JP6252427B2 - Pressure regulator and vehicle hydraulic brake system including the same - Google Patents

Description

  The present invention relates to a pressure regulator that regulates hydraulic fluid supplied from a high-pressure source, and a vehicle hydraulic brake system that includes the pressure regulator.

  In the field of hydraulic brake systems for vehicles, the brake device does not generate the braking force depending on the brake operating force, but the brake device depends solely on the pressure of the hydraulic fluid supplied from the high pressure source. The pressure regulator is used to regulate the hydraulic fluid supplied from the high pressure source. It is disclosed that various pressure regulators can be employed in the system described in the following patent document as an example of such a system.

JP 2008-47104 A

  There are pressure regulators described in the above-mentioned patent documents including a so-called poppet-type valve mechanism and a so-called spool-type valve mechanism. The poppet type valve mechanism has a structure that regulates the hydraulic fluid by seating / separating the valve body with respect to the valve seat, and the clearance of the valve body when the valve body is separated is set relatively large. . For this reason, there is a slight possibility that a foreign object is bitten. On the other hand, a spool type valve mechanism has a spool and an internal port facing the outer periphery of the spool and holds the spool so as to be movable in the axial direction (hereinafter referred to as “spool holder”). The clearance is relatively small and is excellent from the viewpoint of biting of foreign matter. On the other hand, in the spool type valve mechanism, the internal ports communicating with each other of the spool holder are switched in accordance with the relative movement of the spool and the spool holder in the axial direction, and pressure adjustment is performed by the switching. In order to realize a practical pressure regulator, sufficient consideration is required for optimizing the relative positions of the spool and the spool holder in the axial direction. In view of such circumstances, it is an object of the present invention to provide a practical pressure regulator that includes a spool type valve mechanism, and a practical vehicle hydraulic pressure equipped with the pressure regulator. It is an object to provide a brake system.

In order to solve the above-described problems, the pressure regulator of the present invention includes: (a) an urging mechanism that relatively moves the spool constituting the spool valve mechanism and the spool holder to the other end side in the relative movable range; In a pressure regulator that includes a reverse biasing mechanism that moves the spool holder relative to one end side, a relative position on one end side in the relative movable range between the spool and the spool holder is formed in the spool holder. The spool is configured to be defined by directly contacting the stepped surface .

  The hydraulic brake system for a vehicle according to the present invention includes a brake operation member, a brake device provided on a wheel, and a master that pressurizes the hydraulic fluid to a pressure corresponding to the regulated hydraulic fluid and supplies the hydraulic fluid to the brake device. A cylinder device, a high-pressure source device that supplies high-pressure hydraulic fluid, and the pressure regulator according to the present invention are configured so that the hydraulic fluid regulated by the pressure regulator is introduced into the master cylinder device. .

Spool and spool holder are two members that are most involved in the switching of the internal port, the pressure regulator of the present invention, one end side of the relatively movable range as a reference of the relative position of two such members The relative position is accurately defined without any other member interposed between the two members. Therefore, according to the pressure regulator of the present invention, the relative position in the relative movable range of the spool and the spool holder can be optimized, and good pressure regulation is possible. In addition, the vehicle hydraulic brake system of the present invention using the pressure regulator of the present invention can generate an appropriate braking force by taking advantage of the pressure regulator.

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 some 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 items (1) to (5) generally correspond to claims 1 to 5, and the items (11) and (12) correspond to claims 6 and 7, respectively. To do.

(1) A pressure regulator that regulates high-pressure hydraulic fluid from a high-pressure source to a regulated pressure and supplies the regulated hydraulic fluid,
A housing;
Each of the housing includes (a) a high pressure port to which hydraulic fluid from a high pressure source is supplied, (b) a low pressure port in communication with the low pressure source, and (c) a regulated hydraulic fluid. An adjustment pressure port to supply,
A spool and a spool holder that holds the spool, the spool and the spool holder are relatively movable in the axial direction, and the spool and the spool holder are positioned on one end side in the relative movable range. The communication between the low pressure port and the adjustment pressure port is allowed, the communication between the high pressure port and the adjustment pressure port is blocked, and the spool and the spool holder are moved relative to each other side. A spool valve mechanism that blocks communication between the low pressure port and the adjustment pressure port and allows communication between the high pressure port and the adjustment pressure port;
A biasing mechanism for biasing one of the spool and the spool holder in a direction in which the spool and the spool holder are relatively moved toward the other end;
There is an adjustment pressure chamber that communicates with the adjustment pressure port and into which a hydraulic fluid of an adjustment pressure is introduced, and one of the spool and the spool holder is connected to the spool and the spool by the pressure of the hydraulic fluid in the adjustment pressure chamber. A reverse direction urging mechanism that urges the holding body in the direction of relative movement toward the one end side,
A pressure regulator configured such that a relative position on one end side in a relative movable range between the spool and the spool holder is defined by one of the spool and the spool holder being in direct contact with the other. .

  The pressure regulator of this aspect is a pressure regulator configured to include a so-called spool type valve mechanism. The spool type valve mechanism of the pressure regulator according to this aspect is configured so that the spool and the spool holding body that holds the spool in the axial direction are balanced by a balance between the urging force by the urging mechanism and the urging force by the reverse direction urging mechanism. This is a mechanism that switches the communication between the high pressure port and the low pressure port relative to the adjustment pressure port. Generally, there is no seal between the spool and the spool holder, and the clearance between the two is considerably reduced. By doing so, the function of the seal is realized. Therefore, a phenomenon such as the occurrence of foreign matter biting between the spool and the spool holder is less likely to occur, which is advantageous compared to a so-called poppet type valve mechanism.

  On the other hand, as can be seen from the above switching operation, the spool type valve mechanism has an internal port formed in the spool holder and a communication path formed in the spool for communicating between the internal ports ( It is no exaggeration to say that the relative position to the communication groove etc. holds the key to good pressure regulation. Therefore, in order to make the relative position appropriate, the relative position is generally adjusted with due consideration when assembling the pressure regulator. Even if the processing accuracy of the spool and the spool holder is sufficient, if the reference position of the relative position is defined between the spool and the spool holder via some member, Adjustment of the relative position becomes considerably difficult due to the processing accuracy of the interposed member. In the pressure regulator of this aspect, in the state serving as a reference for the relative position, that is, in a state where the spool and the spool holder are located on one end side of the relative movable range, they are not interposed through any other member. It can come into direct contact. In other words, one of the spool and the spool holder is directly locked to the other. Therefore, the relative position adjustment operation can be performed relatively easily. In other words, the relative position in the relative movable range between the spool and the spool holder can be optimized by a relatively simple operation, and a pressure regulator that can perform good pressure regulation can be easily realized. It can be done.

  “Relative movement of the spool and the spool holder” in this aspect does not necessarily mean that both move together. Naturally, for example, the movement of the spool while the spool holding body is fixed, and the movement of the spool holding body when the movement of the spool is prohibited are also included. Further, “located on one end side of the relative movable range” means that both are positioned in the relative movable range in a state where the spool is shifted most in one direction in the axial direction with respect to the spool holder. “Move to the other end” means that the spool moves relative to the spool holder so that the spool is displaced in the opposite direction in the axial direction. In relation to this, the “relative position on one end side in the relative movable range” means the relative position in the axial direction of the spool and the spool holder in the state of being most displaced in the one direction.

  Further, in this aspect, “one of the spool and the spool holder” that is a target of biasing by the biasing mechanism and “one of the spool and the spool holder” that is target of biasing by the reverse direction biasing mechanism. Is not necessarily the same. The pressure regulator of this aspect may be configured such that the biasing mechanism biases one of the spool and the spool holder, and the reverse biasing mechanism biases the other.

  In addition, the thing of various mechanisms can be employ | adopted for the said urging | biasing mechanism in this aspect, including the solenoid type plunger mechanism demonstrated later. For example, a mechanism in which a pilot pressure chamber is provided and one of the spool and the spool holding body is urged by the pressure of the hydraulic fluid introduced into the pilot pressure chamber, that is, the pilot pressure can be employed. When such a mechanism is employed, the pressure of the hydraulic fluid introduced into the pilot pressure chamber is adjusted by, for example, adjusting the hydraulic pressure adjusting device including a pressure increasing linear valve and a pressure reducing linear valve. It is possible to control the pressure of the hydraulic fluid supplied from the pressure device.

(2) The pressure regulator according to (1), wherein the biasing mechanism includes a solenoid type plunger mechanism that generates a biasing force having a magnitude corresponding to a supplied current.

  When energizing one of the spool and the spool holding body with the solenoid type plunger mechanism, if the energizing force is to be increased, the coil or the like must be increased, and the size of the pressure regulator itself is increased. Therefore, in general, when urging is performed by a solenoid type plunger mechanism, the urging force is weaker than when urging is performed using pilot pressure. In view of this, when the solenoid type plunger mechanism is employed as the biasing mechanism, it is necessary to adjust the relative position accuracy described above to a higher level. Therefore, in the pressure regulator of this aspect employing the solenoid type plunger mechanism, the above-described effect, that is, the relative position of the relative movable range of the spool and the spool holder is defined by the direct contact thereof. The effect obtained by this can be fully enjoyed.

(3) The biasing mechanism is configured to bias the spool,
Inside the spool, a space is formed that opens to an end portion on the side in the urging direction by the urging mechanism,
The reverse biasing mechanism is
A pin supported by the housing and inserted into an opening at an end of the spool to close the opening; and the adjustment pressure chamber includes the space in which the opening is closed by the pin; The adjustment according to (1) or (2), wherein the spool is biased in a direction opposite to a biasing direction by the biasing mechanism by the pressure of the hydraulic fluid in the adjustment pressure chamber. Pressure device.

  The reverse direction biasing mechanism in this aspect can make the biasing force by the reverse direction biasing mechanism relatively small by the above configuration. As described above, the pressure regulation by the spool valve mechanism is performed by the balance between the urging force by the urging mechanism and the urging force by the reverse direction urging mechanism. It is possible to combine suitably with the previous aspect which employ | adopts.

(4) When the biasing mechanism is a first biasing mechanism,
The regulator is
There is a pilot pressure chamber into which hydraulic fluid having a pilot pressure is introduced, and one of the spool and the spool holder is connected to the spool and the spool holder by the pressure of the hydraulic fluid in the pilot pressure chamber. The pressure regulator according to any one of (1) to (3), further including a second urging mechanism that urges in a direction of relative movement toward the other end side.

  In the pressure regulator of this aspect, two urging mechanisms are employed. The two urging mechanisms may be arranged in parallel, or may be arranged in series as will be described later. Also, both may be configured to function simultaneously and bias the spool at the same time, and as described later, only one of them may be configured to selectively bias the spool without functioning simultaneously. May be. Since the hydraulic fluid can be regulated by the two urging mechanisms, the regulator is versatile.

  In addition, “one of the spool and the spool holder” to be biased by the second biasing mechanism is “one of the spool and the spool holder” to be biased by the first biasing mechanism, It doesn't necessarily have to be the same. Specifically, for example, the first biasing mechanism may be configured to bias the spool, and the second biasing mechanism may be configured to bias the spool holding body. In relation to this, when the pressure is adjusted by the second urging mechanism, the pressure is adjusted by the balance between the urging force by the second urging mechanism and the urging force by the reverse direction urging mechanism. When the pressure is adjusted by the first urging mechanism, “one of the spool and the spool holding body” to be urged by the reverse urging mechanism and the pressure applied by the second urging mechanism. The “one of the spool and the spool holder” to be energized by the biasing mechanism may be different from each other. Specifically, for example, when the first biasing mechanism is configured to bias the spool and the second biasing mechanism is configured to bias the spool holding body, the reverse biasing is performed. The mechanism may be configured to urge the spool in the case of pressure regulation by the first urging mechanism and to urge the spool holding body in the case of pressure regulation by the second urging mechanism.

(5) When urging by the first urging mechanism is performed, urging by the second urging mechanism is prohibited, and when urging by the first urging mechanism is impossible, The pressure regulator according to item (4), configured to allow urging by a two urging mechanism.

  In short, in the pressure regulator of this aspect, pressure regulation by two urging mechanisms is selectively performed. More specifically, the pressure regulator of this aspect can be considered as a pressure regulator in which the second urging mechanism plays a backup role of the first urging mechanism. By adopting the pressure regulator of this aspect, for example, when the first urging mechanism cannot generate the urging force for some reason, such as an electrical failure, the pressure adjustment by the pilot pressure is performed. Such a system can be constructed. That is, it is possible to construct an excellent system from the viewpoint of fail-safe.

(11) a brake operation member;
A brake device provided on the wheel;
A master cylinder device that introduces the adjusted hydraulic fluid, pressurizes the hydraulic fluid to a pressure corresponding to the pressure of the introduced hydraulic fluid, and supplies the pressurized hydraulic fluid to the brake device;
A high pressure source device as a high pressure source for supplying high pressure hydraulic fluid;
A pressure regulator according to any one of (1) to (5),
A hydraulic brake system for a vehicle configured such that hydraulic fluid regulated by the pressure regulator is introduced into the master cylinder device.

  In short, the vehicle hydraulic brake system according to this aspect is a system in which the pressure regulator according to the above-described various aspects is employed. According to the system of this aspect, the advantages of the pressure regulators of the various aspects described above can be utilized, so that the brake force generated by the brake device can be favorably controlled.

(12) The pressure regulator is the pressure regulator described in (4) or (5),
One of a hydraulic fluid having a pressure corresponding to a brake operating force applied to the brake operating member and a hydraulic fluid supplied from the master cylinder device to the brake device is provided in the pilot pressure chamber. The vehicle hydraulic brake system according to item (11), wherein the vehicle hydraulic brake system is configured to be introduced as hydraulic fluid having pressure.

  In short, the vehicle hydraulic brake system according to this aspect is a system including a pressure regulator capable of adjusting pressure using two urging mechanisms. For example, the system according to this aspect normally uses the first urging mechanism to adjust the hydraulic fluid supplied to the master cylinder device using the first urging mechanism, and in the case of an electrical failure or the like, Pressure of hydraulic fluid at a height corresponding to the operating force (hereinafter sometimes referred to as “operating force dependent pressure”) or pressure of hydraulic fluid supplied to the brake device from the master cylinder device (hereinafter referred to as “master pressure”) The pressure may be adjusted using the pilot pressure. With such a configuration, a highly reliable hydraulic brake system for a vehicle can be realized.

1 is a diagram illustrating an overall configuration of a vehicle hydraulic brake system according to a first embodiment. It is sectional drawing which shows the pressure regulator of 1st Example. It is sectional drawing which shows the pressure regulator of 2nd Example. It is sectional drawing which shows the pressure regulator of 3rd Example.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the claimable invention and modifications thereof will be described in detail with reference to the drawings as modes for carrying out the claimable invention. In addition to the following examples, the claimable invention is implemented in various forms including various modifications and improvements based on the knowledge of those skilled in the art, including the form described in the above [Aspect of the Invention] section. can do.

≪Configuration of hydraulic brake system for vehicles≫
i) Overall Configuration The vehicle hydraulic brake system according to the first embodiment is a hydraulic brake system mounted on a hybrid vehicle using brake oil as hydraulic fluid. As shown in FIG. 1, the present hydraulic braking system is roughly (A) provided on four wheels 10, each of which generates a braking force, and (B) a brake operating member. The operation of the brake pedal 14 is input and a master cylinder device 16 that supplies pressurized hydraulic fluid to each brake device 12; and (C) the master cylinder device 16 and the four brake devices 12 are arranged. An anti-lock unit 18 as an ABS device, and (D) a high-pressure source device 22 as a high-pressure source for supplying a high-pressure hydraulic fluid by pumping and pressurizing the hydraulic fluid from a reservoir 20 as a low-pressure source; ) Regulator 24 that is a pressure regulator that regulates the hydraulic fluid supplied from the high-pressure source device 22 and supplies it to the master cylinder device 16, and (F) controls those devices and equipment. It is configured to include a brake electronic control unit 30 as a control device for controlling of the hydraulic brake system. Incidentally, the anti-lock unit 18 may be referred to as an “ABS unit 18”, and in the drawing, a reference numeral [ABS] is attached. Further, the brake electronic control unit 30 may be hereinafter referred to as “brake ECU 30”, and is represented by a symbol [ECU] in the drawing. The four wheels 10 are represented as a right front wheel 10FR, a left front wheel 10FL, a right rear wheel 10RR, and a left rear wheel 10RL when it is necessary to represent left and right front and rear. Further, when it is necessary to distinguish the left and right and the front and rear, the components such as the four brake devices 12 are denoted by the same reference numerals as those of the wheels 10 and represented as 12FR, 12FL, 12RR, 12RL, and the like.

ii) Brake device and ABS unit The brake device 12 provided corresponding to each wheel 10 is a disc rotor that rotates with the wheel 10, a caliper held by a carrier, a wheel cylinder held by the caliper, and held by a caliper. The disc brake device includes a brake pad that sandwiches the disc rotor by being moved by the wheel cylinder. The ABS unit 18 is a unit that includes a pressure increasing on / off valve, a pressure reducing on / off valve, a pump device, and the like that are provided corresponding to each wheel 10 and are paired. It is a device for preventing the wheel 10 from being kept locked when it is locked. Note that the brake device 12 and the ABS unit 18 are general devices and units, and are not related to the features of the claimable invention, so detailed description of their structures is omitted.

iii) Master Cylinder Device The master cylinder device 16 is a master cylinder device integrated with a stroke simulator. Generally speaking, inside the housing 40, there are two pressure pistons, a first pressure piston 42 and a second pressure piston. A piston 44 and an input piston 46 are disposed, and a stroke simulator mechanism 48 is incorporated. In the following description of the master cylinder device 16, for the sake of convenience, the left side in the figure is referred to as the front side and the right side is referred to as the rear side. , Moving to the right is called retreat.

  The housing 40 has a space in which the first pressurizing piston 42, the second pressurizing piston 44, and the input piston 46 are disposed, and the space is closed with a front end closed and an annular section. The section 50 is divided into a front chamber 52 and a rear chamber 54. The second pressurizing piston 44 has a bottomed cylindrical shape that opens forward, and is disposed on the front side in the front chamber 52. On the other hand, the first pressurizing piston 42 has a main body 58 having a bottomed cylindrical shape and a flange 56 formed at the rear end, and a protrusion 60 extending rearward from the main body 58. 58 is disposed behind the second pressurizing piston 44 in the front chamber 52. Since the partition 50 has an annular shape, an opening 62 is formed at the center, and the protrusion 60 extends through the opening 62 to the rear chamber 54. The input piston 46 is disposed in the rear chamber 54, more specifically, a part of the input piston 46 enters the interior of the rear chamber 54 from the rear, and the brake pedal 14 disposed in the rear moves the link rod 64. And is connected to the input piston 46.

  More specifically, between the first pressurizing piston 42 and the second pressurizing piston 44, two front wheels 10RR and 10RL corresponding to the two rear wheels 10RL are disposed in front of the main body 58 of the first pressurizing piston 42. The first pressurizing chamber R1 in which the hydraulic fluid supplied to the brake devices 12RR and 12RL is pressurized by the advancement of the first pressurizing piston 42 is provided on the front side of the second pressurizing piston 44 with two front wheels 10FR, A second pressurizing chamber R2 is formed in which hydraulic fluid supplied to the two brake devices 12FR and 12FL corresponding to 10FL is pressurized by the advancement of the second pressurizing piston 44, respectively. On the other hand, an inter-piston chamber R <b> 3 is formed between the first pressurizing piston 42 and the input piston 46. More specifically, the first pressurization is performed using the opening 62 so that the rear end of the protrusion 60 extending rearward from the opening 62 formed in the partition 50 faces the front end of the input piston 46. The inter-piston chamber R3 is formed so that the piston 42 and the input piston 46 face each other. Further, in the front chamber 52 of the housing 40, the front end surface of the partition 50 and the rear end surface of the main body 58 of the first pressurizing piston 42, that is, the rear end surface of the flange 56, on the outer periphery of the protrusion 60. The annular input chamber R4 into which the hydraulic fluid supplied from the regulator 24 is introduced so as to be partitioned is opposed to the input chamber R4 with the flange 56 in front of the flange 56 on the outer periphery of the main body portion 58. Each of the annular opposing chambers R5 is formed.

  The first pressurizing chamber R1 and the second pressurizing chamber R2 are respectively connected via the atmospheric pressure ports P1 and P2 when the first pressurizing piston 42 and the second pressurizing piston 44 are located at the rear end in the movement range. It is possible to communicate with the reservoir 20, and also communicate with the brake device 12 via the output ports P 3 and P 4 and the ABS unit 18, respectively. Incidentally, the first pressurizing chamber R1 is communicated with the brake devices 12RR and 12RL via a regulator 24 described later. The input chamber R4 is communicated with an adjustment pressure port of the regulator 24 described later through an input port P5.

  The inter-piston chamber R3 communicates with the communication port P6, and the counter chamber R5 communicates with the communication port P7. The communication port P6 and the communication port P7 are connected by an inter-chamber communication passage 70 that is an external communication passage. ing. In the middle of the inter-chamber communication path 70, there is provided a normally closed electromagnetic on-off valve 72, that is, an on-off valve 72 that is closed when not excited and opened when excited. When the valve 72 is opened, the inter-piston chamber R3 and the counter chamber R5 are communicated with each other. In a state where the inter-piston chamber R3 and the counter chamber R5 communicate with each other, it can be considered that one liquid chamber, that is, a liquid chamber that can be called a reaction force chamber R6 is formed. The on-off valve 72 has a function of switching between communication and non-communication between the inter-piston chamber R3 and the counter chamber R5, and is hereinafter referred to as an “inter-chamber communication switching valve 72”.

  Further, the master cylinder device 16 is further provided with two atmospheric pressure ports P8 and P9, which communicate with each other through an internal passage. One atmospheric pressure port P8 is connected to the reservoir 20, and the other atmospheric pressure port P9 is connected between the chamber communication switching valve 72 and the opposing chamber R5 via an atmospheric pressure release path 74 which is an external communication path. Are connected to the inter-room communication path 70. The atmospheric pressure release path 74 is provided with a normally open type electromagnetic on-off valve 76, that is, an on-off valve 76 that is opened when not excited and closed when excited. Since this on-off valve 76 has a function of opening the facing chamber R5 to atmospheric pressure, it is hereinafter referred to as “atmospheric pressure opening valve 76”.

The housing 40 has a space different from the space where the first pressure piston 42, the second pressure piston 44, and the input piston 46 are disposed. The stroke simulator mechanism 48 includes the space, A reaction force piston 80 disposed in the space and two reaction force springs 82 and 84 (both are compression coil springs) that urge the reaction force piston 80 are configured. A buffer chamber R7 is formed on the rear side of the reaction force piston 80 (represented as a substantially crushed space in the figure). When the input piston 46 moves forward by the operation of the brake pedal 14, the working fluid in the facing chamber R5, that is, the working fluid in the reaction force chamber R6 is introduced into the buffer chamber R7 via the internal passage. An operation reaction force is applied to the brake pedal 14 by the elastic reaction force of the reaction force springs 82 and 84 corresponding to the amount of hydraulic fluid, that is, the advance amount of the input piston 46 acting on the reaction force chamber R6. That is, the stroke simulator mechanism 48 functions as a reaction force applying mechanism that applies a reaction force having a magnitude corresponding to the amount of advance of the input piston 46 to the advance of the input piston 46. Incidentally, the two reaction force springs 82 and 84 are arranged in series, and the reaction force spring 84 has a considerably smaller spring constant than the reaction force spring 82, so that the operation of the brake pedal 14 can be performed. By prohibiting the deformation of the reaction force spring 84 in the course of progress, the stroke simulator mechanism 48 realizes a reaction force characteristic that increases the gradient from the middle. In this system, a reaction force pressure sensor 86 for detecting the pressure (reaction force pressure) of the hydraulic fluid in the reaction force chamber R6 is provided in the inter-chamber communication passage 70 (in the figure, the reaction force pressure is reduced). The symbol “P _RCT ” is attached).

  In a normal state, the inter-chamber communication switching valve 72 is open, the atmospheric pressure release valve 76 is closed, and the reaction force chamber R6 is formed by the inter-piston chamber R3 and the counter chamber R5. Has been. In the master cylinder device 16, the pressure receiving area of the first pressurizing piston 42 against which the pressure of the hydraulic fluid in the inter-piston chamber R3 acts to move the first pressurizing piston 42 forward, that is, the inter-piston chamber pressure receiving area, that is, The area of the rear end surface of the protrusion 60 of the first pressure piston 42 and the pressure receiving area of the first pressure piston 42 on which the pressure of the working fluid in the facing chamber R5 acts to move the first pressure piston 42 rearward. The (opposite chamber receiving pressure area), that is, the area of the front end face of the flange 56 of the first pressurizing piston 42 is made equal. Therefore, even if the brake pedal 14 is operated to advance the input piston 46, the first pressurizing piston 42 and the second pressurizing piston 44 do not advance depending on the operating force, that is, the pressure in the reaction force chamber R6. The hydraulic fluid pressurized by the master cylinder device 16 is not supplied to the brake device 12. On the other hand, when the pressure of the hydraulic fluid from the high pressure source device 22 is introduced into the input chamber R4, the first pressure piston 42 and the second pressure piston 44 move forward depending on the pressure of the hydraulic fluid, The hydraulic fluid pressurized to the pressure corresponding to the pressure of the hydraulic fluid in the input chamber R4 is supplied to the brake device 12. That is, according to the master cylinder device 16, the pressure of the hydraulic fluid supplied from the high-pressure source device 22 to the master cylinder device 16 without depending on the operating force applied to the brake pedal 14 in the normal state (normal time). In other words, a high pressure source pressure dependent braking force generation state in which the braking device 12 generates a braking force having a magnitude depending on the pressure of the hydraulic fluid supplied from the regulator 24 to the master cylinder device 16 is realized.

  The vehicle on which the present system is mounted is a hybrid vehicle as described above, and the regenerative braking force can be used in the vehicle. Therefore, the brake device 12 may generate a braking force that is obtained by subtracting the regenerative braking force from the braking force determined based on the brake operation. In this system, since the high pressure source pressure dependent braking force generation state is realized, the brake device 12 can generate a braking force that does not depend on the brake operation force. From such an action, this system is a hydraulic brake system suitable for a hybrid vehicle.

  On the other hand, when an electrical failure occurs, the inter-chamber communication switching valve 72 is closed, the atmospheric pressure release valve 76 is open, the inter-piston chamber R3 is sealed, and the facing chamber R5 is closed. Is opened to atmospheric pressure. In this state, the operating force applied to the brake pedal 14 is transmitted to the first pressurizing piston 42 via the hydraulic fluid in the inter-piston chamber R3, and the first pressurizing piston 42 and the second pressurizing piston 44 move forward. To do. That is, an operation force-dependent braking force generation state in which the brake device 12 generates a braking force having a magnitude depending on the operation force applied to the brake pedal 14 is realized. If the inter-chamber communication switching valve 72 is closed, the atmospheric pressure release valve 76 is opened, and the working fluid from the high pressure source device 22 is introduced into the input chamber R4, the first pressurizing piston 42 is provided. , The second pressurizing piston 44 is advanced by both the pressure of the hydraulic fluid supplied from the high pressure source device 22 to the master cylinder device 16 and the operating force, and a braking force having a magnitude depending on both of them, that is, The brake device 12 generates a brake force in which a brake force having a magnitude depending on the pressure of the hydraulic fluid supplied from the high pressure source device 22 to the master cylinder device 16 and a brake force having a magnitude depending on the operation force are added. An operating force / high pressure source pressure dependent braking force generation state is realized.

iv) High-pressure source device The high-pressure source device 22 is a pump 90 that pumps and pressurizes hydraulic fluid from the reservoir 20, a motor 92 that drives the pump 90, and an accumulator 94 that stores the hydraulic fluid pressurized by the pump 90 (FIG. In FIG. 2, the symbol [ACC] is attached). In the high pressure source device 22, the pressure of the hydraulic fluid in the accumulator 94, that is, the pressure of the hydraulic fluid to be supplied (hereinafter sometimes referred to as “high pressure source pressure P _ACC ”, so-called “accumulator pressure”). Is provided (in the figure, a symbol [P _ACC ], which is a symbol of the high-pressure source pressure) is provided).

v) Regulator The regulator 24 which is a pressure regulator is the pressure regulator of the first embodiment according to the claimable invention. Since the structure and function of the regulator 24 will be described in detail later, only the outline of the function will be described here. The regulator 24 employs a solenoid type plunger mechanism, and adjusts the hydraulic fluid of the high pressure source pressure P _ACC supplied from the high pressure source device 22 to a height corresponding to the current supplied to the solenoid coil. The adjusted hydraulic fluid, that is, the hydraulic fluid of the adjusted pressure (hereinafter sometimes referred to as “servo pressure P _SRV ”) is supplied to the input chamber R 4 of the master cylinder device 16. Note that the supply passage from the regulator 24 of the hydraulic fluid to the master cylinder unit 16, in the (Figure servo pressure sensor 98 for detecting the servo pressure P _SRV is provided, a symbol title servo pressure [ _PSRV ] is attached.)

Further, in order to cope with an electrical failure or the like, the regulator 24 uses the pressure of a certain hydraulic fluid introduced into the regulator 24 as a pilot pressure P _{PLT to adjust} the high pressure source pressure P _ACC supplied from the high pressure source device 22. It also has a function of adjusting the hydraulic fluid to a height corresponding to the pilot pressure P _PLT . Incidentally, the hydraulic fluid of the pilot pressure _PLT is wheel 10RL for the rear wheels from the master cylinder unit 16, a brake device 12RL corresponding to 10RR, hydraulic fluid supplied to 12RR, that is, is the hydraulic fluid in the master pressure P _MST Yes.

vi) Control system Control of this system, that is, brake control is performed by the brake ECU 30. The brake ECU 30 roughly controls the high-voltage source device 22 (specifically, the motor 92 included therein) and also controls the current supplied to the regulator 24. The brake ECU 30 includes a computer that is a central element, and a drive circuit (driver) for controlling current supply to the motor 92, the regulator 24, and the like of the high-voltage source device 22.

The brake ECU 30 obtains the reaction force pressure P _RCT , the high pressure source pressure P _ACC , and the servo pressure P _SRV as information necessary for control, so that the reaction force pressure sensor 86, the high pressure source pressure sensor 96, the servo pressure sensor described above are acquired. 98 is connected. In addition, this system is provided with a brake operation amount sensor 100 and a brake operation force sensor 102 in order to acquire the brake operation amount and the brake operation force as operation information of the brake pedal 14 that is a brake operation member ( In the figure, the symbols [δ _PDL ] and [F _PDL ] are assigned, respectively), and these sensors 100 and 102 are also connected to the brake ECU 30. The control by the brake ECU 30 in this system is performed based on the detection values of the various sensors mentioned here.

≪Regulator structure≫
As shown in FIG. 2, a regulator 24 that is a pressure regulator according to the first embodiment includes a housing 110 as a main component, and various members disposed inside the housing 110 or attached to the housing 110. It is comprised including. In the drawing, a central axis extending in the left-right direction is an axis of the housing 110. If the left side in the axial direction is called one end side and the right side is called the other end side, the housing 110 has a bottomed cylindrical housing main body 112 that opens at one end side. The lid body 114 is screwed onto one end of the housing body 112 so as to close the opening. A spool holding cylinder 116 as a spool holding body is fitted into the housing body 112 and is fixed by a lid 114. In the regulator 24, it can be considered that the housing 110 is configured including the spool holding cylinder 116.

  The inner diameter of the portion on the other end side from the center of the spool holding cylinder 116 is made small, and the spool 120 is held so as to be movable in the axial direction, specifically, to be slidable. The housing 110 has a high pressure port P10 to which hydraulic fluid is supplied from the high pressure source device 22, an atmospheric pressure port P11 as a low pressure port communicated with the reservoir 20 as a low pressure source via the master cylinder device 16, and is regulated. An adjustment pressure port P12 for supplying the hydraulic fluid to the input chamber R4 of the master cylinder device 16 is provided.

  On the inner peripheral surface of the spool holding cylinder 116, there are three types of internal ports that communicate with the ports P10, P11, P12 through internal passages formed in the housing main body 112 and the spool holding cylinder 116, respectively. A pair of internal high pressure port IP10, internal atmospheric pressure port (internal low pressure port) IP11, and internal adjustment pressure port IP12 are formed. In addition, an annular communication groove 122 is formed on the inner peripheral surface of the spool holding cylinder 116 between the internal high pressure port IP10 and the internal atmospheric pressure port IP11, and another annular groove is formed on one end side of the internal atmospheric pressure port IP11. Each of the communication grooves 124 is formed, and the internal adjustment pressure port IP12 is formed so as to open to the communication groove 124. On the other hand, the spool 120 is formed with a spool internal chamber R8 that is an internal space that extends generally in the axial direction and opens at the end of the other end, and each of the spool internal chambers R8 has a pair of first chambers. The first communication opening 126 and the second communication opening 128 are also open to the outer peripheral surface of the spool 120. Further, an annular communication groove 130 and a communication groove 132 are formed on the outer peripheral surface of the spool 120 so as to be aligned with each other on the other end side of the second communication opening 128. The first communication opening 126 is formed so as to open to the communication groove 132.

  The spool 120 is movable in the axial direction with respect to the spool holding cylinder 116, and the position of the spool 120 shown in the drawing, that is, the position of the spool 120 with respect to the spool holding cylinder 116 is within the movable range of the spool 120. A position on one end side, specifically, a position that becomes a moving end on one end side. From another viewpoint, the relative position of the spool 120 and the spool holding cylinder 116 can be considered as a position on one end side in the relative movable range. Therefore, hereinafter, the spool 120 and the spool holding cylinder 116 in the state shown in FIG. The relative position may be referred to as “one end side position”. The one end side position is defined by the end of one end side of the spool 120 being locked to a step surface 140 as a locking surface formed inside the spool holding cylinder 116. That is, it is defined by the spool 120 and the spool holding cylinder 116 being in direct contact with each other. A separation spring 142, which is a compression coil spring, is disposed on the other end side of the spool 120. Due to the biasing force of the separation spring 142, the relative position between the spool 120 and the spool holding cylinder 116 is a position on the one end side. Maintained. By the way, the energizing force is considered to be quite small.

  In the state where the spool 120 and the spool holding cylinder 116 are positioned at one end side position, the second communication opening 128 opens into the communication groove 124 in which the internal adjustment pressure port IP12 is opened. Communicate with P12. Further, since a part of the internal atmospheric pressure port IP11 is opened in the communication groove 132 in which the first communication opening 126 is opened, the spool internal chamber R8 is also in communication with the atmospheric pressure port P11. On the other hand, the internal high-pressure port IP10 is closed by the outer peripheral surface of the spool 120. Therefore, in a state where the spool 120 and the spool holding cylinder 116 are positioned at one end side position, the communication between the atmospheric pressure port P11 and the adjustment pressure port P12 is permitted via the spool inner chamber R8, and the high pressure port P10 and the adjustment pressure port Communication with P12 is cut off.

When the spool 120 is moved by a distance on the other end side, that is, when the spool 120 and the spool holding cylinder 116 are relatively moved by a distance on the other end side of the relative movable range, at least one of the second communication openings 128 is present. The state where the portion is opened to the communication groove 124 is maintained, and the state where the spool inner chamber R8 and the adjustment pressure port P12 communicate with each other is maintained. Further, the internal atmospheric pressure port IP11 is closed by the outer peripheral surface of the spool 120. On the other hand, a part of the internal high pressure port IP10 opens into the communication groove 130, and the communication groove 132 and the communication groove 122 are connected. The communication between the communication groove 130 and the communication groove 122 is maintained. Therefore, in a state where the spool 120 and the spool holding cylinder 116 are relatively moved by a distance on the other end side, the communication between the atmospheric pressure port P11 and the adjustment pressure port P12 is cut off, and the high pressure port P10 is connected via the spool inner chamber R8. And communication with the adjustment pressure port P12 is allowed. As can be seen from the above description, the spool interior chamber R8 are always for hydraulic fluid of the adjusting push ie servo pressure P _SRV is present, the spool interior chamber R8 is introduced adjustment pressure port P12 and the communication with adjusted pressure It functions as an adjustment pressure chamber.

  As can be seen from the above operation, the regulator 24 includes the spool 120 and the spool holding cylinder 116, and the high pressure port P 10 of the adjustment pressure port P 12, the atmospheric pressure, depending on the relative position of the spool 120 and the spool holding cylinder 116. A spool valve mechanism 144 that realizes selective communication with any one of the ports P11 is configured.

  On one end side of the spool 120, a plunger 150 is disposed so as to penetrate the lid body 114 of the housing 110 and is held by the lid body 114 so as to be movable in the axial direction. A head portion 152 which is a portion on one end side of the plunger 150 is disposed outside the housing 110, and the head portion 152 is covered with a bottomed cylindrical casing 154. A separation spring 156 that is a compression coil spring is disposed between the head 152 and the inner surface of the bottom wall of the casing 154. The urging force of the separation spring 156 is further smaller than the urging force of the separation spring 142, and the tip of the plunger 150 abuts against the spool 120, but the relative position between the spool 120 and the spool holding cylinder 116 is the position at the one end side. Maintained.

  A coil 158 is disposed on the outer periphery of the casing 154. By energizing the coil 158, an urging force for the plunger 150 to push the spool 120 to the other end side is generated by electromagnetic force. The urging force increases as the current increases according to the energized current, that is, the current supplied to the coil 158. Due to such a structure, the regulator 24 includes a coil 158 and a plunger 150 to constitute a solenoid-type plunger mechanism 160. The solenoid-type plunger mechanism 160 includes the spool 120, the spool 120, and the solenoid 120. A first urging mechanism 162 that urges the spool holding cylinder 116 in the direction of relative movement to the other end side in the relative movable range is configured.

An end portion on one end side of the spool holding cylinder 116 has a large inner diameter, and a stepped cylindrical pilot piston 164 is disposed in the end portion. The pilot piston 164 is formed with a through hole penetrating in the axial direction. The pilot piston 164 is movable in the axial direction with the plunger 150 penetrating through the through hole. 114 is held by a protruding portion on the other end side. The portion of the pilot piston 164 on the other end side has a small diameter, and the tip of the portion can be brought into contact with the end surface on the one end side of the spool 120. A pilot pressure chamber R9 is defined on one end side of the pilot piston 164, and the pilot pressure chamber R9 communicates with pilot pressure ports P13 and P14 formed in the housing body 112 via an internal passage. As can be seen from FIG. 1, the first pressure chamber R <b> 1 of the master cylinder device 16 and the brake devices 12 </ b> RL of the rear wheels are communicated with each other through the pilot pressure ports P <b> 13 and P <b> 14. Therefore, the pilot pressure chamber R9 is a part of the hydraulic fluid supply path from the master cylinder device 16 to the brake devices 12RL and 12RR, and the hydraulic fluid of the master pressure P _MST is supplied to the pilot pressure chamber R9. Introduced as hydraulic fluid of pressure P _PLT .

The pilot piston 164 pushes the spool 120 toward the other end side in a state of being in contact with the spool 120 by the pressure of the hydraulic fluid in the pilot pressure chamber R9, that is, by the action of the pilot pressure P _PLT . That is, the second urging mechanism 166 that urges the spool 120 toward the other end side, including the pilot pressure chamber R9 and the pilot piston 164, in other words, the spool 120 and the spool holding cylinder 116 are within a relatively movable range. A second biasing mechanism 166 is configured to bias in the direction of relative movement toward the other end side. Incidentally, the other end of the pilot piston 164, opposite to the pilot pressure chamber R9 across the pilot piston 164, adjustment push ie servo pressure P opposing chamber R10 annular hydraulic fluid is introduced in the _SRV is partitioned and formed ing. The facing chamber R10 can also be considered as a part of the adjustment pressure chamber.

Further, a pin 168 having a flat head is disposed on the other end side of the spool 120 so that the head is pressed against the bottom wall of the housing main body 122 by a separation spring 142 which is a compression coil spring. The pin 168 is inserted into the spool internal chamber R8 from the other end side so as to close the opening on the other end side of the spool internal chamber R8. In other words, the internal space of the spool 120 opens to the side in the biasing direction by the first biasing mechanism 162 and the second biasing mechanism 166 described above, and the pin 168 supported by the housing 110 is inserted into the opening. Thus, by closing the opening, the spool internal chamber R8, which is an adjustment pressure chamber, is defined. When the pressure of the hydraulic fluid in the spool inner chamber R8, that is, the servo pressure _PSRV increases, the spool 120 is urged toward one end side by the pressure. That is, the regulator 24 includes the pin 168 and the spool inner chamber R8, and the spool 120 is biased in the reverse direction to urge the spool 120 and the spool holding cylinder 116 in a direction in which the spool 120 and the spool holding cylinder 116 are relatively moved toward one end in the relative movable range. A biasing mechanism 170 is configured.

An annular hydraulic fluid chamber is defined around the pin 168 on the other end side of the spool 120, and the hydraulic fluid chamber communicates with the atmospheric pressure port P11 via an internal passage. The pressure of the hydraulic fluid in the hydraulic fluid chamber is always the atmospheric pressure P _RSV (the pressure of the hydraulic fluid in the reservoir 20). Further, the housing body 112 is provided with another high-pressure port P15 communicating with the high-pressure port P10 through an internal passage, and another atmospheric pressure port P16 communicating with the atmospheric pressure port P11 through the internal passage. As can be seen from FIG. 1, a relief valve 172 is disposed in an external passage connecting the ports P15 and P16. Therefore, when the high pressure source pressure P _ACC becomes a pressure higher than the set value, the hydraulic fluid from the high pressure source device 22 flows through the regulator 24 to the reservoir 20.

≪Regulator function≫
In the regulator 24, during normal time (in a normal state where no electrical failure or the like has occurred), pressure regulation by the first urging mechanism 162, that is, pressure regulation of the hydraulic fluid by the solenoid plunger mechanism 160 is performed. Is done. When a current is supplied to the coil 158, the spool 120 is urged to the other end side by the first urging mechanism 162 and moves from the moving end on one end side to the other end side. In other words, the spool 120 and the spool holding cylinder 116 relatively move from one end side position toward the other end side in the relative movable range. The movement causes the spool valve mechanism 144 to connect the high pressure port P10 and the adjustment pressure port P12, thereby increasing the pressure of the hydraulic fluid supplied to the input chamber R4 of the master cylinder device 16, that is, the servo pressure _PSRV. It is done. On the other hand, as the servo pressure _PSRV rises, the pressure of the hydraulic fluid in the spool inner chamber R8 also rises, and the spool 120 is biased to one end side by the reverse direction biasing mechanism 170 and moves to one end side. In other words, the spool 120 and the spool holding cylinder 116 relatively move to one end side in the relative movement range. As a result of such an action, a state where the urging force by the first urging mechanism 162 and the urging force by the reverse direction urging mechanism 170 are balanced is maintained, and the pressure of the hydraulic fluid supplied to the master cylinder device 16 is maintained. A certain servo pressure P _SRV is adjusted to a height corresponding to the amount of current supplied to the coil 158.

In addition, the working fluid of the master pressure P _MST is introduced into the pilot pressure chamber R9 as the working fluid of the pilot pressure P _PLT , but the working fluid of the servo pressure P _SRV is also introduced into the facing chamber R10. The pressure increase ratio of the master cylinder device 16, that is, the ratio of the master pressure P _MST to the servo pressure P _SRV is substantially 1, and the urging force due to the hydraulic fluid pressure in the facing chamber R 10 is applied by the second urging mechanism 166. It is configured to win the power. As a result, the second urging mechanism 166 does not substantially apply the urging force to the spool 120 and does not hinder the pressure regulation by the first urging mechanism 162 in the normal time.

On the other hand, when the pressure cannot be adjusted by the first urging mechanism 162, that is, the solenoid type plunger mechanism 160, such as at the time of electrical failure, the pressure is adjusted by the pilot pressure P _PLT . In the master cylinder device 16, as described above, in the case of an electrical failure or the like, an operating force / high pressure source pressure dependent braking force generation state is realized. Therefore, since the master pressure P _MST is obtained depending on both the servo pressure P _SRV and the operating force, the ratio of the master pressure P _MST to the servo pressure P _SRV exceeds 1 in the event of an electrical failure or the like. It becomes. As a result, the pilot pressure P _PLT which is the pressure in the pilot pressure chamber R9 of the regulator 24 becomes higher than the servo pressure _PSRV , and the second urging mechanism 166 applies an urging force corresponding to the difference between them to the spool 120. It will be. Pressure regulation by the second urging mechanism 166 using this urging force is performed. Specifically, when the master pressure P _MST increases, the second urging mechanism 166 urges the spool 120 to the other end side and moves from the moving end on one end side to the other end side in the moving range. . In other words, the spool 120 and the spool holding cylinder 116 relatively move from one end side position toward the other end side in the relative movable range. By the relative movement, the spool valve mechanism 144 causes the high pressure port P10 and the adjustment pressure port P12 to communicate with each other, thereby increasing the pressure of the hydraulic fluid supplied to the input chamber R4 of the master cylinder device 16, that is, the servo pressure _PSRV. Be made. On the other hand, as the servo pressure _PSRV rises, the pressure of the hydraulic fluid in the spool inner chamber R8 also rises, and the spool 120 is biased to one end side by the reverse direction biasing mechanism 170 and moves to one end side. In other words, the spool 120 and the spool holding cylinder 116 relatively move to one end side in the relative movement range. As a result of such an action, a state where the urging force by the second urging mechanism 166 and the urging force by the reverse direction urging mechanism 170 are balanced is maintained, and the pressure of the hydraulic fluid supplied to the master cylinder device 16 is maintained. A certain servo pressure P _SRV is adjusted to a height corresponding to the pilot pressure P _PLT .

As described above, when the spool 120 is biased by the first biasing mechanism 162, the regulator 24 is prohibited from biasing the spool 120 by the second biasing mechanism 166. When the urging of the spool 120 by the 162 is impossible, the urging of the spool 120 by the second urging mechanism 166 is allowed. That is, when the pressure adjustment according to the current supplied to the coil 158 is performed, the pressure adjustment by the pilot pressure P _PLT is prohibited, and the pressure adjustment according to the current supplied to the coil 158 is impossible. _Therefore , pressure regulation by the pilot pressure P _PLT is allowed. By adopting the regulator 24, the hydraulic brake system is an excellent system in fail-safe against electrical failure or the like.

  In this regulator 24, the spool valve mechanism 144 is adopted, and as described above, the internal ports IP10, IP11, IP12 formed in the spool holding cylinder 116, the communication grooves 122, 124, and the spool 120 are formed. The relative positions of the communication openings 126 and 128 and the communication grooves 130 and 132 in the axial direction greatly affect the accuracy of pressure regulation. In view of this, the positioning accuracy between the spool 120 and the spool holding cylinder 116 when the regulator 24 is assembled affects the accuracy of pressure regulation. In the regulator 24, the relative position on one end side in the relative movable range between the spool 120 and the spool holding cylinder 116 is such that the end face on the one end side of the spool 120 and the step surface as a locking surface formed on the spool holding cylinder 116. 140 is defined by contact with 140. That is, the one end side positions of the spool 120 and the spool holding cylinder 116 are defined by the direct contact between the spool 120 and the spool holding cylinder 116. Therefore, positioning of the spool 120 and the spool holding cylinder 116 can be performed with high accuracy without special consideration during assembly. As a result, the regulator 24 has good accuracy in regulating the hydraulic fluid. That is, good pressure regulation can be performed.

  As described above, the regulator 24 is pressure-regulated by the solenoid-type plunger mechanism 160 at a normal time. The urging force by the solenoid plunger mechanism 160 is relatively small, and the urging force by the reverse direction urging mechanism 170 that balances the urging force is also reduced. For this reason, the influence of the displacement of the relative position between the spool 120 and the spool holding cylinder 116 is particularly great. However, the regulator 24 is configured such that the position of the one end side directly contacts the spool 120 and the spool holding cylinder 116. The effect that depends on the regulation, that is, the effect that the accuracy of the pressure regulation is kept good can be fully enjoyed.

≪Operation of hydraulic brake system for vehicles≫
As described above, the operation of the hydraulic brake system is controlled by the brake ECU 30. Regarding the operation of the high pressure source device 22, the brake ECU 30 determines that the high pressure source pressure P _ACC acquired based on the detection by the high pressure source pressure sensor 96 is within a set pressure range defined by the set upper limit pressure and the set lower limit pressure. The pump 90, i.e. the motor 92, is activated so that it is maintained.

Regarding the operation of the master cylinder device 16, as described above, in the normal state, the brake ECU 30 excites the inter-chamber communication switching valve 72 and the atmospheric pressure release valve 76 to open and close the valves, respectively. The high pressure source pressure dependent braking force generation state is realized. Then, a required brake force, which is a required brake force, is calculated from the brake operation amount and the brake operation force acquired based on the detection of the brake operation amount sensor 100 and the brake operation force sensor 102, and from the required brake force. A value obtained by subtracting the regenerative braking force generated by the regenerative braking system is determined as the necessary hydraulic braking force. A target servo pressure is determined based on the necessary hydraulic brake force, and the solenoid plunger mechanism 160 of the regulator 24 is set so that the servo pressure _PSRV acquired based on the detection of the servo pressure sensor 98 becomes the target servo pressure. , And more specifically, the current supplied to its coil 158 is controlled. By such control, the hydraulic brake system is provided with the necessary hydraulic brake force on each wheel 10 depending on the pressure of the hydraulic fluid supplied from the high pressure source device 22 and regulated by the regulator 24. Generated in the brake device 12.

On the other hand, in the case of an electrical failure, the control by the brake ECU 30 is not performed. As described above, the inter-chamber communication switching valve 72 and the atmospheric pressure release valve 76 are not excited, and are closed and opened, respectively, to realize the operating force / high pressure source pressure dependent braking force generation state. Is done. In the master cylinder device 16, the brake operation force is transmitted to the first pressurizing piston 42 and the second pressurizing piston 44 via the hydraulic fluid in the inter-piston chamber R <b> 3. A pressurized hydraulic fluid is supplied from the output port P3 depending on the brake operating force. The hydraulic fluid is introduced into the pilot pressure chamber R9 of the regulator 24, so that the regulator 24 _{As long as} pressure regulation by _MST is performed and high pressure hydraulic fluid remains in the accumulator 94, hydraulic fluid of servo pressure _PSRV corresponding to the master pressure _MST is supplied from the regulator 24 to the input chamber R4 of the master cylinder device 16. The With this supply, a brake force having a magnitude depending on both the brake operation force and the pressure of the hydraulic fluid supplied from the high pressure source device 22 and regulated by the regulator 24 is generated in the brake device 12 of each wheel 10. Will be. Incidentally, after the high-pressure hydraulic fluid no longer remains in the accumulator 94, the brake device 12 of each wheel 10 generates a braking force depending on the brake operation force.

  The vehicle hydraulic brake system of the second embodiment is a system in which the regulator 24 employed in the vehicle hydraulic brake system of the first embodiment is changed to another pressure regulator. Therefore, the description of the vehicle hydraulic brake system according to the second embodiment is limited to the description of the pressure regulator.

  A regulator 200 which is a pressure regulator of the second embodiment employed in the vehicle hydraulic brake system of the second embodiment has a structure as shown in FIG. 3 and includes the regulator 24 of the first embodiment, The structure is somewhat similar. In view of this, members and portions having the same function are denoted by the same reference numerals as those used in the regulator 24, and a description thereof will be omitted to some extent. The description regarding the regulator 200 will be focused on the structure different from the regulator 24.

  In the regulator 200, unlike the regulator 24, the spool holding cylinder 116 is held by the housing body 112 so as to be movable in the axial direction, and the pilot piston 164 is connected to the other end side of the spool 120, specifically, the spool holding cylinder 116. The housing body 112 is disposed on the other end side of the housing movably in the axial direction. A separation spring 202 that is a compression coil spring is interposed between the spool holding cylinder 116 and the lid body 114, and the spool holding cylinder 116 is connected to the other end side together with the pilot piston 164 by a relatively weak biasing force. Is being energized. The pilot piston 164 has a recess formed on one end side, and a pin 168 is disposed in the recess. That is, the pin 168 is supported by the housing 110 via the pilot piston 164. The pin 168 is pressed against the pilot piston 164 by the relatively weak biasing force of the separation spring 142, and the spool 120 is biased to one end side, and the step surface 140 as a locking surface formed on the spool holding cylinder 116. It is pressed against. The relative position in the axial direction of the spool 120 and the spool holding cylinder 116 shown in the drawing is the position on one end side in the relative movable range, that is, the one end side position described above.

  As the spool holding cylinder 116 is movable and the pilot piston 164 is disposed on the other end side of the spool 120, the arrangement of the various ports P10 to P16 is different from the arrangement in the regulator 24. The internal passages connecting P10 to P12 and the internal ports IP10 to IP12 are also different from the internal passages in the regulator 24. Further, in the internal passages connecting the ports P10 to P12 and the internal ports IP10 to IP12, the flow of the hydraulic fluid in the passages is also caused by the movement of the spool holding cylinder 116 between the spool holding cylinder 116 and the housing body 112. Means are provided for security.

The annular chamber R11, which is the annular hydraulic fluid chamber in which the separation spring 202 is disposed, forms a part of an internal passage that connects the internal adjustment pressure port IP12 and the adjustment pressure port P12, and communicates with the spool internal chamber R8. I'm doing it. Thus, the annular chamber R11, the working fluid of the adjusting push ie servo pressure P _SRV is introduced, functions as a part of the adjustment chamber.

  Since the structure and function of the spool valve mechanism 144 are substantially the same as those of the regulator 24, description thereof is omitted here. The structure of the first urging mechanism 162 is substantially the same as that of the regulator 24. However, the separation spring 156 urges the plunger 150 toward one end with a relatively weak urging force. It is disposed between the head 152 and the lid 114. Therefore, although it is difficult to understand in the figure, in the state shown in the figure, the tip of the plunger 150 and the end on the one end side of the spool 120 are slightly separated from each other.

Explaining the second urging mechanism 166, the pilot pressure chamber R9 is _{supplied with} the working fluid of the master pressure P _{MST as} the working fluid of the pilot pressure P _{PLT. By} the action of _PLT , the pilot piston 164 urges the spool 120 toward one end side via the separation spring 142 and also urges the spool holding cylinder 116 toward one end side. Since movement of the spool 120 to one end side is prohibited by the plunger 150, depending on the pilot piston 164, substantially only the spool holding cylinder 116 moves to one end side. That is, the second urging mechanism 166 configured to include the pilot pressure chamber R9 and the pilot piston 164 holds the spool in a direction in which the spool 120 and the spool holding cylinder 116 move relative to the other end side in the relative movable range. The tube 116 is configured to be urged.

Further, the reverse direction biasing mechanism 170 will be described. Similarly to the reverse direction biasing mechanism of the regulator 24, when the servo pressure _PSRV, which is the pressure of the hydraulic fluid introduced into the spool inner chamber R8, rises, The spool 120 is urged toward the one end side by the pressure. Therefore, in the reverse direction urging mechanism 170, the mechanism including the pin 168 and the spool inner chamber R 8 (hereinafter also referred to as “first mechanism”) is similar to that of the regulator 24. Has a function of biasing the spool 120 and the spool holding cylinder 116 in a direction in which the spool 120 and the spool holding cylinder 116 relatively move toward one end side in the relative movable range. On the other hand, in the regulator 200, because the hydraulic fluid in the servo pressure P _SRV to the annular chamber R11 is introduced, if the servo pressure P _SRV rises, due to the pressure, the spool holding cylinder 116 toward the other side Is energized. In other words, in the reverse direction biasing mechanism 170, a mechanism including the annular chamber R11 (hereinafter also referred to as “second mechanism”) includes the spool holding cylinder 116, the spool 120, the spool holding cylinder 116, and the like. Has a function of biasing in the direction of relative movement toward one end in the relative movable range. In summary, in this regulator 200, it can be considered that the reverse direction urging mechanism 170 is constituted by the first mechanism and the second mechanism which are the two mechanisms.

In the regulator 200, in the normal state, as in the regulator 24, the pressure is adjusted by the first urging mechanism 162, that is, the hydraulic fluid is adjusted by the solenoid plunger mechanism 160. Since the normal operation of the regulator 200 is the same as the operation of the regulator 24, detailed description is omitted, but the biasing force by the first biasing mechanism 162 and the biasing force by the first mechanism of the reverse biasing mechanism 170 are not described. The state in which the power is balanced is maintained, and the servo pressure P _SRV that is the pressure of the hydraulic fluid supplied to the master cylinder device 16 is adjusted to a height corresponding to the amount of current supplied to the coil 158. The pilot pressure chamber R9 is _{supplied with} the hydraulic fluid at the master pressure P _MST as the pilot pressure P _PLT , but the servo fluid P _SRV is also introduced into the annular chamber R11. The pressure increase ratio of the master cylinder device 16, that is, the ratio of the master pressure P _MST to the servo pressure P _SRV is substantially 1, and the urging force by the second mechanism of the reverse direction urging mechanism 170 is the second urging mechanism. It is configured to overcome the urging force by 166 slightly. As a result, depending on the urging force, the spool holding cylinder 116 does not move in the axial direction, and pressure regulation by the first urging mechanism 162 during normal operation is not hindered.

On the other hand, when the pressure cannot be adjusted by the first urging mechanism 162, that is, the solenoid type plunger mechanism 160, such as at the time of electrical failure, the pressure is adjusted by the pilot pressure P _PLT . Similar to the regulator 24, when electrical failure occurs, the hydraulic fluid having the master pressure P _MST higher than the servo pressure P _SRV is introduced into the pilot pressure chamber R9 as the hydraulic fluid for the pilot pressure P _PLT . Since the operation of the regulator 200 at the time of electrical failure or the like is the same as the operation of the regulator 24, detailed description is omitted. However, since the movement of the spool 120 is prohibited by the plunger 150, Along with the movement in the axial direction, a state in which the urging force by the second urging mechanism 166 and the urging force by the second mechanism of the reverse direction urging mechanism 170 are maintained is maintained and supplied to the master cylinder device 16. The servo pressure P _SRV that is the pressure of the hydraulic fluid is adjusted to a height corresponding to the pilot pressure P _PLT . The pilot piston 164 is urged toward the other end side by a relatively small urging force that depends on the pressure of the hydraulic fluid in the spool inner chamber R8. Therefore, actually, the urging force and the two urging forces are Thus, the pressure is adjusted so as to maintain the balanced state.

  As described above, the hydraulic brake system that employs the regulator 200 is an excellent system in fail-safe against electrical failure or the like, similar to the hydraulic brake system of the first embodiment that employs the regulator 24. It is. Also in the regulator 200, the relative position on one end side in the relative movable range of the spool 120 and the spool holding cylinder 116 is defined by the direct contact between the spool 120 and the spool holding cylinder 116, and the effect of this is as follows. Since it is the same as the effect in the regulator 24, the description of the effect is omitted. Furthermore, since the operation of the system employing the regulator 200 is the same as that of the hydraulic brake system of the first embodiment, description thereof is omitted here.

  The vehicle hydraulic brake system of the third embodiment is a system in which the regulator 24 employed in the vehicle hydraulic brake system of the first embodiment is simply changed to another pressure regulator. Therefore, the description of the hydraulic brake system for a vehicle according to the third embodiment is limited to the description of the pressure regulator. Further, the regulator is the regulator 250 shown in FIG. 4 and differs from the regulator 200 which is the regulator of the second embodiment only in a part of the configuration, so only the explanation of that part will be given. In view of this, members and parts having the same functions are denoted by the same reference numerals as those used in the regulator 200, and descriptions thereof are omitted.

  In the regulator 250, a rubber friction disk 252 is disposed in the recess of the pilot piston 164. The end of the spool holding cylinder 116 on the other end side is formed so as to have an inner collar, so that a hole 254 is provided, and the periphery of the hole 254 can be brought into contact with the friction disk 252. The end portion on the other end side of the spool 120 is a small-diameter portion having a small outer diameter, and is inserted into a hole 254 provided in the end portion on the other end side of the spool holding cylinder 116 so as to be able to contact the friction disk 252. Has been. The separation spring 142 is disposed between an inner flange provided at an end portion on the other end side of the spool holding cylinder 116 and a step surface as a locking surface that defines a small diameter portion of the spool 120. The spool internal chamber R8, which is the internal space of the spool 120, is not opened at the end face on the other end side of the spool 120.

The annular chamber R11 is introduced with the hydraulic fluid having the servo pressure _PSRV , and the spool holding cylinder 116 is urged toward the other end side by the pressure of the hydraulic fluid. The end on the other end side of the spool holding cylinder 116 comes into contact with the friction disk 252, and the friction disk 252 is deformed by the biasing force, and the center part enters the hole 254 toward one end side. The approaching central portion abuts against the end surface on the other end side of the spool 120 and urges the spool 120 toward one end side with an urging force corresponding to the urging force. Due to such a structure, the regulator 250 includes the friction disk 252 and is provided with a reverse direction biasing the spool 120 in a direction in which the spool 120 and the spool holding cylinder 116 relatively move toward one end in the relative movable range. That is, a mechanism corresponding to the first mechanism of the regulator 200 is configured. In the regulator 250, the spool 120 is not biased to one end side by the pressure of the hydraulic fluid in the spool inner chamber R8.

Further, the second urging mechanism 166 will be described. When the pressure is adjusted by the pilot pressure P _PLT at the time of electrical failure or the like, the pilot piston 164 is connected to the spool holding cylinder 116 via the friction disk 252. However, the second urging mechanism 166 having the same function as that of the second urging mechanism 166 in the regulator 200 is employed.

Modified example

The hydraulic brake systems of the above three embodiments are the hydraulic fluid supplied to the brake device 12 from the master cylinder device 16 as the hydraulic fluid of the pilot pressure P _PLT to the regulators 24, 200, 250, that is, the master pressure P _MST. The hydraulic fluid having a pressure corresponding to the brake operating force is introduced into the pilot pressure chamber R9 in place of the master pressure P _MST hydraulic fluid. Also good. Even with such hydraulic fluid, the regulators 24, 200, 250 can perform good pressure regulation in the event of an electrical failure, and the hydraulic brake system is suitable for the brake device 12 with a suitable braking force. Can be generated. Specifically, for example, the hydraulic fluid in the inter-piston chamber R3 can be introduced. In the master cylinder device 16, the inter-piston chamber R3 is hermetically sealed when the inter-chamber communication switching valve 72 is closed in the event of an electrical failure or the like. In this state, the pressure of the hydraulic fluid in the inter-piston chamber R3 becomes a pressure corresponding to the brake operation force. Therefore, even if the pressure of the hydraulic fluid in the inter-piston chamber R3 is set to the pilot pressure P _PLT , the pressure is adjusted appropriately. Pressure is possible.

12: Brake device 14: Brake pedal [brake operation member] 16: Master cylinder device 20: Reservoir [low pressure source] 22: High pressure source device [high pressure source] 24: Regulator [pressure regulator] 30: Brake electronic control unit (brake ECU ) [ECU] [Control device] 110: Housing 116: Spool holding cylinder [Spool holding body] 120: Spool 140: Step surface (locking surface) 144: Spool valve mechanism 150: Plunger 158: Coil 160: Solenoid plunger mechanism 162: First urging mechanism 164: Pilot piston 166: Second urging mechanism 168: Pin 170: Reverse direction urging mechanism 200: Regulator [pressure regulator] 250: Regulator [pressure regulator] 252: Friction disk R8: Inside of spool Chamber [regulated pressure chamber] R9: Pilot Chamber R10: opposing chamber [adjusting chamber] R11: annular chamber [adjusting chamber] P10: high-pressure port P11: atmospheric port [low pressure port] P12: adjusting pressure port P _ACC: high pressure source pressure P _PLT: pilot pressure P _RSV : Atmospheric pressure P _SRV : Servo pressure [adjusted pressure] _PMST : Master pressure

Claims (7)

A pressure regulator that regulates a high-pressure hydraulic fluid from a high-pressure source to a regulated pressure and supplies the regulated hydraulic fluid,
A housing;
Each of the housing includes (a) a high pressure port to which hydraulic fluid from a high pressure source is supplied, (b) a low pressure port in communication with the low pressure source, and (c) a regulated hydraulic fluid. An adjustment pressure port to supply,
A spool and a spool holder that holds the spool, the spool and the spool holder are relatively movable in the axial direction, and the spool and the spool holder are positioned on one end side in the relative movable range. The communication between the low pressure port and the adjustment pressure port is allowed, the communication between the high pressure port and the adjustment pressure port is blocked, and the spool and the spool holder are moved relative to each other side. A spool valve mechanism that blocks communication between the low pressure port and the adjustment pressure port and allows communication between the high pressure port and the adjustment pressure port;
A biasing mechanism for biasing one of the spool and the spool holder in a direction in which the spool and the spool holder are relatively moved toward the other end;
There is an adjustment pressure chamber that communicates with the adjustment pressure port and into which a hydraulic fluid of an adjustment pressure is introduced, and one of the spool and the spool holder is connected to the spool and the spool by the pressure of the hydraulic fluid in the adjustment pressure chamber. A reverse direction urging mechanism that urges the holding body in the direction of relative movement toward the one end side,
A pressure regulator configured such that a relative position on one end side in a relative movable range between the spool and the spool holder is defined by the spool directly contacting a step surface formed on the spool holder. .   The pressure regulator according to claim 1, wherein the biasing mechanism includes a solenoid type plunger mechanism that generates a biasing force having a magnitude corresponding to a supplied current. The biasing mechanism is configured to bias the spool;
Inside the spool, a space is formed that opens to an end portion on the side in the urging direction by the urging mechanism,
The reverse biasing mechanism is
A pin supported by the housing and inserted into an opening at an end of the spool to close the opening; and the adjustment pressure chamber includes the space in which the opening is closed by the pin; The pressure regulator according to claim 1 or 2, wherein the spool is biased in a direction opposite to a biasing direction by the biasing mechanism by the pressure of the hydraulic fluid in the adjustment pressure chamber. In the case where the urging mechanism is the first urging mechanism,
The regulator is
There is a pilot pressure chamber into which hydraulic fluid having a pilot pressure is introduced, and one of the spool and the spool holder is connected to the spool and the spool holder by the pressure of the hydraulic fluid in the pilot pressure chamber. The pressure regulator according to any one of claims 1 to 3, further comprising a second urging mechanism that urges in a direction of relative movement toward the other end side.   When urging by the first urging mechanism is performed, urging by the second urging mechanism is prohibited, and when the urging by the first urging mechanism is impossible, the second urging is performed. The pressure regulator according to claim 4, wherein biasing by the mechanism is allowed. A brake operating member;
A brake device provided on the wheel;
A master cylinder device that introduces the adjusted hydraulic fluid, pressurizes the hydraulic fluid to a pressure corresponding to the pressure of the introduced hydraulic fluid, and supplies the pressurized hydraulic fluid to the brake device;
A high pressure source device as a high pressure source for supplying high pressure hydraulic fluid;
A pressure regulator according to any one of claims 1 to 5, and
A hydraulic brake system for a vehicle configured such that hydraulic fluid regulated by the pressure regulator is introduced into the master cylinder device. A brake operating member;
A brake device provided on the wheel;
A master cylinder device that introduces the adjusted hydraulic fluid, pressurizes the hydraulic fluid to a pressure corresponding to the pressure of the introduced hydraulic fluid, and supplies the pressurized hydraulic fluid to the brake device;
A high pressure source device as a high pressure source for supplying high pressure hydraulic fluid;
A pressure regulator according to claim 4 or 5,
With
The hydraulic fluid regulated by the pressure regulator is configured to be introduced into the master cylinder device,
One of a hydraulic fluid having a pressure corresponding to a brake operating force applied to the brake operating member and a hydraulic fluid supplied from the master cylinder device to the brake device is provided in the pilot pressure chamber. configured vehicle dual hydraulic braking system to be introduced as a hydraulic fluid pressure to be pressure.

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