JP5583808B2 - Brake device - Google Patents

Description

  The present invention relates to a brake device having a reservoir function capable of storing brake fluid.

  The technique described in Patent Document 1 includes a reservoir piston in a brake device used in an antilock brake device or the like, and a pressure regulating valve installed above the piston, and supports a rod provided in the pressure regulating valve. A guide portion and a passage portion through which the brake fluid flows are individually formed.

JP 2008-106905 A

However, since the fluid passage formed on the outer periphery side of the rod is narrow, the pipe resistance may increase.
An object of the present invention is to provide a brake device with low pipe resistance.

  In order to achieve the above object, in the present invention, a rod that is disposed between a seat portion with which the valve body abuts and a crown surface of the piston body, and separates the valve body from the seat portion, and one end side of the rod in the axial direction. A support hole that is slidably supported, a rod outer peripheral passage portion that is an outer periphery on the other end side of the rod and has an inner diameter larger than the inner diameter of the support hole, and a communication hole that communicates between the rod outer peripheral passage portion and the bottomed hole. A stopper that regulates the stroke amount of the rod in the direction of the piston body to a predetermined stroke amount, and the rod and the piston body are formed so as to be separable, and the piston body has a stroke amount larger than the predetermined stroke amount. Configured to allow stroke.

  Therefore, the entire outer periphery of the rod can be used as a flow path, and the pipe resistance can be reduced by ensuring the effective cross-sectional area of the fluid passage.

FIG. 2 is a hydraulic circuit diagram of the brake hydraulic pressure control device according to the first embodiment. FIG. 3 is a skeleton diagram illustrating a housing of the hydraulic control unit according to the first embodiment. 3 is an enlarged partial cross-sectional view illustrating a configuration of a reservoir according to Embodiment 1. FIG. 2 is an enlarged cross-sectional view illustrating a configuration of a pressure regulating valve according to Embodiment 1. FIG. 3 is a perspective view of a filter member of Example 1. FIG. 4 is a diagram illustrating details of a filter member of Example 1. FIG. FIG. 3 is a cross-sectional view of the housing according to the first embodiment taken along the line AA.

[Example 1]
[Configuration of brake hydraulic circuit]
FIG. 1 is a hydraulic circuit diagram of the brake hydraulic pressure control device 32 according to the first embodiment. The hydraulic circuit is formed in a hydraulic control unit 30 provided between the master cylinder M / C and the wheel cylinder W / C. The hydraulic control unit 30 has a substantially rectangular parallelepiped housing 31 cut out from an aluminum block. A plurality of oil passages and the like are formed in the housing 31, and each valve, pump unit, and motor described later are provided. .
The brake fluid pressure control device 32 performs fluid pressure control according to the required fluid pressure of the vehicle dynamics control (VDC: vehicle behavior control) and the anti-lock brake system (ABS: antilock brake control) from the controller. The brake fluid pressure control device 32 has an X piping structure composed of two systems of a P system brake fluid pressure circuit 21P and an S system brake fluid pressure circuit 21S. The left front wheel cylinder W / C (FL) and the right rear wheel wheel cylinder W / C (RR) are connected to the P system, and the right front wheel wheel cylinder W / C (FR) is connected to the S system. ), Wheel cylinder W / C (RL) for the left rear wheel is connected. The brake fluid pressure control device 32 and each wheel cylinder W / C are connected to wheel cylinder ports 19RL, 19FR, 19FL, 19RR drilled in the upper surface of the housing 31. The pump unit P is a tandem gear pump that drives a rotary gear type gear pump PP and a gear pump PS, each of which has a pair of external gears provided in the P system and the S system, by a single motor M.

The master cylinder M / C and the hydraulic pressure control unit 30 are connected to each other in the liquid passages 18P and 18S via master cylinder ports 20P and 20S formed in the port connection surface of the housing 31. The liquid path 18 and the suction side of the pump unit P are connected by liquid paths 10P and 10S. On the liquid path 18P, a master cylinder pressure sensor 22 is provided between the master cylinder port 20P and a connection portion between the liquid path 10P.
The discharge side of the pump unit P and each wheel cylinder W / C are connected by liquid paths 11P and 11S. On each of the liquid passages 11, pressure increasing valves 3FL, 3RR, 3FR, 3RL, which are normally open solenoid valves corresponding to the respective wheel cylinders W / C, are provided. Further, check valves 6P and 6S are provided on each liquid passage 11 and between each pressure increasing valve 3 and the pump unit P. Each check valve 6 allows the flow of the brake fluid pressure in the direction from the pump unit P toward the pressure increasing valve 3 and prohibits the flow in the opposite direction. Discharge pressure sensors 23P and 23S are provided between the pressure increasing valves 3 and the pump unit P on each liquid passage 11.

Furthermore, each fluid passage 11 is provided with fluid passages 16FL, 16RR, 16FR, and 16RL that bypass each pressure increasing valve 3, and the fluid passage 16 is provided with check valves 9FL, 9RR, 9FR, and 9RL. Yes. Each check valve 9 allows the flow of brake fluid pressure in the direction from the wheel cylinder W / C toward the pump unit P, and prohibits the flow in the opposite direction.
The master cylinder M / C and the liquid path 11 are connected by liquid paths 12P and 12S, and the liquid path 11 and the liquid path 12 merge between the pump unit P and the pressure increasing valve 3. On each liquid passage 12, gate-out valves 2P and 2S, which are normally open solenoid valves, are provided. Each liquid path 12 is provided with liquid paths 17P and 17S that bypass each gate-out valve 2, and the liquid path 17 is provided with check valves 8P and 8S. Each check valve 8 allows the flow of brake fluid pressure in the direction from the master cylinder M / C side toward the wheel cylinder W / C, and prohibits the flow in the opposite direction. The master cylinder M / C and the reservoirs 15P and 15S are connected by liquid passages 10aP and 10aS, and pressure regulating valves 7P and 7S having a check valve function are provided between the reservoir 15 and the master cylinder M / C. Yes.
Reservoirs 15P and 15S are provided on the suction side of the pump unit P, and the reservoir 15 and the pump unit P are connected by liquid passages 10bP and 10bS.
The wheel cylinder W / C and the liquid path 10 are connected by liquid paths 13 </ b> P and 13 </ b> S, and the liquid path 13 and the liquid path 10 merge between the pressure regulating valve 7 and the reservoir 15. The liquid passages 13 are provided with pressure reducing valves 4FL, 4RR, 4FR, 4RL, which are normally closed solenoid valves.

  Here, the operation of the pressure regulating valve 7 provided adjacent to the reservoir 15 will be described. During normal braking, that is, when each valve, pump, etc. is not operating, if brake fluid pressure is generated in the master cylinder M / C, the pressure regulating valve 7 is closed and the master cylinder M / C and the reservoir 15 are shut off. . Then, the brake fluid is supplied to each wheel cylinder W / C through the fluid passage 18. Next, at the time of ABS operation, when the pressure increasing valve 3 is closed and the pressure reducing valve 4 is opened as an initial operation, the brake fluid in the wheel cylinder W / C flows into the reservoir 15 through the liquid passage 13. At this time, the brake fluid that has flowed into the reservoir 15 by the operation of the pump unit P is pumped up through the fluid path 11 and is returned to the master cylinder M / C. At the time of VDC operation, the gate-out valve 2 is closed, the pressure increasing valve 3 corresponding to the desired wheel is opened, and the pump unit P is operated. At this time, even if the pressure regulating valve 7 is closed, the inside of the reservoir 15 is decompressed by pumping up the pump unit P, and the pressure regulating valve 7 is pushed open. As a result, the brake fluid is pumped up from the master cylinder M / C, and the increased brake fluid is supplied to the necessary wheel cylinder W / C.

[Housing configuration]
FIG. 2 is a skeleton diagram showing the housing of the hydraulic control unit according to the first embodiment, and FIG. 3 is an enlarged partial sectional view showing the configuration of the reservoir according to the first embodiment. FIG. 2 shows a state in which the valves, the control unit, and the motor M are removed for easy understanding. In the following description, the surface on which the master cylinder port 20 is open in FIG. 2 is the front surface 311, the back surface of the front surface 311 is the rear surface 312, the surface on which the wheel cylinder port 19 is open is the top surface 313, and the back surface of the top surface 313 is the bottom surface. 314, a left side surface with respect to the front surface 311 is referred to as a left side surface 315, and a right side surface with respect to the front surface 311 is referred to as a right side surface 316. 2A is a view of the housing 31 as viewed from the back surface 312, and FIG. 2B is a view of the housing 31 as viewed from the left side surface 315.
The housing 31 has a substantially rectangular parallelepiped shape. The motor M is attached to the front surface 311 side, the solenoid valve groups of the gate-out valve 2, the pressure increasing valve 3, and the pressure reducing valve 4 on the rear surface 312 side, and the electric for driving these solenoid valve groups. The unit is installed. The electric unit includes a board that performs a predetermined calculation in accordance with an input signal from a wheel speed sensor or the like attached to the vehicle. A predetermined electric signal is supplied to a solenoid attached to a solenoid valve or a motor M. Output. This electric unit is accommodated in a unit case. The housing 31 is formed with a power supply hole 24 that penetrates the front surface 311 and the rear surface 312. The electric unit and the motor M are connected by inserting the electrode of the motor M into the power supply hole 24.

The housing 31 has a valve mounting hole in which each solenoid valve group is mounted by press-fitting or caulking, a plurality of liquid passages connecting between each port and each solenoid valve group, and each cylinder (wheel cylinder W / C). , A port (foil cylinder port 19, master cylinder port 20) connected to the master cylinder M / C) and a hole for arranging the reservoir 15 are formed. These holes, liquid passage holes and the like are drilled from the outside of the housing 31 to each surface by a drill or the like.
A master cylinder port 20 is formed on the upper surface 313 side of the front surface 311. The pump unit P is accommodated in a substantially cylindrical accommodating portion 41 that penetrates from the front surface 311 to the rear surface 312 of the housing 31. The accommodating portion 41 has an opening on the rear surface 312 side sealed with an end plate. Further, discharge portion accommodation holes 47P and 47S are formed from the left side 315 to the right side 316 of the housing 31 so as to be substantially orthogonal to the accommodation portion 41. Check valves 6P and 6S connected to the discharge liquid passage of the pump unit P are inserted into the discharge portion receiving holes 47P and 47S.

FIG. 3 is an enlarged partial cross-sectional view illustrating the configuration of the reservoir according to the first embodiment. This enlarged partial cross-sectional view shows the reservoir 15 on the P system side, but also in the S system, the pump unit P includes the rotation center axis and is arranged around the vertical plane parallel to the side of the housing. The reference numerals will be described without adding S and P in particular. A cylindrical bottomed hole 31 a is formed below the housing 31 from the lower surface 314 upward. A retainer holding surface 31a2 is formed in the lower opening of the housing of the bottomed hole 31a, and the retainer holding surface 31a2 holds the retainer member 151 by caulking fixing 31a3. The retainer member 151 holds one end of a flange portion 151a whose outer peripheral edge is nipped by a caulking fixing 31a3, a cylindrical portion 151b that is bent downward from the flange portion 151a, and a coil spring 152 (first elastic member). The holding surface 151c is formed with a closed portion, and an air hole 151d is formed in the approximate center of the closed portion. Thus, the atmospheric pressure is always applied below the piston main body 153.
The bottomed hole 31a includes a piston contact surface 31a1 that contacts the piston surface 153h of the piston main body 153, and a small diameter cylindrical portion 31b that is smaller in diameter than the piston contact surface 31a1 and formed in the center of the bottomed hole 31a. Have. A liquid passage 13 communicating with the pressure reducing valve 4 and a liquid passage 10b communicating with the suction side of the pump unit P are connected to the small diameter cylindrical portion 31b. A cylindrical pressure regulating valve housing hole 31c having a central axis OR at a position offset from the central axis of the bottomed hole 31a, that is, the central axis OP of the piston main body 153 to the left in the drawing, is further above the small diameter cylindrical portion 31b. Is formed. Above the pressure regulating valve housing hole 31c, there is a liquid that is a small diameter oil passage that is smaller in diameter than the pressure regulating valve housing hole 31c and that is formed in series via a reduced diameter portion 31c1 that is the bottom of the pressure regulating valve housing hole 31c. The path 10a is connected. The liquid passage 10a communicates with the master cylinder M / C.

In the pressure regulating valve housing hole 31c, a filter member 75 for removing impurities in the brake fluid flowing from the fluid passage 10a, and a seat member 71 (corresponding to a passage member) constituting the pressure regulating valve 7 while fitting with the filter member 75 are fitted. And have been stowed. 4 is an enlarged cross-sectional view showing the configuration of the pressure regulating valve of the first embodiment, FIG. 5 is a perspective view of the filter member of the first embodiment, and FIG. 6 is a diagram showing details of the filter member of the first embodiment. 4 shows a state in which the rod 74 is positioned at the lowermost end. The filter member 75 is a mesh-like cylindrical filter 75a, a stopper portion 75b that functions as a stopper for the ball member 72, a pillar portion 75c that is a skeleton member of the filter member 75 and to which the filter 75a is attached, A cylindrical portion 75d formed in an annular shape below the pillar portion 75c and connected to the pillar portion 75c, and a crown surface facing the liquid passage 10a side of the filter member 75 is formed between the liquid passage 10a and the filter 75a. And a protrusion 75e for securing the flow path. The protrusion 75e abuts on the reduced diameter portion 31c1 which is the bottom of the pressure regulating valve housing hole 31c as necessary to secure a flow path. The outer diameter of the filter member 75 is smaller than that of the pressure regulating valve housing hole 31c, and a flow path between the outer periphery of the filter member 75 and the pressure regulating valve housing hole 31c is secured.
The stopper portion 75b has a columnar central stopper portion 75ba extending to the bottom surface 75b2 of the filter member 75, and reinforcing portions 75bb having four tapered surfaces that are equally disposed on the outer periphery of the central stopper portion 75ba. A vertical groove 75bc is provided between the reinforcing portion 75bb and the adjacent reinforcing portion 75bb. The vertical groove 75bc has a spring holding surface 75b1 that is raised from the bottom surface 75b2 and holds the pressure regulating valve return spring 73. In addition, engagement convex portions 75d1 raised on the inner peripheral side are formed at four locations in the circumferential direction at the lower end on the inner peripheral side of the cylindrical portion 75d. The filter member 75 is made of resin.

In a region surrounded by the upper end of the seat member 71 and the filter member 75, a ball member 72 (valve element) and a pressure regulating valve return spring 73 (second valve) that urges the ball member 72 toward the seat member 71 side. (Elastic member) is attached. The elastic force of the pressure regulating valve return spring 73 is set to be weaker than the elastic force of the coil spring 152, and when the brake fluid pressure is not applied, the ball member 72 causes the rod 74 to move by the elastic force of the coil spring 152. It is set as the structure pushed up through.
The sheet member 71 is a cylindrical member having a plurality of stepped portions, and has an upper cylindrical portion 71g that forms a fit with the filter member 75, a diameter larger than that of the upper cylindrical portion 71g, and is substantially the same as the pressure regulating valve housing hole 31c. It has the middle cylindrical part 71h which has the same diameter, and the lower cylindrical part 71j slightly expanded in diameter from the middle cylindrical part 71h. An engaging groove 71e is formed between the upper cylindrical portion 71g and the middle cylindrical portion 71h, and the pressure regulating valve 7 is placed in the pressure regulating valve housing hole 31c between the middle cylindrical portion 71h and the lower cylindrical portion 71j. A fitting groove 71f into which the housing material is fitted is formed during press fitting. The filter member 75 and the seat member 71 are configured such that the pressure control valve return spring 73 and the ball member 72 are placed inside the filter member 75, and the upper cylindrical portion 71 g of the seat member 71 in which the rod 74 is accommodated is passed through the filter member 75. It inserts in the cylindrical part 75d. Then, the engagement convex part 75d1 of the filter member 75 and the engagement groove 71e of the sheet member 71 are fitted together to form an integrated structure, and the pressure regulating valve 7 is configured.

The seat member 71 includes a through hole 71b (corresponding to the rod outer periphery passage portion) that forms a brake fluid passage between the rod 74 and the outer periphery of the rod 74 while accommodating the rod 74 that contacts the ball member 72 at the axial center. A holding hole 71d (corresponding to a support hole) that holds the rod 74 in the radial direction, and a plurality of holes are formed at positions surrounding the holding hole 71d from below the sheet member 71, and a lower end portion of the through hole 71b. It has a flow hole 71c (corresponding to a communication hole) that partially communicates. In other words, the through hole 71b and the flow hole 71c are formed so as to be overlapped in the radial direction, and the passage configuration is facilitated by communicating in the overlap region. A mortar-shaped sheet portion 71a is formed on the ball member 72 side of the through hole 71b. When the ball member 72 is seated on the seat portion 71a, the brake fluid does not flow between the liquid passage 10a and the small diameter cylindrical portion 31b. On the other hand, when the ball member 72 is pushed up against the force of the pressure regulating valve return spring 73 by the rod 74, the brake fluid supplied from the liquid passage 10a passes through the filter 75a of the filter member 75 and the rod 71b and the rod. 74 flows through the gap between the outer periphery and the flow hole 71c to the small diameter cylindrical portion 31b. Thus, by utilizing the entire outer periphery of the rod 74 as a flow path, the effective cross-sectional area of the fluid passage is ensured and the pipe resistance is reduced. In addition, a sheet member 71 is provided as a separate member from the housing 31, and the formability is ensured by forming a through hole 71b and a flow hole 71c corresponding to the rod outer peripheral passage portion in the sheet member 71.
The free length of the pressure regulating valve return spring 73 is set to a length that allows the ball member 72 to always be urged toward the seat member 71. As described above, the filter member 75 and the sheet member 71 are integrated with each other by fitting the engagement convex portion 75d1 and the engagement groove 71e, and the filter member 75 is used to absorb assembly errors. A slight gap is set between the upper end (the upper end of the protrusion 75e) and the bottom of the pressure regulating valve housing hole 31c. At this time, even if the fitting of the filter member 75 and the sheet member 71 is released and the filter member 75 falls off, and the filter member 75 comes into contact with the bottom of the pressure regulating valve housing hole 31c, the protrusion 75e Thus, a flow path between the liquid path 10a and the filter 75a is secured, and the ball member 72 can be pressed against the seat portion 71a by the pressure regulating valve return spring 73.

  The rod 74 is a rod-shaped metal member having a diameter larger than that of the holding hole 71d and a rod front end portion 74a (corresponding to the other end side of the rod) contacting the ball member 72, and substantially the same diameter as the holding hole 71d. A rod intermediate portion 74b (corresponding to one end side of the rod) formed longer than the rod tip portion 74a and a tapered shape gradually reduced in diameter from the rod intermediate portion 74a, and an upper surface 155b of a plate member 155 described later. And a rod lower end portion 74c that comes into contact with. The rod 74 is configured as a separate member from the piston main body 153. When the piston main body 153 strokes more than the length of the rod intermediate portion 74b, the rod lower end 74c is separated from the plate member upper surface 155b. In other words, the rod tip 74a functions as a stopper by contacting the upper end of the holding hole 71d. The rod intermediate portion 74b is a maximum stroke amount value of the ball member 75, which is a distance between the filter member side end of the ball member 72 and the stopper portion 75b when the ball member 72 is seated on the seat portion 71a. Longer than the maximum stroke amount of the piston body 153. As described above, sliding of the rod 74 causes the sliding portion between the rod 74 and the holding hole 71d to shift for each stroke, so that the durability of the rod 74 and the sheet member 71 is improved. As described above, the center axis OR of the rod 74 is arranged offset from the center axis OP (rotation center) of the piston main body 153.

The piston main body 153 is a resin-molded member, and is formed in a bottomed cylindrical shape having a bottom portion 153a1. On the outer periphery of the cylinder of the piston main body 153, there is an upper outer peripheral portion 153f formed slightly smaller than the inner peripheral diameter of the bottomed hole 31a, and an annular shape formed below the upper outer peripheral portion 153f to accommodate the annular seal member 154. A groove 153e, a seal member holding portion 153d formed to have substantially the same diameter as the inner diameter of the bottomed hole 31a and holding the annular seal member 154, and an inner circumference of the bottomed hole 31a formed below the seal member holding portion 153d A reduced diameter portion 153c having a diameter smaller than that of the upper outer peripheral portion 153f and a weld line forming portion 153b formed below the reduced diameter portion 153 and having substantially the same diameter as the inner peripheral diameter of the bottomed hole 31a. And have. The annular seal member 154 is partitioned with the upper part as a hydraulic chamber and the lower part as an air chamber.
Here, the weld line is a position away from the gate position (injection port for injecting molten resin into the mold) when resin molding (insert molding), and the resin flowing into the mold is another It is a portion that remains as a joint trace between the resins when they are cooled and solidified while joining with the resin that has flowed in through the path. In general, a portion where a weld line is formed tends to be less accurate. In the first embodiment, the weld line forming portion 153b is provided below the annular seal member 154, that is, at a position partitioned as an air chamber. That is, the piston main body 153 is configured so that the weld line is formed at a position where accuracy related to liquid tightness is not required, in other words, the weld line is not formed at a location where accuracy is required. .

An inner periphery 153a of the cylindrical portion of the piston main body 153 is formed to have a slightly larger diameter than the coil spring 152, and the other end of the coil spring 152 is held at the bottom portion 153a1. A metal plate member 155 is assembled by insert molding as a hard body harder than the resin of the piston main body 153 in the central region (that is, the crown surface 153j) of the piston surface 153h formed on the upper surface of the piston main body 153. ing. The plate member 155 is a disk-shaped stainless steel member, and the outer diameter DP of the plate member 155 is larger than the outer diameter DS of the coil spring 152.
That is, when the coil spring 152 is held by the bottom portion 153a1 of the resin-made piston main body 153, an elastic force by the coil spring 152 is always applied to the portion. If the outer diameter of the metal plate member 155 is smaller than the outer diameter of the coil spring 152, the contact position of the coil spring 152 and the plate member 155 are separated in the radial direction when viewed from the axial direction. Further, a shearing force acts between the crown surface 153j and the piston bottom 153a, and there is a possibility that the durability of the piston main body 153 is lowered. On the other hand, as in the first embodiment, if the outer diameter DP of the plate member 155 is larger than the outer diameter DS of the coil spring 152, the contact position of the coil spring 152 and the plate member 155 have a diameter when viewed from the axial direction. It overlaps seeing from an axial direction, without separating in a direction. Therefore, only the compression force acts on the crown surface 153j, and the decrease in durability is suppressed.

  FIG. 7 is a cross-sectional view taken along the line AA of the housing of the first embodiment. The bottomed hole 31aP in which the P system reservoir 15P is accommodated is disposed on the left side in FIG. 7, and the bottomed hole 31aS in which the S system reservoir 15S is accommodated is disposed on the right side in FIG. The center axis OR of the pressure regulating valve receiving hole 31cP communicating with the bottomed hole 31aP is arranged offset to the left in FIG. 7 with respect to the center axis OP of the bottomed hole 31aP. Similarly, the center axis OR of the pressure regulating valve receiving hole 31cS communicating with the bottomed hole 31aS is arranged offset to the right side in FIG. 7 with respect to the center axis OP of the bottomed hole 31aS. In other words, both the fluid passages 10 a communicating with the pressure regulating valve housing hole 31 a are formed in directions away from the central axis OP of the piston main body 153. In this way, by arranging the pressure regulating valve housing holes 31c so as to be separated from each other, an area sandwiched between the pressure regulating valve housing holes 31c can be widened. A storage portion 41 for housing the rotary gear type pump is formed immediately above the reservoir 15, and this space is generally determined by the required pump discharge capacity and the like. Therefore, by offsetting the pressure regulating valve housing holes 31c so as to be in directions away from each other, the layout of the rotary gear pump is improved and the overall housing is prevented from being enlarged.

As described above, the effects listed below can be obtained in the first embodiment.
(1) A housing 31 in which an oil passage is formed, a piston main body 153 that is assembled in a bottomed hole 31a that is formed in the housing 31 and communicates with the liquid passages 10a, 10b, and 13 (oil passage); A coil spring 152 (first elastic member) that urges 153 toward the bottom of the bottomed hole 31a, a ball member 72 (valve element) disposed in the liquid passage 10a, and a seat portion 71a with which the ball member 72 abuts. The rod 74 is disposed between the crown surface 153j of the piston main body 153 and the ball member 72, and the rod 74 separates the ball member 72 from the seat portion 71a. One end of the ball member 72 abuts on the ball member 72 and urges it toward the seat portion 71a. A pressure regulating valve return spring 73 (second elastic member) having a weaker elastic force than the coil spring 152 and a rod intermediate portion 74b (one end side of the rod) are used as shafts. A holding hole 71d (supporting hole) that is slidably supported in the direction, a through hole 71b (rod outer peripheral passage portion) having an inner diameter larger than the inner diameter of the holding hole 71d at the rod tip 74a (the other end side of the rod), A through hole 71b and a flow hole 71c (communication hole) communicating with the bottomed hole 31a were provided.
Therefore, the entire outer periphery of the rod 74 can be used as a flow path, and the pipe resistance can be reduced by ensuring the effective cross-sectional area of the fluid passage.
(2) The seat portion 71a, the holding hole 71d, the through hole 71b, and the flow hole 71c are formed by a sheet member 71 (passage member) attached to the pressure regulating valve housing hole 31c. Therefore, by processing the sheet member 71 which is a separate member from the housing 31, all the configurations can be obtained, and the moldability can be ensured.
(3) The through hole 71b and the flow hole 71c are formed to overlap in the radial direction. By communicating in the overlap region, the passage configuration can be simplified. That is, the structure of securing the flow path while holding the rod 74 can be achieved by drilling a plurality of holes.
(4) The length of the rod intermediate portion 74 b of the rod 74 is set to be longer than the maximum stroke value of the ball member 72 and shorter than the maximum stroke amount of the piston body 153. As a result, when the rod 74 slides, the sliding portion between the rod 74 and the holding hole 71d is shifted for each stroke, so that the durability of the rod 74 and the sheet member 71 can be improved.

7 Pressure regulating valve 10 Liquid path 10a Liquid path 10b Liquid path 11 Liquid path 13 Liquid path 15 Reservoir 31 Housing 31a Bottomed hole 31c Pressure regulating valve mounting hole 32 Brake hydraulic pressure control device 71 Seat member 71a Seat portion 71b Through hole 71c Flow hole 72 Ball member 73 Pressure regulating valve return spring 74 Rod 74a Rod tip 74b Rod intermediate portion 75 Filter member 151 Retainer member 152 Coil spring 153 Piston body 155 Plate member
M / C Master cylinder P Pump unit
W / C wheel cylinder

Claims (3)

A housing having an oil passage formed therein;
A piston body assembled in a bottomed hole formed in the housing and communicating with the oil passage;
A first elastic member that urges the piston body toward the bottom of the bottomed hole;
A valve body disposed in the oil passage;
A rod disposed between a seat portion against which the valve body abuts and a crown surface of the piston body, and a rod for separating the valve body from the seat portion;
A second elastic member having an elastic force weaker than that of the first elastic member, one end of which contacts the valve body and urges in the direction of the seat portion;
A support hole for slidably supporting one end side of the rod in the axial direction;
A rod outer peripheral passage portion having an inner diameter larger than the inner diameter of the support hole at the other end of the rod;
A communication hole communicating with the rod outer periphery passage portion and the inside of the bottomed hole;
A stopper that regulates the stroke amount of the rod toward the piston body to a predetermined stroke amount;
With
In the housing, a bottomed pressure regulating valve housing hole in which the valve body and the seat portion are housed is formed continuously to the bottomed hole,
The oil passage has a small diameter oil passage that opens at the bottom of the pressure regulating valve housing hole and has a smaller diameter than the adjustment pressure valve housing hole;
A filter that removes impurities in the brake fluid is provided between the valve body and the small-diameter oil passage,
The filter includes a plurality of protrusions that can come into contact with the bottom of the pressure regulating valve housing hole,
An oil path is configured between the adjacent protrusions,
The rod device and the piston main body are formed to be separable, and the piston main body is configured to be able to stroke up to a stroke amount larger than the predetermined stroke amount. The brake device according to claim 1, wherein
The brake device, wherein the seat portion, the support hole, the rod outer peripheral passage portion, and the communication hole are formed by a passage member attached to the oil passage. The brake device according to claim 1 or 2,
The brake device according to claim 1, wherein the rod outer peripheral passage portion and the communication hole are formed to overlap in a radial direction.

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