JP2012180031A - Braking device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a braking device with a filter member that can miniaturize the device as a whole.SOLUTION: The braking device includes: a housing formed with an oil path therein; a valve body disposed in the oil path; a sheet member having a sheet on which the valve body abuts; a cylindrical filter member fixed to the sheet member and having a body part and a mesh part; a column connecting between bases formed both ends of the body part of the filter member and forming an opening edge defined along an axial direction out of opening edges of the mesh part; and a deformation prevention means for preventing the column from being deformed.

Description

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

  The technology described in Patent Document 1 discloses a configuration including a reservoir piston in a brake device used in an antilock brake device and the like, and a pressure regulating valve installed above the piston.

Japanese Patent No. 3937554

Here, it is common to provide the pressure regulating valve with a filter member in order to prevent contamination or the like mixed in the brake fluid from entering the pump. And in order to ensure a filter passage area, when setting the diameter of the filter member large, there existed a problem that it could not contribute to size reduction of the whole apparatus. That is, the filter member is disposed above the reservoir, and a pump or the like is disposed between the two reservoirs. Therefore, if the filter member has a large diameter, it is necessary to increase the interval between the reservoirs. It will increase in size. Therefore, it is conceivable to secure the filter passage area by reducing the diameter of the filter member and increasing the axial length. In this case, when the hydraulic pressure is applied to the filter due to the inflow of the brake fluid, the member that supports the filter is deformed, which may hinder the proper operation of the pressure regulating valve.
The objective of this invention is providing the brake device provided with the filter member which can attain size reduction of the whole apparatus.

  In order to achieve the above object, in the present invention, a housing in which an oil passage is formed, a valve body arranged in the oil passage, a seat member provided with a seat portion against which the valve body abuts, and the seat A cylindrical filter member fixed to the member and provided with a main body portion and a mesh portion; a main body portion of the filter member; a base portion formed at both ends; and an axial direction of the opening edges of the mesh portion connecting between the base portions And a deformation suppressing means for suppressing deformation of the column part.

  Therefore, the strength of the filter member can be ensured, and the overall size of the apparatus can be reduced by setting the filter member long in the axial direction.

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. 6 is a perspective view of a filter member of Example 2. FIG. 6 is a perspective view of a filter member of Example 3. FIG. 6 is a perspective view of a filter member of Example 4. FIG. 10 is a perspective view of a filter member of Example 5. FIG. 10 is a perspective view of a filter member of Example 6. FIG. 10 is an enlarged cross-sectional view illustrating a configuration of a pressure regulating valve according to Example 6. FIG. 10 is a perspective view of a filter member of Example 7. FIG. FIG. 10 is an enlarged cross-sectional view illustrating a configuration of a pressure regulating valve according to an eighth embodiment.

[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 is formed with a flange portion 151a whose outer peripheral edge is held by a caulking fixing 31a3, a cylindrical portion 151b bent downward from the flange portion 151a, and a holding surface 151c for holding one end of the coil spring 152. The air hole 151d is formed in the approximate center of the closed part. 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. Further above the small-diameter cylindrical portion 31b, a cylindrical and slender pressure regulating valve having a central axis OR at a position offset to the left side in the drawing from the central axis OP of the bottomed hole 31a, that is, the central axis OP of the piston main body 153. An accommodation hole 31c 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.

  A filter member 75 that removes impurities in the brake fluid that has flowed in from the fluid passage 10 a and a seat member 71 that constitutes the pressure control valve 7 while fitting with the filter member 75 are accommodated in the pressure regulating valve housing hole 31 c. Yes. 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. The pressure regulating valve 7 shown in FIG. 4 shows a state where the rod 74 is positioned at the uppermost end. The filter member 75 is a mesh-shaped cylindrical filter 75a, a stopper portion 75b that functions as a stopper for the ball member 72, and a column portion that is a skeleton member of the filter member 75 and to which the filter 75a is attached either inside or by integral molding. 75c, a cylindrical part 75d (corresponding to the base) formed in an annular shape below the pillar part 75c and connected to the pillar part 75c, and formed in a disk shape above the pillar part 75c and connected to the pillar part 75c The bottom surface 75b2 (corresponding to the base) is formed, and a protrusion 75e is formed on the crown surface of the filter member 75 facing the liquid channel 10a to secure a flow path between the liquid channel 10a and the filter 75a. Further, the column portions 75c are formed at even places in the circumferential direction substantially evenly. 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 tapered front end that extends to the bottom surface 75b2 of the filter member 75 and has a cylindrical central stopper portion 75ba. The stopper portion 75b includes a tapered portion 75bb formed in a tapered shape from the central stopper portion 75ba, and a columnar portion 75bc formed in a cylindrical shape. The diameter of the cylindrical portion 75bc is slightly smaller than the inner diameter of the pressure regulating valve return spring 73 described later, and also functions as a retaining member that stably holds the pressure regulating valve return spring 73. On the bottom surface 75b2 side of the cylindrical portion 75bc, there is a deformation suppressing portion 750 provided with a spring holding surface 75b1 for holding the pressure regulating valve return spring 73 raised in the cross direction. The deformation suppressing portion 750 is provided at a position overlapping the column portion 75c in the radial direction, and functions as a deformation suppressing unit that suppresses the column portion 75c from bending toward the inner diameter side of the filter member 75. In other words, the bottom surface 75b2 (one of the base portions) has a deformation suppressing portion 750 (corresponding to a reinforcing portion) that connects the column portion 75c at a position facing the diameter direction of the column portion 75c. The filter 75a covers up to the portion of the deformation suppressing portion 750. In other words, the axial length of the column portion 75c is shorter than the axial length of the filter 75a. Thereby, the pressing force due to the hydraulic pressure acting on the filter 75a can be received by the deformation suppressing unit 750. 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 for urging the ball member 72 toward the seat member 71 are attached. ing. 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 accommodates a rod 74 that contacts the ball member 72 at the center in the axial direction, and forms a brake fluid passage between the rod 74 and the outer periphery of the rod 74, and has a smaller diameter than the through hole 71b. A plurality of holes are formed at positions surrounding the holding hole 71d from below the sheet member 71, and a circulation hole 71c partially communicating with the lower end portion of the through hole 71b. 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 being in contact with the ball member 72. The rod 74 is substantially the same diameter as the holding hole 71d and is longer than the rod front end 74a. The formed rod intermediate portion 74b has a tapered shape gradually reduced in diameter from the rod intermediate portion 74a and has a rod lower end portion 74c that comes into contact with an upper surface 155b of a plate member 155 described later. The rod 74 is configured as a separate member from the piston main body 153, and 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.

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, the layout of the rotary gear pump is improved by making the shape of the pressure regulating valve housing hole 31c elongated in the axial direction and further offset the pressure regulating valve housing holes 31c in directions away from each other. While suppressing the increase in size of the entire housing.

  In this way, when the pressure regulating valve receiving hole 31c has an elongated shape, when the hydraulic pressure is applied to the filter by the inflow of brake fluid, the member supporting the filter may be deformed, and the proper operation of the pressure regulating valve may be hindered. . Therefore, in the first embodiment, the deformation suppressing portion 750 raised in the cross direction is formed on the bottom surface 75b2 side of the cylindrical portion 75bc. Thereby, the substantial length of the column part 75c can be shortened, and even if a pressing force acts on the column part 75c due to the hydraulic pressure acting on the filter 75a, the deformation of the column part 75c is suppressed. Therefore, the operation of the ball member 72 housed in the filter member 75 is not hindered. In other words, by forming the deformation suppressing portion 750, the filter member 75 can be formed into an elongated shape, and the entire housing can be reduced in size. Further, the axial length of the column portion 75c is formed shorter than the axial length of the filter 75a by the deformation suppressing portion 750. Thereby, the pressing force by the brake fluid acting on the filter 75a can be received by the deformation suppressing portion 750, and the deformation amount of the column portion 75c is suppressed by shortening the substantial axial length of the column portion 75c. can do.

As described above, the effects listed below can be obtained in the first embodiment.
(1) A housing 31 having an oil passage formed therein, a ball member 72 (valve element) disposed in the oil passage, a seat member 71 having a seat portion 71a with which the ball member 72 abuts, and a seat member 71 A cylindrical filter member 75 having a column portion 75c, a cylindrical portion 75d, a bottom surface 75b2 (main body portion), and a filter 75a (mesh portion) fixed to the cylindrical portion, and a main body portion of the filter member 75 formed at both ends. A column 75c that connects the portion 75d and the bottom surface 75b2 (base), the cylindrical portion 75d and the bottom surface 75b2, and forms an opening edge along the axial direction among the opening edges of the filter 75a, and the deformation of the column 75c is suppressed. And a deformation suppression unit 750 (deformation suppression means).
Therefore, the strength of the filter member 75 can be ensured, and the size of the entire apparatus can be reduced by setting the filter member 75 long in the axial direction.

  (2) The deformation suppressing portion 750 is formed by making the axial length of the column portion 75c shorter than the axial length of the filter 75a. Thereby, the pressing force by the brake fluid acting on the filter 75a can be received by the deformation suppressing portion 750, and the deformation amount of the column portion 75c is suppressed by shortening the substantial axial length of the column portion 75c. can do.

  (3) The column portion 75c is formed at an even number of locations in the circumferential direction substantially evenly, and the column portion 75c at a position facing the diameter direction of the column portion 75c is connected to the bottom surface 75b2 (one of the base portions). A deformation suppressing part 750 (corresponding to a reinforcing part) was provided. That is, in the first embodiment, four column portions 75c are formed approximately evenly in the circumferential direction, and the deformation suppressing portions 750 are formed in the cross direction so that the column portions 75c face each other. Therefore, since the shear force does not act on the deformation suppressing portion 750 and it is dealt with by compressive deformation, the strength and durability can be improved.

[Example 2]
Next, Example 2 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 8 is a perspective view of the filter member of the second embodiment. In the first embodiment, the diameter of the cylindrical portion 75bc is slightly smaller than the inner peripheral diameter of the pressure regulating valve return spring 73, and is larger than the region where the deformation suppressing portion 750 intersects. On the other hand, the second embodiment is different in that the diameter of the cylindrical portion 75bc1 is formed in a region where the deformation suppressing portion 750 intersects. Thus, the moldability at the time of resin molding using a mold can be improved by making the cylindrical portion 75bc1 have a relatively small diameter and ensuring the distance from the column portion 75c.

[Example 3]
Next, Example 3 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 9 is a perspective view of the filter member of the third embodiment. In the first embodiment, the stopper portion 75b is formed. In contrast, the third embodiment is different in that the stopper portion 75b is not formed. Thereby, the structure of the filter member 75 can be simplified and a moldability can be improved.

[Example 4]
Next, Example 4 will be described. Since the basic configuration is the same as that of the second embodiment, only different points will be described. FIG. 10 is a perspective view of the filter member according to the fourth embodiment. In the second embodiment, a member formed in a cross shape is provided as the deformation suppressing portion 750. On the other hand, in Example 4, it has the column-shaped deformation | transformation suppression part 7501 which is larger diameter than cylinder part 75bc1, and is the same diameter as the internal diameter side of the pillar part 75c. Since the rigidity in the deformation suppressing portion is higher than those in the first and second embodiments, the durability can be further improved.

[Example 5]
Next, Example 5 will be described. Since the basic configuration is the same as that of the fourth embodiment, only different points will be described. FIG. 11 is a perspective view of the filter member according to the fifth embodiment. In Example 4, the stopper part 75b was provided on the upper part of the columnar deformation suppressing part 7501. In contrast, the fifth embodiment is different in that the stopper portion is not provided. Thereby, the structure of the filter member 75 can be simplified and a moldability can be improved.

[Example 6]
Next, Example 6 will be described. Since the basic configuration is the same as that of the third embodiment, only different points will be described. FIG. 12 is a perspective view of the filter member according to the sixth embodiment, and FIG. 13 is an enlarged cross-sectional view illustrating the configuration of the pressure regulating valve according to the sixth embodiment. In Example 3, only the deformation suppressing unit 750 was provided as the deformation suppressing means. On the other hand, in Example 6, it has the metal ring members 800 which each connect the pillar part 75c. The ring member 800 is arranged on the outer diameter side of the radial position where the filter 75a of the column portion 75c is attached. In other words, a radial gap is formed between the filter 75a and the ring member 800. Thereby, the intensity | strength of the pillar part 75c is securable, without inhibiting the brake fluid distribution surface of the filter 75a. Note that the axial position of the ring member 800 may be approximately the center of the column portion 75c, or may be approximately the center from the spring holding surface 75b1 of the deformation suppressing portion 750 to the joint portion between the column portion 75c and the cylindrical portion 75d.

  (4) The deformation suppressing means is a ring member 800 that connects adjacent column portions 75c, and includes a radial gap between the ring member 800 and the filter 75a. Therefore, even if the filter 75a and the column part 75c are pressed by the brake fluid from the outside in the radial direction, the acting force is prevented from being deformed by the ring member 800, so that sufficient strength can be ensured. Further, since a gap is provided between the filter 75a and the ring member 800, a stable brake fluid flow can be ensured without hindering the flow of the brake fluid.

[Example 7]
Next, Example 7 will be described. Since the basic configuration is the same as that of the sixth embodiment, only different points will be described. FIG. 14 is a perspective view of the filter member according to the seventh embodiment. In the sixth embodiment, the deformation suppressing portion 750 is formed together with the ring member 800. In contrast, the seventh embodiment is different in that the deformation suppressing unit 750 is not provided. That is, as long as the deformation of the column part 75c can be suppressed only by the ring member 800, there is no problem even if the deformation suppressing part 750 is not particularly provided. Thereby, the flow path resistance of the brake fluid can be reduced.

[Example 8]
Next, Example 8 will be described. Since the basic configuration is the same as that of the seventh embodiment, only different points will be described. FIG. 15 is an enlarged cross-sectional view illustrating the configuration of the pressure regulating valve according to the eighth embodiment. In the seventh embodiment, the ring member 800 is provided as a deformation suppressing unit. On the other hand, the eighth embodiment is different in that a metal reinforcing member 900 is provided as a deformation suppressing means in the column portion 75c. When the filter member 75 is resin-molded, the strength of the column portion 75c can be secured by integrally molding the filter 75a and the reinforcing member 900. In the case of the eighth embodiment, there is no obstacle on the brake fluid flow surface of the filter 75a, and there is no protrusion such as a deformation suppressing portion inside the filter member 75. The flow path resistance of the liquid can be reduced.

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 adjusting valve return spring 74 Rod 74a Rod tip 74b Rod intermediate part 75 Filter member 75a Filter (mesh part)
750 Deformation suppression unit (deformation suppression means)
800 Ring member (deformation suppression means)
900 Reinforcing member (deformation suppressing means)

Claims (3)

A housing having an oil passage formed therein;
A valve body disposed in the oil passage;
A seat member provided with a seat portion against which the valve body abuts,
A cylindrical filter member fixed to the sheet member and provided with a main body portion and a mesh portion;
The main body of the filter member has a base formed at both ends, a column that connects between the bases and forms an opening edge along the axial direction among the opening edges of the mesh part,
Deformation suppressing means for suppressing deformation of the column part;
A brake device comprising: The brake device according to claim 1, wherein
The said deformation | transformation suppression means forms the axial direction length of the said column part shorter than the axial direction length of the said mesh part, The brake device characterized by the above-mentioned. The brake device according to claim 1 or 2,
The columnar portion is formed at an even number of locations substantially evenly in the circumferential direction, and one of the base portions is provided with a reinforcing portion that connects the columnar portion at a position facing the diameter direction of the columnar portion. Brake device characterized.

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