable in the axial direction in the inserted state; and (c) a low pressure chamber side opening that is formed in the moving member and that opens to the low pressure chamber and functions as a valve seat of the pressure reducing valve. A pressure regulating chamber side opening formed in one of the moving member and the housing and opened to the pressure regulating chamber, and a communication path communicating the low pressure chamber and the pressure regulating chamber; (d) And a plunger that functions as a valve body of a pressure reducing valve that can be seated on the low pressure chamber side opening, and the opening to the pressure regulating chamber between the second chambers functions as a valve seat of the pressure increasing valve Together, the portion located regulating the pressure chamber of the moving member is configured to function as a valve body of the pressure-increasing valve. According to the hydraulic valve device described in this section, the direction in which the valve body separates the flow of the hydraulic fluid flowing between the valve body and the valve seat when the pressure regulating chamber pressure is increased or decreased. That is, it is possible to make the valve open (hereinafter sometimes referred to as “self-opening direction”), suppress the occurrence of hunting and the like, and adjust the pressure regulating chamber pressure with high accuracy.

  The “inter-first chamber portion” and the “second inter-chamber portion” described in this section are only required to communicate between the two liquid chambers. For example, they penetrate the inner wall located between the two liquid chambers. It may be a hole, a passage, or the like, or may be a portion formed by the inner wall surface of an annular member fitted in the housing. The “communication path” described in this section may be anything that allows the low pressure chamber and the pressure regulating chamber to communicate with each other via the low pressure chamber side opening and the pressure regulating chamber side opening. It may communicate with only the through hole, or may communicate with a passage formed in the moving member and a passage formed in the housing.

  The “moving force generator” described in this section may be anything that can controllably generate a force for moving the plunger. Specifically, for example, an electromagnetic force is generated according to the supplied power. A coil may be used. Further, the structure may be such that the hydraulic fluid is regulated by an electromagnetic hydraulic valve device different from the hydraulic valve device, and the plunger is moved by causing the regulated hydraulic fluid to act on the plunger. . If it is a thing of such a structure, it is possible to generate | occur | produce the force for moving a plunger according to the electric power supplied to the electromagnetic hydraulic valve apparatus different from the said hydraulic valve apparatus.

(2) The pressure regulating chamber side opening is formed at the one end of the moving member,
The hydraulic valve device according to item (1), wherein the communication path passes through the inside of the moving member.

(3) While the pressure regulating chamber side opening is formed in the housing,
The communication path is
(a) a moving member communication path formed in the moving member and opening between the first chambers and communicating the opening and the low pressure chamber side opening; and (b) formed in the housing and moving the moving member. The hydraulic valve device according to item (1), including an in-housing communication path that communicates the opening of the in-member communication path to the first chamber portion and the pressure regulation chamber side opening.

  In the hydraulic valve device described in the above two terms, the structure between the low pressure chamber side opening and the pressure regulating chamber side opening term of the communication passage is specifically limited. The “communication path” described in the latter section may be any means as long as the low pressure chamber and the pressure regulation chamber communicate with each other through two paths, ie, the moving member communication path and the housing communication path. A communication chamber which is located at the portion and is provided so as to surround the outer peripheral surface of the moving member, and a liquid passage which is formed in the housing and communicates with the communication chamber and the pressure regulating chamber, and the liquid passage and the communication chamber are The structure may function as an in-housing communication path, and the in-moving member communication path may communicate the communication chamber and the low-pressure chamber.

(4) The moving member is
A pressure receiving area for receiving the hydraulic pressure of the working fluid in the high pressure chamber in a direction in which the one end portion thereof approaches the opening on the pressure regulating chamber side of the second chamber portion, and a direction in which the one end portion is separated from the opening The hydraulic valve device according to any one of items (1) to (3), wherein the pressure receiving area for receiving the hydraulic pressure of the hydraulic fluid in the high pressure chamber is the same.

  The moving member that divides the high-pressure chamber is affected by the hydraulic pressure of the hydraulic fluid in the high-pressure chamber (hereinafter sometimes referred to as “high-pressure chamber pressure”), and the high-pressure chamber pressure affects the movement of the moving member. There is. A force having a magnitude corresponding to the pressure receiving area where the moving member receives the high-pressure chamber pressure acts in the direction in which the pressure increasing valve opens, and the force acts in the direction in which the pressure increasing valve opens. On the other hand, a force having a magnitude corresponding to the pressure receiving area where the moving member receives the high-pressure chamber pressure also acts on the moving member in the direction in which the pressure increasing valve closes, and this force acts in the direction in which the pressure increasing valve closes. It is desirable that the two forces are generally balanced, and when the balance between the two forces is lost, as will be described in detail later, for example, the force required to move the moving member may increase. Therefore, in the hydraulic valve device described in this section, the pressure receiving area of the moving member that receives the high pressure chamber pressure in the direction in which the pressure increasing valve opens, and the pressure receiving area of the moving member that receives the high pressure chamber pressure in the direction in which the pressure increasing valve closes Are made the same, and the force required to move the moving member can be reduced.

(5) The moving member is
The pressure receiving area that receives the hydraulic pressure of the hydraulic fluid in the pressure regulating chamber in a direction in which the low pressure chamber side opening approaches the plunger, and the hydraulic fluid in the pressure regulating chamber in a direction in which the low pressure chamber side opening is separated from the plunger. The hydraulic valve device according to any one of (1) to (4), wherein the pressure receiving area for receiving the hydraulic pressure is the same.

  The moving member also partitions the pressure regulating chamber, and the pressure regulating chamber pressure may act on the moving member, and the pressure regulating chamber pressure may affect the movement of the moving member. A force having a magnitude corresponding to a pressure receiving area where the moving member receives pressure regulation chamber pressure in the direction in which the pressure reducing valve opens (hereinafter, sometimes referred to as “pressure reducing valve opening direction pressure receiving area”) acts. The force acts in the direction in which the pressure reducing valve opens. On the other hand, a force having a magnitude corresponding to the pressure receiving area where the moving member receives the pressure regulation chamber pressure in the direction in which the pressure reducing valve closes (hereinafter, also referred to as “pressure reducing valve closing direction pressure receiving area”) acts. The force acts in the direction in which the pressure reducing valve closes. When the force in the direction in which the pressure reducing valve opens is larger than the force in the direction in which the pressure reducing valve closes, there is a possibility that liquid leakage may occur from the pressure regulating chamber to the low pressure chamber when the pressure regulating chamber pressure is increased. On the other hand, if the force in the direction in which the pressure reducing valve closes is greater than the force in the direction in which the pressure reducing valve opens, the pressure reducing valve is difficult to open when reducing the pressure regulating chamber pressure, and there is a risk that hysteresis will occur in the pressure characteristics. is there. Therefore, in the hydraulic valve device described in this section, the pressure receiving area in the pressure reducing valve opening direction is the same as the pressure receiving area in the pressure reducing valve closing direction, and the liquid leakage and pressure when the pressure regulating chamber pressure is increased. It is possible to suppress the occurrence of characteristic hysteresis.

  The hydraulic valve device described in this section is designed so that the pressure receiving area in the pressure reducing valve opening direction is equal to the pressure receiving area in the pressure reducing valve closing direction. For example, priority is given to liquid leakage when the pressure regulating chamber pressure is increased. When it is desired to suppress the pressure, the pressure receiving area in the pressure reducing valve closing direction may be designed to be larger than the pressure receiving area in the pressure reducing valve opening direction. Also, for example, when it is desired to suppress the occurrence of hysteresis of pressure characteristics, in other words, when it is desired to reduce the force when opening the pressure reducing valve, the pressure receiving area in the pressure reducing valve opening direction is larger than the pressure receiving area in the pressure reducing valve closing direction. You may design as follows.

(6) The housing further includes an auxiliary chamber provided on the opposite side of the pressure regulating chamber from the high pressure chamber side, and a third chamber connecting portion between the auxiliary chamber and the pressure regulating chamber. ,
The hydraulic valve device according to any one of (1) to (5), wherein the moving member extends to the third chamber and is inserted into the third chamber.

  In the hydraulic valve device described in this section, the moving member also penetrates the pressure regulating chamber, and the moving member is supported by the first chamber portion and the third chamber portion. Therefore, according to the hydraulic valve device of this section, for example, it is possible to suppress the axial displacement of the moving member. The “auxiliary chamber” described in this section may be a room filled with the working fluid or a room where the working fluid is prevented from entering. For example, when the “auxiliary chamber” is a chamber filled with hydraulic fluid, it may communicate with a low-pressure source and function as a drain chamber.

(7) The hydraulic valve device is
An internal chamber that is formed inside the moving member, opens to the pressure regulating chamber on an outer peripheral surface of the moving member, and opens to the auxiliary chamber on an end surface on the one end side of the moving member;
(6) Item comprising an opening in the end face of the inner chamber slidably inserted at one end so as to close the opening and a pin supported at the other end by the housing in the auxiliary chamber. The hydraulic valve device according to 1.

  An internal chamber that opens to the end face on the one end portion side of the moving member is formed, and the pressure receiving area in the pressure reducing valve opening direction can be reduced by slidably inserting a pin into the opening. In order to adjust the balance between the pressure receiving area in the pressure reducing valve opening direction and the pressure receiving area in the pressure reducing valve closing direction, it is necessary to change the outer diameter of the moving member, the pressure receiving area of the sealing portion of the moving member, etc. May be complicated. In the hydraulic valve device described in this section, it is possible to adjust the balance between the pressure receiving area in the pressure reducing valve opening direction and the pressure receiving area in the closing direction of the pressure reducing valve only by changing the size of the opening to the end face of the inner chamber. The shape of the moving member can be made relatively simple.

(8) The moving member has a stepped shape having a stepped surface facing the auxiliary chamber at a portion inserted in the third inter-chamber portion,
The auxiliary chamber communicates with the low pressure source;
The hydraulic valve device is
An annular third chamber that is provided between the third chambers, penetrates the moving member, and blocks the flow of hydraulic fluid between the auxiliary chamber and the pressure regulating chamber while being in close contact with the step surface. The hydraulic valve device according to item (6) or (7), comprising an inner rubber member.

(9) The moving member extends to and inserted into the third chamber so that the end surface on the one end side thereof is located in the third chamber.
The auxiliary chamber communicates with the low pressure source;
The hydraulic valve device is
A third inter-chamber rubber member that is provided in the inter-third chamber portion and blocks the flow of hydraulic fluid between the auxiliary chamber and the pressure regulating chamber in a state of being in close contact with the end surface of the moving member. The hydraulic valve device according to (6) or (7).

(10) The moving member has a stepped shape having a step surface facing the low-pressure chamber at a portion inserted in the first inter-chamber portion,
The hydraulic valve device is
Between the first chambers, provided between the first chambers, between the annular first chambers that penetrates the moving member and blocks the flow of the working fluid between the low pressure chambers and the high pressure chambers in close contact with the step surface. The hydraulic valve device according to any one of (1) to (9), comprising an internal rubber member.

  In a general hydraulic valve device, what is slidably provided in a housing is usually fitted with a seal such as an O-ring on the outer peripheral surface of the sliding member. By mounting a seal such as an O-ring on the outer peripheral surface, liquid leakage or the like is suppressed, but the sliding resistance of the one that slides in the housing increases. In the hydraulic valve device described in the above three items, the rubber member is caused to function as a seal by bringing the rubber member into close contact with the stepped surface or the end surface instead of the outer peripheral surface. Therefore, according to the hydraulic valve device described in this section, it is possible to reduce the sliding resistance of the moving member in the housing as compared with the hydraulic valve device in which a seal such as an O-ring is mounted on the outer peripheral surface of the moving member. It becomes.

  The “rubber member in the third chamber” described in the second section may be in a shape that prohibits leakage of the working fluid from the end face of the moving member, and may be flat or annular. . Further, when the “rubber member in the third chamber” is annular, the pin inserted into the inner chamber described in the above section is fitted to the annular “rubber member in the third chamber”. May be arranged. By disposing the pins in this way, it is possible to suppress pin misalignment and the like.

  (11) The moving force generator includes a coil for generating an electromagnetic force for moving the plunger in a direction in which the plunger approaches the low pressure chamber side opening. The hydraulic valve device according to one.

(12) The housing further includes a moving force generating chamber provided on the opposite side of the low pressure chamber from the high pressure chamber side, and a fourth chamber connecting the moving force generating chamber and the low pressure chamber. Have
The plunger is slidably inserted between the fourth chambers,
The moving force generator is
An electromagnetic pressure increasing valve that communicates with the high-pressure source and can increase the hydraulic pressure of the hydraulic fluid to a height corresponding to the electric power supplied to the high-pressure source, and communicates with the low-pressure source and reduces the hydraulic pressure of the hydraulic fluid. An electromagnetic pressure-reducing valve that can be depressurized to a height corresponding to power different from the power supplied to itself, and adjusts the hydraulic fluid by the electromagnetic pressure-increasing valve and the electromagnetic pressure-reducing valve. The pressurized hydraulic fluid is supplied to the moving force generation chamber, thereby generating a force for moving the plunger in a direction in which the plunger approaches the low pressure chamber side opening (1). Thru | or the hydraulic valve apparatus as described in any one of (10).

  In the hydraulic valve device described in the above two terms, the moving force generator is specifically limited. According to the hydraulic valve device described in the above two items, the force for moving the plunger can be changed by changing the amount of power supplied to the coil or the electromagnetic pressure increasing valve and the electromagnetic pressure reducing valve. This is possible, and the force for moving the plunger can be easily controlled.

1 is a diagram schematically illustrating a vehicle hydraulic brake system including a hydraulic valve device according to a first embodiment of the claimable invention; FIG. It is a schematic sectional drawing which shows the pressure increase / reduction valve which comprises the hydraulic valve apparatus with which the hydraulic brake system for vehicles of FIG. 1 is provided. It is a figure which shows the pressure receiving area which each member of the pressure increase / reduction valve of FIG. 2 receives. It is a figure which shows roughly the hydraulic brake system for vehicles provided with the hydraulic valve apparatus of 2nd Example of claimable invention. It is a schematic sectional drawing which shows the hydraulic valve apparatus with which the hydraulic brake system for vehicles of FIG. 4 is provided. It is a figure which shows the pressure receiving area which each member of the hydraulic valve apparatus of FIG. 5 receives. It is a schematic sectional drawing which shows the hydraulic valve apparatus of 3rd Example of claimable invention. It is a figure which shows the pressure receiving area which each member of the hydraulic valve apparatus of FIG. 7 receives. It is a schematic sectional drawing which shows the hydraulic valve apparatus of 4th Example of claimable invention. It is a figure which shows the pressure receiving area which each member of the hydraulic valve apparatus of FIG. 9 receives. It is a schematic sectional drawing which shows the hydraulic valve apparatus of 5th Example of claimable invention. It is a figure which shows the pressure receiving area which each member of the hydraulic valve apparatus of FIG. 11 receives.

  Several embodiments of the claimable invention will now be described in detail with reference to the drawings. The claimable invention is not limited to the embodiments described below, and includes various aspects in which various modifications and improvements have been made 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 vehicle brake system>
FIG. 1 shows a vehicle hydraulic brake system 10 having a hydraulic valve device according to a first embodiment. The hydraulic brake system 10 has a cylinder device 20 for pressurizing brake fluid. The driver of the vehicle can operate the cylinder device 20 by operating the operation device 22 connected to the cylinder device 20, and the cylinder device 20 pressurizes the brake fluid by its own operation. The pressurized brake fluid is supplied to a brake device 26 provided on each wheel via an antilock device 24 connected to the cylinder device 20. The brake device 26 generates a force for stopping the rotation of the wheel, that is, a hydraulic braking force, depending on the pressure of the pressurized brake fluid.

  Although a detailed description of the structure of the brake device 26 is omitted, each brake device 26 includes a brake caliper, a wheel cylinder (brake cylinder) and a brake pad attached to the brake caliper, and a brake disk that rotates with each wheel. It is comprised including. The brake cylinder presses the brake pad against the brake disc depending on the output pressure of the brake fluid pressurized by the cylinder device 20. Due to the friction generated by the pressing, each brake device 26 generates a hydraulic braking force that stops the rotation of the wheel, and the vehicle is braked.

  In the following description, some components such as “brake device 26” are used as a general term, but in the case of indicating that they correspond to any of the four wheels, the left front wheel, the right Subscripts “FL”, “FR”, “RL”, and “RR” are attached to the front wheel, the left rear wheel, and the right rear wheel, respectively. “Front” represents the left side in FIG. 1, and “Back” represents the right side in FIG. In addition, “front side”, “front end”, “forward”, “rear side”, “rear end”, “reverse”, and the like are also represented in the same manner.

i) Configuration of Cylinder Device The cylinder device 20 includes a housing 30 that is a housing of the cylinder device 20, a first pressurizing piston 32 and a second pressurizing piston 34 that pressurize brake fluid supplied to the brake device 26, and a driver's It includes an intermediate piston 36 that moves forward by operating force, and an input piston 38 to which a driver's operation is input through the operating device 22. FIG. 1 shows a state where the cylinder device 20 is not operating, that is, a state where the brake operation is not performed.

  The housing 30 is mainly composed of two members, specifically, a first housing member 40 and a second housing member 42. The first housing member 40 has a generally cylindrical shape with the front end closed, and a flange 44 is formed on the outer periphery of the rear end. The first housing member 40 is fixed to the vehicle body at the flange 44. The first housing member 40 has three portions having different inner diameters, specifically, a front small diameter portion 46 having the smallest inner diameter located on the front side, and a rear large diameter portion 48 having the largest inner diameter located on the rear side. The intermediate portion 50 is located between the front small-diameter portion 46 and the rear large-diameter portion 48 and has an intermediate inner diameter between them.

  The second housing member 42 has a cylindrical shape having a front large diameter portion 52 having a large outer diameter located on the front side and a rear small diameter portion 54 having a small outer diameter located on the rear side. The second housing member 42 is fitted into the rear large diameter portion 48 in a state where the front end portion of the front large diameter portion 52 is in contact with the step surface between the intermediate portion 50 and the rear large diameter portion 48 of the first housing member 40. Yes. The first housing member 40 and the second housing member 42 are fastened to each other by a lock ring 56 fitted on the inner peripheral surface of the rear end portion of the first housing member 40.

  Each of the first pressurizing piston 32 and the second pressurizing piston 34 has a bottomed cylindrical shape whose rear end is closed, and is slidably fitted to the front small-diameter portion 46 of the first housing member 40. Are combined. The first pressure piston 32 is disposed behind the second pressure piston 34. Between the first pressurizing piston 32 and the second pressurizing piston 34, a first pressurizing chamber R1 for pressurizing the brake fluid supplied to the brake device 26FR for the right front wheel is defined. In front of the second pressurizing piston 34, a second pressurizing chamber R2 for pressurizing the brake fluid supplied to the brake device 26FL provided on the left front wheel is defined. The first pressure piston 32 and the second pressure piston 34 are fixed to the headed pin 60 erected at the rear end portion of the first pressure piston 32 and the rear end surface of the second pressure piston 34. The separation distance is limited within the set range by the pin holding cylinder 62 provided. In addition, compression coil springs 64 and 66 are disposed in the first pressurizing chamber R1 and the second pressurizing chamber R2, respectively. The two pressurizing pistons 34 are biased in a direction in which they are separated from each other, and the first pressurizing piston 32 and the second pressurizing piston 34 are biased rearward, and the first pressurizing piston 32 is It is in contact with the front end surface of the intermediate piston 36.

  The intermediate piston 36 includes a cylindrical main body 70 having both ends opened and a lid 72 that closes the front end of the main body 70. The intermediate piston 36 is slidably fitted to the inner peripheral surface of the intermediate portion 50 of the first housing member 40 with the front end in contact with the rear end of the first pressure piston 32. An input chamber R3 is defined between the rear end of the intermediate piston 36 and the front end portion of the second housing member 42. Incidentally, in FIG. 1, it is shown in the almost collapsed state. In addition, a space formed between the inner peripheral surface of the first housing member 40 and the outer peripheral surface of the first pressurizing piston 32 exists inside the housing 30. The space is partitioned by the front end surface of the intermediate piston 36 and the step surface between the front small-diameter portion 46 and the intermediate portion 50 of the first housing member 40, so that an annular liquid chamber (hereinafter referred to as atmospheric pressure) that is always at atmospheric pressure (hereinafter referred to as the atmospheric pressure chamber). , Sometimes referred to as “atmospheric pressure chamber”).

  The input piston 38 is mainly composed of an outer cylinder member 80 having a cylindrical shape whose front end is closed and whose rear end is open, and a rod member 82 having a generally columnar shape. As for the input piston 38, the rod member 82 is inserted in the outer cylinder member 80 from the rear end side. The input piston 38 is inserted from the front end portion of the main body 70 of the intermediate piston 36 while being held by the second housing member 42, and can be advanced and retracted with respect to the intermediate piston 36. Inside the intermediate piston 36 configured in this manner, a liquid chamber R5 (hereinafter sometimes referred to as “internal chamber”) whose volume changes due to the relative movement of the intermediate piston 36 and the input piston 38 is partitioned. Has been. Incidentally, the backward movement of the input piston 38 is restricted by the flange portion formed at the front end portion of the outer cylinder member 80 coming into contact with the rear end portion of the main body portion 70 of the intermediate piston 36.

  In the internal chamber R5, a first reaction force spring 90 and a second reaction force spring 92, which are two compression coil springs, are disposed between the inner bottom surface of the intermediate piston 36 and the front end surface of the input piston 38. . The first reaction force spring 90 is arranged in series in front of the second reaction force spring 92, and a rod-shaped floating seat 94 is supported by floating between the reaction force springs 90, 92. ing. The first reaction force spring 90 has a front end portion supported by the front end portion of the intermediate piston 36 and a rear end portion supported by the seat surface on the front side of the floating seat 94. On the other hand, the front end of the second reaction force spring 92 is supported by the seat surface on the rear side of the floating seat 94, and the rear end is supported by the front end of the input piston 38. A first buffer rubber 96 is fitted into the front end portion of the floating seat 94 and a second buffer rubber 98 is fitted into the rear end portion. The first buffer rubber 96 abuts against the front end surface of the intermediate piston 36, Since the second buffer rubber 98 abuts against the front end surface of the input piston 38, the approach between the floating seat 94 and the intermediate piston 36 and the approach between the floating seat 94 and the input piston 38 are limited to a certain range. .

  At the rear end of the rod member 82 of the input piston 38, the operating force applied to the brake pedal 100 of the operating device 22 is transmitted to the input piston 38, and the input piston 38 is controlled according to the operation amount of the brake pedal 100. The front end portion of the operation rod 102 of the operating device 22 is connected to advance and retract. Incidentally, the backward movement of the input piston 38 is restricted by the rear end portion of the rod member 82 being locked by the rear end portion of the second housing member 42. In addition, a circular support plate 104 is attached to the operation rod 102, and a boot 106 is passed between the support plate 104 and the housing 30, so that the dust at the rear part of the cylinder device 20 is achieved. Yes.

  The first pressurizing chamber R1 communicates with a main liquid passage 112 connected to the brake device 26FL of the right front wheel through a communication hole 110 whose opening serves as an output port, and communicates with the first pressurizing piston 32. A hole 114 and a communication hole 116 whose opening is a drain port communicate with a reservoir 118 serving as a low-pressure source in a state where it is allowed to be disconnected. On the other hand, the second pressurizing chamber R2 communicates with the main liquid passage 122 connected to the brake device 26FL of the left front wheel via the communication hole 120 whose opening serves as an output port, and is provided in the second pressurizing piston 34. The communication hole 124 and the communication hole 126 whose opening is a drain port communicate with the reservoir 118 in a state where it is allowed to be non-communication.

  The intermediate piston 36 has an outer diameter that is somewhat smaller than the inner diameter of the intermediate portion 50 of the first housing member 40, and a liquid passage 130 having a certain flow path area is formed between them. The input chamber R3 can communicate with the outside through a communication hole 131 having a liquid passage 130 and an opening serving as a connection port. The communication hole 131 is connected to the control pressure communication path 133 via the communication path 132.

The intermediate piston 36 is provided with a communication hole 134 in the lid portion 72 for communicating the atmospheric pressure chamber R4 and the internal chamber R5. The first pressurizing piston 32 has an outer diameter that is somewhat smaller than the inner diameter of the front small-diameter portion 46 of the first housing member 40, and a liquid passage 136 having a certain flow passage area is formed between them. ing. The atmospheric pressure chamber R4 is communicated with the reservoir 118 through the liquid passage 136 and the communication hole 116. Therefore, the atmospheric pressure chamber R4 and the inner chamber R5 are always at atmospheric pressure, and their brake fluid can flow into and out of the reservoir 118.
ii) Configuration of anti-lock device and liquid passage

  The main liquid passage 112 and the main liquid passage 122 are electromagnetic open / close valves (hereinafter, also referred to as “cylinder device cut valves”) 140, 142 that open in a non-excited state and close in an excited state, respectively. The state where the supply of the brake fluid pressurized by the cylinder device 20 to the brake devices 26FL and FR is permitted and the state where the supply is prohibited are selectively realized by opening and closing them.

  The anti-lock device 24 has four electromagnetic on-off valves (hereinafter sometimes referred to as “pressure reducing valves”) 150 that close in the non-excited state and open in the excited state. The valve 150 communicates with a decompression communication path 152 that is connected to the reservoir 118. Further, the anti-lock device 24 is closed in a non-excited state and is opened in the excited state by two electromagnetic on-off valves (hereinafter sometimes referred to as “normally closed pressure increasing valves”) 154, It has two electromagnetic on-off valves (hereinafter sometimes referred to as “normally open pressure increasing valves”) 156 that are opened and closed in an excited state, and these four pressure increasing valves 154 and 156 It communicates with a control pressure communication path 133 connected to the pressure valve device 158.

  Two pressure reducing valves 150 and two normally closed pressure increasing valves 154 are provided for each of the front wheel brake devices 26FL and FR, and each of the pair of normally closed pressure increasing valves 154 and pressure reducing valves 150 is a front wheel. Are connected to main liquid passages 112 and 122 connected to corresponding ones of the brake devices 26FL and FR by connecting passages 160FL and FR. In addition, two pressure reducing valves 150 and two normally open pressure increasing valves 156 are provided for each of the brake devices 26RL and RR of the rear wheel, and one set of normally open pressure increasing valves 156 and pressure reducing valves 150 are Respectively connected to the corresponding ones of the brake devices 26RL, RR of the rear wheels by connecting passages 160RL, RR.

  The hydraulic valve device 158 communicates with a high-pressure communication path 164 connected to a high-pressure source device 162 serving as a high-pressure source. The high-pressure source device 162 includes a hydraulic pump 166 that pumps brake fluid from the reservoir 118, A motor 168 that drives the pressure pump 166 and an accumulator 170 that stores the brake fluid discharged from the hydraulic pump 166 in a pressurized state are provided. The hydraulic valve device 158 further communicates with a backup passage 172 connected to the downstream side of the cylinder device cut valve 140 in the main fluid passage 112 and also communicates with the decompression communication passage 152.

iii) Configuration of Fluid Pressure Valve Device The fluid pressure valve device 158 includes a pressure increasing linear valve 180 as an electromagnetic pressure increasing valve, a pressure reducing linear valve 182 as an electromagnetic pressure reducing valve, and a pressure increasing / reducing valve 184. The pressure increasing / decreasing valve 184 causes the brake fluid pressurized by the high pressure source device 160 to flow in according to the height of the brake fluid increased by the pressure increasing linear valve 180 or reduced by the pressure reducing linear valve 182. The hydraulic pressure of the brake fluid can be adjusted by increasing the hydraulic pressure of the brake fluid or by reducing the hydraulic pressure of the brake fluid by flowing the brake fluid into the reservoir 118. The adjusted brake fluid is supplied to the wheel cylinder of each brake device 26 via the input chamber R3 of the cylinder device 20 and the antilock device 24. That is, the hydraulic valve device 158 can continuously change the wheel cylinder pressure, which is the hydraulic pressure of the wheel cylinder, and can control the wheel cylinder pressure to an arbitrary height.

  As shown in FIG. 2, the pressure increasing / reducing valve 184 is a hollow housing 190, a plunger 192 provided in the housing 190 so as to be movable in the axial direction thereof, and movable in the axial direction below the plunger 192. A cylindrical rod-shaped piston 194 provided on the movable member 196 and a moving member 196 provided above the plunger 192 so as to be movable in the axial direction. The housing 190 includes a generally cylindrical outer member 198, a bottomed cylindrical member 200 to which a lower end portion of the outer member 198 is fixedly fitted, and a lid member 202 that closes the upper end of the outer member 198. The brake fluid is filled inside.

  The inner peripheral surface of the outer member 198 is composed of portions having five different inner diameters, and the inner diameter increases toward the top. That is, in order from the lower end, the first inner diameter portion 204 having the smallest inner diameter, the second inner diameter portion 206 having an inner diameter larger than the inner diameter of the first inner diameter portion 204, and the third inner diameter larger than the inner diameter of the second inner diameter portion 206. An inner diameter portion 208, a fourth inner diameter portion 210 having an inner diameter larger than the inner diameter of the third inner diameter portion 208, and a fifth inner diameter portion 212 having the largest inner diameter are located, and the inner peripheral surface of the outer shell member 198 has a stepped shape. ing.

  The outer peripheral surface of the rod-shaped piston 194 has a stepped shape, and is divided into a large-diameter portion 214 having a large outer diameter located at the upper end portion and a small-diameter portion 216 having a small outer diameter located at the lower end portion. The small diameter portion 216 of the rod-shaped piston 194 is slidably fitted to the first inner diameter portion 204 of the outer member 198, and the large diameter portion 214 is slidably fitted to the second inner diameter portion 206. The step surface between the large diameter portion 214 and the small diameter portion 216 and the step surface between the first inner diameter portion 204 and the second inner diameter portion 206 are in contact with each other, and the downward movement range of the rod-shaped piston 194 is small. Limited. The first liquid chamber 218 is defined by the outer member 198, the rod-shaped piston 194, and the bottomed cylindrical member 200 in a state where the rod-shaped piston 194 is fitted to the outer member 198.

  The plunger 192 includes a cylindrical main body 220, an intermediate part 222 having an outer diameter smaller than the outer diameter of the main body part 220, and an intermediate part 222 positioned above the intermediate part 222. And a rod portion 224 having an outer diameter smaller than the outer diameter. The main body portion 220 of the plunger 192 is slidably fitted to the second inner diameter portion 206 as the fourth chamber portion of the outer member 198, and the lower end surface of the main body portion 220 is formed on the upper end surface of the rod-shaped piston 194. It is in contact with the projected portion 226. Even in a state in which the convex portion 226 and the lower end surface of the main body portion 220 are in contact with each other, there is a clearance between the lower end surface of the main body portion 220 and the upper end surface of the rod-shaped piston 194, and the clearance serves as the second liquid chamber 228. It is functioning.

  The outer peripheral surface of the moving member 196 is also stepped, and has a flange portion 230 having the largest outer diameter, and an upper first outer diameter portion located above the flange portion 230 and having an outer diameter smaller than the outer diameter of the flange portion 230. 232, an upper second outer diameter portion 234 having an outer diameter smaller than the outer diameter of the upper first outer diameter portion 232 located above the upper first outer diameter portion 232, and a flange portion located below the flange portion 230 The lower first outer diameter portion 236 having an outer diameter smaller than the outer diameter of 230, and the lower second outer portion having an outer diameter smaller than the outer diameter of the lower first outer diameter portion 236, which is located below the lower first outer diameter portion 236. And a diameter portion 238. The lower second outer diameter portion 238 is slidably fitted to the third inner diameter portion 208 of the outer member 198, and the moving member 196 is disposed at an opening upward of the third inner diameter portion 208 as the second chamber portion. The outer peripheral surface can be seated. More specifically, the step surface 240 between the third inner diameter portion 208 and the fourth inner diameter portion 210 is tapered, and the step between the lower first outer diameter portion 236 and the lower second outer diameter portion 238. The surface functions as a valve body and can be seated on the stepped surface 240 having a tapered shape.

  A concave portion 250 is formed on the lower surface of the lid member 202 fixedly fitted to the upper end of the housing 190, and the second upper portion of the moving member 196 is inserted into the lower opening of the concave portion 250 as the third chamber portion. The outer diameter part 234 is slidably fitted. A coil spring 252 is disposed between the lower surface of the lid member 202 and the flange portion 230 of the moving member 196 in a compressed state, and the moving member 196 is biased downward by the elastic force of the coil spring 252. ing. That is, due to the elastic force of the coil spring 252, the moving member 196 is biased in a direction in which a portion functioning as a valve body on the outer peripheral surface of the moving member 196 approaches the stepped surface 240 formed on the inner peripheral surface of the outer member 198. Has been. Incidentally, the third liquid chamber 254 is partitioned by the fourth inner diameter portion 210 of the outer member 198 and the moving member 196 in a state where the outer peripheral surface of the moving member 196 is seated on the stepped surface 240. In addition, the outer peripheral surface of the lower second outer diameter portion 238 of the moving member 196 is slightly recessed, and the recessed portion of the outer peripheral surface of the lower second outer diameter portion 238 and the third inner diameter portion of the outer member 198 in the seated state. 208 divides the fourth liquid chamber 256.

  A through hole 260 penetrating in the axial direction of the moving member 196 is formed inside the moving member 196, and the through hole 260 is open to the upper end surface and the lower end surface of the moving member 196. Inside the moving member 196, a connection hole 261 that opens to the outer peripheral surface of the lower first outer diameter portion 236 and the through hole 260 is further formed to extend in the radial direction. A generally cylindrical pin 262 is slidably inserted into the through-hole 260 as an internal chamber from the opening at the upper end thereof, and the upper end surface of the pin 262 is formed in a recess 250 as an auxiliary chamber of the lid member 202. Supported on the inner surface. An annular rubber member 266 is provided inside the concave portion 250 of the lid member 202 with the pin 262 penetrated, and the upper end surface of the moving member 196 is in close contact with the lower surface of the rubber member 266. The rubber member 266 functions as a seal, and liquid leakage between the moving member 196 and the lid member 202 is prohibited by the rubber member 266.

  The rod portion 224 and the intermediate portion 222 of the plunger 192 are inserted into the through hole 260 from the lower end opening thereof, and the outer peripheral surface of the plunger 192 can be seated in the opening of the lower end of the through hole 260. More specifically, the opening at the lower end of the through hole 260 is tapered, and the step surface between the intermediate portion 222 of the plunger 192 and the main body portion 220 functions as a valve body. It can be seated. In addition, a coil spring 270 is disposed in a compressed state between a step surface between the rod portion 224 and the intermediate portion 222 of the plunger 192 and a step surface formed inside the through hole 260. The plunger 192 is biased downward by the elastic force of the coil spring 270. That is, due to the elastic force of the coil spring 270, the plunger 192 is biased in a direction in which a portion functioning as a valve body on the outer peripheral surface of the plunger 192 is separated from the opening at the lower end of the through hole 260. Incidentally, in a state where the plunger 192 is seated on the opening at the lower end of the through hole 260 against the elastic force of the coil spring 270, the third inner diameter portion 208 of the outer member 198, the main body portion 220 of the plunger 192, The fifth liquid chamber 272 is partitioned by the end face.

  A first communication passage 274 that opens to the fourth liquid chamber 256 and the outer peripheral surface of the outer member 198 is formed in the third inner diameter portion 208 of the outer member 198 so as to extend in the radial direction. The high-pressure communication path 164 is connected to an opening to the outer peripheral surface of 274. That is, the fourth fluid chamber 256 is configured such that the brake fluid pressurized by the high-pressure source device 162 flows in through the high-pressure communication passage 164 and the first communication passage 274, and functions as a high-pressure chamber. . Hereinafter, the fourth liquid chamber 256 may be referred to as a high pressure chamber 256. Further, a second communication path 276 that opens to the fifth liquid chamber 272 and the outer peripheral surface of the outer member 198 is formed in the third inner diameter portion 208 of the outer member 198 so as to extend in the radial direction. The decompression communication path 152 is connected to an opening to the outer peripheral surface of the communication path 276. That is, the fifth fluid chamber 272 is configured to cause the brake fluid to flow out to the reservoir 118 via the decompression communication passage 152 and the second communication passage 276, and functions as a low pressure chamber. Hereinafter, the fifth liquid chamber 272 may be referred to as a low pressure chamber 272. Incidentally, the flow of the brake fluid between the low pressure chamber 272 and the high pressure chamber 256 is achieved by fitting the lower second outer diameter portion 238 of the moving member 196 into the third inner diameter portion 208 as the second chamber portion. Blocked. A drain path 278 that opens to the first inner diameter portion 204 of the outer member 198 is connected to the second communication path 276.

  A third communication passage 280 that opens to the second liquid chamber 228 and the outer peripheral surface of the outer member 198 is formed in the second inner diameter portion 206 of the outer member 198 so as to extend in the radial direction. A connection passage 282 connected to the high-pressure communication passage 164 is connected to the opening to the outer peripheral surface of 280. As shown in FIG. 1, the connection passage 282 is provided with an electromagnetic pressure-increasing linear valve 180 that is a normally closed valve. A branch passage 284 connected to the pressure reducing communication passage 152 is connected between the pressure increasing linear valve 180 and the pressure increasing / decreasing valve 184 in the connection passage 282. A linear valve 182 is provided.

  A fourth communication passage 286 that opens to the third liquid chamber 254 and the outer peripheral surface of the outer member 198 is formed in the fourth inner diameter portion 210 of the outer member 198 so as to extend in the radial direction. The control pressure communication path 133 is connected to the opening to the outer peripheral surface of 286. That is, the third liquid chamber 254 functions as a pressure regulating chamber, and hereinafter, the third liquid chamber 254 may be referred to as a pressure regulating chamber 254. The bottomed cylindrical member 200 is formed with a port 288 that opens to the first liquid chamber 218, and the backup passage 172 is connected to the first liquid chamber 218 via the port 288.

iv) Operation of Hydraulic Pressure Valve Device Due to the above-described structure, the pressure increasing / reducing valve 184 may be referred to as the hydraulic pressure of the brake fluid supplied to the second hydraulic chamber 228 as the moving force generating chamber (hereinafter referred to as “control hydraulic pressure”). ), The fluid pressure of the brake fluid in the pressure regulating chamber 254 (hereinafter sometimes referred to as “pressure regulating chamber pressure”) is controlled and increased in a controllable manner. It is possible. More specifically, when the control hydraulic pressure is atmospheric pressure, the flow of brake fluid between the high pressure chamber 256 and the pressure regulating chamber 254 is blocked, and the pressure regulating chamber 254 and the low pressure chamber 272 are Brake fluid flow between is allowed. That is, when the control hydraulic pressure is atmospheric pressure, the pressure regulating chamber 254 communicates with the reservoir 118 via the low pressure chamber 272, and the pressure regulating chamber pressure is also atmospheric pressure. When the control hydraulic pressure is increased, the flow of the brake fluid between the pressure regulating chamber 254 and the low pressure chamber 272 is interrupted, and the brake fluid between the high pressure chamber 256 and the pressure regulating chamber 254 is blocked. By allowing the flow, the pressure regulating chamber pressure can be increased. Further, when the control hydraulic pressure is reduced after increasing the pressure regulating chamber pressure, the flow of the brake fluid between the high pressure chamber 256 and the pressure regulating chamber 254 is interrupted, and the pressure regulating chamber 254 and the low pressure are reduced. By allowing the flow of the brake fluid to and from the chamber 272, it is possible to reduce the pressure-regulating chamber pressure that has been increased.

  Specifically, when the control hydraulic pressure is atmospheric pressure, the outer peripheral surface of the moving member 196 is formed on the outer member 198 by the elastic force of the coil spring 252 as the first biasing member. It is seated on the stepped surface 240 and the flow of brake fluid between the high pressure chamber 256 and the pressure regulating chamber 254 is blocked. Further, the plunger 192 is separated from the opening to the lower end of the through hole 260 formed in the moving member 196 by the elastic force of the coil spring 270 as the second urging member, and the brake fluid is separated from the through hole 260 and the connection hole. Through the H.261, the pressure regulating chamber 254 and the low pressure chamber 272 can be circulated. That is, the through hole 260 and the connection hole 261 function as a communication path, and the pressure regulation chamber pressure is atmospheric pressure by the communication path. In addition, the opening to the lower end of the through hole 260 functions as a low pressure chamber side opening, and the opening to the outer peripheral surface of the connection hole 261 functions as a pressure regulating chamber side opening.

  Incidentally, the control hydraulic pressure is increased or decreased by controlling the energization amount to the pressure increasing linear valve 180 and the pressure reducing linear valve 182. More specifically, the pressure-increasing linear valve 180 is closed and the pressure-decreasing linear valve 182 is opened while the energization amount to the pressure-increasing linear valve 180 and the pressure-decreasing linear valve 182 is zero. The hydraulic pressure for control is atmospheric pressure. The depressurization linear valve 182 is closed while the depressurization linear valve 182 is closed by increasing the energization amount to the depressurization linear valve 182 to some extent and controlling the energization amount to the depressurization linear valve 180. The amount is controlled. At this time, the control hydraulic pressure is increased according to the energization amount to the pressure increasing linear valve 180. After the control hydraulic pressure is increased, the energization amount to the pressure increasing linear valve 180 is set to 0, and the energizing amount to the pressure reducing linear valve 182 is controlled, whereby the pressure increasing linear valve 180 is closed. The valve opening amount of the pressure reducing linear valve 182 is controlled. At this time, the control hydraulic pressure is reduced according to the amount of current supplied to the pressure-reducing linear valve 182.

  As described above, when the pressure reducing linear valve 182 is closed and the valve opening amount of the pressure increasing linear valve 180 is controlled, the control hydraulic pressure is increased and the plunger 192 is urged upward. That is, the plunger 192 is opened to the lower end of the through hole 260 (hereinafter, may be referred to as “low pressure chamber side opening”) by the moving force generator composed of the pressure increasing linear valve 180 and the pressure reducing linear valve 182. A force for moving the plunger 192 in the approaching direction is generated. By this force, first, the plunger 192 moves upward against the elastic force of the coil spring 270, and the outer peripheral surface of the plunger 192 is seated on the opening at the lower end of the through hole 260. In this state, the flow of brake fluid between the pressure regulating chamber 254 and the low pressure chamber 272 is blocked, and the flow of brake fluid between the high pressure chamber 256 and the pressure regulating chamber 254 is also blocked. When the plunger 192 moves upward with the outer peripheral surface of the plunger 192 seated on the low-pressure chamber side opening, that is, with the plunger 192 in contact with the moving member 196, the moving member 196 also moves upward. As the moving member 196 moves upward, the outer peripheral surface of the moving member 196 is separated from the step surface 240 formed on the outer member 198, so that the brake fluid between the high pressure chamber 256 and the pressure adjusting chamber 254 is removed. Flow is allowed. At this time, the pressure regulating chamber pressure can be increased in a controllable manner by controlling the control hydraulic pressure. That is, the pressure regulating chamber pressure can be increased in accordance with the amount of current supplied to the pressure increasing linear valve 180.

In addition, as shown in FIG. 3, the pressure receiving area A _{1 of the} portion that receives the pressure difference between the hydraulic pressure of the brake fluid in the high pressure chamber 256 (hereinafter sometimes referred to as “high pressure chamber pressure”) and the pressure regulating chamber pressure, has become a low-pressure chamber of the brake fluid in 272 hydraulic, that is, the pressure receiving area a ₂ of a portion receiving a pressure difference between the atmospheric pressure and the pressure in the high pressure chamber same. In other words, the pressure receiving area A ₁ of the moving member 196 that receives the high pressure chamber pressure in the upward direction is the same as the pressure receiving area A ₂ of the moving member 196 that receives the high pressure chamber pressure in the downward direction. For this reason, when the pressure adjusting chamber pressure is atmospheric pressure, a force slightly exceeding the force corresponding to the elastic force of the coil spring 252 is applied to the moving member 196 if the sliding resistance due to the seal or the like is ignored. Thus, the outer peripheral surface of the moving member 196 can be separated from the step surface 240 of the outer member 198. In other words, in the initial operation of the moving member 196, if the sliding resistance due to the seal or the like is ignored, the pressure adjustment is performed if a force slightly exceeding the force corresponding to the elastic force of the two coil springs 252 and 270 is applied to the plunger 192. The chamber pressure can be increased. That is, the energization amount to the pressure-increasing linear valve 180 in the initial operation of the moving member 196 can be reduced, and the power consumption can be reduced.

  Further, in a state where the pressure regulating chamber 254 is sealed, a force for moving the moving member 196 in the axial direction by the pressure regulating chamber pressure acts on the moving member 196. More specifically, a force having a magnitude corresponding to the pressure receiving area of the moving member 196 that receives the pressure adjusting chamber pressure in the upward direction acts as a force for moving the moving member 196 upward, and is adjusted in the downward direction. A force having a magnitude corresponding to the pressure receiving area of the moving member 196 that receives the pressure chamber pressure acts as a force for moving the moving member 196 downward. Therefore, when the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the upward direction is larger than the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the downward direction, There is a risk of liquid leakage from the pressure regulating chamber 254 to the low pressure chamber 272 when the pressure is increased. On the other hand, when the pressure receiving area of the moving member 196 receiving the pressure regulating chamber pressure in the downward direction is larger than the pressure receiving area of the moving member 196 receiving the pressure regulating chamber pressure in the upward direction, the pressure regulating chamber pressure is reduced. In doing so, the plunger 192 becomes difficult to separate from the opening of the through hole 260, and there is a risk that hysteresis will occur in the pressure characteristics. Therefore, the pressure increasing / reducing valve 184 is designed such that the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the downward direction is the same as the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the upward direction. Therefore, the occurrence of liquid leakage and pressure characteristic hysteresis when the pressure regulating chamber pressure is increased is suppressed.

Specifically, the seating from the pressure receiving area of a portion the outer peripheral surface of the moving member 196 is seated on the stepped surface 240 of the outer member 198 (corresponding to the pressure area A ₁₎ outer peripheral surface of the plunger 192 to the low pressure chamber side opening The reduced pressure receiving area A ₃ (see FIG. 3) corresponding to the position corresponds to the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the downward direction, and the moving member 196 is the recess 250 of the lid member 202. Is obtained by subtracting the cross-sectional area A ₅ (see FIG. 3) of the pin 262 from the pressure receiving area A ₄ (see FIG. 3) of the portion slidably fitted in the pressure chamber, and receives the pressure regulating chamber pressure in the upward direction. This corresponds to the pressure receiving area of the moving member 196. That is, it is designed so that the relationship between the pressure receiving areas satisfies the following formula.
A ₁ −A ₃ = A ₄ −A ₅
In the pressure increase valve 184, since it is the same as the pressure receiving area A ₁ and the pressure receiving area A _4, has the same the cross-sectional area A ₅ of the pressure receiving area A ₃ and the pin 262.

  Further, after the pressure regulating chamber pressure is increased, when the control hydraulic pressure is reduced by closing the pressure increasing linear valve 180 and controlling the valve opening amount of the pressure reducing linear valve 182, the moving member 196. Is seated on the stepped surface 240 of the outer member 198. In a state where the outer peripheral surface of the moving member 196 is seated on the stepped surface 240 and the plunger 192 is seated in the low pressure chamber side opening, the pressure regulating chamber pressure is maintained at the increased hydraulic pressure. Then, by further reducing the control hydraulic pressure from this state, the plunger 192 is separated from the low-pressure chamber side opening, and the flow of brake fluid between the low-pressure chamber 272 and the pressure regulating chamber 254 is allowed. That is, the pressure regulation chamber pressure can be reduced in accordance with the amount of current supplied to the pressure-reducing linear valve 182.

  As described above, the main pressure increasing / decreasing valve 184 can increase or decrease the pressure regulation chamber pressure in a controllable manner by controlling the energization amount to the pressure increasing linear valve 180 and the pressure reducing linear valve 182. . When the pressure is increased, the outer peripheral surface of the moving member 196 is separated from the step surface 240 formed on the outer member 198, and the brake fluid flows from the high pressure chamber 256 to the pressure adjusting chamber 254. At this time, the brake fluid flows in a direction in which the outer peripheral surface that functions as the valve body of the moving member 196 is separated from the step surface 240 that functions as the valve seat. On the other hand, at the time of depressurization, the outer peripheral surface of the plunger 192 is separated from the low-pressure chamber side opening, and the brake fluid flows from the adjustment chamber 254 to the low-pressure chamber 272. At this time, the brake fluid flows in a direction in which the outer peripheral surface that functions as the valve body of the plunger 192 is separated from the opening of the through hole 260 that functions as the valve seat. That is, in the pressure increasing / decreasing valve 184, when the pressure adjusting chamber pressure is controlled, the brake fluid is separated from the valve seat, that is, in the direction in which the valve is opened by the brake fluid (hereinafter, “self-opening”). It may be called “direction”).

  On the other hand, in the conventional pressure increasing / decreasing valve, when controlling the pressure regulating chamber pressure, the brake fluid is in the direction in which the valve body approaches the valve seat, that is, the direction in which the valve is closed by the brake fluid (hereinafter referred to as “self-closing direction”). It may be said that the structure flows through. When the brake fluid flows in the self-closing direction at the time of pressure adjustment, the valve body may be brought close to the valve seat by the flow of the brake fluid and may be closed. For this reason, during pressure regulation, there is a possibility that a so-called hunting phenomenon may occur, in which the valve closing due to the flow of the brake fluid and the valve opening for controlling the pressure regulating chamber pressure are frequently repeated. There is a possibility that the control of the room pressure cannot be executed. In the present pressure increasing / decreasing valve 184, as described above, the brake fluid flows in the self-opening direction even at the time of pressure increase and pressure reduction, and the occurrence of the hunting phenomenon is suppressed. Therefore, in the pressure increasing / reducing valve 184, the control accuracy of the pressure regulating chamber pressure is good.

  Further, the pressure increasing / reducing valve 184 can adjust the pressure regulating chamber pressure to a pressure corresponding to the energization amount to the pressure increasing linear valve 180 and the pressure reducing linear valve 182 by the operation as described above. Yes. However, if the energization of the pressure-increasing linear valve 180 and the pressure-reducing linear valve 182 is stopped for some reason, the plunger 192 cannot be moved and the pressure-regulating chamber pressure cannot be increased. There is a fear. In such a case, the pressure increasing / reducing valve 184 increases the pressure regulating chamber pressure depending on the brake fluid pressurized by the operation of the cylinder device 20 without relying on electric power.

  More specifically, when power supply to the hydraulic brake system 10 is cut off, as will be described in detail later, brake fluid pressurized by the operation of the cylinder device 20 flows into the backup passage 172, and the pressurization is performed. The brake fluid thus made flows into the first fluid chamber 218. For this reason, as the hydraulic pressure of the brake fluid in the first fluid chamber 218 increases, the rod-shaped piston 194 moves upward, and the plunger 192 also moves upward by the rod-shaped piston 194. As the plunger 192 moves upward, the plunger 192 is seated on the low-pressure chamber side opening, and the outer peripheral surface of the moving member 196 is separated from the step surface 240 of the outer member 198, so that the high-pressure chamber 256 and the pressure regulating chamber 254 are separated. Brake fluid flow between is allowed. As described above, in the present pressure increasing / decreasing valve 184, it is possible to increase the adjustment chamber pressure without depending on the electric power even when the electric power fails.

v) Control of the hydraulic brake system When the brake pedal 100 is operated by the driver, the input piston 38 moves forward by the operation force applied to the brake pedal 100, and the two reaction force springs 90 and 92 are moved. Compressed. The intermediate piston 36 moves forward and the first pressurizing piston 32 moves forward due to the elastic reaction force of the reaction force springs 90 and 92. As the first pressurizing piston 32 advances, the second pressurizing piston 34 advances, and the brake fluid in the first pressurizing chamber R1 and the second pressurizing chamber R2 is pressurized. On the other hand, when the brake fluid regulated by the hydraulic valve device 158 is inputted to the input chamber R3, the intermediate piston 36 is advanced by the regulated brake fluid, and similarly, the first pressurizing chamber R1, The brake fluid in the second pressurizing chamber R2 is pressurized. That is, in the cylinder device 20, the brake fluid is pressurized by both the operating force by the driver and the fluid pressure of the brake fluid regulated by the fluid pressure valve device 158, and when both of them are input, The brake fluid pressurized depending on both of them can be output.

  However, in the brake system 10, the brake cylinder of the brake device 26 is operated based on the brake fluid regulated by the hydraulic valve device 158 without relying on the brake fluid pressurized by the cylinder device 20 in the normal state. Electric braking control that is control to be performed is executed. Since electric braking control is not directly related to the present invention, in brief explanation, in this control, the cylinder device cut valves 140 and 142 are energized to be in a closed state, and two anti-lock devices 24 are normally connected. The closed pressure increasing valve 154 is excited and opened. In addition, the two normally open pressure increasing valves 156 of the antilock device 24 are not excited and are opened, and the four pressure reducing valves 150 are not excited and are closed. A target target hydraulic pressure is determined according to the depression amount of the brake pedal 100, and the pressure increasing linear valve 180 and the pressure reducing linear valve 182 are energized as described above so that the control chamber pressure becomes the target hydraulic pressure. The Then, the brake fluid adjusted to the target hydraulic pressure is supplied to the brake device 26 of each wheel via the control pressure communication path 133. Thus, by controlling the operation of the hydraulic valve device 158, a braking force corresponding to the amount of depression of the brake pedal 100 is generated.

  On the other hand, when power is lost, power is not supplied to each control valve. Therefore, the cylinder device cut valves 140 and 142 are opened, and the two normally open pressure increasing valves 156 of the antilock device 24 are opened. The two normally closed pressure increasing valves 154 are closed. Further, the four pressure reducing valves 150 are closed. In this state, the brake fluid pressurized by the cylinder device 20 flows into the backup passage 172 via the main fluid passage 112 and further flows into the first fluid chamber 218 of the pressure increasing / reducing valve 184. As described above, as the brake fluid pressure in the first fluid chamber 218 increases, the rod-shaped piston 194 is moved to increase the control chamber pressure. The increased brake fluid is supplied to the brake devices 26RL and RR on the rear wheel side via the control pressure communication path 133. Further, the increased brake fluid is supplied to the input chamber R3 through the communication passage 132, and the cylinder device 20 applies the brake fluid by the hydraulic pressure of the supplied brake fluid and the operating force by the driver. Press. The brake fluid pressurized by the cylinder device 20 is supplied to the brake devices 26FL and FR on the front wheel side through the main fluid passages 112 and 122. That is, at the time of power failure, the brake devices 26RL and RR on the rear wheel side generate braking force based on the brake fluid increased through the hydraulic valve device 158, and also the brake device 26FL on the front wheel side. , FR generates a braking force based on the brake fluid increased in pressure via the hydraulic valve device 158 and the operating force by the driver.

  FIG. 4 shows a vehicle hydraulic brake system 302 including a hydraulic valve device 300 according to the second embodiment. The brake system 302 has substantially the same configuration as that of the previous brake system 10 except for the hydraulic valve device 300, and includes many components common to the previous system 10. For this reason, in the description of the present system 302, the same reference numerals are used for the components common to the previous system 10, and the description thereof will be omitted or simplified.

  As shown in FIG. 5, the hydraulic valve device 300 has a hollow housing 310, a plunger 312 that is provided in the housing 310 so as to be movable in the axial direction thereof, and is movable in the axial direction above the plunger 312. And a cylindrical coil 316 provided on the outer periphery of the housing 310. The housing 310 includes a bottomed cylindrical lower outer shell member 318 provided at the lower end portion, a covered cylindrical upper outer shell member 320 provided at the upper end portion, the lower outer shell member 318, and the upper outer shell member 320. And a generally cylindrical core 322 connecting the two.

  The core 322 includes a flange portion 330 having the largest outer diameter, a lower portion 332 having an outer diameter smaller than the outer diameter of the flange portion 330 that is located below the flange portion 330, and a flange portion 330 that is located above the flange portion 330. An upper first outer diameter portion 334 having an outer diameter smaller than the outer diameter of the upper first outer diameter portion 334 and an upper second outer diameter having an outer diameter smaller than the outer diameter of the upper first outer diameter portion 334. Part 336. The lower portion 332 of the core 322 is fixedly fitted to the lower outer shell member 318, and the coil 316 is fixed to the lower surface of the flange portion 330 of the core 322 and the outer peripheral surface of the lower outer shell member 318.

  The core 322 is formed with a through hole 338 penetrating in the axial direction of the housing 310, and the plunger 312 has a rod portion 340 inserted into the through hole 338, a lower end surface of the core 322, and a lower outer shell member 318. And a main body portion 342 disposed between the inner bottom surface and the inner bottom surface. The rod portion 340 has a large diameter portion 344 having a large outer diameter located at the lower end portion and a small diameter portion 346 having a small outer diameter located at the upper end portion, and the through hole 338 is located at the lower end portion and has an inner diameter. Large inner diameter part 348 and a small inner diameter part 350 having a small inner diameter located at the upper end. The large diameter portion 344 of the rod portion 340 is slidably fitted to the large inner diameter portion 348 of the through hole 338, and the small diameter portion 346 of the rod portion 340 is in a state where there is a clearance in the small inner diameter portion 350 of the through hole 338. Has been inserted. A coil spring 352 is disposed in a compressed state between a step surface between the large diameter portion 344 and the small diameter portion 346 and a step surface between the large inner diameter portion 348 and the small inner diameter portion 350. The plunger 312 is urged downward by the elastic force of the coil spring 352.

  The upper outer shell member 320 has a first inner diameter portion 360 having the largest inner diameter located at the lower end portion, and a second inner diameter portion 362 having an inner diameter smaller than the inner diameter of the first inner diameter portion 360 located above the first inner diameter portion 360. And the third inner diameter portion 364 having the smallest inner diameter located at the upper end portion, and located between the third inner diameter portion 364 and the second inner diameter portion 362 and smaller than the inner diameter of the second inner diameter portion 362 and the third inner diameter portion. And a fourth inner diameter portion 366 having an inner diameter larger than the inner diameter of the portion 364. The upper second outer diameter portion 336 of the core 322 is fixedly fitted to the second inner diameter portion 362 of the upper outer shell member 320, and the upper first outer diameter portion 334 of the core 322 is the upper outer shell member 320 of the upper outer shell member 320. The inner diameter portion 360 is fixedly fitted. The step surface between the upper first outer diameter portion 334 and the upper second outer diameter portion 336 and the step surface between the first inner diameter portion 360 and the second inner diameter portion 362 are separated from each other. A first liquid chamber 368 is defined by the step surface, the upper second outer diameter portion 336, and the first inner diameter portion 360.

  A generally cylindrical cylindrical member 370 is slidably fitted to the fourth inner diameter portion 336 of the upper outer shell member 320, and the cylindrical member 370 is located at the lower end portion and the lower end portion 372 having the smallest inner diameter. A first intermediate portion 374 that is located above the lower end portion 372 and has an inner diameter larger than the inner diameter of the lower end portion 372, an upper end portion 376 that is located at the upper end portion and has the largest inner diameter, and the upper end portion 376 and the first intermediate portion And a second intermediate portion 378 having an inner diameter larger than the inner diameter of the first intermediate portion 374 and smaller than the inner diameter of the upper end portion 376. A cylindrical lid member 380 is fixedly fitted to the upper end portion 376, and the upper portion of the lid member 380 extends from the upper end of the cylindrical member 370 and the third inner diameter portion 364 of the upper outer member 320. It is slidably fitted to.

  A coil spring 382 is disposed in a compressed state between the lower end surface of the cylindrical member 370 and the upper end surface of the core 322. The cylindrical member 370 and the lid member 380 are biased upward by the elastic force of the coil spring 382, and the upper end surface of the lid member 380 and the lid inner surface of the upper outer shell member 320 are in contact with each other. The upper end surface of the lid member 380 is slightly recessed, and the second liquid chamber 384 is defined by the recessed portion and the inner surface of the lid of the upper outer shell member 320. Further, the step surface between the third inner diameter portion 364 and the fourth inner diameter portion 336 of the upper outer member 320 is separated from the upper end surface of the cylindrical member 370, and these two surfaces, the lid member 380, and the fourth inner diameter portion are separated. A third liquid chamber 386 is partitioned by the portion 336.

  A recess 388 is formed on the lower surface of the lid member 380, and a moving member 314 is inserted into the recess 388 and the cylindrical member 370. The moving member 314 includes a flange portion 390 having the largest outer diameter, a lower first outer diameter portion 392 having an outer diameter smaller than the outer diameter of the flange portion 390 and a lower first outer diameter thereof. A lower second outer diameter portion 394 having an outer diameter smaller than the outer diameter of the lower first outer diameter portion 392 and an outer diameter smaller than the outer diameter of the flange portion 390, which is positioned above the flange portion 390. It has an upper first outer diameter portion 396 and an upper second outer diameter portion 398 that is located above the upper first outer diameter portion 396 and has an outer diameter smaller than the outer diameter of the upper first outer diameter portion 396. . The lower first outer diameter portion 392 is slidably fitted to the first intermediate portion 374 of the cylindrical member 370, and the lower second outer diameter portion 394 is slidably fitted to the lower end portion 372 as the first inter-chamber portion. The upper second outer diameter portion 398 and the upper end portion of the upper first outer diameter portion 396 are inserted into the recess 388. The lower end portion of the upper first outer diameter portion 396 and the flange portion 390 are located in the second intermediate portion 378, and the flange portion 390 opens upwardly of the first intermediate portion 374 as the second chamber portion. It is possible to sit on. More specifically, the step surface 400 between the first intermediate portion 374 and the second intermediate portion 378 is tapered, and the step surface 400 functions as a valve seat, and a flange portion 390 that functions as a valve body is provided. It is possible to sit on the step surface 400.

  A coil spring 402 as a first urging member is disposed in a compressed state between the upper end surface of the flange portion 390 and the lower surface of the lid member 380. The coil spring 402 is lowered by the elastic force of the coil spring 402. That is, the moving member 314 is biased in a direction in which the flange portion 390 is seated on the step surface 400 formed in the cylindrical member 370. In a state where the flange portion 390 is seated on the step surface 400, the fourth liquid chamber 404 is defined by the second intermediate portion 378, the moving member 314, and the lid member 380 of the cylindrical member 370. The outer peripheral surface of the lower first outer diameter portion 392 of the moving member 314 is slightly recessed, and the fifth liquid is formed by the recessed portion of the lower first outer diameter portion 392 and the first intermediate portion 374 of the cylindrical member 370. A chamber 406 is defined.

  An annular rubber member 410 is provided in the recess 388 serving as the third chamber portion of the lid member 380. The upper second outer diameter portion 398 of the moving member 314 is inserted into the rubber member 410 as the third inter-chamber rubber member, and the upper first outer diameter portion 396 and the upper second outer diameter are formed on the lower surface of the rubber member 410. The step surface between the portions 398 is in close contact. The rubber member 410 functions as a seal, and liquid leakage between the moving member 314 and the lid member 380 is prohibited by the rubber member 410. An annular rubber member 412 is also provided at the lower end 372 as the first chamber portion of the cylindrical member 370. The lower second outer diameter portion 394 of the moving member 314 is inserted into the rubber member 412 as the first inner chamber rubber member, and the lower first outer diameter portion 392 and the lower second outer diameter are formed on the upper surface of the rubber member 412. The step surface between the portions 394 is in close contact. The rubber member 412 also functions as a seal, and liquid leakage between the moving member 314 and the lower end 372 of the cylindrical member 370 is prohibited by the rubber member 412.

  The lower second outer diameter portion 394 of the moving member 314 extends from the lower end of the cylindrical member 370 and is slidable on the small inner diameter portion 350 as the first chamber portion of the through hole 338 formed in the core 322. It is mated. With such a structure, the sixth liquid chamber 414 is defined by the lower second outer diameter portion 394, the upper end surface of the core 322, the lower end surface of the cylindrical member 370, and the fourth inner diameter portion 366 of the upper outer member 320. The lower second outer diameter portion 394 is formed with a moving member communication path 416 that opens to the outer peripheral surface and opens to the lower end surface, and the inside of the through hole 338 and the sixth liquid chamber 414 are located inside the moving member. The communication path 416 communicates. The opening of the moving member communication path 416 into the through hole 338 is tapered and faces the tip of the rod portion 340 of the plunger 312. The plunger 312 is urged in the direction in which the plunger 312 is separated from the opening of the moving member communication path 416 by the elastic force of the coil spring 352 as the second urging member, and resists the elastic force of the coil spring 352. When the plunger 312 moves upward, the distal end of the plunger 312 is seated on the opening of the moving member communication path 416.

  In addition, a low pressure port 420 that opens to the first liquid chamber 368 is formed in the first inner diameter portion 360 of the upper outer shell member 320, and the decompression communication path 152 is connected to the first liquid chamber via the low pressure port 420. 368. That is, the first liquid chamber 368 functions as a low pressure chamber. A first communication passage 422 that communicates the first liquid chamber 368 and the large inner diameter portion 348 of the through hole 338 is formed in the core 322 so as to extend in the radial direction, and the first communication hole 422 and the through hole are formed. 338 also functions as a low pressure chamber. Hereinafter, the first liquid chamber 368, the first communication hole 422, and the through hole 338 may be collectively referred to as a low pressure chamber 368 or the like. In addition, a drain port 424 that opens to the third liquid chamber 386 as an auxiliary chamber is formed in the fourth inner diameter portion 366 of the upper outer shell member 320, and the connection path 426 that leads to the decompression communication path 152 is connected to the drain port. It is connected to the third liquid chamber 386 via 424. A second communication passage 428 that communicates the third liquid chamber 386 and the recess 388 of the lid member 380 is formed in the lid member 380, and the volume change in the recess 388 accompanying the movement of the moving member 314 is allowed. ing.

  There is a slightly recessed portion on the outer peripheral surface of the cylindrical member 370, and a clearance 430 is formed between the recessed portion and the fourth inner diameter portion 366 of the upper outer shell member 320. A high-pressure port 432 that opens to the clearance 430 is formed in the fourth inner diameter portion 366, and a third communication path 434 that communicates the clearance 430 and the fifth liquid chamber 406 is formed to extend in the radial direction of the cylindrical member 370. Has been. The high pressure port 432 is connected to the high pressure communication path 164. That is, the high pressure communication path 164 is connected to the fifth liquid chamber 406 via the high pressure port 432, the clearance 430, and the third communication path 434, and the fifth liquid chamber 406 functions as a high pressure chamber. Hereinafter, the fifth liquid chamber 406 may be referred to as a high pressure chamber 406.

  The cylindrical member 370 is formed with a communication passage 440 in the cylindrical member that opens to the fourth liquid chamber 404 and the sixth liquid chamber 414 and communicates the two liquid chambers. A pressure adjustment port 442 that opens to the sixth liquid chamber 414 is formed in the fourth inner diameter portion 366 of the upper outer shell member 320, and the control pressure communication path 133 is connected to the pressure adjustment port 442. That is, the fourth liquid chamber 404 is connected to the control pressure communication path 133 via the pressure adjustment port 442, the sixth liquid chamber 414, and the cylindrical member communication path 440, and functions as a pressure adjustment chamber. Hereinafter, the fourth liquid chamber 404 may be referred to as a pressure regulating chamber 404. An auxiliary port 444 that opens to the second liquid chamber 384 is formed in the lid portion of the upper outer shell member 320, and the backup passage 172 is connected to the second liquid chamber 384 via the auxiliary port 444. ing.

  With the above-described structure, in the hydraulic valve device 300, when no current is supplied to the coil 316, the flange portion 390 of the moving member 314 is formed on the inner peripheral surface of the cylindrical member 370 by the elastic force of the coil spring 402. Sitting on the stepped surface 400. For this reason, the flow of brake fluid between the high pressure chamber 406 and the pressure regulating chamber 404 is blocked. Further, the tip of the plunger 312 is separated from the downward opening of the moving member communication path 416 of the moving member 314 by the elastic force of the coil spring 352, and the brake fluid is separated from the cylindrical member communication path 440 and the sixth liquid. It is possible to circulate between the pressure regulating chamber 404 and the low pressure chamber 368 and the like via the chamber 414 and the moving member communication path 416. That is, the cylindrical member communication path 440, the sixth liquid chamber 414, and the moving member communication path 416 function as a communication path, and the pressure adjustment chamber pressure is atmospheric pressure by the communication path. Incidentally, the cylindrical member communication path 440 and the sixth liquid chamber 414 function as a housing communication path, and the opening of the cylindrical member communication path 440 to the pressure regulation chamber functions as a pressure regulation chamber side opening.

  When a current is supplied to the coil 316 as a moving force generator, the tip of the plunger 312 opens the low pressure chamber 368 of the moving member communication path 416 (hereinafter, may be referred to as “low pressure chamber side opening”). An electromagnetic force is generated to move the plunger 312 in a direction approaching the. By this electromagnetic force, first, the plunger 312 moves upward against the elastic force of the coil spring 352, and the tip of the plunger 312 is seated on the low-pressure chamber opening. In this state, the flow of brake fluid between the pressure regulating chamber 404 and the low pressure chamber 368 is cut off, and the flow of brake fluid between the high pressure chamber 406 and the pressure regulating chamber 404 is also cut off. When the plunger 312 moves upward in a state where the tip of the plunger 312 is seated in the low-pressure chamber side opening, that is, in a state where the plunger 312 is in contact with the moving member 314, the moving member 314 also moves upward. As the moving member 314 moves upward, the flange portion 390 of the moving member 314 moves away from the step surface 400 of the cylindrical member 370, so that the flow of brake fluid between the high pressure chamber 406 and the pressure adjusting chamber 404 is increased. It is acceptable. At this time, it is possible to controllably increase the pressure regulation chamber pressure by controlling the energization amount to the coil 316.

  Further, after the pressure regulating chamber pressure is increased, the amount of current supplied to the coil 316 is decreased, so that the flange portion 390 of the moving member 314 is seated on the step surface 400 of the cylindrical member 370 by the elastic force of the coil spring 402. . In a state where the flange portion 390 is seated on the step surface 400 and the tip of the plunger 312 is seated in the low-pressure chamber side opening, the pressure regulating chamber pressure is maintained at the increased hydraulic pressure. Then, by further reducing the amount of current supplied to the coil 316 from that state, the tip of the plunger 312 is separated from the low-pressure side opening by the elastic force of the coil spring 352, and the low-pressure chamber 368 and the pressure-regulating chamber 404 are separated from each other. Brake fluid flow is allowed. At this time, by controlling the amount of current supplied to the coil 316, the pressure regulation chamber pressure can be reduced in a controllable manner.

  As described above, the pressure increasing / decreasing valve 300 can control and increase / decrease the pressure regulating chamber pressure by controlling the amount of current supplied to the coil 316. When the pressure is increased, the flange portion 390 of the moving member 314 is separated from the step surface 400 of the cylindrical member 370, and the brake fluid flows from the high pressure chamber 406 to the pressure adjusting chamber 404. For this reason, the brake fluid flows in a direction in which the flange portion 390 that functions as the valve body of the moving member 314 is separated from the step surface 400 that functions as the valve seat. On the other hand, at the time of decompression, the plunger 312 is separated from the low pressure side opening, and the brake fluid flows from the adjustment chamber 404 to the low pressure chamber 368 and the like. Therefore, the brake fluid flows in a direction in which the tip that functions as the valve body of the plunger 312 is separated from the low-pressure side opening that functions as the valve seat. That is, also in the hydraulic valve device 300, when the pressure regulating chamber pressure is controlled, the brake fluid flows in a direction in which the valve body separates from the valve seat, and the hunting phenomenon during pressure regulation is suppressed. This makes it possible to control the pressure regulating chamber pressure with high accuracy.

  Further, in the present pressure increasing / reducing valve 158 as well, the pressure regulating chamber pressure is increased by relying on the brake fluid pressurized by the operation of the cylinder device 20 without relying on electric power, similarly to the previous pressure increasing / decreasing device 158. It is possible. More specifically, when the power supply to the hydraulic brake system 302 is cut off, the brake fluid pressurized by the operation of the cylinder device 20 flows into the backup passage 172 as in the case of the previous system 10, and the pressure is applied. The pressurized brake fluid flows into the second fluid chamber 384. For this reason, as the hydraulic pressure of the brake fluid in the second fluid chamber 384 increases, the force by which the lid member 380 and the cylindrical member 370 are pushed downward by the hydraulic pressure of the brake fluid in the second fluid chamber 384 is When the lid member 380 and the cylindrical member 370 become larger than the force by which the lid member 380 and the cylindrical member 370 are pushed upward by the pressure regulation chamber pressure, the lid member 380 and the cylindrical member 370 move downward. As the lid member 380 and the cylindrical member 370 move downward, the moving member 314 also moves downward. First, the tip of the plunger 312 is seated in the low-pressure side opening. In this state, the flow of brake fluid between the low pressure chamber 368 and the pressure regulating chamber 404 is blocked. When the lid member 380 and the cylindrical member 370 move further downward, the lid member 380 and the cylindrical member 370 move downward. However, since the moving member 314 is in contact with the plunger 312, the moving member 314 moves downward. Instead, the flange portion 390 of the moving member 314 is separated from the step surface 400 of the cylindrical member 370, so that the flow of the brake fluid between the high pressure chamber 406 and the pressure regulating chamber 404 is allowed. As described above, in the present pressure reducing valve 300, it is possible to increase the adjustment chamber pressure without depending on the electric power even when the electric power fails.

Also, as shown in FIG. 6, the pressure receiving area A ₆ of the moving member 314 that receives the high pressure chamber pressure in the upward direction is the same as the pressure receiving area A ₇ of the moving member 314 that receives the high pressure chamber pressure in the downward direction. ing. For this reason, also in this hydraulic valve apparatus 300, the force required for the initial operation of the moving member 314 is reduced, and the power consumption of the coil 316 is suppressed. Further, in order to suppress the occurrence of liquid leakage and pressure characteristic hysteresis when the pressure regulating chamber pressure is increased, the pressure receiving area of the moving member 196 that receives the pressure regulating chamber pressure in the downward direction and the pressure regulating chamber in the upward direction. In order to make the pressure receiving area of the moving member 196 that receives pressure the same, the relationship between the pressure receiving areas is designed to satisfy the following expression.
A ₆ -A ₈ = A ₉
Here, A ₈ is the pressure receiving area of a portion moving member 314 upward first outer diameter section 396 is slidably fitted in the recess 388 of the cover member 380, A _9, the tip of the plunger 312 is low It is a pressure-receiving area of the place seated to the chamber side opening.

  Since the hydraulic brake system of the present embodiment has the same configuration as the previous brake system 302 except for the hydraulic valve device, only the hydraulic valve device 500 is shown in FIG. 7, and the entire drawing is omitted. I will do it. In addition, the hydraulic valve device 500 has substantially the same configuration as the hydraulic valve device 300 of the previous system 302 except for the moving member and the cylindrical member. The description will be omitted or simplified using the same reference numerals.

  As shown in FIG. 7, in the hydraulic valve device 500, a generally cylindrical cylindrical member 510 is slidably fitted to the fourth inner diameter portion 366 of the upper outer member 320, and the cylindrical member 510 is A lower end portion 512 having the smallest inner diameter located at the lower end portion, a first intermediate portion 514 having an inner diameter larger than the inner diameter of the lower end portion 512 located above the lower end portion 512, and an upper end located at the upper end portion and having the largest inner diameter. And a second intermediate portion 518 having an inner diameter which is located between the upper end portion 516 and the first intermediate portion 514 and is larger than the inner diameter of the first intermediate portion 514 and smaller than the inner diameter of the upper end portion 516. Yes. A lid member 380 is fixedly fitted to the upper end portion 516, and the upper portion of the lid member 380 extends from the upper end of the cylindrical member 510 and slides on the third inner diameter portion 364 of the upper outer member 320. It can be fitted.

  A recess 388 is formed on the lower surface of the lid member 380, and the moving member 520 is inserted into the recess 388 and the cylindrical member 510. The moving member 520 includes a flange portion 522 having the largest outer diameter, a lower first outer diameter portion 524 having an outer diameter smaller than the outer diameter of the flange portion 522 and a lower first outer diameter thereof. A lower second outer diameter portion 526 positioned below the lower portion 524 and having an outer diameter smaller than that of the lower first outer diameter portion 524; and a lower second outer diameter portion positioned below the lower second outer diameter portion 526. A lower third outer diameter portion 528 having an outer diameter smaller than the outer diameter of 526, an upper first outer diameter portion 530 having an outer diameter smaller than the outer diameter of the flange portion 522, which is located above the flange portion 522, and an upper first And an upper second outer diameter portion 532 having an outer diameter smaller than the outer diameter of the upper first outer diameter portion 530 and positioned above the outer diameter portion 530.

  The lower second outer diameter portion 526 is slidably fitted to the first intermediate portion 514 of the cylindrical member 510, and the lower third outer diameter portion 528 is slidably fitted to the lower end portion 512 serving as the first chamber portion. The upper second outer diameter portion 532 and the upper end portion of the upper first outer diameter portion 530 are inserted into the recess 388. The lower end portion of the upper first outer diameter portion 530, the flange portion 522, and the lower first outer diameter portion 524 are located in the second intermediate portion 518, and the lower first outer diameter portion 524 and the lower second outer diameter portion A step surface 534 between the first member 526 and the second member 526 can be seated in an opening upward of the first intermediate portion 514 serving as the second chamber portion of the cylindrical member 510. Specifically, the step surface 536 between the first intermediate portion 514 and the second intermediate portion 518 is tapered, the step surface 536 functions as a valve seat, and the step surface 536 functions as a valve body. The step surface 534 between the lower first outer diameter portion 524 and the lower second outer diameter portion 526 is seatable.

  A coil spring 540 as a first urging member is disposed in a compressed state between the upper end surface of the flange portion 522 of the moving member 520 and the lower surface of the lid member 380, and the elasticity of the coil spring 540 is provided. Due to the force, the moving member 520 is biased in a direction in which the step surface 534 formed on the outer peripheral surface of the moving member 520 is seated on the step surface 536 formed on the inner peripheral surface of the cylindrical member 510. In the seated state, the pressure adjusting chamber 542 is defined by the second intermediate portion 518 of the cylindrical member 520, the moving member 520, and the lid member 380. The outer peripheral surface of the lower second outer diameter portion 526 of the moving member 520 is slightly recessed, and the high pressure chamber 544 is formed by the recessed portion of the lower second outer diameter portion 526 and the first intermediate portion 514 of the cylindrical member 510. Is partitioned. A third communication passage 546 that opens to the high-pressure chamber 544 is formed so as to extend in the radial direction of the cylindrical member 510, and the high-pressure chamber is interposed via the third communication passage 546, the clearance 430, and the high-pressure port 432. 544 is connected to the high-pressure communication path 164.

  A communicating path 550 that penetrates in the axial direction of the moving member 520 is formed inside the moving member 520, and the communicating path 550 opens at the upper end surface and the lower end surface of the moving member 520. The communication path 550 is also open to the outer peripheral surface of the lower first outer diameter portion 524 and the outer peripheral surface of the lower third outer diameter portion 528. A generally cylindrical pin 556 is slidably inserted into the opening at the upper end of the communication passage 550 functioning as an internal chamber, and the upper end surface of the pin 556 is supported by the inner surface of the recess 388 of the lid member 380. Yes. An annular rubber member 558 is provided inside the concave portion 388 of the lid member 380 with the pin 556 penetrating therethrough, and the lower surface of the rubber member 558 as the third inter-chamber rubber member is provided on the lower surface of the moving member 520. The upper end surface is in close contact. The rubber member 558 functions as a seal, and liquid leakage between the moving member 520 and the lid member 380 is prohibited by the rubber member 558. Incidentally, the step surface between the lower second outer diameter portion 526 and the lower third outer diameter portion 528 of the moving member 520 is in close contact with the upper surface of the annular rubber member 412 and is sealed between them. .

  The lower end portion of the lower third outer diameter portion 528 of the moving member 520 in which the communication passage 550 is formed is slidably fitted to the small outer diameter portion 350 of the through hole 338 formed in the core 322. The opening at the lower end of the passage 550 opens into the through hole 338. In addition, the opening to the outer peripheral surface of the lower first outer diameter portion 524 of the communication path 550 is open to the pressure regulating chamber 542. That is, the pressure regulating chamber 542 and the low pressure chamber 368 are communicated by the communication path 550, and the opening to the outer peripheral surface of the first outer diameter portion 524 below the communication path 550 functions as the pressure regulating chamber side opening. An opening to the lower end surface of the communication path 550 functions as a low pressure chamber side opening. An opening to the lower end surface of the communication path 550 (hereinafter, sometimes referred to as “low pressure chamber side opening”) is tapered and faces the tip of the plunger 312. The plunger 312 is biased in a direction away from the low-pressure chamber side opening by the elastic force of the coil spring 352, and the plunger 312 moves upward against the elastic force, so that the tip of the plunger 312 is moved upward. It is configured to be seated in the low pressure chamber side opening.

  With this structure, in the hydraulic valve device 500 as well, as in the hydraulic valve device 300 of the previous system 302, the amount of current supplied to the coil 316 is controlled so that the pressure regulating chamber pressure can be increased or decreased in a controllable manner. It is possible. In addition, when the pressure regulating chamber pressure is controlled, the brake fluid flows in the direction away from the valve seat, and the hunting phenomenon at the time of pressure regulation is suppressed, so that the pressure regulation is performed accurately. The chamber pressure can be controlled. Furthermore, even when power is lost, the lid member 380 and the cylindrical member 510 can be moved downward as the pressurized brake fluid flows into the second fluid chamber 384, and the coil 316 is moved. It is possible to increase the control chamber pressure without relying on the electromagnetic force.

Further, as shown in FIG. 8, the pressure receiving area A ₁₀ of the moving member 520 that receives the high-pressure chamber pressure in the upward direction is the same as the pressure receiving area A ₁₁ of the moving member 520 that receives the high-pressure chamber pressure in the downward direction. ing. For this reason, also in this hydraulic valve apparatus 500, the force required for the initial operation of the moving member 520 is reduced, and the power consumption of the coil 316 is suppressed. Furthermore, in order to suppress the occurrence of liquid leakage and pressure characteristic hysteresis when the pressure adjusting chamber pressure is increased, the pressure receiving area of the moving member 520 that receives the pressure adjusting chamber pressure in the downward direction, and the pressure adjustment in the upward direction. The pressure receiving area of the moving member 520 that receives the chamber pressure is the same. Specifically, from the pressure receiving area (corresponding to the pressure receiving area A ₁₀ ) where the step surface 534 of the moving member 520 is seated on the step surface 536 of the cylindrical member 510, the tip of the plunger 312 is seated on the low pressure chamber side opening. The reduced pressure receiving area A ₁₂ at the position corresponding to the position corresponds to the pressure receiving area of the moving member 520 that receives the pressure regulating chamber pressure in the downward direction, and the upper second outer diameter portion 532 of the moving member 520 is the lid member 380. from the pressure receiving area a ₁₃ of the portion which is slidably fitted into the recess 388 minus the cross-sectional area a ₁₄ of the pin 556, the pressure receiving area of the moving member 520 which receives the pressure regulating chamber pressure to the upward Equivalent to. That is, it is designed so that the relationship between the pressure receiving areas satisfies the following formula.
A ₁₀ -A ₁₂ = A ₁₃ -A ₁₄
In the liquid valve 500, since it is the same as the pressure receiving area A ₁₀ and the pressure receiving area A _13, has the same the cross-sectional area A ₁₄ of the pressure receiving area A ₁₂ and the pin 556.

  Also in the hydraulic brake system of the present embodiment, except for the hydraulic valve device, the configuration is the same as that of the previous brake system 302. Therefore, only the hydraulic valve device 600 is shown in FIG. I will do it. The hydraulic valve device 600 has substantially the same configuration as that of the hydraulic valve device 300 of the previous system 302 except for the moving member, the cylindrical member, and the like. The description will be omitted or simplified using the same reference numerals.

  As shown in FIG. 9, in the hydraulic valve device 600, a generally cylindrical cylindrical member 610 is slidably fitted to the fourth inner diameter portion 366 of the upper outer member 320, and the cylindrical member 610 is The upper end 612 having the largest inner diameter located at the upper end, the lower end 614 having the smaller inner diameter than the upper end 612 located at the lower end, and the middle having the smallest inner diameter located between the upper end 612 and the lower end 614 Part 616. A lidded cylindrical lid member 618 is fixedly fitted to the upper end portion 612, and the upper portion of the lid member 618 extends from the upper end of the cylindrical member 610 and the third inner diameter portion of the upper outer member 320. 364 is slidably fitted. The upper end surface of the lid member 618 is slightly recessed, and the second liquid chamber 619 is defined by the recessed portion of the lid member 618 and the inner surface of the lid of the upper outer member 320.

  A moving member 620 is inserted into the lid member 380 and the cylindrical member 610. The moving member 620 is located at the upper end and has a flange portion 622 having the largest outer diameter, and is positioned below the flange portion 622. A lower first outer diameter portion 624 having an outer diameter smaller than the outer diameter of the flange portion 622 and a lower outer diameter located below the first outer diameter portion 624 and smaller than the outer diameter of the lower first outer diameter portion 624 A second outer diameter portion 626. Incidentally, an annular member 628 having an outer diameter larger than the outer diameter of the lower first outer diameter portion 624 is fixedly fitted to the lower second outer diameter portion 626, and the annular member 628 is connected to the lower first outer diameter portion 626. It contacts the step surface between the diameter portion 624 and the lower second outer diameter portion 626. Since the annular member 628 is fixed to the moving member 620, it is regarded as a constituent of the moving member 620.

  The lower first outer diameter portion 624 is slidably fitted to the intermediate portion 616 of the cylindrical member 610. The lower end portion of the lower first outer diameter portion 624 and the annular member 628 are located at the lower end portion 614 as the first chamber portion, and the lower end portion of the lower first outer diameter portion 624 and the annular member 628 and the lower end portion 614 The space is sealed by an annular seal member 630. The flange portion 622 is positioned in the lid member 618, that is, the upper end portion 612 of the cylindrical member 610, and the flange portion 622 can be seated in an opening above the intermediate portion 616 as the second chamber portion of the cylindrical member 610. It is said that. More specifically, the step surface 632 between the upper end portion 612 and the intermediate portion 616 is tapered, and the step surface 632 functions as a valve seat, and the step member 620 functions as a valve body on the step surface 632. The flange portion 622 can be seated.

  A coil spring 634 as a first biasing member is disposed in a compressed state between the upper end surface of the flange portion 622 of the moving member 620 and the inner surface of the lid member 618. The moving member 620 is urged downward by the elastic force, that is, in a direction in which the flange portion 622 is seated on the step surface 632 formed on the inner peripheral surface of the cylindrical member 610. In the seated state, the pressure regulating chamber 636 is defined by the flange portion 622 of the moving member 620, the lid member 618, and the step surface 632 of the cylindrical member 610. Further, the outer peripheral surface of the lower first outer diameter portion 624 of the moving member 620 is slightly recessed, and the high pressure chamber 638 is partitioned by the recessed portion of the lower first outer diameter portion 624 and the intermediate portion 616 of the cylindrical member 610. Has been. A third communication passage 640 that opens to the high-pressure chamber 638 is formed so as to extend in the radial direction of the cylindrical member 610, and the high-pressure chamber is connected via the third communication passage 640, the clearance 430, and the high-pressure port 432. 638 is connected to the high pressure communication path 164.

  A communicating path 650 that penetrates in the axial direction of the moving member 620 is formed inside the moving member 620, and the communicating path 650 opens to the upper end surface and the lower end surface of the moving member 620. The lower end portion of the lower second outer diameter portion 626 of the moving member 620 in which the communication path 650 is formed is slidably fitted to the small inner diameter portion 350 of the through hole 338 formed in the core 322. The opening at the lower end of the passage 650 opens into the through hole 338. On the other hand, the opening at the upper end of the communication path 650 opens to the pressure regulating chamber 363. That is, the pressure regulating chamber 636 and the low pressure chamber 368 are communicated by the communication passage 650, and the opening to the upper end surface of the communication passage 650 functions as the pressure regulating chamber side opening, and the lower end surface of the communication passage 650 is connected to the lower end surface. The opening functions as a low pressure chamber side opening. The opening to the lower end surface of the communication path 650 (hereinafter, sometimes referred to as “low pressure chamber side opening”) is tapered and faces the tip of the plunger 312. The plunger 312 is biased in a direction away from the low-pressure chamber side opening by the elastic force of the coil spring 352, and the plunger 312 moves upward against the elastic force, so that the tip of the plunger 312 is moved upward. It is configured to be seated in the low pressure chamber side opening. The communication passage 650 is also opened on the outer peripheral surface of the lower second outer diameter portion 626 and communicates with the sixth liquid chamber 414.

With this structure, the present hydraulic valve device 600 can exhibit the same effects as the hydraulic valve device 300 of the previous system 302. Also, as shown in FIG. 10, the pressure receiving area A ₁₅ of the moving member 620 that receives the high pressure chamber pressure in the upward direction is the same as the pressure receiving area A ₁₆ of the moving member 620 that receives the high pressure chamber pressure in the downward direction. ing. For this reason, also in this hydraulic valve apparatus 600, the force required for the initial operation of the moving member 620 is reduced, and the power consumption of the coil 316 is suppressed. Furthermore, in order to suppress the occurrence of liquid leakage and pressure characteristic hysteresis when the pressure regulating chamber pressure is increased, the pressure receiving area of the moving member 620 that receives the pressure regulating chamber pressure in the downward direction, and the pressure regulating in the upward direction. The pressure receiving area of the moving member 620 that receives the chamber pressure is the same. Specifically, the tip of the plunger 312 is seated on the low pressure chamber side opening from the pressure receiving area (corresponding to the pressure receiving area A ₁₅ ) where the flange portion 622 of the moving member 620 is seated on the stepped surface 632 of the cylindrical member 610. The reduced pressure receiving area A ₁₇ at the position corresponding to the pressure corresponds to the pressure receiving area of the moving member 620 that receives the pressure-adjusting chamber pressure in the downward direction, and from the pressure receiving area A ₁₈ of the annular member 628 constituting the moving member 620. A value obtained by reducing the pressure receiving area A ₁₉ of the lower second outer diameter portion 626 of the moving member 620 corresponds to the pressure receiving area of the moving member 620 that receives the pressure regulating chamber pressure in the upward direction. That is, it is designed so that the relationship between the pressure receiving areas satisfies the following formula.
A ₁₅ -A ₁₇ = A ₁₈ -A ₁₉

  Also in the hydraulic brake system of this embodiment, except for the hydraulic valve device, the configuration is the same as that of the previous brake system 302. Therefore, only the hydraulic valve device 700 is shown in FIG. I will do it. The hydraulic valve device 700 has substantially the same configuration as the hydraulic valve device 300 of the previous system 302 except for the moving member, the plunger, and the like. The description will be omitted or simplified using the same reference numerals.

  As shown in FIG. 11, in the hydraulic valve device 700, the lid member 380 is slidably fitted to the third inner diameter portion 364 of the upper outer member 320, and the cylindrical member 370 is slid on the fourth inner diameter portion 366. The lid member 380 is fixedly fitted to the cylindrical member 370. A moving member 710 is inserted into a recess 388 formed on the lower surface of the cylindrical member 370 and the lid member 380. The moving member 710 includes a flange portion 712 having the largest outer diameter, a lower first outer diameter portion 714 having an outer diameter smaller than the outer diameter of the flange portion 712 and a lower first outer diameter thereof. A lower second outer diameter portion 716 having an outer diameter smaller than the outer diameter of the lower first outer diameter portion 714 and an outer diameter smaller than the outer diameter of the flange portion 712 which is positioned above the flange portion 712. It has an upper first outer diameter portion 718 and an upper second outer diameter portion 720 that is located above the upper first outer diameter portion 718 and has an outer diameter smaller than the outer diameter of the upper first outer diameter portion 718. .

  The cylindrical member 370 is located at the lower end and has the smallest inner diameter 722, the upper end located at the upper end and the largest inner diameter 724, and the lower end 722 and the upper end 724. The intermediate portion 726 is larger and has an inner diameter smaller than the inner diameter of the upper end portion 724. The lower second outer diameter portion 716 of the moving member 710 is slidably fitted to the lower end portion 722 of the cylindrical member 370, and the upper second outer diameter portion 720 is inserted into the concave portion 388 of the lid member 380. The upper first outer diameter portion 718, the flange portion 712, and the lower first outer diameter portion 714 are located in the intermediate portion 726, and are located between the lower first outer diameter portion 714 and the lower second outer diameter portion 716. The step surface 728 can be seated in an opening above the lower end 722 as the second chamber portion of the cylindrical member 370. More specifically, the step surface 730 between the lower end portion 722 and the intermediate portion 726 is tapered, and the step surface 730 functions as a valve seat, and the step first surface outside the step surface 730 functions as a valve body. A step surface 728 between the diameter portion 714 and the lower second outer diameter portion 716 can be seated.

  A coil spring 732 serving as a first urging member is disposed between the upper end surface of the flange portion 712 of the moving member 710 and the inner surface of the lid member 380 in a compressed state. The moving member 710 is urged downward by the elastic force, that is, in a direction in which the step surface 728 formed on the outer peripheral surface of the moving member 710 is seated on the step surface 730 formed on the inner peripheral surface of the cylindrical member 370. . In the seated state, the pressure regulating chamber 734 is defined by the moving member 710, the lid member 380, and the intermediate portion 726 of the cylindrical member 370. Further, the outer peripheral surface of the lower second outer diameter portion 716 of the moving member 710 is slightly recessed, and the high pressure chamber 736 is defined by the recessed portion and the intermediate portion 726 of the cylindrical member 370. The cylindrical member 370 is formed with a third communication path 434 that communicates the high-pressure chamber 736 and the clearance 430, and a cylindrical member communication path 440 that communicates the pressure regulating chamber 734 and the sixth liquid chamber 414. Yes.

  The moving member 710 is formed with an internal passage 737 as an internal chamber that opens to the upper end surface and the lower first outer diameter portion 714. A generally cylindrical pin 738 is slidably inserted into the opening at the upper end of the internal passage 737, and the upper end surface of the pin 738 is supported by the inner surface of the recess 388 of the lid member 380. An annular rubber member 739 is provided inside the concave portion 388 of the lid member 380 with the pin 738 penetrating therethrough, and the moving member 710 The upper end surface is in close contact. The rubber member 739 functions as a seal, and liquid leakage between the moving member 710 and the lid member 380 is prohibited by the rubber member 739.

  The lower second outer diameter portion 716 of the moving member 710 extends from the lower end of the cylindrical member 370, and the lower end of the extended second lower outer diameter portion 716 is a small inner diameter of the through hole 338 formed in the core 322. The portion 350 is slidably fitted. A recess 740 is formed on the lower end surface of the lower second outer diameter portion 716, and a connection hole 742 that opens to the outer peripheral surface of the lower second outer diameter portion 716 and also opens to the recess 740 is also formed. The connection hole 742 opens to the sixth liquid chamber 414, and the low pressure chamber 368 and the like and the pressure regulating chamber 734 are constituted by the recess 740, the connection hole 742, the sixth liquid chamber 414, and the communication passage 440 in the cylindrical member. The communication path is connected. Here, the recess 740 and the connection hole 742 function as a moving member communication path, and the sixth liquid chamber 414 and the cylindrical member communication path 440 function as a housing communication path. Further, the opening of the communication passage 440 in the cylindrical member to the pressure adjusting chamber 734 functions as a pressure adjusting chamber side opening, and the opening of the recess 740 to the low pressure chamber 368 and the like functions as a low pressure chamber side opening.

  A plunger 750 is provided below the moving member 710. The plunger 750 includes a rod portion 752 inserted into the through hole 338, a lower end surface of the core 322, and an inner bottom surface of the lower outer shell member 318. And a main body portion 754 disposed therebetween. The rod portion 752 is positioned at the lower end portion and has a large outer diameter portion 756, is positioned at the upper end portion and has a small outer diameter portion 758, and is positioned between the large diameter portion 756 and the small diameter portion 758, and is large. And an intermediate diameter portion 760 having an outer diameter smaller than the outer diameter of the diameter portion 756 and larger than the outer diameter of the small diameter portion 758. The large diameter portion 756 is slidably fitted into the large inner diameter portion 348 of the through hole 338, and the intermediate diameter portion 760 is inserted into the large inner diameter portion 348 and the small inner diameter portion 350 of the through hole 338 with clearance. ing. The small diameter portion 758 is inserted into the concave portion 740 of the moving member 710 fitted in the through hole 338.

  A step surface 770 between the small-diameter portion 758 and the intermediate inner-diameter portion 760 of the plunger 750 faces an opening below the recess 740 of the moving member 740 (hereinafter sometimes referred to as “low-pressure chamber side opening”). The low-pressure chamber side opening is tapered. A second urging member is provided between the step surface between the large diameter portion 756 and the intermediate diameter portion 760 of the plunger 750 and the step surface between the large inner diameter portion 348 and the small inner diameter portion 350 of the through hole 338. The coil spring 772 is arranged in a compressed state, and the plunger 750 is urged downward by the elastic force of the coil spring 772. That is, the plunger 750 is biased in a direction in which the stepped surface 770 formed on the outer peripheral surface of the plunger 750 is separated from the low-pressure chamber side opening by the elastic force of the coil spring 772, and the plunger 750 is resisted against the elastic force. By moving upward, the step surface 770 is seated in the low-pressure chamber side opening. In addition, the rod portion 752 of the plunger 750 is formed with an in-rod portion communication passage 776 that opens to the upper end surface and the outer peripheral surface, and the volume change in the concave portion 740 is allowed as the plunger 750 moves.

With this structure, the present hydraulic valve device 700 can also exhibit the same effects as the hydraulic valve device 300 of the previous system 302. Also, as shown in FIG. 12, the pressure receiving area A ₂₀ of the moving member 710 that receives the high pressure chamber pressure in the upward direction is the same as the pressure receiving area A ₂₁ of the moving member 710 that receives the high pressure chamber pressure in the downward direction. ing. For this reason, also in this hydraulic valve apparatus 700, the force required for the initial operation of the moving member 710 is reduced, and the power consumption of the coil 316 is suppressed. Furthermore, in order to suppress the occurrence of liquid leakage and pressure characteristic hysteresis when the pressure regulating chamber pressure is increased, the pressure receiving area of the moving member 710 that receives the pressure regulating chamber pressure in the downward direction, and the pressure regulating in the upward direction. The pressure receiving area of the moving member 710 that receives the chamber pressure is the same. Specifically, the pressure receiving area (corresponding to the pressure receiving area A ₂₀ ) where the stepped surface 728 of the moving member 710 is seated on the stepped surface 730 of the cylindrical member 370 receives the pressure regulating chamber pressure in the downward direction. This corresponds to the pressure receiving area of the moving member 710. On the other hand, the one obtained by subtracting the cross-sectional area A ₂₃ of the pin 738 from the pressure receiving area A ₂₂ where the upper second outer diameter portion 720 of the moving member 710 is slidably fitted in the recess 388 of the lid member 380, This corresponds to the pressure receiving area of the moving member 710 that receives the pressure regulating chamber pressure in the upward direction. Further, the pressure-regulating chamber pressure in the upward direction is also obtained by subtracting the pressure-receiving area A ₂₅ of the small-diameter portion 758 of the plunger 750 from the pressure-receiving area A ₂₄ where the stepped surface 770 of the plunger 750 is seated on the low-pressure chamber side opening. This corresponds to the pressure receiving area of the moving member 710 that receives the pressure. That is, it is designed so that the relationship between the pressure receiving areas satisfies the following formula.
A ₂₀ = (A ₂₂ −A ₂₃ ) + (A ₂₄ −A ₂₅ )
In the hydraulic pressure valve device 700, since the pressure receiving area A ₂₀ and the pressure receiving area A ₂₂ are the same, the relationship between the pressure receiving areas satisfies the following expression.
A ₂₃ = A ₂₄ -A ₂₅

  118: reservoir (low pressure source) 158: hydraulic pressure valve device 162: high pressure reducing device 180: pressure increasing linear valve (electromagnetic pressure increasing valve) (moving force generator) 182: pressure reducing linear valve (electromagnetic pressure reducing valve) (moving force) 190): Housing 192: Plunger 196: Moving member 206: Second inner diameter portion (fourth chamber portion) 208: Third inner diameter portion (first chamber portion) (second chamber portion) 228: Second Liquid chamber (moving force generating chamber) 250: Recessed portion (inter-third chamber portion) 252: Coil spring (first biasing member) 254: Third liquid chamber (pressure regulating chamber) 256: Fourth liquid chamber (high pressure chamber) 260: Through hole (communication path) (inner chamber) 261: Connection hole (communication path) 262: Pin 270: Coil spring (second biasing member) 272: Fifth fluid chamber (low pressure chamber) 300: Fluid pressure valve device 310 Housing 312: Plunger 314: Moving member 316: Coil (moving force generator) 350: Small inner diameter portion (inter-first chamber portion) 352: Coil spring (second urging member) 368: First liquid chamber (low pressure chamber) 372: Lower end (first chamber) 374: First intermediate (second chamber) 386: Third liquid chamber (auxiliary chamber) 388: Recess (third chamber) 402: Coil spring (first 404: Fourth liquid chamber (pressure regulating chamber) 406: Fifth liquid chamber (high pressure chamber) 410: Rubber member (rubber member in the third chamber) 412: Rubber member (rubber in the first chamber) 414: sixth fluid chamber (communication path in housing) (communication path) 416: communication path in moving member (communication path) 440: communication path in cylindrical member (communication path in housing) (communication path) 500: hydraulic valve Device 5 12: Lower end portion (first inter-chamber portion) 514: First intermediate portion (second inter-chamber portion) 520: Moving member 540: Coil spring (first biasing member) 542: Pressure regulating chamber 544: High-pressure chamber 550: Communication path (inner chamber) 556: Pin 558: Rubber member (rubber member in the third chamber) 600: Hydraulic valve device 614: Lower end diameter portion (first chamber) 616: Intermediate portion (second chamber) 620: moving member 634: coil spring (first urging member) 636: pressure regulating chamber 638: high pressure chamber 650: communication path 700: hydraulic valve device 710: moving member 722: lower end portion (first chamber portion) (first chamber) 732: Coil spring (first biasing member) 734: Pressure regulating chamber 736: High pressure chamber 737: Internal passage (internal chamber) 738: Pin 739: Rubber member (between third chamber) 750: Plunger 772: Coil spring (second biasing member) 740: Recessed portion (communication passage in moving member) (communication passage) 742: Connection hole (communication passage in moving member) (communication passage)

Claims (9)

A hydraulic valve device for regulating hydraulic fluid,
A low pressure chamber communicating with the low pressure source, a pressure regulating chamber filled with a regulated hydraulic fluid, a high pressure chamber provided between the low pressure chamber and the pressure regulating chamber and communicating with the high pressure source, and the low pressure chamber And a first chamber connecting the high pressure chamber and a second chamber connecting the high pressure chamber and the pressure regulating chamber, and a housing that divides them so as to be aligned in the axial direction of the chamber.
It is inserted into the first chamber and the second chamber so as to penetrate the high pressure chamber in the axial direction, and one end portion extends into the pressure regulating chamber and is movable in the axial direction. The high pressure chamber and the pressure regulating chamber are disposed in the housing, block the portion between the first chambers, and the one end portion is seated in an opening on the pressure regulating chamber side of the second chamber portion. A moving member that blocks the flow of hydraulic fluid between the
A first biasing member that biases the moving member in a direction in which the one end is seated in the opening;
A low pressure chamber side opening that is formed at the other end of the moving member and opens to the low pressure chamber, and is formed at one of the one end of the moving member and the housing and is open to the pressure regulating chamber. A pressure adjusting chamber side opening that communicates with the low pressure chamber and the pressure adjusting chamber;
A plunger that is disposed in the housing so as to be movable in the axial direction, and that blocks the flow of hydraulic fluid between the pressure regulating chamber and the low pressure chamber by being seated in the low pressure chamber side opening;
A second urging member that urges the plunger in a direction in which the plunger is separated from the low-pressure chamber side opening;
A hydraulic valve device comprising: a moving force generator that generates a force for moving the plunger in a direction in which the plunger is seated on the low-pressure chamber side opening in a magnitude corresponding to the electric power supplied to the plunger. The pressure regulating chamber side opening is formed at the one end of the moving member,
The hydraulic valve device according to claim 1, wherein the communication path passes through the inside of the moving member. The pressure regulating chamber side opening is formed in the housing,
The communication path is
(a) a moving member communication path formed in the moving member and opening between the first chambers and communicating the opening and the low pressure chamber side opening; and (b) formed in the housing and moving the moving member. 2. The hydraulic valve device according to claim 1, further comprising an in-housing communication path that communicates an opening of the in-member communication path to the first chamber portion and the pressure regulating chamber side opening. The moving member is
A pressure receiving area for receiving the hydraulic pressure of the working fluid in the high pressure chamber in a direction in which the one end portion thereof approaches the opening on the pressure regulating chamber side of the second chamber portion, and a direction in which the one end portion is separated from the opening The hydraulic valve device according to any one of claims 1 to 3, wherein the pressure receiving area that receives the hydraulic pressure of the hydraulic fluid in the high-pressure chamber is made equal. The moving member is
The pressure receiving area that receives the hydraulic pressure of the hydraulic fluid in the pressure regulating chamber in a direction in which the low pressure chamber side opening approaches the plunger, and the hydraulic fluid in the pressure regulating chamber in a direction in which the low pressure chamber side opening is separated from the plunger. The hydraulic valve device according to any one of claims 1 to 4, wherein the hydraulic pressure device has a shape that is equal to a pressure receiving area that receives hydraulic pressure. The housing further includes an auxiliary chamber provided on the opposite side of the pressure regulating chamber from the high pressure chamber side, and a third chamber connecting the auxiliary chamber and the pressure regulating chamber,
The moving member extends to and inserted into the third chamber,
The hydraulic valve device is
An internal chamber that is formed inside the moving member, opens to the pressure regulating chamber on an outer peripheral surface of the moving member, and opens to the auxiliary chamber on an end surface on the one end side of the moving member;
A pin having one end slidably inserted into an opening in the end face of the internal chamber so as to close the opening and a pin supported by the housing in the auxiliary chamber. The hydraulic valve device according to claim 5. The housing is further provided on the opposite side of the pressure regulating chamber from the high pressure chamber side, communicates with the low pressure source, and an inter-third chamber connecting the auxiliary chamber and the pressure regulating chamber. Have
The moving member extends to the third inter-chamber portion and is inserted into the third chamber, and a stepped shape having a step surface facing the auxiliary chamber at a portion inserted into the third inter-chamber portion,
The hydraulic valve device is
An annular third chamber that is provided between the third chambers, penetrates the moving member, and blocks the flow of hydraulic fluid between the auxiliary chamber and the pressure regulating chamber while being in close contact with the step surface. The hydraulic valve device according to any one of claims 1 to 6, further comprising an intermediate rubber member. The housing is further provided on the opposite side of the pressure regulating chamber from the high pressure chamber side, communicates with the low pressure source, and an inter-third chamber connecting the auxiliary chamber and the pressure regulating chamber. Have
The moving member extends to and inserted into the third chamber so that the end surface on the one end side thereof is located in the third chamber.
The hydraulic valve device is
A third inter-chamber rubber member that is provided in the inter-third chamber portion and blocks the flow of hydraulic fluid between the auxiliary chamber and the pressure regulating chamber in a state of being in close contact with the end surface of the moving member. The hydraulic valve device according to any one of claims 1 to 6. The moving member has a stepped shape having a step surface facing the low-pressure chamber at a portion inserted in the first inter-chamber portion,
The hydraulic valve device is
Between the first chambers, provided between the first chambers, between the annular first chambers that penetrates the moving member and blocks the flow of the working fluid between the low pressure chambers and the high pressure chambers in close contact with the step surface. The hydraulic valve device according to any one of claims 1 to 8, further comprising an internal rubber member.

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