JP6308587B2 - Brake device - Google Patents

Description

  The present invention relates to a brake device mounted on a vehicle.

  2. Description of the Related Art Conventionally, a brake device in which a plurality of oil passages open at the bottom of a reservoir accommodation hole in which a piston strokes is known (for example, Patent Document 1).

JP 2012-131436 A

  However, in the conventional apparatus, there is a possibility that connection between a plurality of oil passages may be hindered. An object of the present invention is to provide a brake device that can maintain a state in which a plurality of oil passages are connected to each other.

In order to achieve the above object, in the brake device according to an embodiment of the present invention, preferably, a connecting oil passage that connects countersinks formed at the opening edges of the plurality of oil passages is formed facing the crown surface of the piston. did.

  Therefore, it is possible to maintain a state where a plurality of oil passages are connected to each other.

The oil-path structure of the brake device of Example 1 is shown. The cross section of the pressure regulation valve and reservoir | reserver of Example 1 is shown. FIG. 3 is a schematic perspective view of a reservoir accommodation hole and the like according to the first embodiment. FIG. 3 is a schematic front view of a reservoir accommodation hole and the like according to the first embodiment. FIG. 3 is a schematic side view of a reservoir accommodation hole and the like according to the first embodiment. FIG. 6 is a schematic perspective view of a reservoir accommodation hole and the like according to Embodiment 2. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like according to the second embodiment. FIG. 10 is a schematic side view of a reservoir accommodation hole and the like according to the second embodiment. FIG. 10 is a schematic perspective view of a reservoir accommodation hole and the like of Example 3. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like of Example 3. FIG. 10 is a schematic side view of a reservoir accommodation hole and the like according to the third embodiment. FIG. 10 is a schematic perspective view of a reservoir accommodation hole and the like of Example 4. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like of Example 4. FIG. 10 is a schematic side view of a reservoir accommodation hole and the like of Example 4. FIG. 10 is a schematic perspective view of a reservoir accommodation hole and the like according to a fifth embodiment. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like according to a fifth embodiment. FIG. 10 is a schematic side view of a reservoir accommodation hole and the like of Example 5. FIG. 10 is a schematic perspective view of a reservoir accommodation hole and the like of Example 6. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like of Example 6. It is typical side views, such as a reservoir accommodation hole of Example 6. FIG. 10 is a schematic perspective view of a reservoir accommodation hole and the like of Example 7. FIG. 10 is a schematic front view of a reservoir accommodation hole and the like of Example 7. FIG. 10 is a schematic side view of a reservoir accommodation hole and the like of Example 7. It is a front view of the channel member of Example 7. The bottom part of the reservoir | reserver accommodation hole of the modification of Example 4 is shown. The bottom part of the reservoir | reserver accommodation hole of the modification of Example 5 is shown.

  Hereinafter, the form which implement | achieves the brake device of this invention is demonstrated based on drawing.

[Example 1]
First, the configuration of the brake device 1 of the first embodiment (hereinafter simply referred to as the device 1) will be described. FIG. 1 shows an oil passage configuration of the apparatus 1. The device 1 is applied to a hydraulic brake system for a vehicle. The hydraulic brake system includes a device 1, a brake pedal BP, a booster BS, a master cylinder M / C, a wheel cylinder W / C, and a brake controller CU. The brake pedal BP is a member to which a brake operation by the driver's foot is input. The booster BS is a brake booster that amplifies the brake operation force (the force to step on the brake pedal BP) and transmits it to the master cylinder M / C. The master cylinder M / C is operated by a force applied from the booster BS, and generates a hydraulic pressure proportional to this force, that is, a hydraulic pressure (master cylinder pressure) corresponding to the state of the brake operation. The master cylinder M / C is integrally provided with a reservoir tank RES. The reservoir tank RES is a fluid source (master reservoir) that replenishes the working fluid (brake fluid) to the master cylinder M / C while storing excess brake fluid. The master cylinder M / C is a so-called tandem type and has a first hydraulic chamber (primary chamber) and a second hydraulic chamber (secondary chamber).

  The master cylinder M / C is a wheel cylinder W / provided on each wheel FL, FR, RL, RR of the vehicle via two independent (primary P system, secondary S system) brake pipes 10P, 10S. Connected to C. The wheel cylinder W / C applies hydraulic braking force to the wheels FL to RR by generating a hydraulic pressure (foil cylinder pressure) in response to the supply of the brake fluid. The device 1 is a brake hydraulic pressure control device provided so as to be able to control the hydraulic braking force of each wheel FL, FR, RL, RR independently of the driver's brake operation. Hereinafter, in order to distinguish between the configuration provided for the P system and the configuration provided for the S system, the suffixes P and S are added to the end of each symbol. About the structure provided corresponding to each wheel FL, FR, RL, RR, the symbol of FL, FR, RL, RR is attached and distinguished as needed. The brake pipes 10P and 10S have a diagonal type so-called X pipe structure. The P system pipe 10P exiting from the primary chamber of the master cylinder M / C branches to the brake pipes 10a and 10d and is connected to the wheel cylinders W / C of the front left wheel FL and the rear right wheel RR, respectively. The S system piping 10S exiting from the secondary chamber of the master cylinder M / C branches to the brake piping 10b and 10c and is connected to the wheel cylinders W / C of the front right wheel FR and the rear left wheel RL, respectively. Note that so-called front and rear piping, that is, an H-shaped piping structure divided into two systems of front wheels FL and FR and rear wheels RL and RR may be employed.

  The device 1 is a hydraulic unit provided between the master cylinder M / C and the wheel cylinder W / C. The device 1 is connected to the master cylinder M / C via the brake pipes 10P and 10S, and is connected to the wheel cylinder W / C via the brake pipes 10FL to 10RR. The device 1 has a substantially rectangular parallelepiped housing 2 made of an aluminum-based metal material. Inside the housing 2, a plurality of oil passages (liquid passages) 11 are formed as hydraulic circuits. The oil passage 11 or the like is a passage through which the brake fluid moves (circulates), and is provided corresponding to the P and S systems. The device 1 includes a pump P as a hydraulic pressure generation source and a plurality of electromagnetic valves (control valves) 50 as hydraulic devices (actuators) for generating a control hydraulic pressure to be supplied to each wheel cylinder W / C. doing. The electromagnetic valve 50 or the like opens and closes in response to a control signal, and controls the flow of brake fluid by switching the communication state of the oil passage 11 and the like. The device 1 also includes a hydraulic pressure sensor 6 that detects the master cylinder pressure. When the brake pedal BP is depressed, the master cylinder M / C supplies brake fluid (master cylinder pressure) to the device 1 through the brake pipes 10P and 10S. The apparatus 1 is provided so that the master cylinder pressure or the control hydraulic pressure can be individually supplied to each wheel cylinder W / C via the brake pipes 10FL to 10RR. The device 1 is controlled by the brake controller CU so that the hydraulic pressure (wheel cylinder pressure) of each wheel cylinder W / C can be controlled to a value lower than the master cylinder pressure, or to a value higher than the master cylinder pressure. It can be controlled and can be kept substantially constant.

  The brake controller CU receives a detection value sent from the hydraulic pressure sensor 6 and information (wheel speed, steering angle, etc.) related to the running state sent from the vehicle side (other controller etc.) via the communication line. The brake controller CU performs information processing according to a built-in program based on these various types of information. Further, according to the processing result, a control command is output to each actuator of the device 1 to control them. Specifically, the brake controller CU controls the opening / closing operation of the electromagnetic valve 50 and the like, and the rotation speed of the motor M that drives the pump P (that is, the discharge amount of the pump P). By controlling the wheel cylinder pressure of each wheel FL to RR, anti-lock brake control (hereinafter referred to as ABS control) for Anti-lock Brake System that suppresses slip (lock tendency) of wheels FL to RR due to braking is suppressed. .), Brake control for vehicle dynamics control (vehicle behavior stabilization control such as skidding prevention) (hereinafter referred to as VDC control), and for assisting the driver's brake operation force in an emergency. Realizes Brake Assist control. The brake controller CU calculates the required hydraulic pressure for each control described above, and performs hydraulic pressure control of each wheel cylinder W / C according to the calculated required hydraulic pressure. For example, in ABS control, the speed of each wheel FL-RR is taken in as vehicle information. When it is determined that a wheel has a tendency to lock, that is, when it is determined that the slip amount of the wheel (the deviation of the speed of the wheel from the pseudo vehicle speed) is excessive, the wheel cylinder pressure of the wheel is controlled, The slip amount is set to an appropriate predetermined value. In the VDC control, for example, the wheel cylinder pressure of each wheel FL to RR is controlled so as to realize a desired vehicle motion state based on the detected vehicle motion state amount (lateral acceleration or the like).

  Hereinafter, the configuration of the hydraulic circuit of the apparatus 1 will be described with reference to FIG. First, the P-system hydraulic circuit 2P will be described. The supply oil passage 11P communicates with the primary chamber of the master cylinder M / C by being connected to the brake pipe 10P via a connection port 20P formed in the surface of the housing 2. Further, the supply oil passage 11P communicates with the wheel cylinders W / C FL and W / C RR by connecting to the brake pipes 10FL and 10RR via connection ports 20FL and 20RR formed in the surface of the housing 2. The supply oil passage 11P is provided with a shutoff valve (cut valve) 50P for switching between communication and shutoff. In the supply oil passage 11P, a hydraulic pressure sensor 6 is provided between the connection port 20P and the shutoff valve 50P. The hydraulic pressure sensor 6 detects the hydraulic pressure of this part, that is, the master cylinder pressure, and inputs the detected value to the brake controller CU. The supply oil passage 11P branches to the supply oil passages 11FL and 11RR on the wheel cylinder W / C side with respect to the shutoff valve 50P. The supply oil passage 11FL communicates with the wheel cylinder W / C of the front left wheel FL, and the supply oil passage 11RR communicates with the wheel cylinder W / C of the rear right wheel RR. The supply oil passages 11FL and 11RR are respectively provided with pressure increasing valves 51FL and 51RR for switching between communication and cutoff.

  A check valve 55P is provided on the bypass oil passage 15P provided in parallel with the shutoff valve 50P. The check valve 55P only allows the brake fluid to flow from the master cylinder M / C side to the wheel cylinder W / C side. When the check valve 55P becomes “master cylinder pressure> (pressure on the wheel cylinder W / C side or pressure on the discharge side of the pump PP)”, the master cylinder pressure is set to the discharge side of the pump PP and the pressure increasing valves 51FL, 51RR. Open operation to tell to the side. Check valves 56FL and 56RR are provided on bypass oil passages 16FL and 16RR provided in parallel with the pressure increasing valves 51FL and 51RR, respectively. The check valves 56FL and 56RR allow only the brake fluid to flow from the wheel cylinder W / C side to the master cylinder M / C side. Check valves 56FL and 56RR should release the wheel cylinder pressure to the master cylinder M / C side when “wheel cylinder pressure> (pressure on the master cylinder M / C side or pressure on the discharge side of the pump PP)” Open operation.

  A pump PP is connected to the supply oil passage 11P through a discharge oil passage 12P. The discharge oil passage 12P connects between the shutoff valve 50P and the pressure increasing valves 51FL and 51RR in the supply oil passage 11P and the discharge portion of the pump PP. The discharge oil passage 12P is provided with a check valve 54 as a discharge valve of the pump PP. The check valve 54 allows only the brake fluid to flow from the discharge part of the pump PP to the supply oil passage 11P. Further, a pump PP is connected to the supply oil passage 11P through a suction oil passage 13P. The suction oil passage 13P connects between the connection port 20P and the shutoff valve 50P in the supply oil passage 11P and the suction portion of the pump PP. An internal reservoir 3P is provided in the suction oil passage 13P. The internal reservoir 3P is a reservoir tank that is built in the apparatus 1 and is provided so as to store a predetermined amount of brake fluid. The internal reservoir 3P (hereinafter simply referred to as “reservoir 3P”) is a pressure regulating reservoir provided so that the hydraulic pressure can be adjusted (regulated pressure), and includes a pressure regulating valve 4P that regulates the amount of brake fluid flowing into the reservoir 3P. Yes. The pressure regulating valve 4P is provided between the connection portion of the suction oil passage 13P with the supply oil passage 11P and the reservoir 3P. Hereinafter, the portion of the suction oil passage 13P connected to the supply oil passage 11P rather than the pressure regulating valve 4P (the side communicating with the primary chamber of the master cylinder M / C) will be referred to as a suction oil passage 13aP. The side of the pump PP from the reservoir 3P (the side connected to the suction part) is referred to as a suction oil passage 13bP.

  The intake oil passage 13bP is provided with a check valve 53P as an intake valve of the pump PP. The check valve 53P only allows the brake fluid to flow from the reservoir 3P to the suction portion of the pump PP. The pump P is a hydraulic pressure source that can pressurize the hydraulic pressure of the wheel cylinder W / C using the brake fluid of the master cylinder M / C (reservoir tank RES), and is driven to rotate by the motor M to suck in brake fluid.・ Discharge. In this embodiment, a reciprocating pump, specifically, a piston pump (plunger pump) is employed as the pump P. The type of the pump P is not limited to the reciprocating type, and may be a rotary type such as a gear pump. The pump PP is supplied with brake fluid from the primary chamber of the master cylinder M / C (suctions brake fluid from the primary chamber), and supplies brake fluid to the wheel cylinder W / C via the discharge oil passage 12P and the supply oil passage 11P. Supply.

  The supply oil passages 11FL and 11RR are connected to the suction oil passage 13P through the decompression oil passages 14FL and 14RR, respectively. Specifically, the pressure reducing oil passages 14FL and 14RR branch from between the pressure increasing valves 51FL and 51RR and the wheel cylinders W / C FL and W / C RR in the supply oil passages 11FL and 11RR, respectively. The decompression oil passages 14FL and 14RR are respectively provided with decompression valves 52FL and 52RR for switching between communication and blocking. The decompression oil passages 14FL and 14RR merge to form a decompression oil passage 14P. The decompression oil passage 14P is connected between the check valve 53P and the reservoir 3P in the suction oil passage 13bP, and merges therewith (unified as the suction oil passage 13bP).

  Next, the S-system hydraulic circuit 2S will be described. The supply oil passage 11S communicates with the secondary chamber of the master cylinder M / C and the wheel cylinder W / C by connecting to the brake pipe 10S. The hydraulic pressure sensor 6 is not provided in the supply oil passage 11S. Of the oil passages branched from the supply oil passage 11S, the supply oil passage 11FR is connected to the wheel cylinder W / C of the front right wheel FR, and the supply oil passage 11RL is connected to the wheel cylinder W / C of the rear left wheel RL. . Other configurations are the same as the P system.

  One motor M is provided and drives the pumps P of both systems simultaneously. The rotational speed of the motor M is controlled by a command voltage from the brake controller CU. Each of the solenoid valves 50 to 52 is a known solenoid valve that opens and closes by generating electromagnetic force when a drive current is applied to the solenoid (coil) and reciprocating the valve body (plunger). The shut-off valve 50 and the pressure increasing valve 51 are normally open type, that is, a normally open type that opens in a non-energized state, and the pressure reducing valve 52 is normally closed type, that is, a normally closed type that closes in a non-energized state. The shut-off valve 50 and the pressure increasing valve 51 are proportional control valves in which the opening degree of the valve is adjusted according to the current supplied to the solenoid. The pressure reducing valve 52 is an on / off valve whose opening and closing is controlled in a binary manner.

  The housing 2 accommodates a plurality of oil passages 11 and the like, connection ports 20, a valve accommodation hole for accommodating a valve body such as each electromagnetic valve 50, a pump accommodation hole for accommodating a pump P unit, and a reservoir 3. Holes such as the reservoir accommodation hole 22 are formed. These holes and the like are formed in each surface from the outside of the housing 2 using, for example, a milling machine. The vertical direction is the vertical direction when the apparatus 1 is installed in the vehicle. Among the four side surfaces excluding the upper and lower surfaces of the housing 2, the two predetermined opposite side surfaces are defined as a front surface and a rear surface. The other two opposite sides are the left side and the right side. A motor M is attached to the front side of the housing 2, and a solenoid valve, a hydraulic pressure sensor 6, and a brake controller CU (unit in which a substrate is accommodated in a case) are attached to the rear side. A power supply hole is formed in the housing 2 so as to penetrate the front surface and the rear surface. The brake controller CU and the motor M are connected by inserting the electrode of the motor M into the power supply hole. The shafts of the pistons of the pumps PP and PS housed in the pump housing holes extend toward the left and right side surfaces of the housing 2 (in the left and right direction). The discharge part of the pump P is located on the side close to the left and right side surfaces of the housing 2, and the suction part of the pump P is located on the side far from the left and right side surfaces (the intermediate side in the left and right direction of the housing 2).

  FIG. 2 shows a cross section of the piston 31 and the like and the housing 2 constituting the P-system reservoir 3P taken along a plane including the axis of the piston 31 and parallel to the front and rear surfaces of the housing 2. In the drawing, the upper side is the upper surface side of the housing 2 and the left side is the left side of the housing 2. The P-system reservoir 3 </ b> P is disposed on the left side surface of the housing 2. The S system reservoir 3S is arranged on the right side surface side of the housing 2 symmetrically with respect to the surface extending parallel to the left and right side surfaces at a substantially intermediate position in the left and right direction of the housing 2 with respect to the P system reservoir 3P. Except for other points, the configuration of the S-system reservoir 3S is the same as that of the P-system reservoir. Therefore, the reference numerals will be described without adding S and P in particular. The housing 2 includes a reservoir accommodation hole 22 inside. The reservoir accommodation hole 22 is formed by an inner wall surface of a recess formed upward from the lower surface 21 of the housing 2. The reservoir accommodation hole 22 has a bottom portion 22a on the upper side and has a substantially cylindrical shape with an opening on the lower side. A central axis of the reservoir accommodation hole 22 extending in the vertical direction is denoted by A. Hereinafter, a direction in which each central axis extends is referred to as an axial direction.

  FIG. 3 is a perspective view schematically showing the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b. 4 is a schematic front view of the space in FIG. 3 as viewed from the upper side in the axial direction. FIG. 5 is a schematic side view of the space shown in FIG. 3 as seen from the direction perpendicular to the axis as in FIG. In addition, illustration of the intake oil path 13a is abbreviate | omitted in FIGS. The bottom 22a is substantially circular when viewed from the axial direction. One counterbore 23 is formed on the bottom 22a. The counterbore 23 is a bottomed, relatively shallow concave portion drilled upward from the bottom 22a. The counterbore 23 is a cylindrical portion (small-diameter cylindrical portion) slightly smaller in diameter than the reservoir accommodation hole 22, has a bottom portion 23 a on the upper side, and opens on the lower side. The central axis B of the counterbore 23 is substantially coaxial with the central axis A of the reservoir accommodation hole 22 (bottom portion 22a). The counterbore 23 is substantially circular when viewed from the axial direction. A retainer holding surface 22b is formed on the inner wall constituting the opening of the reservoir accommodation hole 22. This inner wall has a shape with a step in the axial direction.

  The housing 2 includes a pressure regulating valve accommodation hole 24 therein. The pressure regulating valve accommodation hole 24 is formed by an inner wall surface of a concave portion drilled upward from the bottom 23 a of the counterbore 23. The pressure regulating valve accommodation hole 24 has a bottom portion 24a on the upper side, and has a substantially cylindrical shape with an opening on the lower side. The central axis of the pressure regulating valve housing hole 24 extending in the vertical direction is C. The central axis C is substantially parallel to the central axis A of the reservoir housing hole 22. The central axis C is located at a position offset radially outward of the reservoir housing hole 22 (on the side away from the central axis A), specifically, on the left side in the figure (on the side close to the left side of the housing 2) with respect to the central axis A. is there. The pressure regulating valve accommodating holes 24P and 24S (central axis C) of both the P and S systems are arranged offset from the central axis A of the respective reservoir accommodating holes 22P and 22S so as to be separated from each other.

  A suction oil passage 13a opens at the bottom 24a of the pressure regulating valve housing hole 24. Hereinafter, a portion of the suction oil passage 13a that is connected to the pressure regulating valve accommodation hole 24 is referred to as a first oil passage 13a. The central axis of the first oil passage 13 a is substantially coaxial with the central axis C of the pressure regulating valve accommodation hole 24. The pressure regulating valve accommodation hole 24 is an oil passage (large diameter oil passage) slightly larger in diameter than the first oil passage 13a, and constitutes a part of the first oil passage 13a. In other words, the portion connected to the counterbore 23 in the suction oil passage (first oil passage) 13a is configured as a large-diameter oil passage (pressure regulating valve accommodation hole 24). The pressure regulating valve accommodation hole 24 as the first oil passage 13 a opens at the bottom 23 a of the counterbore 23. The said opening part of the pressure regulation valve accommodation hole 24 is substantially circular seeing from an axial direction. A seat member holding surface 24b is formed on the inner wall constituting the opening of the pressure regulating valve housing hole 24. This inner wall has a shape with a step in the axial direction. The pressure regulating valve housing hole 24 has a shape in which large, medium, and small diameter cylindrical portions 241, 242, and 243 are stacked substantially coaxially from the bottom to the top in this order, and has a plurality of step portions. A large-diameter cylindrical portion 241 of the pressure regulating valve accommodation hole 24 opens at the bottom 23 a of the counterbore 23.

  In addition, a suction oil passage 13b opens in the bottom 23a of the counterbore 23. Hereinafter, a portion connected to the counterbore 23 in the suction oil passage 13b is referred to as a second oil passage 13b. The central axis D of the second oil passage 13b is substantially parallel to the central axis A of the reservoir housing hole 22. The diameter of the opening of the second oil passage 13b is smaller than the diameter of the opening of the pressure regulating valve housing hole 24 (large diameter cylindrical portion 241). The central axis D is located at a position offset radially outward of the reservoir housing hole 22, specifically, on the right side in the drawing (the side away from the left side surface of the housing 2) with respect to the central axis A. The second oil passages 13bP and 13bS (central axis D) of both the P and S systems are arranged offset from the central axis A of the respective reservoir accommodation holes 22P and 22S so as to approach each other. The counterbore 23 includes the opening of the first oil passage 13a and the opening of the second oil passage 13b. The first oil passage 13 a is connected to the supply oil passage 11 and is connected to the counterbore 23, and opens to the bottom 22 a side of the reservoir accommodation hole 22. The second oil passage 13b is connected to the suction portion of the pump P and connected to the counterbore 23, and opens to the bottom portion 22a side of the reservoir accommodation hole 22. Therefore, the pump P can suck the brake fluid in the reservoir accommodation hole 22 or from the master cylinder M / C.

  A stopper 22d is provided at the bottom 22a of the reservoir housing hole 22. The stopper 22d is configured by a portion of the bottom 22a of the reservoir accommodation hole 22 where the countersink 23 is not provided, that is, a stepped portion on the radially outer side of the reservoir accommodation hole 22 relative to the countersink 23. The stopper 22d has a contact surface 220 that contacts the contact portion 311 of the piston 31. The contact surface 220 extends annularly over the entire circumferential range surrounding the central axis A of the reservoir accommodation hole 22 and is provided so as to be continuous on the same plane.

  A piston 31 is installed in the reservoir accommodation hole 22. The piston 31 is provided so as to be able to stroke (reciprocate in the axial direction) in the reservoir accommodation hole 22 as a cylinder, and divides the interior of the reservoir accommodation hole 22 into two chambers. The piston 31 is a cylindrical shape having a disk-shaped bottom portion 31a and a cylindrical portion 31b extending in a cylindrical shape from the outer periphery of the bottom portion 31a to the one axial side, and is formed of a resin material. The diameter of the outer peripheral surface of the piston 31 is slightly smaller than the diameter of the inner peripheral surface of the reservoir accommodation hole 22. On the outer peripheral surface of the piston 31, a groove 31c that extends in an annular shape so as to surround the axis of the piston 31 is formed. An annular seal member 32 made of an elastic body such as rubber is installed in the groove 31c. The seal member 32 is an O-ring, and the inner diameter side is in contact with the bottom of the groove 31c, the outer diameter side is in contact with the inner peripheral surface of the reservoir accommodation hole 22, and is installed in a state where it is crushed in the radial direction of the reservoir accommodation hole 22. .

  The surface on the other side in the axial direction of the bottom 31 a constitutes a piston crown surface 310 as the upper surface of the piston 31. The piston crown surface 310 faces the bottom 22 a of the reservoir housing hole 22 and the opening of the counterbore 23. A contact portion 311 is provided on the radially outer side of the piston crown surface 310. The contact portion 311 is a planar portion of the piston crown surface 310 that is opposed to the contact surface 220 of the stopper 22d of the reservoir accommodation hole 22 in the axial direction and can contact the stopper 22d (contact surface 220). The contact portion 311 extends annularly over the entire circumferential range surrounding the axis of the piston 31, and is provided so as to be continuous on the same plane. A convex portion 312 that surrounds the axis of the piston 31 and extends in the circumferential direction is provided at a substantially intermediate position in the radius of the piston crown surface 310. A concave portion 313 having the convex portion 312 as an outer peripheral wall is provided on the inner side in the radial direction from the convex portion 312 on the piston crown surface 310. The bottom surface of the recess 313 is substantially flush with the contact portion 311.

  The cylindrical portion 31 b of the piston 31 faces the opening of the reservoir accommodation hole 22. A cylindrical portion 31d having a smaller diameter than the cylindrical portion 31b is provided on the inner peripheral side of the cylindrical portion 31b. The cylindrical portion 31d extends substantially coaxially with the cylindrical portion 31b from the surface on one axial side of the bottom portion 31a. An annular recess 314 is formed between the inner periphery of the cylindrical portion 31b and the outer periphery of the cylindrical portion 31d. The annular bottom surface 315 of the recess 314 is disposed so as to substantially overlap the annular projection 312 in the axial direction of the piston 31. One end of the coil spring 33 is accommodated and held in the recess 314, and one end of the coil spring 33 abuts on the bottom surface 315 of the recess 314 (the bottom 31a of the piston 31). A bottomed cylindrical retainer member 34 is installed at the opening of the reservoir housing hole 22. The retainer member 34 has a flange portion 34a, a cylindrical portion 34b, and a bottom portion 34c. The other end side of the coil spring 33 is accommodated and held in the cylindrical portion 34b. The bottom part 34c closes one axial side of the cylindrical part 34b. The other end of the coil spring 33 is in contact with the bottom 34c. The flange portion 34a has a ring shape extending radially outward from the opening end on the other axial side of the cylindrical portion 34b, and is sandwiched between the retainer holding surface 22b and the caulking fixing portion 22c on the inner wall of the reservoir housing hole 22. . The bottom 34c protrudes slightly below the lower surface 21 of the housing 2. The coil spring 33 is installed in a state of being compressed between the retainer member 34 and the piston 31, and constantly urges the piston 31 toward the bottom 22 a of the reservoir accommodation hole 22. An air hole 340 is formed substantially at the center of the bottom 34c. Thereby, atmospheric pressure always acts below the piston 31.

  The upper space (excluding the counterbore 23) in the reservoir accommodation hole 22 defined by the piston 31 is a reservoir chamber 30a in which brake fluid can be stored. Brake fluid flows into the reservoir chamber 30a through the counterbore 23 from the first oil passage 13a (pressure regulating valve housing hole 24) as an inflow passage. The reservoir chamber 30a stores the inflow brake fluid and supplies the brake fluid to the second oil passage 13b as an outflow passage through the counterbore 23. A lower space in the reservoir accommodation hole 22 defined by the piston 31 becomes a back pressure chamber 30b opened to atmospheric pressure. Specifically, the reservoir chamber 30a and the back pressure chamber 30b are defined by the seal member 32 installed on the outer periphery of the piston 31. The seal member 32 is liquid-tightly partitioned with the reservoir chamber 30a above and the back pressure chamber 30b below. Thereby, leakage of the brake fluid from the reservoir chamber 30a to the back pressure chamber 30b (external) is suppressed. The piston 31 strokes according to the amount of brake fluid in the reservoir accommodation hole 22 (reservoir chamber 30a). The reservoir 3 stores an amount of brake fluid corresponding to the stroke of the piston 31.

  When the piston 31 is at a predetermined stroke position above (close to the bottom portion 22 a) in the reservoir accommodation hole 22, the piston crown surface 310 contacts the stopper 22 d of the reservoir accommodation hole 22. The stopper 22d is in contact with the piston crown surface 310, thereby restricting the piston 31 to the predetermined stroke position. By restricting the piston 31 from being displaced upward, the predetermined stroke position becomes the top dead center position of the piston 31. As shown in FIG. 2, when the piston 31 is located at the top dead center, the amount of brake fluid in the reservoir chamber 30a is minimum. A predetermined axial clearance exists between the bottom 23a of the counterbore 23 and the piston crown surface 310 at the top dead center. The space near the opening of the first oil passage 13a (the through hole 450 of the rod support member 45) in the axial gap constitutes a part of the first oil passage 13a. This space formed in the vicinity of the opening of the first oil passage 13a by the counterbore 23 is hereinafter referred to as a first space 131. A space near the opening of the second oil passage 13b in the axial gap constitutes a part of the second oil passage 13b. This space formed near the opening of the second oil passage 13b by the counterbore 23 is hereinafter referred to as a second space 132. Spaces other than the first and second spaces 131 and 132 in the axial gap constitute an oil passage that connects the first and second spaces 131 and 132 to each other. This is formed facing the piston crown surface 310 by the counterbore 23 and connects the first space 131 (opening portion of the first oil passage 13a) and the second space 132 (opening portion of the second oil passage 13b). Hereinafter, the space is referred to as a connection oil passage 133.

  A unit of the pressure regulating valve 4 is fixedly installed in the pressure regulating valve accommodation hole 24. This unit includes a filter member 41, a seat member 42, a valve body 43, and a return spring 44. The filter member 41 is formed in a substantially cup shape with resin. A plurality of columnar portions 41b are arranged in the circumferential direction on the outer peripheral side of one surface of the disc-shaped bottom portion 41a of the filter member 41. A mesh-like filter 410 is attached so as to cover a hollow portion (window portion) sandwiched between adjacent columnar portions 41b. A valve body 43 and a return spring 44 are held inside the filter member 41. One end of the return spring 44 is held on the one side surface of the bottom portion 41a (the inner diameter side surrounded by the plurality of columnar portions 41b). The filter member 41 constitutes a part of the first oil passage 13a, and removes impurities in the brake fluid flowing from the first oil passage 13a toward the reservoir housing hole 22. Since the diameter of the outer peripheral surface of the filter member 41 is provided smaller than the diameter of the inner peripheral surface of the pressure regulating valve housing hole 24, a flow path is secured between both surfaces. A plurality of protrusions 41 c are formed on the other surface of the bottom 41 a of the filter member 41. The protrusion 41c is in contact with the bottom 24a of the pressure regulating valve housing hole 24 (on the outer diameter side from the opening of the first oil passage 13a) as necessary, whereby the flow path between the first oil passage 13a and the bottom 24a. Secure.

  The sheet member 42 has a shape in which a small-diameter cylindrical portion 42a, a flange portion 42b, and a large-diameter cylindrical portion 42c are stacked substantially coaxially from top to bottom in this order, and has a plurality of step portions. A small diameter hole 421 is formed in the small diameter cylindrical portion 42a so as to extend on the central axis. A portion surrounding the opening at one axial end of the small-diameter cylindrical portion 42a is formed in a mortar shape, and constitutes a valve seat (seat portion) 420. The diameter of the flange portion 42b is larger than the diameter of the large-diameter cylindrical portion 42c. A large-diameter hole 422 is formed in a part of the flange portion 42b and the large-diameter cylindrical portion 42c so as to extend on the central axis. The large diameter hole 422 is tapered in the flange portion 42b and connected to the small diameter hole 421. The opening of the filter member 41 is fitted into the outer periphery of the small diameter cylindrical portion 42a of the sheet member 42 by press fitting. The valve seat 420 faces the inner peripheral side of the filter member 41. The flange portion 42b of the sheet member 42 is held by the inner wall of the reservoir accommodation hole 22 by the sheet member holding surface 24b and the caulking fixing portion 24c. The lower end of the large-diameter portion 42 c of the seat member 42 is at the same position as the bottom surface of the counterbore 23.

  The valve body 43 is ball-shaped. The valve body 43 is installed between the other end of the return spring 44 and the valve seat 420. The return spring 44 constantly biases the valve body 43 toward the seat member 42 (valve seat 420). The elastic force of the return spring 44 is set to be weaker than the elastic force of the coil spring 33. A stepped cylindrical rod support member 45 is installed at the opening of the large-diameter hole 422. The rod support member 45 has a large-diameter cylindrical portion 45a, an annular portion 45b, and a small-diameter cylindrical portion 45c. The annular portion 45b is an annular portion connecting the large diameter cylindrical portion 45a and the small diameter cylindrical portion 45c, and a plurality of through holes 450 are provided in the circumferential direction. The rod support member 45 has a large-diameter cylindrical portion 45a fitted into the large-diameter hole 422 of the sheet member 42, an annular portion 45b closing the opening of the large-diameter hole 422, and a small-diameter cylindrical portion 45c having a large diameter. The sheet member 42 is installed so as to protrude from the hole 422. The small diameter cylindrical portion 45c is disposed inside the counterbore 23, and the tip of the small diameter cylindrical portion 45c is located above the contact surface 220 of the stopper 22d.

  The rod 46 is made of metal and is configured as a rod-like member that is separate from the piston 31. The rod 46 is one member for associating the operation of the pressure regulating valve 4 with the operation of the reservoir 3 (piston 31). The rod 46 has a small diameter portion 46a and a large diameter portion 46b. The small diameter portion 46 a has a smaller diameter than the small diameter hole 421 of the sheet member 42. The large diameter portion 46b is slightly smaller in diameter than the inner peripheral side of the small diameter cylindrical portion 45c of the rod support member 45. The axial length of the large diameter portion 46b is longer than the axial length of the small diameter cylindrical portion 45c. A stopper member 47 is fixedly installed at the step between the small diameter portion 46a and the large diameter portion 46b. The stopper member 47 is installed such that its flange-like portion 47a extends outward in the radial direction from the large-diameter portion 46b.

  The rod 46 is installed in the unit of the pressure regulating valve 4 so as to be held by the rod support member 45. The large diameter portion 46 b of the rod 46 is fitted to the inner peripheral side of the small diameter cylindrical portion 45 c of the rod support member 45. The small-diameter cylindrical portion 45c of the rod support member 45 holds the rod 46 (large-diameter portion 46b) so that axial movement is possible while restricting radial movement of the rod 46 (large-diameter portion 46b). The tip of the large-diameter portion 46b of the rod 46 protrudes from the small-diameter cylindrical portion 45c of the rod support member 45 into the counterbore 23 or the reservoir chamber 30a so as to be able to contact the piston crown surface 310 (the bottom surface of the recess 313). ing. Corresponding to the fact that the central axis C of the pressure regulating valve accommodating hole 24 is offset to the left in the figure with respect to the central axis A of the reservoir accommodating hole 22, the central axis C of the rod 46 is the central axis A (rotation) of the piston 31. It is arranged offset from the center. The tip of the small diameter portion 46a of the rod 46 is located on the valve seat 420 side of the seat member 42 (inside the small diameter hole 421 of the small diameter cylindrical portion 42a). The tip of the small diameter portion 46 a of the rod 46 is provided so as to be able to contact the valve body 43. The stopper member 47 is positioned in a space on the inner peripheral side of the sheet member 42 that is closed by the annular portion 45b of the rod support member 45. The stopper member 47 (flange-like portion 47a) abuts against the annular portion 45b of the rod support member 45 when the rod 46 moves downward by a predetermined amount, thereby restricting the downward movement of the rod 46. When viewed from the axial direction, the flange-like portion 47 a of the stopper member 47 is provided so as not to overlap the through hole 450 in the annular portion 45 b of the rod support member 45.

  “Between the inner peripheral surface of the pressure regulating valve housing hole 24 and the outer peripheral surface of the filter member 41 → the filter 410 → the inner peripheral side of the filter member 41 → the inner peripheral side of the sheet member 42 (inside the small diameter hole 421 and the large diameter hole 422 The passage of the brake fluid from the first oil passage 13a to the reservoir accommodation hole 22 (spot counterbore 23) in the order of “between the peripheral surface) and the outer peripheral surface of the rod 46 → the through hole 450 of the rod support member 45” A part of the oil passage 13a) is formed. The valve body 43 is seated on the valve seat 420 to close the passage (first oil passage 13a), and is separated from the valve seat 420 to connect the passage (first oil passage 13a).

[Action]
Next, the operation of the device 1 will be described. First, the operation of the reservoir 3 and the pressure regulating valve 4 will be described. The reservoir 3 is sent from the wheel cylinder W / C side via the pressure reducing valve 52 (pressure reducing oil passage 14) or from the master cylinder M / C side via the pressure regulating valve 4 (suction oil passage 13a). Accumulate the incoming brake fluid. The pump P sucks out the brake fluid stored in the reservoir 3 and supplies it to the supply oil passage 11 by discharging it to the discharge oil passage 12. Further, the pump P sucks brake fluid from the master cylinder M / C side through the pressure regulating valve 4 and the reservoir 3 (suction oil passage 13) and discharges the brake fluid to the discharge oil passage 12 to the supply oil passage 11. Supply. The brake fluid supplied to the supply oil passage 11 is used to pressurize the wheel cylinder pressure by being supplied to the wheel cylinder W / C via the pressure increasing valve 51, or the master cylinder M via the shut-off valve 50. Return to the / C side (primary room or secondary room). The pressure regulating valve 4 is interlocked with the piston 31 of the reservoir 3 and adjusts the amount of brake fluid flowing into the reservoir 3 from the intake oil passage 13. When pressure is applied from the master cylinder M / C side while the pump P is stopped, the pressure regulating valve 4 shuts off the communication of the suction oil passage 13 and connects the pump P via the reservoir 3 from the master cylinder M / C side. Suppresses the flow of brake fluid into the intake. On the other hand, when the pump P is operated, the suction oil passage 13 is communicated, and the inflow of the brake fluid from the master cylinder M / C side to the suction portion of the pump P via the reservoir 3 is preferentially made effective.

  During normal braking, that is, when each solenoid valve 50 or the like or the pump P is inactive, when the hydraulic pressure is generated in the master cylinder M / C, the pressure regulating valve 4 is closed and the master cylinder M / C and the reservoir 3 are closed. To block between. Brake fluid is supplied from the master cylinder M / C to each wheel cylinder W / C via the supply oil passage 11. At the time of ABS operation, as the initial operation, the pressure increasing valve 51 is controlled in the valve closing direction and the pressure reducing valve 52 is controlled in the valve opening direction. Then, the brake fluid in the wheel cylinder W / C flows into the reservoir 3 through the decompression oil passage 14. At this time, the brake fluid that has flowed into the reservoir 3 by the operation of the pump P is pumped up through the suction fluid passage 13 and is returned to the master cylinder M / C. During VDC operation, the shutoff valve 50 is controlled in the valve closing direction, the pressure increasing valve 51 corresponding to the desired wheel FL, FR, RL, RR is controlled in the valve opening direction, and the pump P is operated. At this time, even if the pressure regulating valve 4 is closed, the pressure inside the reservoir 3 is reduced by pumping up the pump P, so that the pressure regulating valve 4 operates in the valve opening direction. As a result, the pump P sucks and discharges the brake fluid from the master cylinder M / C, thereby supplying the brake fluid to the wheel cylinder W / C of the wheel.

  This will be specifically described below. When the pump P is inactive and no brake fluid is supplied from the master cylinder M / C, the piston 31 of the reservoir 3 is urged by the coil spring 33 and returns to the valve element 43 of the pressure regulating valve 4 via the rod 46. Push up against the force of the spring 44. When the piston 31 is displaced by a predetermined amount or more toward the bottom 22a side of the reservoir accommodation hole 22 (in the direction of decreasing the volume of the reservoir chamber 30a), the rod 46 lifts the valve body 43 from the valve seat 420 to adjust the pressure regulating valve. 4 is opened. At this time, the suction oil passage 13 communicates with the suction side of the pump P via the reservoir 3. When the pump P is inactive and no brake fluid is supplied from the master cylinder M / C, the piston 31 is at the top dead center position, and the valve body 43 is separated from the valve seat 420 by a predetermined amount. On the other hand, when a predetermined amount of brake fluid flows (stores) into the reservoir 3, the pressure regulating valve 4 is closed, and the brake fluid from the master cylinder M / C side to the suction side of the pump P via the suction oil passage 13 is closed. Block the distribution of

  When the master cylinder pressure Pm is supplied from the suction oil passage 13, the pressure regulating valve 4 changes from the open state to the closed state. The biasing force of the coil spring 33 (the discount of the biasing force of the return spring 44) is F, and the pressure receiving area of the piston 31 is S1. When the master cylinder pressure Pm is applied to the piston 31 with the pressure regulating valve 4 opened, and Pm × S1> F, the piston 31 moves (strokes) in the direction in which the coil spring 33 is compressed. Move (stroke) toward the seat 420. When the valve body 43 strokes downward by the predetermined amount and is seated on the valve seat 420, the flow of brake fluid from the suction oil passage 13 into the reservoir 3 is blocked. When brake fluid in the wheel cylinder W / C flows into the reservoir 3 via the pressure reducing passage 14, or when brake fluid in the master cylinder M / C flows into the reservoir 3 via the suction oil passage 13, the piston 31 is coiled. The volume of the reservoir chamber 30a is increased by moving the spring 33 in the compressing direction, and the brake fluid is stored. The piston 31, the rod 46, and the valve body 43 are separate bodies, and the upper limit of the stroke amount of the piston 31 is set larger than the upper limit of the stroke amount of the valve body 43. For this reason, even after the valve body 43 is stroked downward by the predetermined amount and is seated on the valve seat 420, the piston 31 is stroked into the reservoir 3 even when the stroke of the rod 46 is restricted by the stopper member 47. It is possible to increase the amount of brake fluid stored.

  With the pressure regulating valve 4 closed, the pressure on the master cylinder M / C side of the valve body 43 is the master cylinder pressure Pm. On the other hand, the pressure Ps on the reservoir 3 side of the valve body 43 is F / S1 at the maximum. Therefore, the pressure Ps applied to the suction side of the pump P does not exceed F / S1, but is kept below a predetermined pressure. When the pump P is activated, the brake fluid stored in the reservoir 3 is pumped up and supplied to the supply passage 11 side. At this time, even if the pressure regulating valve 4 is closed, the inside of the reservoir 3 is decompressed by pumping up by the pump P, and the pressure regulating valve 4 is pushed open. That is, when the pump P sucks the brake fluid in the reservoir 3 while the pressure regulating valve 4 is closed, the pressure Ps decreases, so that the piston 31 is pushed toward the valve element 43 by the urging force F of the coil spring 33. At this time, assuming that the oil passage diameter (valve seat diameter) of the pressure regulating valve 4, that is, the pressure receiving area constituted by the valve seat 420 and the valve body 43 in the pressure regulating valve 4 is S 2, the valve body 43 is satisfied if Pm × S 2 <F. Is away from the valve seat 420 and the pressure regulating valve 4 is opened. The valve opening pressure F / S2 is set to a predetermined pressure. In this valve-opened state, the pump P is in a state where it can suck brake fluid from the reservoir 3 and can suck brake fluid from the master cylinder M / C (suction oil passage 13). When the master cylinder pressure Pm is applied to the piston 31 of the reservoir 3 and the piston 31 moves in the direction in which the coil spring 33 is compressed, the valve closing operation is performed as described above. As described above, the pressure regulating valve 4 automatically repeats opening and closing when the pump P is operated, so that the pump P sucks brake fluid from the master cylinder M / C (suction oil passage 13), and the wheel cylinder pressure Pw. Can be increased and the pressure applied to the suction side of the pump P is regulated to a predetermined value or less.

  Hereinafter, the operation of the specific configuration will be described. Since the large-diameter portion 46b, not the small-diameter portion 46a of the rod 46, is supported by the rod support member 45 (small-diameter cylindrical portion 45c), the operation (stroke) of the rod 46 can be stabilized. Further, by providing the large-diameter portion 46b of the rod 46 instead of the small-diameter portion 46a in contact with the piston crown surface 310, the surface pressure acting on the piston crown surface 310 from the rod 46 is reduced, and the durability of the piston 31 is increased. Can be improved. Further, by providing the convex portion 312 so as to substantially overlap the concave portion 314 in the axial direction on the piston crown surface 310, the durability of the piston 31 against the elastic force acting from the coil spring 33 can be improved. By arranging the pressure regulating valve accommodating holes 24P and 24S of both systems P and S so as to be separated from each other, a wide area between the pressure regulating valve accommodating holes 24P and 24S can be taken. For example, when the housing part of the unit of the pump P is formed immediately above the reservoir 3, this space is generally determined by the required pump discharge capacity and the like. Therefore, by offsetting the pressure regulating valve housing holes 24P and 24S so as to be away from each other, the overall size of the housing 2 can be suppressed while improving the layout of the pump P.

  Next, the effect | action by the structure of the connection oil path 133 is demonstrated. Using a contact between the bottom 22a of the reservoir housing hole 22 and the crown surface 310 of the piston 31 (a contact portion 311 provided on the piston 31) as a configuration that serves as a stopper function for restricting the piston 31 to a predetermined stroke position. Convenient. Thereby, the configuration of the reservoir 3 can be simplified and the size thereof can be reduced. On the other hand, an oil passage 13a connected to the master cylinder M / C (provided with the pressure regulating valve 4), an oil passage 13b connected to the suction portion of the pump P, and the like are opened at the bottom 22a of the reservoir accommodation hole 22. It is desirable that the openings of these oil passages 13a and 13b communicate with each other even when the piston 31 is at the top dead center position, for example, regardless of the operating state of the reservoir 3 (pressure regulating valve 4). This is because the pump P can smoothly suck the brake fluid from the master cylinder M / C, and the operation of the device 1 can be smoothed. Here, the rotation of the piston 31 in the reservoir housing hole 22 is not restricted in the circumferential direction, and the piston 31 can rotate. Therefore, if the connection oil passage 133 for communicating the openings of the oil passages 13a and 13b is provided on the piston 31 side (piston crown surface 310), the rotational direction position (rotation phase) of the piston 31 The opening of one of the oil passages 13a and 13b in the bottom portion 22a of the reservoir housing hole 22 is blocked by a piston crown surface 310 (a surface other than the connection oil passage 133 in the surface contacting the bottom portion 22a). There is a risk that. That is, the communication between the openings of the oil passages 13a and 13b may be hindered. It is also conceivable to separately provide a configuration for restricting the rotation of the piston 31 in the reservoir accommodation hole 22. However, in this case, the configuration of the reservoir 3 may be complicated, and it may be difficult to reduce the size of the reservoir.

  In order to avoid a situation in which the openings of the oil passages 13a and 13b are blocked by the piston 31, the arrangement of the oil passages 13a and 13b in the vicinity of the bottom portion 22a of the reservoir accommodation hole 22 (installation position of the opening) is determined. Adjustments are also possible. However, there are many restrictions. For example, as the oil passages 13a and 13b, a lateral oil passage that is substantially parallel to the bottom portion 22a of the reservoir housing hole 22 may be formed, and a side surface of the lateral oil passage may be opened to the bottom portion 22a. However, in this case, there is a risk that the number of steps increases, such as a step of additionally processing the lateral oil passage and a step of sealing the opening of the lateral oil passage to the outside of the housing 2, and the processing cost increases. Further, the lateral oil path complicates the oil path configuration inside the housing 2, which may increase the size of the housing 2. In contrast, in the present embodiment, the connecting oil passage 133 is provided not on the piston 31 side (piston crown surface 310) but on the piston crown surface 310. Specifically, the connection oil passage 133 is provided on the bottom 22 a side of the reservoir accommodation hole 22. Therefore, regardless of the operating state of the reservoir 3 (pressure regulating valve 4) or the rotational position of the piston 31, any one of the oil passages 13a, 13b is closed by the piston crown surface 310 (the opening of the oil passages 13a, 13b). It is possible to avoid a situation where communication between the parts is hindered). That is, it is possible to maintain a state in which the openings of the oil passages 13a and 13b communicate with each other through the connection oil passage 133. Accordingly, the configuration and the arrangement of the oil passages 13a and 13b in the vicinity of the bottom portion 22a of the reservoir accommodation hole 22 can be simplified while smoothing the operation of the device 1, and thus the above-described fear can be suppressed.

  Further, the connection oil passage 133 is not provided on the piston 31 side (piston crown surface 310). Therefore, it is not necessary to provide unevenness on the piston 31 side (piston crown surface 310) in order to provide the connection oil passage 133. Thereby, the shape of the piston crown surface 310 can be simplified. For example, as in the present embodiment, the contact portion 311 of the piston 31 in contact with the stopper 22d can be provided in a shape that extends annularly over the entire circumferential range and is continuous on the same plane. Therefore, the processing cost of the piston 31 can be suppressed. The piston 31 may be made of metal. By making the piston 31 made of resin as in the present embodiment, the sliding resistance with the reservoir housing hole 22 can be reduced.

  The piston 31 becomes a top dead center position when its contact portion 311 comes into contact with the stopper 22d, and the stroke beyond that is restricted. As shown in FIG. 2, even when the piston 31 is located at the top dead center, the connection oil passage 133 connects the first space 131 and the second space 132 while facing the piston crown surface 310, Stay in communication with each other. In other words, the first oil passage 13a and the second oil passage 13b communicate with each other through the connection oil passage 133. That is, even when the piston 31 is at the top dead center, the connection oil passage 133 holds the state where the openings of the oil passages 13a and 13b communicate with each other. Therefore, the communication state between the openings of the oil passages 13a and 13b can be ensured more reliably. Even when the piston 31 strokes downward and there is a gap between the contact portion 311 and the stopper 22d of the reservoir housing hole 22, the connection oil passage 133 passes through the first space 131 and the second space 132. Connect and stay connected.

  By forming a counterbore 23 (which is substantially circular when viewed from the axial direction) on the bottom 22a, first and second spaces 131 and 132 are formed in the vicinity of the openings of the first and second oil passages 13b, respectively. Yes. Thus, the workability can be improved by forming the spaces 131 and 132 that are part of the oil passages 13a and 13b by the counterbore 23 that is relatively easy to process. Similarly, the connection which connects the 1st space 131 (opening part of the 1st oil passage 13a) and the 2nd space 132 (opening part of the 2nd oil passage 13b) by forming countersink 23 in bottom 22a. An oil passage 133 is formed. Thus, the workability can be improved by forming a space that becomes the connection oil passage 133 by the counterbore 23. Further, the configuration of the connection oil passage 133 can be simplified. Specifically, one counterbore 23 including the opening of the first oil passage 13a and the opening of the second oil passage 13b is formed in the bottom 22a of the reservoir accommodation hole 22. Thus, the first counterbore 23 forms the first and second spaces 131 and 132 and the connecting oil passage 133 at the same time. Therefore, the first and second spaces 131 and 132 and the connecting oil passage 133 can be easily formed as compared with the case where the plurality of counterbore 23 are used.

  The central axis C of the first oil passage 13a (the portion excluding the pressure regulating valve accommodation hole 24) or the central axis D of the second oil passage 13b may be inclined with respect to the central axis A of the reservoir accommodation hole 22. . Further, the first oil passage 13a (at least a part thereof) and the second oil passage 13b (at least a part thereof) may be opened not on the bottom surface of the reservoir accommodation hole 22 but on the inner wall surface (extending in the axial direction). . In this embodiment, since the central axis C of the first oil passage 13a and the central axis D of the second oil passage 13b are substantially parallel to the central axis A of the reservoir accommodation hole 22, the step of forming the reservoir accommodation hole 22 It is possible to relate the steps of forming the first oil passage 13a and the second oil passage 13b, for example, to make these steps continuous. Therefore, workability can be improved and these can be formed more easily. Further, since the first oil passage 13a and the second oil passage 13b are opened in the bottom surface of the reservoir accommodation hole 22, for example, the first oil passage 13a and the second oil passage 13b can be drilled from the bottom surface. is there. Therefore, workability can be improved and these can be formed more easily. Further, since the central axis B of the counterbore 23 and the central axis A of the reservoir accommodation hole 22 (bottom 22a) are substantially coaxial, the process of forming the reservoir accommodation hole 22 and the process of forming the counterbore 23 are related, for example These processes can be integrated or continuous. Therefore, the workability can be further improved, and the first and second spaces 131 and 132 and the connection oil passage 133 can be formed more easily.

[effect]
Hereinafter, effects exhibited by the brake device 1 of the first embodiment will be listed.
(A1) A housing 2 having a bottomed reservoir housing hole 22 inside, a piston 31 that strokes in the reservoir housing hole 22 and separates the inside of the reservoir housing hole 22 into two chambers, and a bottom portion 22a of the reservoir housing hole 22 The first oil passage 13a that opens to the master cylinder M / C, the second oil passage 13b that opens to the bottom portion 22a of the reservoir housing hole 22 and connects to the suction portion of the pump P, the first oil passage 13a and the first oil passage 13a Two oil passages 13b were connected, and a connection oil passage 133 formed facing the crown surface 310 of the piston 31 was provided.
Therefore, it is possible to maintain a state in which the oil passages 13a and 13b are connected (the openings of the oil passages 13a and 13b communicate with each other). Further, the oil passage configuration inside the housing 2 can be simplified.

(A2) A stopper 22d that contacts the piston 31 and regulates to a predetermined stroke position is provided. When the piston 31 contacts the stopper 22d, the first oil passage 13a and the second oil passage 13b are connected via the connection oil passage 133. Communicate.
Therefore, it is possible to ensure a state where the openings of the oil passages 13a and 13b communicate with each other more reliably.

(A9) The crown surface 310 of the piston 31 has an annular contact portion 311 in contact with the stopper 22d.
Therefore, the shape of the piston crown surface 310 can be simplified.

(B1) A housing 2 having a bottomed reservoir housing hole 22 inside, a pump P provided in the housing 2 and capable of sucking brake fluid in the reservoir housing hole 22, and a reservoir housing hole 22 at the top dead center. A piston 31 that can be stroked in the reservoir housing hole 22 so as to be located near the bottom portion 22a of the cylinder, a first oil passage 13a that opens to the bottom portion 22a of the reservoir housing hole 22 and is connected to the master cylinder M / C, and a reservoir A second oil passage 13b that opens to the bottom 22a of the housing hole 22 and connects to the suction portion of the pump P, a first space 131 that forms an oil passage formed in the opening of the first oil passage 13a, and a second oil A second space 132 formed in the opening of the passage 13b and constituting an oil passage; and a connecting oil passage 133 that connects the first space 131 and the second space 132 when at least the piston 31 is located at the top dead center; Equipped with.
Therefore, the same effect as the above (A1) (A2) can be obtained.

[Example 2]
First, the configuration will be described. FIG. 6 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the second embodiment. FIG. 7 is a front view of the space similar to FIG. FIG. 8 is a side view of the space similar to FIG. In the apparatus 1 of this embodiment, first and second spaces 131 and 132 and a connecting oil passage 133 are formed by a plurality of counterbore 231 and 232. A first counterbore 231 is formed at the bottom 22 a of the reservoir housing hole 22 at the periphery of the opening of the pressure regulating valve housing hole 24. The first counterbore 231 is formed in a cylindrical shape extending substantially parallel to the central axis A of the reservoir accommodation hole 22 and is substantially circular when viewed from the axial direction. The first counterbore 231 is formed so as to surround the entire circumference of the opening of the pressure regulating valve housing hole 24. The diameter of the first counterbore 231 is provided smaller than the diameter of the counterbore 23 of the first embodiment. The first counterbore 231 has a bottom portion 231a on the upper side and opens on the lower side. By the first counterbore 231, a first space 131 is formed in the vicinity of the opening of the pressure regulating valve accommodation hole 24 (first oil passage 13 a). The first space 131 (first counterbore 231) constitutes an oil passage.

  A second counterbore 232 is formed at the bottom 22a of the reservoir accommodation hole 22 at the periphery of the opening of the second oil passage 13b. The second counterbore 232 is formed in a cylindrical shape extending substantially parallel to the central axis A of the reservoir accommodation hole 22 and is substantially circular when viewed from the axial direction. The second counterbore 232 is formed so as to surround the entire circumference of the opening of the second oil passage 13b. Corresponding to the fact that the diameter of the opening of the second oil passage 13b is smaller than the diameter of the opening of the first oil passage 13a (pressure regulating valve accommodation hole 24), the diameter of the second counterbore 232 is It is provided smaller than the diameter of the counterbore 231. The sum of the diameters of the first and second counterbore 231 and 232 is larger than the diameter of the reservoir accommodation hole 22. The depth (axial dimension) of the second counterbore 232 is provided approximately equal to the depth of the first counterbore 231. The second counterbore 232 has a bottom portion 232a on the upper side and opens on the lower side. Due to the second counterbore 232, a second space 132 is formed in the vicinity of the opening of the second oil passage 13b. The second space 132 (second counterbore 232) constitutes an oil passage.

  The central axis E of the first counterbore 231 is substantially coaxial with the central axis C of the first oil passage 13a (pressure regulating valve accommodation hole 24). The central axis C of the first oil passage 13a (pressure regulating valve accommodation hole 24) is radially inward of the reservoir accommodation hole 22 with respect to the central axis C of the first oil passage 13a (pressure regulating valve accommodation hole 24) of the first embodiment. It is offset. The central axis F of the second counterbore 232 is substantially coaxial with the central axis D of the second oil passage 13b. The central axis D of the second oil passage 13b is offset inward in the radial direction of the reservoir accommodation hole 22 with respect to the central axis D of the second oil passage 13b of the first embodiment. The connection oil passage 133 is an overlap portion in which the first counterbore 231 and the second counterbore 232 are overlapped. The connection oil passage 133 constitutes an oil passage that connects the first countersink 231 (first space 131) and the second countersink 232 (second space 132). Regardless of whether or not the piston 31 is in contact with the stopper 22d (the piston 31 is at the top dead center), the first counter 231 and the second counter 232 (that is, the first and second countersinks 232). The first oil passage 13a and the second oil passage 13b communicate with each other (via the spaces 131 and 132 and the connecting oil passage 133). Other configurations are the same as those of the first embodiment.

  Next, the operation will be described. A compression force caused by the elastic force of the coil spring 33 acts on the piston 31 (contact portion 311) and the stopper 22d (contact surface 220) that are in contact with each other. If the contact area between the piston 31 (contact portion 311) and the stopper 22d is small, the compression force per unit area increases, and the piston 31 and the like may be deformed. In particular, when the piston 31 is formed of resin as in the present embodiment, the deformation amount of the piston crown surface 310 increases, and the durability of the piston 31 may decrease. Further, for example, the piston crown surface 310 may bite into the inner peripheral side of the annular stopper 22d, and the piston 31 may not easily stroke. On the other hand, the apparatus 1 of the present embodiment can suppress the above-mentioned fear by increasing the contact area between the piston 31 and the stopper 22d. Specifically, instead of forming one counterbore 23 including the opening of the first oil passage 13a and the opening of the second oil passage 13b at the bottom 22a of the reservoir housing hole 22, the counterbore 23 is A plurality of oil passages 13a and 13b are communicated with each other through the plurality of counterbore 231 and 232. Therefore, since the area occupied by the counterbore 231 and 232 as a whole can be reduced in the bottom portion 22a, the area occupied by the stopper 22d can be increased. Thereby, the contact area (area of the contact part 311 of the piston 31) between the piston 31 and the stopper 22d can be increased. Therefore, even when the piston 31 is formed of resin, it is possible to suppress a decrease in durability by suppressing an increase in the amount of deformation. Further, it is possible to suppress a situation where the piston 31 is deformed and it is difficult to make a stroke. In the present embodiment, the diameters of the first counterbore 231 and the second counterbore 232 are set to the diameters of the openings of the first oil passage 13a (pressure regulating valve housing hole 24) and the second oil passage 13b. Therefore, the area occupied by the stopper 22d can be made as large as possible.

  The connection oil passage 133 is an overlap portion in which the first counterbore 231 and the second counterbore 232 are overlapped. Therefore, the connection oil passage 133 can be formed by simply overlapping the first counterbore 231 and the second counterbore 232 without providing a special configuration as the connection oil passage 133. The connection oil passage 133 can be easily formed while simplifying. Further, the central axis E of the first counterbore 231 is substantially coaxial with the central axis C of the first oil passage 13a (pressure regulating valve accommodation hole 24). Therefore, the process of forming the first oil passage 13a (pressure regulating valve housing hole 24) and the process of forming the first counterbore 231 can be associated, and for example, these processes can be integrated or continuous. Therefore, workability can be improved and the first oil passage 13a (pressure regulating valve housing hole 24) and the first counterbore 231 (first space) can be easily formed. Similarly, the center axis F of the second counterbore 232 is substantially coaxial with the center axis D of the second oil passage 13b. Therefore, since the process of forming the second oil passage 13b and the process of forming the second counterbore 232 can be integrated or continuous, these can be easily formed. In addition, the same effect as that of the first embodiment is obtained by the same configuration as that of the first embodiment.

Hereinafter, effects exhibited by the brake device 1 of the second embodiment will be listed.
(A3) A first counterbore 231 formed at the opening edge of the first oil passage 13a and a second counterbore 232 formed at the opening edge of the second oil passage 13b. The first counterbore 231 and the second counterbore 232 are connected.
By forming the counterbore 231 and 232 on the bottom 22a side of the reservoir housing hole 22 in this way, the state where the oil passages 13a and 13b are connected to each other (the openings of the oil passages 13a and 13b communicate with each other) is maintained. Can do. Further, the oil passage configuration inside the housing 2 can be simplified. Moreover, the fall of durability of piston 31 grade | etc., Can be suppressed.

(A4) The connection oil passage 133 is an overlap portion in which the first counterbore 231 and the second counterbore 232 are overlapped.
Therefore, the connection oil passage 133 can be easily formed.

(A7) The opening of the first oil passage 13a and the first counterbore 231 are circular, and their centers are coaxial.
Therefore, the first oil passage 13a and the first counterbore 231 can be easily formed.

(A8) The opening of the second oil passage 13b and the second counterbore 232 are circular, and their centers are coaxial.
Therefore, the second oil passage 13b and the second counterbore 232 can be easily formed.

(B2) The first space 131 and the second space 132 are a first counterbore 231 and a second counterbore 232 formed at the opening edges of the first oil passage 13a and the second oil passage 13b, respectively.
In this way, the workability can be improved by forming the spaces 131 and 132 by the counterbore 231 and 232.

(C1) A housing 2 having a bottomed reservoir housing hole 22 formed therein, a pump P provided in the housing 2 and capable of sucking brake fluid from the reservoir housing hole 22 or from the master cylinder M / C, and the reservoir housing A piston 31 provided in the hole 22 and provided with a stroke according to the amount of brake fluid in the reservoir accommodation hole 22, and a piston 31 provided in the reservoir accommodation hole 22 when the piston 31 is at the top dead center position. A stopper 22d that comes into contact, a first oil passage 13a that opens to the bottom 22a of the reservoir accommodation hole 22 and connects to the master cylinder M / C, and a first oil passage 13a that opens to the bottom 22a of the reservoir accommodation hole 22 and connects to the suction portion of the pump P. Two oil passages 13b, a first counterbore 231 formed at the opening edge of the first oil passage 13a and constituting the oil passage, and a second seat formed at the opening edge of the second oil passage 13b and constituting the oil passage. The piston 31 is The first oil passage 13a and the second oil passage 13b communicate with each other by the first counterbore 231 and the second counterbore 232 when in contact with the pad 22d.
Therefore, the same effect as the above (A3) can be obtained. Further, it is possible to ensure the state where the openings of the oil passages 13a and 13b communicate with each other more reliably.

[Example 3]
First, the configuration will be described. FIG. 9 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the third embodiment. FIG. 10 is a front view similar to FIG. 4 of the space. FIG. 11 is a side view of the space similar to FIG. The configurations of the first and second counterbore 231 and 232 (diameter, positions of the central axes E and F, etc.) are the same as those in the second embodiment. The position of the central axis C of the first oil passage 13a (pressure regulating valve accommodation hole 24) is the same as that in the first embodiment, and is located on the radially outer side of the reservoir accommodation hole 22 relative to the second embodiment. The central axis C is the left side (the side closer to the left side of the housing 2 in the figure) with respect to the central axis E of the first counterbore 231 (the central axis C of the first oil passage 13a of the second embodiment. In other words, It is offset in the direction away from the intermediate position between the two reservoirs 3P, 3S. The position of the central axis D of the second oil passage 13b is the same as that in the first embodiment, and is located on the outer side in the radial direction of the reservoir accommodation hole 22 relative to the second embodiment. The center axis D is the right side (the side away from the left side surface of the housing 2) with respect to the center axis F of the second counterbore 232 (the center axis C of the second oil passage 13b of the second embodiment). It is offset in the direction approaching the intermediate position between the reservoirs 3P and 3S. Other configurations are the same as those of the second embodiment.

  Next, the operation will be described. The central axis C of the first oil passage 13a is offset with respect to the central axis E of the first counterbore 231. Therefore, the arrangement of the first oil passage 13a with respect to the first counterbore 231 in the vicinity of the bottom 22a can be freely set. Thereby, the layout property of the reservoir 3 in the housing 2 and, in turn, the layout property of each component in the housing 2 can be improved. For example, when the reservoir 3 is disposed in the housing 2 adjacent to a valve portion of a pump P or a solenoid valve (hereinafter referred to as a pump P or the like), the first oil passage 13a (the pressure regulating valve housing hole 24). ) And the pump P or the like, while avoiding interference between the reservoir 3 and the pump P or the like. Thus, the housing 2 can be downsized by effectively utilizing the space.

  In the present embodiment, the central axis C of the first oil passage 13a is radially outward of the reservoir housing hole 22, specifically, relative to the central axis E of the first counterbore 231. It is offset in the direction away from the intermediate position. Therefore, it is possible to improve the above-described operational effect of the first embodiment by arranging the pressure regulating valve housing holes 24P and 24S so as to be separated from each other. The offset direction is not limited to this. Similarly, the center axis D of the second oil passage 13 b is offset with respect to the center axis F of the second counterbore 232. Therefore, since the arrangement of the second oil passage 13b with respect to the second counterbore 232 in the vicinity of the bottom 22a can be freely set, the same effect as described above can be obtained. In the present embodiment, the central axis D of the second oil passage 13b is radially outward of the reservoir accommodation hole 22, specifically, with respect to the central axis F of the second counterbore 232, the two reservoirs 3P and 3S. It is offset in the direction of approaching the intermediate position. Therefore, the second oil passage 13b can be brought close to the suction portion of the pump P. This makes it easy to shorten the second oil passage 13b and reduce the suction resistance of the pump P. The offset direction is not limited to this. In addition, the same effects as those of the first and second embodiments are obtained by the same configuration as that of the first and second embodiments.

[Example 4]
First, the configuration will be described. FIG. 12 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the fourth embodiment. FIG. 13 is a front view similar to FIG. 4 of the space. FIG. 14 is a side view of the space similar to FIG. The configurations of the first and second oil passages 13a, 13b (positions of the central axes C, D, etc.) are the same as in the first and third embodiments. The diameter of the first counterbore 231 is smaller than those in the second and third embodiments. The central axis E of the first counterbore 231 is substantially coaxial with the central axis C of the first oil passage 13a. The diameter of the second counterbore 232 is smaller than those of the second and third embodiments and smaller than the diameter of the first counterbore 231. The central axis F of the second counterbore 232 is substantially coaxial with the central axis D of the second oil passage 13b. The total diameter of the first and second counterbore 231 and 232 is smaller than the diameter of the reservoir accommodation hole 22.

  A groove extending linearly connecting the opening (center axis C, E) of the first oil passage 13a and the opening (center axes D, F) of the second oil passage 13b is formed in the bottom 22a of the reservoir housing hole 22. 233 is formed. One end of the groove 233 is connected to the first counterbore 231, and the other end of the groove 233 is connected to the second counterbore 232. The width of the groove 233 is substantially the same from one of the openings of the first and second oil passages 13a and 13b to the other, and is substantially the same as the diameter of the second counterbore 232. The depth (axial dimension) of the groove 233 is substantially equal to the depth of the first and second counterbore 231,232. The groove 233 constitutes a connecting oil passage 133 that connects the first counterbore 231 (first space 131) and the second counterbore 232 (second space 132). Regardless of whether or not the piston 31 is in contact with the stopper 22d (the piston 31 is at the top dead center), the first counter 231, the second counter 232, and the groove 233 (that is, The first oil passage 13a and the second oil passage 13b communicate with each other (via the second spaces 131 and 132 and the connecting oil passage 133). Other configurations are the same as those of the third embodiment.

  Next, the operation will be described. The diameter of the first counterbore 231 is smaller than those in the second and third embodiments. Therefore, the first counterbore 231 is substantially coaxial with the first oil passage 13a while the opening portion of the first oil passage 13a in the bottom portion 22a is disposed on the radially outer side of the reservoir accommodation hole 22 with respect to the second embodiment. be able to. Accordingly, the first counterbore 231 can be easily formed as in the second embodiment while improving the layout as in the third embodiment. In addition, the area occupied by the first countersink 231 in the bottom portion 22a can be reduced by an amount corresponding to the reduction in the diameter of the first countersink 231. Therefore, it is possible to more effectively suppress the situation where the durability of the piston 31 is reduced or the piston 31 is deformed and difficult to stroke. Similarly, the diameter of the second counterbore 232 is provided smaller than in the second and third embodiments. Therefore, the same effect as the above about the first counterbore 231 can be obtained.

  In addition, a groove 233 that connects the first counterbore 231 and the second counterbore 232 is formed in the bottom 22a. Therefore, as the diameters of the first and second countersinks 231 and 232 are made smaller than those in the second and third embodiments, the first and second countersinks 232 are arranged depending on the arrangement of the first and second oil passages 13a and 13b. Even when they are separated from each other, the first and second counterbore 231 and 232 can always be kept in communication with each other. The groove 233 is formed not on the piston 31 side but on the piston crown surface 310 (on the bottom 22a side). For this reason, regardless of the operating state of the reservoir 3 (pressure regulating valve 4) and the rotational position of the piston 31, the state in which the openings of the first and second oil passages 13a and 13b are communicated with each other by the connection oil passage 133 is maintained. be able to.

The width and depth of the groove 233 are substantially the same as the diameter and depth of the first counterbore 231. Therefore, first, the step of forming the groove 233 and the step of forming the first counterbore 231 can be associated, and for example, these steps can be integrated or continuous. Therefore, workability is improved and the groove 233 and the first counterbore 231 (first space 131) can be easily formed. Secondly, a necessary and sufficient cross-sectional area of the flow path between the opening (first space 131) of the first oil passage 13a and the opening (second space 132) of the second oil passage 13b is ensured. be able to. The groove 233 is formed to extend in a straight line (and substantially equal in width) connecting the central axis C of the opening of the first oil passage 13a and the central axis D of the opening of the second oil passage 13b. ing. Therefore, the flow path length between these openings can be shortened, and loss due to flow path resistance can be reduced. Further, since the width of the groove 233 is provided substantially with a second counterbore 23 and second diameter the same, first at the bottom 22a, and a second counterbore 231, 232 and grooves 233, reducing the space occupied as a whole be able to. Therefore, since the area occupied by the stopper 22d can be increased, the above-described situation such as a decrease in durability of the piston 31 can be suppressed. In addition, the effect similar to Examples 1-3 is acquired by the structure similar to Examples 1-3.

[Example 5]
First, the configuration will be described. FIG. 15 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the fifth embodiment. FIG. 16 is a front view similar to FIG. 4 of the space. FIG. 17 is a side view of the space similar to FIG. The configuration of the first and second oil passages 13a and 13b (positions of the central axes C and D, etc.) and the configuration of the first counterbore 231 (diameter, position of the central axis E, etc.) are the same as in the fourth embodiment. . A second counterbore 232 is formed at the bottom 22 a of the reservoir accommodation hole 22. The second counterbore 232 is formed in a cylindrical shape extending substantially coaxially with the central axis A of the reservoir accommodation hole 22 and is substantially circular when viewed from the axial direction. The depth (axial dimension) of the second counterbore 232 is provided approximately equal to the depth of the first counterbore 231. The second counterbore 232 has a bottom portion 232a on the upper side and opens on the lower side. The diameter of the second counterbore 232 is larger than the distance between the outer edge of the opening of the first counterbore 231 and the outer edge of the opening of the second oil passage 13b. The second counterbore 232 has a part on the outer side in the radial direction that overlaps (overlaps) a part of the first counterbore 231 (inward in the radial direction of the reservoir housing hole 22), and the other part on the outer side in the radial direction. A part thereof is formed so as to overlap with a part of the opening of the second oil passage 13b (in the radial direction of the reservoir housing hole 22). A second space 132 is formed near the opening of the second oil passage 13b by the second counterbore 232, and the first counterbore 231 (first space 131) and the second space 132 are A connecting oil passage 133 to be connected is configured. Other configurations are the same as those of the fourth embodiment.

  Next, the operation will be described. The second counterbore 232 constitutes a second space 132 and a connecting oil passage 133 that connects the first counterbore 231 (first space 131) and the second space 132. Therefore, compared with the case where the second space 132 and the connection oil passage 133 are formed with different configurations, these configurations can be simplified and the formation thereof can be facilitated. The second counterbore 232 has a part on the outer side in the radial direction overlapping a part of the opening of the second oil passage 13b. Therefore, the second space 132 is not provided on the radially outer side of the reservoir accommodation hole 22 with respect to the second oil passage 13b. Therefore, it is possible to arrange the second oil passage 13b more radially outside the reservoir accommodation hole 22. Further, compared to the case where the shape of the second counterbore 232 is set so as to include the entire circumference of the opening of the second oil passage 13b (the radially outer side of the reservoir housing hole 22 in this opening), the stopper 22d. The area occupied by can be increased.

  By forming a second counterbore 232 (which is substantially circular when viewed from the axial direction) on the bottom 22a, a second space 132 and a connecting oil passage 133 are formed. Therefore, workability can be improved. By appropriately adjusting the arrangement and diameter of the second counterbore 232, the second counterbore 232 can be simultaneously overlapped (stranded) over both the first counterbore 231 and the second oil passage 13b. it can. Thereby, these can be easily formed while simplifying the configuration of the second space 132 and the connection oil passage 133. Further, since the central axis F of the second countersink 232 and the central axis A of the reservoir accommodation hole 22 are substantially coaxial, the step of forming the reservoir accommodation hole 22 and the step of forming the second countersink 232 are associated with each other. For example, these processes can be integrated or continuous. Therefore, workability can be further improved, and the second space 132 and the connecting oil passage 133 can be formed more easily. In addition, the effect similar to Examples 1-4 is acquired by the structure similar to Examples 1-4.

[Example 6]
First, the configuration will be described. FIG. 18 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the sixth embodiment. FIG. 19 is a front view of the space similar to FIG. FIG. 20 is a side view of the space similar to FIG.
The configurations of the first and second oil passages 13a and 13b (positions of the central axes C and D, etc.) and the configuration of the first counterbore 231 (diameter, position of the central axis E, etc.) are the same as in the fourth and fifth embodiments. It is. The position of the central axis F of the second counterbore 232 is the same as in the fourth embodiment. The diameter of the second counterbore 232 is slightly larger than the diameter of the second counterbore 232 of the fourth embodiment and smaller than the diameter of the second counterbore 232 of the second and third embodiments. The configuration of the third counterbore 233 (diameter, position of the central axis G, etc.) is the same as the configuration of the second counterbore 232 (diameter, position of the central axis F, etc.) of the fifth embodiment. The diameter of the third counterbore 233 is larger than the distance between the outer edge of the opening of the first counterbore 231 (pressure regulating valve accommodation hole 24) and the outer edge of the opening of the second counterbore 232. The third counterbore 233 is formed so as to straddle both the first counterbore 231 and the second counterbore 232. The third counterbore 233 has a part on the outer side in the radial direction that overlaps (overlaps) a part of the first counterbore 231 (the inner side in the radial direction of the reservoir accommodation hole 22), and the other part on the outer side in the radial direction. A part thereof is formed so as to overlap with a part of the second counterbore 232 (in the radial direction of the reservoir housing hole 22). By the first and second counterbore 231 and 232, first and second spaces 131 and 132 are formed in the vicinity of the openings of the first and second oil passages 13a and 13b, respectively. The third counterbore 233 constitutes a connection oil passage 133 that connects the first counterbore 231 (first space 131) and the second counterbore 232 (second space 132). Other configurations are the same as those of the fifth embodiment.

  Next, the operation will be described. As in the fourth embodiment, the diameters of the first and second counterbore 231 and 232 are smaller than those in the second and third embodiments. In addition, a third counterbore 233 that connects the first counterbore 231 and the second counterbore 232 is formed on the bottom 22a. The third counterbore 233 is formed not on the piston 31 side but on the piston crown surface 310 (on the bottom 22a side). With these configurations, the same effects as those of the fourth embodiment can be obtained.

  A connection oil passage 133 is formed by forming a third counterbore 233 (which is substantially circular when viewed from the axial direction) on the bottom 22a. Therefore, workability can be improved. By appropriately adjusting the arrangement and diameter of the third counterbore 233, the third counterbore 233 is simultaneously overlapped (stranded) on both the first counterbore 231 and the second counterbore 232. Can do. Thereby, it is possible to easily form the connection oil passage 133 while simplifying the configuration. Further, since the central axis G of the third countersink 233 and the central axis A of the reservoir accommodation hole 22 are substantially coaxial, the step of forming the reservoir accommodation hole 22 and the step of forming the third countersink 233 are associated with each other. For example, these processes can be integrated or continuous. Therefore, the workability can be further improved, and the reservoir accommodation hole 22 and the connection oil passage 133 can be easily formed.

  The first and second counterbore 231 and 232 constitute first and second spaces 131 and 132, respectively. The connection oil passage 133 (third counterbore 233) connects the first space 131 and the second space 132. Therefore, when the first counterbore 231 or the second counterbore 232 is omitted (for example, the third counterbore 233 is set to a part of the opening of the first oil passage 13a or the opening of the second oil passage 13b). Compared to a case where the piston 31 is at the top dead center, the connecting oil passage 133 (third oil passage 13a is formed from the opening of the first oil passage 13a or the opening of the second oil passage 13b. It is possible to ensure a large cross-sectional area of the flow path leading to the counterbore 233). Therefore, the communication state between the oil passages 13a and 13b can be more effectively ensured. In addition, the effect similar to Examples 1-5 is acquired by the structure similar to Examples 1-5.

Hereinafter, effects exhibited by the brake device 1 of the sixth embodiment will be listed.
(A5) The connection oil passage 133 is a third counterbore 233 formed so as to straddle the first counterbore 231 and the second counterbore 232.
Therefore, the connection oil passage 133 can be easily formed.

(A6) The bottom 22a of the reservoir accommodation hole 22 and the third counterbore 233 are circular, and their centers are coaxial.
Therefore, the reservoir accommodation hole 22 and the connection oil passage 133 can be formed more easily.

(C2) A third counterbore 233 formed to straddle the first counterbore 231 and the second counterbore 232 is provided.
Therefore, the connection oil passage 133 can be easily formed.

[Example 7]
First, the configuration will be described. FIG. 21 is a perspective view similar to FIG. 3 of the space constituting the reservoir accommodation hole 22, the pressure regulating valve accommodation hole 24, and the suction oil passage 13b of the seventh embodiment. Only the portion of the reservoir accommodation hole 22 is seen through. FIG. 22 is a front view of the space similar to FIG. FIG. 23 is a side view of the space similar to FIG. The bottom portion 22a of the reservoir accommodation hole 22 is not provided with the counterbore 23 and the groove 233 as in the first to sixth embodiments. Instead, the passage member 7 is interposed between the bottom 22 a in the reservoir accommodation hole 22 and the piston 31.

  FIG. 24 is a front view of the passage member 7 as seen from the axial direction thereof. The passage member 7 has an annular portion 70 and a plurality of protrusions 71. The passage member 7 is formed of, for example, a resin material. The annular portion 70 has a ring shape with a substantially rectangular cross section cut by a plane orthogonal to the circumferential direction. The thickness of the annular portion 70 (the thickness in the radial direction) is not more than the distance from the outer peripheral edge of the bottom 22a to the outer peripheral edge of the opening of the second oil passage 13b. The protrusion 71 is provided integrally with the annular portion 70 so as to protrude radially inward from the inner periphery of the annular portion 70. The thickness of the protrusion 71 in the axial direction of the annular portion 70 (direction orthogonal to the plane including the annular ring) is substantially equal to the height of the annular portion 70 (thickness in the axial direction). When viewed from the axial direction of the annular portion 70, the protrusion 71 has a substantially rectangular shape. The passage member 7 is installed by press-fitting into the reservoir accommodation hole 22. In this state, the passage member 7 (on one side in the axial direction thereof) contacts the bottom portion 22 a of the reservoir accommodation hole 22. Further, the outer peripheral side (radially outer side) of the annular portion 70 contacts the inner peripheral surface (extending in the axial direction) of the reservoir accommodation hole 22. The passage member 7 is prevented from rotating by being press-fitted (the rotational displacement in the reservoir accommodation hole 22 is restricted).

  In the state where the passage member 7 is installed in the reservoir accommodation hole 22, the central axis H of the passage member 7 is substantially coaxial with the central axis A of the reservoir accommodation hole 22. In the above state, the circumferential distance between the protrusions 71 adjacent in the circumferential direction of the annular portion 70 is set larger than the diameter of the opening of the second oil passage 13b in the bottom 22a. The rotational phase (reservoir) of the passage member 7 is such that the opening of the second oil passage 13b is located between the protrusions 71 adjacent in the circumferential direction (the opening of the second oil passage 13b is not covered by the protrusion 71). It is preferable that the circumferential position in the accommodation hole 22 is adjusted. The distance from the outer peripheral edge of the annular portion 70 to the tip of each projection 71 is equal to or less than the distance from the outer peripheral edge of the bottom 22a to the opening of the first oil passage 13a (through hole 450 of the rod support member 45). Is provided below the distance from the outer peripheral edge of the piston 31 to the convex portion 312 (in the piston crown surface 310). A first space 131 is formed in a space radially inward of the annular portion 70 and in the vicinity of the opening of the first oil passage 13a. The first space 131 constitutes an oil passage. A second space 132 is formed in the space on the radially inner side of the annular portion 70 (between the protrusions 71 adjacent in the circumferential direction) and in the vicinity of the opening of the second oil passage 13b. The second space 132 constitutes an oil passage. A connecting oil passage that connects the first space 131 (opening portion of the first oil passage 13a) and the second space 132 (opening portion of the second oil passage 13b) in the radially inner space of the annular portion 70. 133 is formed.

  The passage member 7 restricts the piston 31 to a predetermined stroke position by contacting the piston 31 on the other axial side (the side opposite to the side contacting the bottom 22a). By restricting the piston 31 from being displaced upward, the predetermined stroke position becomes the top dead center position of the piston 31. In other words, the passage member 7 functions as a stopper, and contacts the piston 31 when the piston 31 is at the top dead center position. An annular contact portion 311 that contacts the passage member 7 (the annular portion 70 and the plurality of protrusions 71) is provided on the crown surface 310 of the piston 31. The connecting oil passage 133 is formed facing the piston crown surface 310. Similar to the first embodiment, the connection oil passage 133 connects the first space 131 and the second space 132 at least when the piston 31 is located at the top dead center. That is, when the piston 31 comes into contact with the passage member 7, the first space 131 (opening portion of the first oil passage 13 a) and the second space 132 (opening portion of the second oil passage 13 b) are connected to the connecting oil passage 133. Are in communication with each other. Other configurations are the same as those of the first embodiment.

  Next, the operation will be described. A connecting oil passage 133 is provided not on the piston 31 side but on the piston crown surface 310. Therefore, as in the first embodiment, the openings of the first and second oil passages 13a and 13b are communicated with each other by the connection oil passage 133 regardless of the operating state of the reservoir 3 (pressure regulating valve 4) and the rotational position of the piston 31. Can be maintained. Therefore, the configuration and arrangement of the oil passages 13a and 13b in the bottom 22a of the reservoir accommodation hole 22 can be simplified while smoothing the operation of the device 1. Specifically, the passage member 7 forms a connection oil passage 133 that connects the first space 131 (first oil passage 13a) and the second space 132 (second oil passage 13b). Therefore, the configuration of the connection oil passage 133 can be simplified. A connecting oil passage 133 is formed by the passage member 7 separate from the housing 2 (the bottom 22a of the reservoir accommodation hole 22). Therefore, since it is not necessary to process the connection oil passage 133 in the bottom portion 22a of the reservoir accommodation hole 22, it is possible to easily form the connection oil passage 133 while saving the trouble of processing the housing 2. The passage member 7 can be easily created by molding a resin material. In other words, the passage member 7 has a step portion excluding the wall portion (the counterbore 23 and the like) constituting the connection oil passage 133 (the counterbore 23 and the groove 233) in the bottom portion 22a of the reservoir accommodation hole 22 of the first to sixth embodiments. Part) is separately taken out and configured as a passage member 7. Therefore, the passage member 7 may have the shape of the wall portion (the step portion excluding the counterbore 23) in the bottom portion 22a of the first to sixth embodiments. On the other hand, since the passage member 7 of the present embodiment has a simple annular shape, the configuration can be simplified.

  The passage member 7 also has a function as a stopper for the piston 31. Since the passage member 7 is formed of a resin material, the load acting on the piston crown surface 310 at the top dead center position can be reduced, so that the possibility that the durability of the piston 31 is lowered can be suppressed. The cross section of the annular portion 70 is not limited to a substantially rectangular shape, and may be a substantially circular shape. It is also possible to omit the plurality of protrusions 71 in the passage member 7. However, in this case, the contact portion between the passage member 7 and the piston 31 (the contact portion 311 on the piston crown surface 310) is limited to the annular portion 70. For this reason, a contact area becomes small, the load per unit area of the said contact part becomes large, and there exists a possibility that piston 31 etc. may deform | transform. In addition, for example, the crown surface 310 of the piston 31 bites into the inner peripheral side of the annular portion 70, and there is a high possibility that the piston 31 will not easily stroke. On the other hand, since a plurality of projections 71 are provided on the inner peripheral side of the annular portion 70, the above-mentioned fear may be caused by an increase in the contact area between the piston 31 (the contact portion 311 in the piston crown surface 310) and the passage member 7, or the like. Can be suppressed. The above effect can be improved by providing a plurality of protrusions 71 at substantially equal intervals in the circumferential direction.

  In addition, since each protrusion 71 is provided so as not to cover the opening of the first oil passage 13a (the through hole 450 of the rod support member 45), the operating oil is not supplied through the opening of the first oil passage 13a. There is no risk of disruption of distribution. Further, if the rotational phase of the passage member 7 with respect to the reservoir accommodation hole 22 changes, there is a possibility that the protrusion 71 may block the opening of the second oil passage 13b. However, the passage member 7 is press-fitted so that the opening of the second oil passage 13b is positioned in the gap between the adjacent protrusions 71, and the rotation of the passage member 7 with respect to the reservoir accommodation hole 22 is restricted. Therefore, the above fear can be suppressed. It is also possible to prevent the passage member 7 from rotating with a pin or the like. In this embodiment, the passage member 7 is prevented from rotating by press-fitting. Therefore, the configuration can be simplified. Further, by press-fitting, it is possible to prevent the passage member 7 from being separated from the bottom portion 22a of the reservoir housing hole 22 and falling to the piston 31 side while fixing the rotational phase of the passage member 7. In addition, the effect similar to Examples 1-6 is acquired by the structure similar to Examples 1-6.

[Other embodiments]
As mentioned above, although the form for implement | achieving this invention has been demonstrated based on the Example, the concrete structure of this invention is not limited to an Example, The design change of the range which does not deviate from the summary of invention Are included in the present invention. For example, the configuration of the hydraulic brake system to which the brake device of the present invention is applied is not limited to the embodiment. Further, the specific configuration of the hydraulic circuit and control of the brake device is not limited to that of the embodiment.

  For example, in the embodiment, in each system, two decompression oil passages 14 corresponding to the wheels of the system join together to form one decompression oil passage 14, and the decompression oil passage 14 is connected to the suction oil passage 13b. An example is shown in which they are joined (unified as the intake oil passage 13b) and connected to the reservoir 3. Since the plurality of decompression oil passages 14 and the suction oil passages 13b are unified as described above, the arrangement of the oil passages in the vicinity of the bottom portion 22a can be set relatively freely. Thereby, the layout property of the reservoir 3 in the housing 2 and, in turn, the layout property of each component inside the housing 2 can be improved. On the other hand, the two decompression oil passages 14 corresponding to each wheel are not combined into one, and the decompression oil passage 14 and the suction oil passage 13b are not integrated into one, but these oil passages are individually connected to the reservoir 3. It is good also as connecting. In this case, if each oil passage is arranged in the same manner as the second oil passage 13b of the embodiment, the same effects as those of the embodiment can be obtained.

  FIG. 25 shows a modification of the fourth embodiment in the case where the two decompression oil passages 14 and the suction oil passages 13b corresponding to the respective wheels are connected to the reservoir 3 separately, and the bottom 22a of the reservoir accommodation hole 22 is shown. It is the schematic diagram which looked at from the axial direction. The openings of the three oil passages are arranged side by side on substantially the same circumference around the central axis A. A first counterbore 231 similar to that of the fourth embodiment is formed. A second counterbore 232 and a groove 233 similar to those in the fourth embodiment are formed for each of the three oil passages. Regardless of whether or not the piston 31 is at the top dead center, the first oil passage 13a and the second oil passage 13b are connected to the first counterbore 231 and the second counterbore 232 and the groove 233 (connection oil indicated by hatching). It communicates with the road 133). Further, the reduced pressure oil passage 14 and the second oil passage 13b communicate with each other through the first counterbore 231, the second counterbore 232, and the groove 233 (connection oil passage 133 shown by oblique lines).

  FIG. 26 shows a modification of the fifth embodiment in which two decompression oil passages 14 and suction oil passages 13b corresponding to the respective wheels are separately connected to the reservoir 3, and the bottom 22a of the reservoir accommodation hole 22 is shown. It is the schematic diagram which looked at from the axial direction. The openings of the three oil passages 13b, 14FL, 14RR are arranged side by side on substantially the same circumference centering on the central axis A. First and second counterbore 231 and 232 similar to the fifth embodiment are formed. The second counterbore 232 is formed such that a portion on the outer side in the radial direction overlaps a portion of the opening of each oil passage 13b, 14FL, 14RR. Regardless of whether or not the piston 31 is at the top dead center, the first oil passage 13a and the second oil passage 13b are connected to the first counterbore 231 and the second counterbore 232 (connected oil passage 133 shown by diagonal lines). It communicates with. Further, the respective reduced pressure oil passages 14FL, 14RR and the second oil passage 13b are communicated with each other by a second counterbore 232 (connection oil passage 133 shown by hatching). Similar modifications can be assumed for the other embodiments.

In the following, inventions other than those described in the scope of claims ascertained from the examples are listed.
(B3) In the brake device according to claim 12,
The brake system according to claim 1, wherein the connection oil passage is an overlap portion in which the first counterbore overlaps the second counterbore.
(B4) In the brake device according to claim 12,
The brake device, wherein the connection oil passage is a third counterbore formed so as to straddle the first counterbore and the second counterbore.
(B5) In the brake device described in (B4) above,
The brake device according to claim 1, wherein a bottom portion of the reservoir accommodation hole and the third counterbore are circular, and their centers are coaxial.
(B6) In the brake device according to claim 12,
The brake device according to claim 1, wherein the opening of the first oil passage and the first counterbore are circular, and their centers are coaxial.
(B7) In the brake device according to claim 12,
The brake device according to claim 1, wherein the opening of the second oil passage and the second counterbore are circular, and the centers of the openings are coaxial.
(C3) In the brake device according to claim 13,
A connecting oil passage connecting the first counterbore and the second counterbore;
The brake system according to claim 1, wherein the connection oil passage is an overlap portion in which the first counterbore overlaps the second counterbore.

DESCRIPTION OF SYMBOLS 1 Brake apparatus 13a 1st oil path 13b 2nd oil path 131 1st space 132 2nd space 133 Connection oil path 2 Housing 22 Reservoir accommodation hole 22a Bottom part 22d Stopper 231 1st counterbore 232 2nd counterbore 233 Third counterbore 31 Piston 310 Crown surface 311 Contact part M / C Master cylinder P Pump

Claims (12)

A housing with a bottomed reservoir receiving hole inside;
A piston for stroking the reservoir housing hole and separating the reservoir housing hole into two chambers;
A first oil passage that will be connected to the opening and the master cylinder to the bottom of the reservoir housing hole,
A second oil passage that will be connected to the suction portion of the opening and the pump at the bottom of the reservoir housing hole,
A first counterbore formed at an opening edge of the first oil passage;
A second counterbore formed at the opening edge of the second oil passage;
The formed facing the crown surface of the piston, said first counterbore and said second counterbore and the brake device characterized by Ru and a connecting oil path connecting. The brake device according to claim 1, wherein
The brake system according to claim 1, wherein the connection oil passage is an overlap portion in which the first counterbore overlaps the second counterbore. The brake device according to claim 1, wherein
Said connecting oil passage, the brake system, characterized in that said first counterbore and said second third formed to straddle the counterbored of is repeated seat. The brake device according to claim 3,
The brake device according to claim 1, wherein a bottom portion of the reservoir accommodation hole and the third counterbore are circular, and their centers are coaxial. The brake device according to claim 1, wherein
The brake device according to claim 1, wherein the opening of the first oil passage and the first counterbore are circular, and their centers are coaxial. The brake device according to claim 5,
The brake device according to claim 1, wherein the opening of the second oil passage and the second counterbore are circular, and the centers of the openings are coaxial. A housing with a bottomed reservoir receiving hole inside;
A piston for stroking the reservoir housing hole and separating the reservoir housing hole into two chambers;
A first oil passage that will be connected to the opening and the master cylinder to the bottom of the reservoir housing hole,
A second oil passage that will be connected to the suction portion of the opening and the pump at the bottom of the reservoir housing hole,
Connecting said second oil passage and the first oil passage, and connecting oil passage formed facing the crown surface of the piston,
A stopper that contacts the piston and regulates the piston at a predetermined stroke position ;
When the piston contacts the stopper, the first oil passage and the second oil passage communicate with each other through the connection oil passage,
There is a contact portion that contacts the stopper on the crown surface of the piston, and the contact portion is an annular shape having a plurality of projecting portions projecting inwardly of the crown surface . A housing with a bottomed reservoir receiving hole inside;
A piston for stroking the reservoir housing hole and separating the reservoir housing hole into two chambers;
A first oil passage that will be connected to the opening and the master cylinder to the bottom of the reservoir housing hole,
A second oil passage that will be connected to the suction portion of the opening and the pump at the bottom of the reservoir housing hole,
A passage member interposed between the bottom of the reservoir accommodation hole and the piston;
Said passage is formed by a member, the braking device, characterized in that Ru and a connecting oil path connecting said second oil passage and the first oil passage. A housing with a bottomed reservoir receiving hole inside;
A pump provided in the housing and capable of sucking brake fluid in the reservoir accommodation hole;
A piston provided so as to be able to stroke in the reservoir accommodation hole so as to be positioned near the bottom of the reservoir accommodation hole at a top dead center;
A first oil passage that will be connected to the open master cylinder to the bottom of the reservoir housing hole,
A second oil passage that will be connected to the open suction portion of the pump on the bottom of the reservoir housing hole,
A first space formed in the opening of the first oil passage and constituting the oil passage;
A second space formed in the opening of the second oil passage and constituting the oil passage;
A connecting oil passage connecting the first space and the second space at least when the piston is located at a top dead center, and opening the first oil passage in a plane along the bottom of the reservoir accommodation hole When the direction perpendicular to the straight line connecting the part and the opening of the second oil passage is the width direction, the larger of the width direction dimension of the first space and the width direction dimension of the second space brake device according to claim <br/> also Ru and a said connecting oil passage having a small width dimension. The brake device according to claim 9,
The first space and the second space are a first countersink and a second countersink formed on the opening edge of the first oil passage and the opening edge of the second oil passage, respectively. Brake device characterized. A housing reservoir housing hole with a bottom formed therein,
A pump provided in the housing and capable of sucking brake fluid from the reservoir accommodation hole or from a master cylinder ;
A first oil passage that will be connected to open the master cylinder to the bottom of the reservoir housing hole,
A second oil passage that opens in the bottom of the reservoir housing hole Ru is connected to the suction portion of said pump,
A first counterbore formed at an opening edge of the first oil passage and constituting an oil passage;
A second counterbore formed on the opening edge of the second oil passage and constituting the oil passage ;
A piston provided in the reservoir housing hole, and provided with a strokeable stroke according to the amount of brake fluid in the reservoir housing hole;
A stopper provided in the reservoir accommodation hole and in contact with the piston when the piston is at a top dead center position , wherein the first countersink and the second countersink are in contact with the stopper. The stopper and the first oil passage and the second oil passage communicate with each other
Brake device characterized by Ru with a. The brake device according to claim 11,
A brake device comprising a third counterbore formed to straddle the first counterbore and the second counterbore.

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