HYDRAULIC PRESSURE CONTROL DEVICE AND BRAKING SYSTEM

Provided is a hydraulic pressure control device and a braking system capable of improving the productivity. The hydraulic pressure control device includes: a normally-closed electromagnetic valve, which includes a first valve part arranged so as to extend from a surface of a housing to an inside of the housing, and is configured to close an oil passage in the housing when a current is not supplied; and a normally-open electromagnetic valve, which includes a second valve part being arranged so as to extend from the surface of the housing to the inside of the housing, and including a common portion having a shape common to the first valve part, and is configured to open the oil passage in the housing when a current is not supplied.

TECHNICAL FIELD

The present invention relates to a hydraulic pressure control device and a braking system.

BACKGROUND ART

As a technology of this type, a technology described in Patent Literature 1 is disclosed. In Patent Literature 1, there is disclosed a technology including normally-open electromagnetic valves and normally-closed electromagnetic valves mounted to a base body (housing) in which flow passages (oil passages) are internally formed, and configured to open/close flows of brake fluid in the flow passages.

CITATION LIST

Patent Literature

SUMMARY OF INVENTION

Technical Problem

In the technology of Patent Literature 1, the normally-open electromagnetic valves and the normally-closed electromagnetic valves have structures different from each other, and dedicated components are thus specified respectively therefor. Productivity may thus degraded due to an increase in number of the components and working steps.

The present invention has been made in view of the above-mentioned problem, and therefore has an object to provide a hydraulic pressure control device and a braking system capable of improving the productivity.

Solution to Problem

According to a first embodiment of the present invention, there is provided a hydraulic pressure control device, including: a normally-closed electromagnetic valve, which includes a first valve part arranged so as to extend from a surface of a housing to an inside of the housing, and is configured to close an oil passage in the housing when a current is not supplied; and a normally-open electromagnetic valve, which includes a second valve part being arranged so as to extend from the surface of the housing to the inside of the housing, and including a common portion having a shape common to the first valve part, and is configured to open the oil passage in the housing when a current is not supplied.

According to a second embodiment of the present invention, there is provided a hydraulic pressure control device, including: a normally-closed electromagnetic valve, which includes a first valve part arranged so as to extend from a surface of a housing to an inside of the housing, and is configured to close an oil passage in the housing when a current is not supplied; and a normally-open electromagnetic valve, which includes a second valve part being arranged so as to extend from the surface of the housing to the inside of the housing, having an axial length set to be equal to an axial length of the first valve part, and including a common portion having a shape common to the first valve part, and is configured to open the oil passage in the housing when a current is not supplied.

According to a third embodiment of the present invention, there is provided a braking system, including: a first unit including a stroke simulator, into which brake fluid flowed out from the master cylinder flows, and which is configured to generate a simulated operation reaction force of a brake operation member; and a second unit integrally including: a hydraulic pressure source, which is provided inside the housing, and is configured to generate an operation hydraulic pressure for a wheel cylinder provided to a wheel via an oil passage; an electromagnetic switching valve, which is a normally-closed electromagnetic valve including a first valve part arranged so as to extend from a surface of the housing to an inside of the housing, and being configured to close when a current is not supplied, and is configured to permit an inflow of the brake fluid into the stroke simulator; an electromagnetic shutoff valve, which is a normally-open electromagnetic valve including a second valve part being arranged so as to extend from the surface of the housing to the inside of the housing, including a common portion having a shape common to the first valve part, and being configured to open when a current is not supplied, and is configured to switch a communication state of an oil passage between the master cylinder and the wheel cylinder; and a control unit, which is configured to drive the hydraulic pressure source, the electromagnetic shutoff valve, and the electromagnetic switching valve.

Thus, with the hydraulic pressure control device and the braking system according to the embodiments of the present invention, the productivity can be improved.

DESCRIPTION OF EMBODIMENTS

First Embodiment

FIG. 1is a schematic configuration diagram for illustrating a braking device of a first embodiment of the present invention.FIG. 2is a perspective for illustrating a part of the braking device of the first embodiment.

The braking device1is applied to an electrically driven vehicle. The electrically driven vehicle refers to, for example, a hybrid vehicle including a motor generator in addition to an engine, or an electric automobile including only a motor generator as a motor for driving wheels. In the electrically driven vehicle, regenerative braking, that is, breaking of the vehicle by regenerating electric energy from kinetic energy of the vehicle can be performed with use of a regenerative braking device including a motor generator. The braking device1is a hydraulic pressure braking device configured to apply friction braking forces through hydraulic pressures to wheels FL to RR of the vehicle. A brake operation unit is provided for each of the wheels FL to RR. The brake operation unit is a hydraulic pressure generation part including a wheel cylinder W/C. The brake operation unit is of, for example, a disc type, and includes a caliper (hydraulic brake caliper). The caliper includes a brake disc and brake pads. The brake disc is a brake rotor rotating integrally with a tire. The brake pads are arranged so as to have predetermined clearances to the brake disc, and are moved by the hydraulic pressures of the wheel cylinder W/C, to thereby come into contact with the brake disc. As a result, a friction braking force is generated. The braking device1includes two systems (primary P system and secondary S system) of brake pipes. The brake pipe type is, for example, an X-split pipe type. Other pipe types such as a front/rear-split pipe may be employed. Hereinafter, when a member correspondingly provided to the P system and a member correspondingly provided to the S system are distinguished from one other, suffixes P and S are added to respective reference symbols. The braking device1is configured to supply the brake fluid serving as working fluid (working oil) to each of the brake operation units through the brake pipes, to thereby generate hydraulic pressures (brake hydraulic pressures) in the wheel cylinders W/C. As a result, a hydraulic pressure braking force is applied to each of the wheels FL to RR.

The braking device1includes a first unit1A and a second unit1B. The first unit1A and the second unit1B are provided in a motor room isolated from a cabin of the vehicle, and are connected to each other by a plurality of pipes. The plurality of pipes include master cylinder pipes10M (primary pipe10MP and secondary pipe10MS), wheel cylinder pipes10W, a back pressure pipe10X, and a suction pipe10R. Each of the pipes10M,10W, and10X other than the suction pipe10R is a brake pipe made of metal (metal pipe), specifically, for example, a double-wound steel pipe. Each of the pipes10M,10W, and10X has straight portions and bent portions, and is arranged between ports while the direction is changed at the bent portions. Both ends of each of the pipes10M,10W, and10X include flared male pipe joints. The suction pipe10R is a brake hose (hose pipe) made of a material such as rubber so as to be flexible. Ends of the suction pipe10R are connected to a port873and the like by nipples10R1and10R2. The nipples10R1and10R2are resin connection members including pipe portions.

A brake pedal100is a brake operation member configured to receive an input of a brake operation by a driver. A pushrod101is connected to the brake pedal100in a rotatable manner. The first unit1A is a brake operation unit mechanically connected to the brake pedal100, and is a master cylinder unit including a master cylinder5. The first unit1A includes a reservoir tank4, a housing7, the master cylinder5, a stroke sensor94, and a stroke simulator6. The reservoir tank4is a brake fluid source for reserving the brake fluid, and is a low-pressure part opened to the atmospheric pressure. Supplement ports40and a supply port41are formed in the reservoir tank4. The suction pipe10R is connected to the supply port41. The housing7is a casing for accommodating (build in) the master cylinder5and the stroke simulator6therein. A cylinder70for the master cylinder5, a cylinder71for the stroke simulator6, and a plurality of oil passages (liquid passages) are formed in the housing7. The plurality of oil passages include supplement oil passages72, supply oil passages73, and a positive pressure oil passage74. A plurality of ports are formed in the housing7, and those ports are opened in outer surfaces of the housing7. The plurality of ports include supplement ports75P and75S, supply ports76, and a back pressure port77. The supplement ports75P and75S are connected to supplement ports40P and40S of the reservoir tank4, respectively. The master cylinder pipes10M are connected to the supply ports76, and the back pressure pipe10X is connected to the back pressure port77. One end of the supplement oil passage72is connected to the supplement port75, and another end is connected to the cylinder70.

The master cylinder5is a first hydraulic pressure source capable of supplying an operation hydraulic pressure to the wheel cylinders W/C, is connected to the brake pedal100by the pushrod101, and is operated in accordance with an operation on the brake pedal100by the driver. The master cylinder5includes a piston51which is moved in an axial direction in accordance with the operation on the brake pedal100. The piston51is accommodated in the cylinder70, and defines hydraulic pressure chambers50. The master cylinder5is of a tandem type, and includes a primary piston51P connected to the pushrod101and a secondary piston51S of a free piston type in series as pistons51. A primary chamber50P is defined by the pistons51P and51S, and a secondary chamber50S is defined by the secondary piston51S. One end of the supply oil passage73is connected to the hydraulic pressure chamber50, and another end is connected to the supply port76. Each of the hydraulic pressure chambers50P and50S is supplemented with the brake fluid from the reservoir tank4to generate a hydraulic pressure (master cylinder hydraulic pressure) through the movement of the piston51. A coil spring52P serving as a return spring is interposed between both the pistons51P and51S in the primary chamber50P. A coil spring52S serving as a return spring is interposed between a bottom portion of the cylinder70and the piston51S in the secondary chamber50S. A stroke sensor94is configured to detect a stroke (pedal stroke) of the primary piston51P. A magnet for detection is provided in the primary piston51P, and a sensor main body is mounted to an outer surface of the housing7of the first unit1A.

The stroke simulator6is operated in accordance with the brake operation by the driver, and is configured to apply a reaction force and a stroke to the brake pedal100. The stroke simulator6includes a piston61, a positive pressure chamber601and a back pressure chamber602defined by the piston61, and elastic bodies (first spring64, second spring65, and damper66) configured to urge the piston61in a direction in which the volume of the positive pressure chamber601decreases. A retainer member62having a bottomed tubular shape is interposed between the first spring64and the second spring65. One end of a positive pressure oil passage74is connected to a supply oil passage73S on the secondary side, and another end is connected to the positive pressure chamber601. The pedal stroke is generated by inflow of the brake fluid from the master cylinder5(secondary chamber50S) to the positive pressure chamber601in accordance with the brake operation by the driver, and a reaction force against a brake operation by the driver is generated by the urging force of the elastic body. The first unit1A does not include an engine negative pressure booster configured to boost the brake operation force through use of an intake negative pressure generated in the engine of the vehicle.

The second unit1B is a hydraulic pressure control device provided between the first unit1A and the brake operation units. The second unit1B is connected to the primary chamber50P by the primary pipe10MP, is connected to the secondary chamber50S by the secondary pipe10MS, is connected to the wheel cylinders W/C by the wheel cylinder pipes10W, and is connected to the back pressure chamber602by the back pressure pipe10X. Moreover, the second unit1B is connected to the reservoir tank4by the suction pipe10R. The second unit1B includes a housing8, a motor20, a pump3, a plurality of electromagnetic valves21, a plurality of hydraulic pressure sensors91, and an electronic control unit90(hereinafter referred to as “ECU”). The housing8is a casing for accommodating (build in) the pump3, valve bodies of the electromagnetic valves21, and the like therein. Circuits (brake hydraulic pressure circuits) of the two systems (P system and S system), through which the brake fluid circulates, are formed of a plurality of oil passages in the housing8. The plurality of oil passages include supply oil passages11, a suction oil passage12, discharge oil passages13, a pressure regulating oil passage14, pressure reducing oil passages15, a back pressure oil passage16, a first simulator oil passage17, and a second simulator oil passage18. Moreover, a reservoir (internal reservoir)120, which is a liquid reservoir, and a damper130are formed in the housing8. A plurality of ports are formed in the housing8, and those ports are opened in outer surfaces of the housing8. The plurality of ports include master cylinder ports871(primary ports871P and secondary ports871S), a suction port873, a back pressure port874, and wheel cylinder ports872. The primary pipe10MP, the secondary pipe10MS, the suction pipe10R, the back pressure pipe10X, and the wheel cylinder pipes10W are mounted and connected to the primary port871P, the secondary port871S, the suction port873, the back pressure port874, and the wheel cylinder ports872, respectively.

The motor20is an electric motor of a rotation type, and includes a rotation shaft configured to drive the pump3. The motor20may be a brushless motor or a brush motor. The motor20includes a resolver configured to detect a rotation angle of the rotation shaft. The resolver functions as a number-of-revolution sensor configured to detect the number of revolutions of the motor20. The pump3is a hydraulic pressure source capable of supplying an operation hydraulic pressure to the wheel cylinders W/C, and includes five pump parts driven by the single motor20. The pump3is used for the S system and the P system in common. Each of the electromagnetic valves21and the like is a solenoid valve configured to operate in accordance with a control signal. A valve body is configured to perform a stroke in accordance with a current supply to the solenoid to switch opening and closing of an oil passage (open/close the oil passage). Each of the electromagnetic valves21and the like controls the communication state of the circuit and adjusts the circulation state of the brake fluid to generate a control hydraulic pressure. The plurality of electromagnetic valves21and the like include shutoff valves21, pressure boosting valves (hereinafter referred to as “SOL/V IN”)22, communication valves23, a pressure regulating valve24, pressure reducing valves (hereinafter referred to as “SOL/V OUT”)25, a stroke simulator-in valve (hereinafter referred to as “SSN IN”)27, and a stroke simulator-out valve (hereinafter referred to as “SS/V OUT”)28. Each of the shutoff valve21, the SOLN IN22, and the regulating valve24is a normally-open electromagnetic valve which is opened in a non-current supply state. Each of the communication valve23, the pressure reducing valve25, the SS/V IN27, and the SS/V OUT28is a normally-closed electromagnetic valve, which is closed in the non-current supply state. Each of the shutoff valve21, the SOL/V IN22, and the pressure regulating valve24is a proportional control valve which has an opening degree adjusted in accordance with the current supplied to the solenoid. Each of the communication valve23, the pressure reducing valve25, the SS/V N27, and the SSN OUT28is an ON/OFF valve which is subjected to binary switching control between an opening state and a closing state. A proportional control valve may be used for each of those valves. Each of the hydraulic pressure sensor91and the like is configured to detect a discharge pressure of the pump3or a master cylinder hydraulic pressure. The plurality of hydraulic pressure sensors include a master cylinder hydraulic pressure sensor91, a discharge pressure sensor93, and wheel cylinder hydraulic pressure sensors92(primary pressure sensor92P and secondary pressure sensor92S).

Now, based onFIG. 1, description is given of the brake hydraulic pressure circuit of the second unit1B. For members corresponding to the respective wheels FL to RR, suffixes of “a” to “d” are added to respective reference symbols for proper distinction. One end side of a supply oil passage11P is connected to the primary port871P. Another end side of the supply oil passage11P is branched into an oil passage11afor a front left wheel and an oil passage11dfor a rear right wheel. Each of the oil passages11aand11dis connected to the corresponding wheel cylinder port872. One end side of a supply oil passage11S is connected to the secondary port871S. Another end side of the supply oil passage11S is branched into an oil passage11bfor the front right wheel and an oil passage11cfor the rear left wheel. Each of the oil passages11band11cis connected to the corresponding wheel cylinder port872. The shutoff valve21is provided on the one end side of each of the supply oil passages11. The SOL/V IN22is provided on the another end side of each of the oil passages11. A bypass oil passage110configured to bypass the SOL/V IN22is provided in parallel with each of the oil passages11. A check valve220is provided in the bypass oil passage110. The check valve220permits only a flow of the brake fluid from the wheel cylinder port872to the master cylinder port871.

The suction oil passage12connects the reservoir120and suction ports823of the pump3to each other. One end side of the discharge oil passage13is connected to discharge ports821of the pump3. Another end side of the discharge oil passage13is branched into the oil passage13P for the P system and the oil passage13S for the S system. Each of the oil passages13P and13S connects the shutoff valve21in the supply oil passage11and the SOL/V IN22to each other. A damper130is provided on the one end side of the discharge oil passage13. The communication valve23is provided in each of the oil passages13P and13S on the another end side. The respective oil passages13P and13S function as communication passages for connecting the supply oil passage11P in the P system and the supply oil passage11S in the S system to each other. The pump3is connected to the respective wheel cylinder ports872by the communication passages (discharge oil passages13P and13S) and the supply oil passages1113and11S. The pressure regulating oil passage14connects an intermediate portion of the discharge oil passages13between the damper130and the communication valves23and the reservoir120to each other. The pressure regulating valve24is provided in the pressure regulating passage14. The pressure reducing oil passage15connects an intermediate portion between the SOLN IN22in each of the oil passages11ato11dof the supply oil passage11and the wheel cylinder port872and the reservoir120to each other. The SOL/V OUT25is provided in the pressure reducing oil passage15.

One end side of the back pressure oil passage16is connected to the back pressure port874. Another end side of the back pressure oil passage16is branched into a first simulator oil passage17and a second simulator oil passage18. The first simulator oil passage17connects the shutoff valve21S in the supply oil passage11S and the SOL/V IN22band22cto each other. The SSN IN27is provided in the first simulator oil passage17. A bypass oil passage170configured to bypass the SS/V IN27is provided in parallel with the first simulator oil passages17. A check valve270is provided in the bypass oil passage170. The check valve270permits only a flow of the brake fluid from the back pressure oil passage16to the supply oil passage11S. The second simulator oil passage18is connected to the reservoir120. The SS/V OUT28is provided in the second simulator oil passage18. A bypass oil passage180configured to bypass the SS/V OUT28is provided in parallel with the second simulator oil passages18. A check valve280is provided in the bypass oil passage180. The check valve280permits only a flow of the brake fluid from the reservoir120to the back pressure oil passage16.

A hydraulic pressure sensor91configured to detect a hydraulic pressure (hydraulic pressure in the positive pressure chamber601of the stroke simulator6, or the master cylinder hydraulic pressure) at an intermediate position between the shutoff valve21S in the supply oil passage11S and the secondary port871S is provided at this position. A hydraulic pressure sensor92configured to detect a hydraulic pressure (corresponding to the wheel cylinder hydraulic pressure) at a point between the shutoff valve21in the supply oil passage11and the SOL/V INs22is provided at this point. A hydraulic pressure sensor93configured to detect a hydraulic pressure (pump discharge pressure) at a point between the damper130in the discharge oil passage13and the communication valves23is provided at this point.

Hereinafter, for convenience of description, a three-dimensional Cartesian coordinate system including an X axis, a Y axis, and a Z axis is given. In a state in which the first unit1A and the second unit1B are mounted to the vehicle, a Z-axis direction is the vertical direction, and a positive side in the Z-axis direction is a top side in the vertical direction. An X-axis direction is a front/rear direction of the vehicle, and a positive side in the X-axis direction is the vehicle front side. A Y-axis direction is a lateral direction of the vehicle.

In the first unit1A, the pushrod101extends from the end on a negative side in the X-axis direction, which is connected to the brake pedal100, to the positive side in the X-axis direction. A rectangular flange part78is provided at an end on the negative side in the X-axis direction of the housing7. Bolt holes are formed in four corners of the flange part78. A bolt B1passes through the bolt hole for fixing and mounting the first unit1A to a dash panel on a vehicle body side. The reservoir tank4is provided on the positive side in the Z-axis direction of the housing7.

The housing8is a block having an approximately rectangular parallelepiped shape made of aluminum alloy as a material in the second unit1B. Outer surfaces of the housing8include a front surface801, a rear surface802, a top surface803, a bottom surface804, a right side surface805, and a left side surface806(refer toFIG. 3andFIG. 4). The recessed parts807and808are formed at the corners of the housing8on the front surface801side and the top surface803side. The housing8is fixed to a vehicle body side (a bottom surface of the motor room) via the mount102. Insulators103and104are interposed between the housing8and the mount102. The motor20is arranged on the front surface801of the housing8, and the motor housing200is mounted. An ECU90is mounted to the rear surface802of the housing8. In other words, the ECU90is integrally provided to the housing8. The ECU90includes a control board (not shown) and a control unit housing (case)901. The control board is configured to control current supply states to the motor20and the solenoids such as the electromagnetic valves21. Various sensors configured to detect a motion state of the vehicle such as an acceleration sensor configured to detect an acceleration of the vehicle and an angular velocity sensor configured to detect an angular velocity (yaw rate) of the vehicle may be mounted on the control board. Moreover, a complex sensor (combined sensor) in which those sensors are combined as a unit may be mounted on the control board. The control board is accommodated in the case901. The case901is a cover member fixed to the rear surface802of the housing8through fastening with bolts.

The case901is a cover member made of a resin material, and includes a board accommodating part902and a connector part903. The board accommodating part902is configured to accommodate the control board and a part of the solenoids such as the electromagnetic valves21. The connector part903is arranged on a positive side in the X-axis direction with respect to the terminals and the conductive members in the board accommodating part902, and protrudes on a positive side in the Y-axis direction of the board accommodating part902. The connector part903is arranged more or less on the outside (on the positive side in the X-axis direction) with respect to the left side surface806of the housing8as viewed from the X-axis direction. Terminals of the connector part903are exposed toward the positive side in the Y-axis direction, and extend to a negative side in the Y-axis direction so as to be connected to the control board. Each of the terminals (exposed toward the positive side in the Y-axis direction) of the connector part903can be connected to external devices and the stroke sensor94(hereinafter referred to as “external devices and the like”). Electrical connections between the external devices and the like and the control board (ECU90) are established when another connector to be connected to the external devices and the like is inserted into the connector part903from the positive side in the Y-axis direction. Moreover, a current is supplied from an external power supply (battery) to the control board via the connector part903. The conductive members function as a connection part for electrically connecting the control board and (a stator of) the motor20to each other, and a current is supplied to (the stator of) the motor20from the control board via the conductive members.

FIG. 3toFIG. 4are views for transparently illustrating passages, recessed parts, and holes of the housing8.FIG. 3is a rear transparent view for illustrating the housing8as viewed from the negative side in the Y-axis direction.FIG. 4is a right side view in which the second unit1B is viewed from the positive side in the X-axis direction, for illustrating the passages and the like transparently though the housing8.

The housing8includes a cam accommodating hole81, the plurality of (five) cylinder accommodating holes82A to82E, a reservoir chamber830, a damper chamber831, a liquid reservoir chamber832, a plurality of valve body accommodating holes (mounting hole)84x(x represents 1 to 5, 7, and 8), a plurality of sensor accommodating holes85x(x represents 1 to 3), a power supply hole86, a plurality of ports87x(x represents 1 to 4), a plurality of oil passage holes88x(x represents −1 y to −5y, 0, and 1), and a plurality of bolt holes (pin holes)89x(x represents 1 to 5). Those holes and ports are formed by drills and the like. The cam accommodating hole81has a bottomed tubular shape extending in the Y-axis direction, and is opened in the front surface801. An axial center O of the cam accommodating hole81is approximately at a center in the X-axis direction on the front surface801, and is present more or less on the negative side in the Z-axis direction with respect to a center in the Z-axis direction.

The cylinder accommodating hole82has a stepped tubular shape, and extends in a radial direction (radiation direction about the axial center O) of the cam accommodating hole81. The cylinder accommodating holes82are formed approximately equiangularly (at approximately equal intervals) in a circumferential direction about the axial center O. An angle formed by the axial centers of the cylinder accommodating holes82which are adjacent to each other in the circumferential direction of the axial center O is approximately 72° (in a predetermined range including 72°). The plurality of cylinder accommodating holes82A to82E are arranged in a single row along the Y-axis direction, and are formed on the positive side in the Y-axis direction of the housing8. The reservoir chamber830has a bottomed tubular shape, which has an axial center extending in the Z-axis direction, and is opened approximately at a center in the X-axis direction and at a center in the Y-axis direction on the top surface803. The reservoir chamber830is arranged in a region surrounded by the master cylinder ports871and the wheel cylinder ports872. (A bottom part on the negative side in the Z-axis direction of) the reservoir chamber830is arranged on the positive side in the Z-axis direction with respect to the suction ports823of the respective cylinder accommodating holes82. The reservoir chamber830is formed in a region between the cylinder accommodating holes82A and82E which are adjacent to each other in the circumferential direction of the axial center O. The cylinder accommodating holes82A to82E and the reservoir chamber830partially overlap with each other in the Y-axis direction (as viewed from the X-axis direction). The damper chamber831has a bottomed tubular shape, which has an axial center extending in the Z-axis direction, and is opened approximately at the center in the X-axis direction and more or less on the negative side in the Y-axis direction with respect to the center in the Y-axis direction on the bottom surface804. The damper chamber831is arranged on the negative side in the Z-axis direction with respect to the cam accommodating hole81. The liquid reservoir chamber832has a stepped bottomed tubular shape, which has an axial center extending in the Z-axis direction, and is opened on the negative side in the X-axis direction and the positive side in the Y-axis direction in the bottom surface804. The liquid reservoir chamber832is arranged on the negative side in the Z-axis direction with respect to the cam accommodating hole81. The liquid reservoir chamber832has a large-diameter part832lon a side closer to the bottom surface804(negative side in the Z-axis direction), a small-diameter part832son a side farther from the bottom surface804(positive side in the Z-axis direction), and a medium-diameter part832mbetween the large-diameter part832land the small-diameter part832s.

Each of the plurality of the valve body accommodating holes84xhas a stepped tubular shape, extends in the Y-axis direction, and is opened in the rear surface802. Each of the plurality of the valve body accommodating holes84xhas a large-diameter part on a side closer to the rear surface802(negative side in the Y-axis direction), a small-diameter part on a side farther from the rear surface802(outer side in the positive side in the Y-axis direction), and a medium-diameter part between the large-diameter part and the small-diameter part. The plurality of valve body accommodating holes84xare arranged in a single row along the Y-axis direction, and are formed on the negative side in the Y-axis direction of the housing8. The cylinder accommodating holes82and the valve body accommodating holes84xare arrayed along the Y-axis direction. The plurality of the valve body accommodating holes84xat least partially overlap with the cylinder accommodating holes82as viewed from the Y-axis direction. Most of the plurality of the valve body accommodating holes84xare contained in a circle connecting the ends on the large-diameter part side (side farther from the axial center O) of the plurality of cylinder accommodating holes82to each other. In other words, an outer periphery of this circle and the valve body accommodating holes84xat least partially overlap with each other.

The SOL/V OUT25is accommodated in the SOL/V OUT accommodating hole845. The bypass oil passage1100and the check valve220are formed of, for example, a seal member, which has a cup shape and is provided in the hole842. The SOL/V OUT accommodating holes845ato845dare arranged in a single row in the X-axis direction on the positive side in the Z-axis direction of the rear surface802. Two SOL/V OUT accommodating holes in the P system are formed on the positive side in the X-axis direction. Two SOL/V OUT accommodating holes in the S system are formed on the negative side in the X-axis direction. In the P system, the hole845ais formed on the positive side in the X-axis direction with respect to the hole845d. In the S system, the hole845bis formed on the negative side in the X-axis direction with respect to the hole845c. The SOL/V IN22is accommodated in the SOL/V IN accommodating hole842. The SOL/V IN accommodating holes842ato842dare arranged in a single row in the X-axis direction more or less on the positive side in the Z-axis direction with respect to the axial center O (or at the center in the Z-axis direction of the housing8). The SOL/V IN accommodating hole842is adjacent to the SOL/V OUT accommodating hole845on the negative side in the Z-axis direction. Two SOL/V IN accommodating holes in the P system are formed on the positive side in the X-axis direction. Two SOL/V IN accommodating holes in the S system are formed on the negative side in the X-axis direction. In the P system, the hole842ais formed on the positive side in the X-axis direction with respect to the hole842d. In the S system, the hole842bis formed on the negative side in the X-axis direction with respect to the hole842c. The axial centers of the holes842ato842dare approximately at the same positions in the X-axis direction as the axial centers of the holes845ato845d, respectively.

The shutoff valve21is accommodated in the shutoff valve accommodating hole841. The shutoff valve accommodating holes841P and841S are arrayed in the X-axis direction more or less on the negative side in the Z-axis direction with respect to the center in the Z-axis direction of the housing8. The hole841P is formed more or less on the positive side in the X-axis direction with respect to a center in the X-axis direction. The hole841S is formed more or less on the negative side in the X-axis direction with respect to the center in the X-axis direction. Axial centers of the holes841P and841S are slightly on the negative side in the Z-axis direction with respect to the axial center O, and are at approximately the same positions in the X-axis direction as the axial centers of the holes842dand842c. The communication valve23is accommodated in the communication valve accommodating hole843. The communication valve accommodating holes843P and843S are arrayed in the X-axis direction on the negative side in the Z-axis direction with respect to the axial center O. The communication valve accommodating hole843is adjacent to the shutoff valve accommodating hole841on the negative side in the Z-axis direction. The hole843P is formed on the positive side in the X-axis direction with respect to the center in the X-axis direction. The hole843S is formed on the negative side in the X-axis direction with respect to the center in the X-axis direction. An axial center of the hole843P is slightly on the negative side in the X-axis direction with respect to the axial center of the hole842a. An axial center of the hole843S is slightly on the positive side in the X-axis direction with respect to the axial center of the hole842b. An end on the positive side in the Z-axis direction of the opening of the communication valve accommodating hole843overlaps with an end on the negative side in the Z-axis direction of the opening of the shutoff valve accommodating hole841in the Z-axis direction (as viewed from the X-axis direction) on the rear surface802. The pressure regulating valve24is accommodated in the pressure regulating valve accommodating hole844. The pressure regulating valve accommodating hole844is formed on the negative side in the Z-axis direction with respect to the axial center O, and is formed at approximately the same position in the X-axis direction as the axial center O. The pressure regulating valve accommodating hole844is formed between the communication valve accommodating holes843P and843S in the X-axis direction, and is adjacent to the shutoff valve accommodating holes841on the negative side in the Z-axis direction. The pressure regulating valve accommodating hole844is at approximately the same position in the Z-axis direction as the communication valve accommodating holes843, and is arrayed together with the holes843P and843S in a single row in the X-axis direction. Both ends in the X-axis direction of the opening of the pressure regulating valve accommodating hole844overlap with ends in the X-axis direction of the openings of the shutoff valve accommodating holes841in the X-axis direction (as viewed from the Z-axis direction) on the rear surface802.

The SS/V IN27is accommodated in the SS/V IN accommodating hole847. The bypass oil passage170and the check valve270are each formed of, for example, a seal member, which has a cup shape and is provided in the hole847. The SS/V OUT28is accommodated in the SS/V OUT accommodating hole848. The bypass oil passage180and the check valve280are formed of a seal member, which has a cup shape and is provided in the hole848. The holes847and848are arrayed in the X-axis direction on the negative side in the Z-axis direction with respect to the axial center O. The holes847and848are adjacent to the communication valve accommodating holes843and the pressure regulating valve accommodating holes844on the negative side in the Z-axis direction. An axial center of the hole848is positioned between the axial center of the hole844and the axial center of the hole843P in the X-axis direction, and is positioned more or less on the positive side in the X-axis direction with respect to an axial center of the hole841P. An end on the positive side in the X-axis direction of the opening of the hole848overlaps with an end on the negative side in the X-axis direction of the opening of the hole843P in the X-axis direction (as viewed from the Z-axis direction) on the rear surface802. An end on the positive side in the Z-axis direction of the opening of the hole848overlaps with an end on the negative side in the Z-axis direction of the opening of the hole843P in the Z-axis direction (as viewed from the Y-axis direction). An axial center of the hole847is positioned between the axial center of the hole844and the axial center of the hole843S in the X-axis direction, and is positioned more or less on the negative side in the X-axis direction with respect to an axial center of the hole841S. An end on the negative side in the X-axis direction of the opening of the hole847overlaps with an end on the positive side in the X-axis direction of the opening of the hole843S in the X-axis direction (as viewed from the Z-axis direction) on the rear surface802. An end on the positive side in the Z-axis direction of the opening of the hole847overlaps with an end on the negative side in the Z-axis direction of the opening of the hole843S in the Z-axis direction (as viewed from the Y-axis direction).

Each of the plurality of sensor accommodating holes85xhas a bottomed tubular shape, which has an axial center extending in the Y-axis direction, and is opened in the rear surface802. A pressure sensitive part of the master cylinder pressure sensor91is accommodated in a master cylinder pressure sensor accommodating hole851. The hole851is formed at approximately at the center in the X-axis direction and approximately at the center in the Z-axis direction of the housing8, and an axial center of the hole851is more or less on the positive side in the Z-axis direction with respect to the axial center O. The holes851are formed in a region surrounded by the holes842,845,841P, and841S. A pressure sensitive part of the discharge pressure sensor93is accommodated in a discharge pressure sensor accommodating hole853. The hole853is formed approximately at the center in the X-axis direction and on the negative side in the Z-axis direction of the housing8, and an axial center of the hole853is slightly on the negative side in the Z-axis direction with respect to the holes847and848. The hole853is formed in a region surrounded by the holes844,847, and848. A pressure sensitive part of the wheel cylinder hydraulic pressure sensor92is accommodated in a wheel cylinder hydraulic pressure sensor accommodating hole852. The holes852P and852S are arrayed in the X-axis direction at approximately the same positions in the Z-axis direction as the axial center O. The hole852P is formed on the positive side in the X-axis direction with respect to the center in the X-axis direction. The hole852S is formed on the negative side in the X-axis direction with respect to the center in the X-axis direction. An axial center of the hole852P is slightly on the positive side in the X-axis direction with respect to the axial center of the hole842a. An axial center of the hole852S is slightly on the negative side in the X-axis direction with respect to the axial center of the hole842b. The hole852is formed in a region surrounded by the holes841,842, and843. The power supply hole86has a tubular shape, and passes through the housing8(between the front surface801and the rear surface802) in the Y-axis direction. The hole power supply86is formed approximately at the center in the X-axis direction and on the positive side in the Z-axis direction of the housing8. The hole power supply86is formed in a region surrounded by the holes842cand842dand the holes845cand845d, and in a region between the cylinder accommodating holes82A and82E which are adjacent to each other.

Each of the master cylinder ports871has a bottomed tubular shape, which has an axial center extending in the Y-axis direction, and is opened in a portion at an end on the positive side in the Z-axis direction between the recessed parts807and808on the front surface801. A primary port871P is formed on the positive side in the X-axis direction. The secondary port871S is formed on the negative side in the X-axis direction. Both the ports871P and871S are arrayed in the X-axis direction, and are on both sides of the reservoir chamber830and a bolt hole891in the X-axis direction (as viewed from the Y-axis direction). The ports871P and871S are formed respectively between the reservoir chamber830and the cylinder accommodating holes82A and82E in the circumferential direction of the axial center O (as viewed from the Y-axis direction). Openings of the master cylinder ports871and an opening of the bolt hole891partially overlap with each other in the Z-axis direction (as viewed from the X-axis direction). Each of the wheel cylinder ports872has a bottomed tubular shape, which has an axial center extending in the Z-axis direction, and is opened on the negative side in the Y-axis direction (position closer to the rear surface802than to the front surface801) in the top surface803. The ports872ato872dare arranged in a single row in the X-axis direction. Two ports in the P system are formed on the positive side in the X-axis direction. Two ports in the S system are formed on the negative side in the X-axis direction. In the P system, the port872ais formed on the positive side in the X-axis direction with respect to the port872d. In the S system, the port872bis formed on the negative side in the X-axis direction with respect to the port872c. The ports872cand872dare on both sides of the suction port873(reservoir chamber830) as viewed from the Y-axis direction. An opening of each of the ports872and the suction port873(opening of the reservoir chamber830) partially overlap with each other in the X-axis direction (as viewed from the Y-axis direction). The opening of each of the ports872and an opening of the suction port873partially overlap with each other in the Y-axis direction (as viewed from the X-axis direction).

The suction port873is the opening of the reservoir chamber830on the top surface803, is formed so as to be directed to the top side in the vertical direction, and is opened on the top side in the vertical direction. The port873is opened at a position on a center side in the X-axis direction and on a center side in the Y-axis direction closer to the front surface801than the wheel cylinder ports872on the top surface803. The port873is formed on the positive side in the Z-axis direction with respect to the suction ports823of the cylinder accommodating holes82A to82E. The cylinder accommodating holes82A and82E are on both sides of the port873as viewed from the Y-axis direction. An opening of each of the cylinder accommodating holes82A and82E and the port873partially overlap with each other in the Y-axis direction (as viewed from the X-axis direction). The back pressure port874has a bottomed tubular shape, which has an axial center extending in the X-axis direction, and is opened more or less on the negative side in the Y-axis direction and on the negative side in the Z-axis direction with respect to the axial center O on the right side surface805. The axial center of the port874is positioned between an axial center of the communication valve accommodating hole843and an axial center of the SS/V OUT accommodating hole848in the Z-axis direction.

The plurality of oil holes88x include first to fifth hole groups88-ly to88-5yand oil passage holes880and881. The first hole group88-ly connects the master cylinder ports871, the shutoff valve accommodating holes841, and the master cylinder pressure sensor accommodating hole851to one another. The second hole group88-2yconnects the shutoff valve accommodating holes841, the communication valve accommodating holes843, the SOL/V IN accommodating holes842, the SS/V IN accommodating hole847, and the wheel cylinder pressure sensor accommodating holes852to one another. The third hole group88-3yconnects the discharge ports821of the cylinder accommodating holes82, the communication valve accommodating holes843, the pressure regulating valve accommodating holes844, and the discharge pressure sensor accommodating hole853to one another. The fourth hole group88-4yconnects the reservoir chamber830, the suction ports823of the cylinder accommodating holes82, the SOL/V OUT accommodating holes845, the SSN OUT accommodating hole848, and the pressure regulating valve accommodating hole844to one another. The fifth hole group88-5yconnects the back pressure port874, the SSN IN accommodating hole847, and the SS/V OUT accommodating hole848to one another. Each of the oil holes880connects the SOLN IN accommodating hole842and the wheel cylinder port872to each other. The oil passage hole881connects the cam accommodating hole81and the liquid reservoir chamber832to each other.

The first hole group88-1yincludes first holes88-11to seventh holes88-17. First, description is given of the P system. The first hole88-11P extends from a bottom part of the primary port871P to the negative side in the Y-axis direction. The second hole88-12P extends from the right side surface805to the negative side in the X-axis direction, and is connected to the first hole88-11P. The third hole88-13P extends from the rear surface802to the positive side in the Y-axis direction, and is connected to the second hole88-12P. The fourth hole88-14P extends from the positive side in the Y-axis direction of the third hole88-13P to the negative side in the Z-axis direction. The fifth hole88-15P extends from the rear surface802to the positive side in the Y-axis direction, and is connected to the fourth hole88-14P. The sixth hole88-16P extends from an end on the positive side in the Y-axis direction of the fifth hole88-15P to the positive side in the X-axis direction, the negative side in the Y-axis direction, and the negative side in the Z-axis direction, and is connected to the medium-diameter part of the shutoff valve accommodating hole841P. The seventh hole88-17extends from the left side surface806to the positive side in the X-axis direction, is connected to the fifth hole88-15P, and is connected to the master cylinder pressure sensor accommodating hole851. The S system is symmetrical with the P system about the center in the X-axis direction of the housing8except that the seventh hole88-17is not included.

The second hole group88-2includes first holes88-21to seventh holes88-27. First, description is given of the P system. The first hole88-21P extends over a short distance from a bottom part of the shutoff valve accommodating holes841to the positive side in the Y-axis direction. The second hole88-22P extends from the right side surface805to the negative side in the X-axis direction, and is connected to the first hole88-21P. The third hole88-23P extends from the top surface803to the negative side in the Z-axis direction, and is connected to the second hole88-22P on the positive side in the X-axis direction. The fourth hole88-24P extends from the right side surface805to the negative side in the X-axis direction, and is connected to an intermediate portion of the third hole88-23P. The fifth holes88-25aand88-25dextend over short distances from the positive side in the X-axis direction of the fourth hole88-24P to the positive side in the Y-axis direction, and are connected to bottom parts of the SOL/V IN accommodating holes842aand842d, respectively. The sixth hole88-26P extends from an intermediate portion of the second hole88-22P to the negative side in the Y-axis direction and the negative side in the Z-axis direction, and is connected to the medium-diameter part of the communication valve accommodating hole843P. The seventh hole88-27P extends from a bottom part of the wheel cylinder hydraulic pressure sensor accommodating hole852P to the positive side in the Y-axis direction, and is connected to an intermediate portion of the second hole88-22P. The S system is symmetrical with the P system about the center in the X-axis direction of the housing8except that the eighth hole88-28is included. The eighth hole88-28extends from the negative side in the X-axis direction of the bottom surface804to the positive side in the Z-axis direction, is connected to the medium-diameter part of the SS/V IN accommodating hole847, and is connected to the medium-diameter part of the communication valve accommodating hole843S.

The third hole group88-3yincludes a first hole88-31to a twelfth hole88-312. The first hole88-31extends from the discharge port821of the cylinder accommodating hole82A to the negative side in the Z-axis direction. The second hole88-32extends from an end of the first hole88-31to the negative side in the X-axis direction and the negative side in the Z-axis direction, and is connected to the discharge port821of the cylinder accommodating hole82B. The third hole88-33extends from the discharge port821of the cylinder accommodating hole82B to the positive side in the X-axis direction and the negative side in the Z-axis direction. The fourth hole88-34extends from an end of the third hole88-33to the positive side in the X-axis direction and the negative side in the Z-axis direction, and is connected to the discharge port821of the cylinder accommodating hole82C. The fifth hole88-35extends from the discharge port821of the cylinder accommodating hole82C to the positive side in the X-axis direction and the positive side in the Z-axis direction. The sixth hole88-36extends from an end of the fifth hole88-35to the positive side in the X-axis direction and the positive side in the Z-axis direction, and is connected to the discharge port821of the cylinder accommodating hole82D. The seventh hole88-37extends from the discharge port821of the cylinder accommodating hole82D to the negative side in the X-axis direction and the positive side in the Z-axis direction. The eighth hole88-38extends from an end of the seventh hole88-37to the positive side in the Z-axis direction, and is connected to the discharge port821of the cylinder accommodating hole82E. The ninth hole88-39extends from a bottom part of the discharge pressure sensor accommodating hole853to the positive side in the Y-axis direction, is connected to the damper chamber831, and is connected to the discharge port821of the cylinder accommodating hole82C. The tenth hole88-310extends from a bottom part of the damper chamber831to the positive side in the Z-axis direction. The eleventh hole88-311extends from the right side surface805to the negative side in the X-axis direction, is connected to bottom parts of both of the communication valve accommodating holes843, and is connected to an end of the tenth hole88-310. The twelfth hole88-312(not shown) extends over a short distance from a bottom part of the pressure regulating valve accommodating hole844to the positive side in the Y-axis direction, and is connected to the eleventh hole88-311.

The fourth hole group88-4yincludes a first hole88-41to a ninth hole88-49. The first hole88-41extends from the left side surface806to the positive side in the X-axis direction, is connected to a bottom part of the reservoir chamber830, and is connected to bottom parts of the SOL/V OUT accommodating holes845. The second hole88-42extends from the bottom part of the reservoir chamber830to the positive side in the X-axis direction, the positive side in the Y-axis direction, and the negative side in the Z-axis direction, and is connected to the suction port823of the cylinder accommodating hole82A. The third hole88-43extends from the bottom part of the reservoir chamber830to the positive side in the X-axis direction, the positive side in the Y-axis direction, and the negative side in the Z-axis direction, and is connected to the suction port823of the cylinder accommodating hole82E. The fourth hole88-44extends from the left side surface806to the positive side in the X-axis direction, and is connected to the suction port823of the cylinder accommodating hole82A. The fifth hole88-45extends from the right side surface805to the negative side in the X-axis direction, and is connected to the suction port823of the cylinder accommodating hole82E. The sixth hole88-46extends from a bottom part of the liquid reservoir chamber832to the positive side in the Z-axis direction, is connected to the suction port823of the cylinder accommodating hole82B, and is connected to an intermediate portion of the fourth hole88-44. The seventh hole88-47extends from the bottom surface804to the positive side in the Z-axis direction, is connected to the suction port823of the cylinder accommodating hole82D, and is connected to an intermediate portion of the fifth hole88-45. The eighth hole88-48extends from the right side surface805to the negative side in the X-axis direction and the positive side in the Z-axis direction, is connected to the suction port823of the cylinder accommodating hole82C, and is connected to an intermediate portion of the sixth hole88-46and an intermediate portion of the seventh hole88-47. The ninth hole88-49extends from a bottom part of the SS/V OUT accommodating hole848to the positive side in the Y-axis direction, and is connected to an intermediate portion of the seventh hole88-47.

The fifth hole group88-5yincludes a first hole88-51to a sixth hole88-56. The first hole88-51extends from a bottom part of the back pressure port874to the negative side in the X-axis direction. The second hole88-52extends from an end of the first hole88-51to the negative side in the Z-axis direction. The third hole88-53extends from the rear surface802to the positive side in the Y-axis direction. The third hole88-53is connected to the second hole88-52in the course. The fourth hole88-54extends from the left surface806to the positive side in the X-axis direction. An end of the third hole88-53is connected to an intermediate portion of the fourth hole88-54. The fifth hole88-55extends from an end of the fourth hole88-54to the negative side in the Y-axis direction over a short distance, and is connected to a bottom part of the SS/V IN accommodating hole847. The sixth hole88-56extends from an intermediate portion of the first hole88-51to the negative side in the Y-axis direction and the negative side in the Z-axis direction over a short distance, and is connected to the medium-diameter part of the SS/V OUT accommodating hole848. Each of the holes880extends from a bottom part of the wheel cylinder port872to the negative side in the Z-axis direction, is connected to the medium-diameter part of the SOL/V OUT accommodating hole845, and is connected to the medium-diameter part of the SOL/V IN accommodating hole842. The hole881extends from the cam accommodating hole81to the negative side in the X-axis direction and the negative side in the Z-axis direction, and is connected to the medium-diameter part832mof the liquid reservoir chamber832.

The first hole88-11to the sixth hole88-16P of the first hole group88-1yconnect the master cylinder ports871and the shutoff valve accommodating holes841to each other, and function as a part of the supply oil passages11. The first hole88-21to the fifth hole88-25of the second hole group88-2yconnect the shutoff valve accommodating holes841and the SOL/V IN accommodating holes842to each other, and function as a part of the supply oil passages11. The sixth hole88-26P connects the communication valve accommodating hole843and the second hole88-22P to each other, and functions as a part of the discharge oil passage13. The eighth hole88-28connects the SS/V IN accommodating hole847and the communication valve accommodating hole843S to each other, and functions as a part of the first simulator oil passage17. Each of the holes880connects the SOL/V IN accommodating hole842and the wheel cylinder port872to each other, and functions as a part of the supply oil passage11. Moreover, each of the holes880connects the SOLN IN accommodating hole842and the SOL/V OUT accommodating hole845to each other, and functions as a part of the pressure reducing oil passage15. The first hole88-31to the eleventh hole88-311of the third hole group88-3yconnect the discharge ports821of the cylinder accommodating holes82and the communication valve accommodating holes843to each other, and function as a part of the discharge oil passages13. The twelfth hole88-312connects the eleventh hole88-311and the pressure regulating valve accommodating hole844to each other, and functions as a part of the pressure regulating oil passage14. The first hole88-41of the fourth hole group88-4yconnects the SOL/V OUT accommodating hole845and the reservoir chamber830to each other, and functions as a part of the pressure reducing oil passage15. The second hole88-42to the eighth hole88-48connect the reservoir chamber830and the suction ports823of the cylinder accommodating holes82to each other, and function as the suction oil passage12. The ninth hole88-49connects the SS/V OUT accommodating hole848and the seventh hole88-47to each other, and functions as the second simulator oil passage18. The first hole88-51to the fifth hole88-55of the fifth hole group88-5yconnect the back pressure port874and the SS/V IN accommodating hole847to each other, and function as a part of the back pressure oil passage16and the first simulator oil passages17. The sixth hole88-56connects the first hole88-51and the SS/V OUT accommodating hole848to each other, and functions as a part of the second simulator oil passage18. The hole881connects the cam accommodating hole81and the liquid reservoir chamber832to each other, and serves as a drain oil passage.

A plurality of bolt holes89xinclude bolt holes891to895. The bolt hole891has a bottomed tubular shape, which has an axial center extending in the Y-axis direction, and is opened in the front surface801. Three holes891are formed at positions approximately symmetrical about the axial center O of the cam accommodating hole81. Distances from the axial center O to the respective holes891are approximately the same. One hole891is formed approximately at the center in the X-axis direction (position overlapping with the axial center O in the X-axis direction) and on the positive side in the Z-axis direction with respect to the axial center O in the front surface801. This hole891is positioned between the master cylinder ports871P and871S in the X-axis direction, and overlaps with the reservoir chamber830as viewed from the Y-axis direction. Other two holes891are on both sides in the X-axis direction with respect to the axial center O, and on the negative side in the Z-axis direction with respect to the axial center O. The bolt hole892has a bottomed tubular shape, which has an axial center extending in the Y-axis direction, and is opened in the rear surface802. A total of four holes892are formed at four corners of the rear surface802, respectively. The bolt hole893has a bottomed tubular shape, which has an axial center extending in the Z-axis direction, and is opened in the top surface803. One hole893is formed approximately at the center in the X-axis direction (position overlapping with the axial center O in the X-axis direction) on the positive side in the Y-axis direction in the top surface803. The bolt hole894has a bottomed tubular shape, which has an axial center extending in the Y-axis direction, and is opened in the front surface801. Two holes894are formed on the negative side in the Z-axis direction with respect to the axial center O and at both ends in the X-axis direction in the front surface801. The holes894are positioned on an opposite side of the master cylinder port871with respect to the axial center O. The hole894on the negative side in the X-axis direction is approximately on the opposite side of the primary port871P with respect to the axial center O. The hole894on the positive side in the X-axis direction is approximately on the opposite side of the secondary port871S with respect to the axial center O. The axial centers of the holes894are arranged on the negative side in the Z-axis direction with respect to the axial centers of the bolt holes891on the negative side in the Z-axis direction, and on sides (outer sides) closer to the side surfaces805and806in the X-axis direction. The bolt hole895has a bottomed tubular shape, which has an axial center extending in the Z-axis direction, and two bolt holes895are provided, and are opened approximately at the center in the Y-axis direction, and on both ends in the X-axis direction on the bottom surface804. An end on the positive side in the Z-axis direction of the hole895overlaps with the bolt hole894as viewed from the Y-axis direction.

The ECU90is configured to input detection values of the stroke sensor94, the hydraulic pressure sensor91, and the like, and information on the travel state from the vehicle side, and control the opening/closing operations of the electromagnetic valves21and the like and the number of revolutions (namely a discharge amount of the pump3) of the motor20based on a built-in program, to thereby control the wheel cylinder hydraulic pressures) of the respective wheels FL to RR. With such control, the ECU90carries out various types of brake control (for example, antilock brake control of suppressing slip of wheels caused by the braking, boost control of decreasing a brake operation force of the driver, brake control for motion control for the vehicle, automatic brake control, for example, preceding vehicle following control, and regeneration cooperative brake control). The motion control for the vehicle includes stabilization control of vehicle behavior such as lateral slipping. The regeneration cooperative brake control controls the wheel cylinder hydraulic pressures so as to achieve a target deceleration (target braking forces) in cooperation with regenerative braking.

The ECU90includes a brake operation amount detection part90a, a target wheel cylinder hydraulic pressure calculation part90b, a stepping force braking generation part90c, a boost control part90d, and a control switching part90e. The brake operation amount detection part90ais configured to receive input of the detection value of the stroke sensor94, to thereby detect a displacement amount (pedal stroke) of the brake pedal100as a brake operation amount. The target wheel cylinder hydraulic pressure calculation part90bis configured to calculate target wheel cylinder hydraulic pressures. Specifically, the target wheel cylinder hydraulic pressure calculation part90bis configured to calculate the target wheel cylinder hydraulic pressures for achieving a predetermined boost ratio, namely an ideal relationship between the pedal stroke and required brake hydraulic pressures of the driver (vehicle deceleration G required by the driver) based on the detected pedal stroke. Moreover, the target wheel cylinder hydraulic pressure calculation part90bis configured to calculate the target wheel cylinder hydraulic pressures based on a relationship with a regenerative braking force during the regeneration cooperative brake control. For example, the target wheel cylinder hydraulic pressure calculation part90bis configured to calculate such target wheel cylinder hydraulic pressures that a sum of a regenerative braking force input from a control unit of a regenerative braking device and a hydraulic pressure braking force corresponding to the target wheel cylinder hydraulic pressures satisfies the vehicle deceleration required by the driver. The target wheel cylinder hydraulic pressure calculation part90bis configured to calculate the target wheel cylinder hydraulic pressures of the respective wheels FL to RR in order to achieve a desired vehicle motion state, for example, based on a detected vehicle motion state amount (for example, a lateral acceleration) during the motion control.

The stepping force braking generation part90cis configured to set the pump3to a non-operation state, and control the shutoff valves21toward the open direction, control the SS/V IN27toward the closed direction, and control the SS/V OUT28toward the closed direction. In the state in which the shutoff valves21are controlled toward the open direction, the oil passage system (for example, the supply oil passages11) configured to connect the hydraulic pressure chambers50of the master cylinder5and the wheel cylinders W/C to each other achieves stepping force braking (non-boost control) of generating the wheel cylinder hydraulic pressures through the master cylinder hydraulic pressure generated by the pedal stepping force. The SS/V OUT28is controlled toward the closed direction, and the stroke simulator6does not thus function. In other words, the operation of the piston61of the stroke simulator6is suppressed, and the inflow of the brake fluid from the hydraulic pressure chamber50(secondary chamber50S) to the positive pressure chamber601is thus suppressed. As a result, the wheel cylinder hydraulic pressures can more efficiently be boosted. The S/V IN27may be controlled toward the closed direction.

In the state in which the SS/V IN27is controlled toward the closed direction, and the SS/V OUT28is controlled toward the open direction while the shutoff valves21are controlled toward the closed direction, a braking system (the suction oil passage12, the discharge oil passage13, and the like) configured to connect the reservoir120and the wheel cylinders W/C to each other functions as a so-called brake-by-wire system configured to generate the wheel cylinder hydraulic pressures through the hydraulic pressure generated by the pump3, to thereby achieve the boost control, the regeneration cooperative control, and the like. The boost control part90dis configured to operate the pump3, control the shutoff valves21toward the closed direction, and control the communication valves23toward the open direction, to thereby bring the state of the second unit1B into a state in which the wheel cylinder hydraulic pressures can be generated by the pump3during the brake operation by the driver. As a result, the boost control part90dis configured to carry out the boost control of using the discharge pressure of the pump3as a hydraulic pressure source to generate the wheel cylinder hydraulic pressures higher than the master cylinder hydraulic pressure, to thereby generate the hydraulic pressure braking force that is not sufficiently generated by the brake operation force of the driver. Specifically, the boost control part90dis configured to control the pressure regulating valve24while operating the pump3at a predetermined number of revolutions to adjust the brake fluid amount supplied from the pump3to the wheel cylinders W/C, to thereby achieve the target wheel cylinder hydraulic pressures. In other words, the braking device1is configured to operate the pump3of the second unit1B in place of an engine negative pressure booster, to thereby provide a boost function of assisting the brake operation force. Moreover, the boost control part90dis configured to control the SS/V IN27toward the closed direction, and control the SS/V OUT28toward the open direction. With such control, the boost control part90dcauses the stroke simulator6to function. The control switching part90eis configured to control the operation of the master cylinder5, to thereby switch between the stepping force braking and the boost control based on the calculated target wheel cylinder hydraulic pressures. Specifically, when the start of the brake operation is detected by the brake operation amount detection part90a, the control switching part90eis configured to cause the stepping force braking generation part90cto generate the wheel cylinder hydraulic pressures when the calculated target wheel cylinder hydraulic pressures are equal to or less than predetermined values (for example, values corresponding to the maximum value of the vehicle deceleration G generated during normal braking, which is not sudden braking). Meanwhile, when the target wheel cylinder hydraulic pressures calculated upon the brake stepping operation exceed the predetermined values, the control switching part90ecauses the boost control part90dto generate the wheel cylinder hydraulic pressures.

Moreover, the ECU90includes a sudden brake operation state determination part90fand a second stepping force braking generation part90g. The sudden brake operation state determination part90fis configured to detect a brake operation state based on input, for example, from the brake operation amount detection part90aand the like, to thereby determine (decide) whether or not the brake operation state is a predetermined sudden brake operation state. For example, the sudden brake operation state determination part90fis configured to determine whether or not a change amount of the pedal stroke per unit time exceeds a predetermined threshold amount. The control switching part90eis configured to switch the control so that the wheel cylinder hydraulic pressures are generated by the second stepping force braking generation part90gwhen the brake operation state is determined to be the sudden brake operation state. The second stepping force braking generation part90gis configured to operate the pump3, and control the shutoff valves21toward the closed direction, control the SS/V IN27toward the open direction, and control the SS/V OUT28toward the closed direction. With such control, there is achieved second stepping force braking of using the brake fluid having flowed out from the back pressure chamber602of the stroke simulator6to generate the wheel cylinder hydraulic pressures until the pump3can generate sufficiently high wheel cylinder hydraulic pressures. The shutoff valves21may be controlled toward the open direction. Moreover, the SS/V IN27may be controlled toward the closed direction, and, in this case, the brake fluid from the back pressure chamber602is supplied to the wheel cylinder W/C side via the check valve270(in the valve open state because the pressure on the wheel cylinder W/C side is still lower than that on the back pressure chamber602side). In this embodiment, the brake fluid can efficiently be supplied from the back pressure chamber602side to the wheel cylinder W/C side by controlling the SS/V IN27toward the open direction. Then, when the brake operation state is no longer determined to be the sudden brake operation state, and/or a predetermined condition indicating that a discharge performance of the pump3has become sufficient is satisfied, the control switching part90eswitches the control so as to cause the boost control part90dto generate the wheel cylinder hydraulic pressures. In other words, the boost control part90dcontrols the SS/V IN27toward the closed direction, and controls the SS/V OUT28toward the open direction. With such control, the boost control part90dcauses the stroke simulator6to function. The control may be switched to the regeneration cooperative brake control after the second stepping force braking.

Referring toFIG. 5toFIGS. 13, a description is now given of configurations of the shutoff valve21, the SOL/V IN22, the communication valve23, the pressure regulating valve24, the SS/V IN27, and the SS/V OUT28.

In general, for each of valves of a hydraulic pressure control device such as a braking device, dedicated components are specified. In this embodiment, as described later, focus is given on such a point that the degradation in productivity of the entire hydraulic pressure control device can be suppressed by finding out portions of the respective valves which can be common components.

[Shutoff Valve and Pressure Regulating Valve]

Structures of the shutoff valve21and the pressure regulating valve24are the same, and a description is given only of the shutoff valve21.FIG. 5is a longitudinal sectional view of the shutoff valve21.FIGS. 6are exploded perspective views of the shutoff valve21.FIG. 6(a)is a view as viewed from the positive side in the Y-axis direction, andFIG. 6(b)is a view as viewed from the negative side in the Y-axis direction.

The shutoff valve21includes a coil21-1, a cylinder21-2, an armature21-3, a plunger (21-4, a valve body21-5, a seat member21-6, a body member21-7, a first filter member21-8, a second filter member21-9, and a seal member21-10. An electromagnetic drive part21-15is formed of the coil21-1, the cylinder21-2, the armature21-3, and the valve body21-5.

The coil21-1is configured to generate an electromagnetic force through a current supply. The coil21-1is accommodated in a yoke21-11made of a magnetic material.

The cylinder21-2is made of a non-magnetic material formed into a tubular shape. An end on the positive side in the Y-axis direction of the cylinder21-2is opened, and an end on the negative side in the Y-axis direction is closed by a semispherical bottom portion. The end on the positive side in the Y-axis direction of the cylinder21-2is welded to a first tubular part21-5aof the valve body21-5described later.

The armature21-3is made of a magnetic material, and is provided so as to be movable in the Y-axis direction inside the cylinder21-2. A recessed part21-3ainto which the plunger21-4is press-fitted is formed at a center of an end on the positive side in the Y-axis direction of the armature21-3. The armature21-3is moved toward the positive side in the Y-axis direction by the electromagnetic force generated by the coil21-1when a current is supplied to the coil21-1.

The plunger21-4is made of a non-magnetic material such as resin formed into a rod shape. The plunge21-4is arranged along the Y-axis direction inside the cylinder21-2. A large-diameter part21-4alager in diameter than an end on the positive side in the Y-axis direction of the plunger21-4is formed on the negative side in the Y-axis direction of the plunger21-4. A tip part21-4b, which is an end on the positive side in the Y-axis direction of the plunger21-4, is formed into a semispherical shape. The large-diameter part21-4ais press-fitted into the recessed part21-3aof the armature21-3. The plunger21-4is driven integrally with the armature21-3.

The valve body21-5is made of a magnetic material formed into a tubular shape. The valve body21-5includes a first tubular part21-5aprovided on the negative side in the Y-axis direction, and configured to function as a magnetic path formation member, a crimped part21-5bincreased in diameter, and fixed to the housing8through crimping, and a second tubular part21-5cprovided on the positive side in the Y-axis direction, and inserted into the shutoff valve accommodating hole841. A first accommodating hole (insertion hole)21-5dis formed in an inner periphery of the first tubular part21-5a. A second accommodating hole21-5elarger in diameter than the first accommodating hole21-5dis formed in an inner periphery of the second tubular part21-5c. A lock part21-5fprotruding inward in the radial direction is formed on an end on the positive side in the Y-axis direction of the first accommodating hole21-5d. A coil spring21-12is provided in a compressed state between the lock part21-5fand the large-diameter part21-4aof the plunger21-4. The coil spring21-12is configured to urge the plunger21-4toward the negative side in the Y-axis direction. A plurality of axial oil passages21-5gare formed in the second accommodating hole21-5e.

The seat member21-6is arranged in the shutoff valve accommodating hole841. The seat member21-6includes a bottom part21-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape having an opening21-6iopened at an end on the positive side in the Y-axis direction. The seat member21-6includes a small-diameter part21-6b, a large-diameter part21-6c, and a first step part21-6d. The small-diameter part21-6bincludes a bottom part21-6a, is provided on the negative side in the Y-axis direction, and is press-fitted into and fixed to the second accommodating hole21-5eof the valve body21-5. A first communication hole21-6eis formed in the bottom part21-6a. A valve seat21-6fagainst which the tip part21-4bof the plunger21-4abuts is formed around the first communication hole21-6e. The large-diameter part21-6cis provided on the positive side in the Y-axis direction with respect to the small-diameter part21-6b, and is formed so as to be larger in diameter than the small-diameter part21-6b. The first step part21-6dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part21-6band the large-diameter part21-6cto each other.

The body member21-7is arranged in the shutoff valve accommodating hole841, and is provided at a position outside the seat member21-6. The body member21-7includes a bottom part21-7aat an end on the positive side in the Y-axis direction, and is formed into a tubular shape having an opening21-7hopened at an end on the positive side in the Y-axis direction. The body member21-7includes a small-diameter part21-7b, a large-diameter part21-7c, and a second step part21-7d. The small-diameter part21-7bincludes a bottom part21-7a, and is provided on the positive side in the Y-axis direction. A second communication hole21-7eis formed in the bottom part21-7a. The second communication hole21-7eis connected to the first hole88-21. The large-diameter part21-7cis provided on the negative side in the Y-axis direction with respect to the small-diameter part21-7b, and is formed so as to be larger in diameter than the small-diameter part21-7b. The large-diameter part21-6cof the seat member21-6is fitted to the large-diameter part21-7c. An inner abutment surface21-7gthat abuts against an outer peripheral surface21-6gof the large-diameter part21-6cof the seat member21-6ais provided on an inner peripheral surface of the large-diameter part21-7c. A plurality of circulation holes21-7fare formed in the large-diameter part21-7con the negative side in the Y-axis direction with respect to the inner abutment surface21-7g. The circulation holes21-7fare connected to the sixth hole88-16. The second step part21-7dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part21-7band the large-diameter part21-7cto each other. An internal space surrounded by the seat member21-6and the body member21-7is a flow passage (internal oil passage)21-13through which the brake fluid flows. A valve part21-14is formed of the seat member21-6and the body member21-7.

The first filter member21-8is provided in the flow passage21-13. The first filter member21-8is configured to filter the brake fluid flowing from the second communication hole21-7einto the first communication hole21-6e, to thereby prevent contamination and the like in the brake fluid from being transmitted to the plunger21-4and the valve seat21-6f. The first filter member21-8engages with the first step part21-6dof the seat member21-6and the second step part21-7dof the body member21-7so that a position in the Y-axis direction is maintained. The first filter member21-8is provided so as to face an inner peripheral surface21-6hof the large-diameter part21-6cof the seat member21-6. A gap smaller than coarseness of a mesh part21-8adescribed later is provided between the inner peripheral surface21-6hof the seat member21-6and the outer peripheral surface21-8cof the first filter member21-8.

FIGS. 7are views for illustrating a shape of the first filter member21-8.FIG. 7(a)is a plan view, andFIG. 7(b)is a side sectional view. The first filter member21-8is injection-molded of a resin material, and includes the mesh part21-8aand a frame body21-8b. The mesh part21-8ais formed into a net form having a predetermined coarseness. The frame body21-8bis formed into an annular shape, and is provided on an outer periphery of the mesh part21-8a. A recessed part21-8dis formed at a position corresponding to a gate in one end surface of the frame body21-8b. A height of a remaining portion of the gate can be prevented from exceeding the one end surface of the frame body21-8bby providing the recessed part21-8d. The first filter member21-8is arranged in a state in which the recessed part21-8dfaces the negative side in the Y-axis direction.

A second filter member21-9is injection-molded of a resin material. The second filter member21-9is arranged at a position outside the body member21-7, and overlaps the first filter member21-8in the Y-axis direction. The second filter member21-9is configured to filter the brake fluid flowing from the sixth hole88-16into the circulation holes21-7f, to thereby prevent contamination and the like in the brake fluid from being transmitted to the plunger21-4and the valve seat21-6f.

The seal member21-10is an O ring, and is mounted on an outer periphery of the small-diameter part21-7bof the body member21-7, thereby sealing a gap between an outer peripheral surface of the small-diameter part21-7band an inner peripheral surface of the shutoff valve accommodating hole841.

A description is now given of an operation of the shutoff valve21.

When the current is not supplied to the coil21-1, the armature21-3and the plunger21-4are urged by an urging force of the coil spring21-12toward the negative side in the Y-axis direction, and the tip part21-4bof the plunger21-4is thus separated from the valve seat21-6f. Therefore, the sixth hole88-16and the first hole88-21communicate with each other via the circulation holes21-7f, the axial oil passages21-5g, the first communication hole21-6e, and the second communication hole21-7e.

When a predetermined current is supplied to the coil21-1, a magnetic path is formed in the yoke21-1l, the armature21-3, and the first tubular part21-5a, and an attraction force is generated between the armature21-3and the first tubular part21-5a. The armature21-3and the plunger21-4move toward the positive side in the Y-axis direction by the attraction force, and when the tip part21-4bof the plunger21-4abuts against the valve seat21-6f, the sixth hole88-16and the first hole88-21are shut off from each other. Moreover, a gap (flow passage cross sectional area) between the tip part21-4band the valve seat21-6fcan be controlled by controlling supplied power to the coil21-1through PWM control, to proportionally control the attraction force, to thereby achieve a desired flow rate (hydraulic pressure).

In the following description, reference numeral of each component of the pressure regulating valve24is obtained by replacing21of the reference numeral for the same component of the shutoff valve21with24.

FIG. 8is a longitudinal sectional view of the SOL/V IN22.FIGS. 9are exploded perspective views of the SOL/V IN22.FIG. 9(a)is a view as viewed from the positive side in the Y-axis direction, andFIG. 9(b)is a view as viewed from the negative side in the Y-axis direction.

The SOL/V IN22includes a coil22-1, a cylinder22-2, an armature22-3, a plunger22-4, a valve body22-5, a seat member22-6, a body member22-7, a first filter member22-8, a second filter member22-9, and a seal member22-10. An electromagnetic drive part22-15is formed of the coil22-1, the cylinder22-2, the armature22-3, and the valve body22-5.

The coil22-1is configured to generate an electromagnetic force through a current supply. The coil22-1is accommodated in a yoke22-11made of a magnetic material.

The cylinder22-2is made of a non-magnetic material formed into a tubular shape. An end on the positive side in the Y-axis direction of the cylinder22-2is opened, and an end on the negative side in the Y-axis direction is closed by a semispherical bottom part. The end on the positive side in the Y-axis direction of the cylinder22-2is welded to a first tubular part22-5aof the valve body22-5described later.

The armature22-3is made of a magnetic material, and is provided so as to be movable in the Y-axis direction inside the cylinder22-2. The armature22-3is moved toward the positive side in the Y-axis direction by the electromagnetic force generated by the coil22-1when a current is supplied to the coil22-1.

The plunger22-4is made of a non-magnetic material such as resin formed into a rod shape. The plunge22-4is arranged along the Y-axis direction inside the cylinder22-2. A large-diameter part22-4alarger in diameter than an end on the positive side in the Y-axis direction of the plunger22-4is formed on the negative side in the Y-axis direction of the plunger22-4. A tip part22-4b, which is an end on the positive side in the Y-axis direction of the plunger22-4, is formed into a semispherical shape. An end on the negative side in the Y-axis direction of the large-diameter part22-4aabuts against an end on the positive side in the Y-axis direction of the armature22-3. The plunger22-4is driven integrally with the armature22-3.

The valve body22-5is made of a magnetic material formed into a tubular shape. The valve body22-5includes a first tubular part22-5aprovided on the negative side in the Y-axis direction, and configured to function as a magnetic path formation member, a crimped part22-5bincreased in diameter, and fixed to the housing8through crimping, and a second tubular part22-5cprovided on the positive side in the Y-axis direction, and inserted into an SOL/V IN accommodating hole842. A first accommodating hole (insertion hole)22-5dis formed in an inner periphery of the first tubular part22-5a. A second accommodating hole22-5elarger in diameter than the first accommodating hole22-5dis formed in an inner periphery of the second tubular part22-5c. A lock part22-5fprotruding inward in the radial direction is formed at an end on the positive side in the Y-axis direction of the first accommodating hole22-5d. A coil spring22-12is provided in a compressed state between the lock part22-5fand the large-diameter part22-4aof the plunger22-4. The coil spring22-12is configured to urge the plunger22-4toward the negative side in the Y-axis direction. A plurality of axial oil passages22-5gare formed in the second accommodating hole22-5e.

The seat member22-6is arranged in the SOL/V IN accommodating hole842. The seat member22-6includes a bottom part22-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape having an opening22-6iopened at an end on the positive side in the Y-axis direction. The seat member22-6includes a bottom part22-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape opened at an end on the positive side in the Y-axis direction. The seat member22-6includes a small-diameter part22-6b, a large-diameter part22-6c, and a first step part22-6d. The small-diameter part22-6bincludes a bottom part22-6a, is provided on the negative side in the Y-axis direction, and is press-fitted into and fixed to the second accommodating hole22-5eof the valve body22-5. A first communication hole22-6eis formed in the bottom part22-6a. A valve seat22-6fagainst which the tip part22-4bof the plunger22-4abuts is formed around the first communication hole22-6e. The large-diameter part22-6cis provided on the positive side in the Y-axis direction with respect to the small-diameter part22-6b, and is formed so as to be larger in diameter than the small-diameter part22-6b. The first step part22-6dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part22-6band the large-diameter part22-6cto each other.

The body member22-7is arranged in the SOL/V IN accommodating hole842, and is provided at a position outside the seat member22-6. The body member22-7includes a bottom part22-7aat an end on the positive side in the Y-axis direction, and is formed into a tubular shape having an opening22-7hopened at an end on the positive side in the Y-axis direction. The body member22-7includes a small-diameter part22-7b, a large-diameter part22-7c, and a second step part22-7d. The small-diameter part22-7bincludes a bottom part22-7a, and is provided on the positive side in the Y-axis direction. A second communication hole22-7eis formed in the bottom part22-7a. The second communication hole22-7eis connected to the fifth hole88-25. The large-diameter part22-7cis provided on the negative side in the Y-axis direction with respect to the small-diameter part22-7b, and is formed so as to be larger in diameter than the small-diameter part22-7b. The large-diameter part22-6cof the seat member22-6is fitted to the large-diameter part22-7c. An inner abutment surface22-7gthat abuts against an outer peripheral surface22-6gof the large-diameter part22-6cof the seat member22-6ais provided on an inner peripheral surface of the large-diameter part22-7c. A plurality of circulation holes22-7fare formed in the large-diameter part22-7con the negative side in the Y-axis direction with respect to the inner abutment surface22-7g. The circulation holes22-7fare connected to the oil passage hole880. The second step part22-7dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part22-7band the large-diameter part22-7cto each other. An internal space surrounded by the seat member22-6and the body member22-7is a flow passage (internal oil passage)22-13through which the brake fluid flows. A valve part22-14is formed of the seat member22-6and the body member22-7.

The first filter member22-8is provided in the flow passage22-13. The first filter member22-8is configured to filter the brake fluid flowing from the second communication hole22-7einto the first communication hole22-6e, to thereby prevent contamination and the like in the brake fluid from being transmitted to the plunger22-4and the valve seat22-6fThe first filter member22-8engages with the first step part22-6dof the seat member22-6and the second step part22-7dof the body member22-7, to thereby maintain a position in the Y axis-direction. The first filter member22-8is provided so as to face an inner peripheral surface22-6hof the large-diameter part22-6cof the seat member22-6. A gap smaller than coarseness of a mesh part22-8adescribed later is provided between the inner peripheral surface22-6hof the seat member22-6and the outer peripheral surface22-8cof the first filter member22-8. The shape of the first filter member22-8is the same as that of the first filter member21-8illustrated inFIGS. 7, and a description thereof is therefore omitted. The first filter22-8is arranged in a state in which a recessed portion faces the positive side in the Y axis-direction.

A second filter member22-9is injection-molded of a resin material. The second filter member22-9is arranged at a position outside the body member22-7, and overlaps the first filter member22-8in the Y-axis direction. The second filter member22-9is configured to filter the brake fluid flowing from the oil passage hole880into the circulation holes22-7f, to thereby prevent contamination and the like in the brake fluid from being transmitted to the plunger22-4and the valve seat22-6f.

The seal member22-10is a cup seal, and is mounted on an outer periphery of the small-diameter part22-7bof the body member22-7. The seal member22-10is configured to function as the check valve220by sealing a leak of the brake fluid from the fifth hole88-25to the oil passage hole880when (hydraulic pressure in fifth hole88-25>hydraulic pressure in oil passage hole880), and permitting a flow of the brake fluid from the oil passage hole880to the fifth hole88-25when (hydraulic pressure in fifth hole88-25<hydraulic pressure in oil passage hole880).

A description is now given of an operation of the SOL/V IN22.

When the current is not supplied to the coil22-1, the armature22-3and the plunger22-4are urged by an urging force of the coil spring22-12toward the negative side in the Y-axis direction, and the tip part22-4bof the plunger22-4is thus separated from the valve seat22-6f. Therefore, the fifth hole88-25and the oil passage hole880communicate with each other via the circulation holes22-7f, the axial oil passages22-5g, the first communication hole22-6e, and the second communication hole22-7e.

When a predetermined current is supplied to the coil22-1, a magnetic path is formed in the yoke22-11, the armature22-3, and the first tubular part22-5a, and an attraction force is generated between the armature22-3and the first tubular part22-5a. The armature22-3and the plunger22-4move toward the positive side in the Y-axis direction through the attraction force, and when the tip part22-4bof the plunger22-4abuts against the valve seat22-6f, the fifth oil passage88-25and the oil passage hole880are shut off from each other. Moreover, a gap (flow passage cross sectional area) between the tip part22-4band the valve seat22-6fcan be controlled by controlling supplied power to the coil22-1through PWM control to proportionally control the attraction force, to thereby achieve a desired flow rate (hydraulic pressure).

FIG. 10is a longitudinal sectional view of the communication valve23.FIGS. 11are exploded perspective views of the communication valve23.FIG. 11(a)is a view as viewed from the positive side in the Y-axis direction, andFIG. 11(b)is a view as viewed from the negative side in the Y-axis direction.

The communication valve23includes a coil23-1, a cylinder23-2, a body center23-3, an armature23-4, a flange ring23-5, a seat member23-6, a body member23-7, a first filter member23-8, a second filter member23-9, and a seal member23-10. An electromagnetic drive part23-15is formed of the coil23-1, the cylinder23-2, and the armature23-4.

The coil23-1is configured to generate an electromagnetic force through a current supply. The coil23-1is accommodated in a yoke23-11made of a magnetic material.

The cylinder23-2is made of a non-magnetic material formed into a tubular shape opened at both ends.

The body center23-3is made of a magnetic material. An end on the positive side in the Y-axis direction of the body center23-3is welded to an end on the negative side in the Y-axis direction of the cylinder23-2. The body center23-3is configured to attract the armature23-4by the electromagnetic force generated by the coil23-1when the current is supplied to the coil23-1.

The armature23-4is made of a magnetic material. The armature23-4is arranged along the Y-axis direction inside the cylinder23-2. A recessed part23-4aextending toward the positive side in the Y-axis direction is formed at an end on the negative side in the Y-axis direction of the armature23-4. A coil spring23-12is provided in a compressed state between a bottom portion of the recessed part23-4aand the body center23-3. The coil spring23-12is configured to urge the armature23-4toward the positive side in the Y-axis direction. When a current is not supplied to the coil23-1, a predetermined gap is provided between an end on the positive side in the Y-axis direction of the cylinder23-2and an end on the negative side in the Y-axis direction of the armature23-4. A spherical valve body23-4bis fixed to an end on the positive side in the Y-axis direction of the armature23-4.

The flange ring23-5is made of a magnetic material formed into a tubular shape opened at both ends, and is arranged in the communication valve accommodating hole843. The flange ring23-5includes a crimped part23-5aincreased in diameter, and fixed to the housing8through crimping.

The seat member23-6is arranged in the communication valve accommodating hole843. The seat member23-6includes a bottom part23-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape having an opening23-6iopened at an end on the positive side in the Y-axis direction. The seat member23-6includes a small-diameter part23-6b, a large-diameter part23-6c, and a first step part23-6d. The small-diameter part23-6bincludes a bottom part23-6a, and is provided on the negative side in the Y-axis direction. A first communication hole23-6eis formed in the bottom part23-6a. A valve seat23-6fagainst which the tip part23-4bof the armature23-4abuts is formed around the first communication hole23-6e. The large-diameter part23-6cis provided on the positive side in the Y-axis direction with respect to the small-diameter part23-6b, and is formed so as to be larger in diameter than the small-diameter part23-6b. The first step part23-6dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part23-6band the large-diameter part23-6cto each other.

The body member23-7is arranged in the communication valve accommodating hole843, and is provided at a position outside the seat member23-6. The body member23-7includes a bottom part23-7aat an end on the positive side in the Y-axis direction, and is formed into a tubular shape having an opening23-7hopened at an end on the positive side in the Y-axis direction. The body member23-7includes a small-diameter part23-7b, a large-diameter part23-7c, and a second step part23-7d. The small-diameter part23-7bincludes a bottom part23-7a, and is provided on the positive side in the Y-axis direction. A second communication hole23-7eis formed in the bottom part23-7a. The second communication hole23-7eis connected to the eleventh hole88-31l. The large-diameter part23-7cis provided on the negative side in the Y-axis direction with respect to the small-diameter part23-7b, and is formed so as to be larger in diameter than the small-diameter part23-7b. The large-diameter part23-6cof the seat member23-6is fitted to the large-diameter part23-7c. The large-diameter part23-7cis inserted in an inner periphery of an end on the positive side in the Y-axis direction of the cylinder23-2. A tip end of the large-diameter part23-7cis inserted to a position of abutment against a side surface on the positive side in the Y-axis direction of the crimped part23-5avia the cylinder23-2. The large-diameter part23-7cis fixed by crimping an end on the positive side in the Y-axis direction of the cylinder23-2along an outer peripheral surface of the large-diameter part23-7c. An inner abutment surface23-7gthat abuts against an outer peripheral surface23-6gof the large-diameter part23-6cof the seat member23-6ais provided on an inner peripheral surface of the large-diameter part23-7c. A plurality of circulation holes23-7fare formed in the large-diameter part23-7con the negative side in the Y-axis direction with respect to the inner abutment surface23-7g. The circulation holes23-7fare connected to the sixth hole88-26. The second step part23-7dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part23-7band the large-diameter part23-7cto each other. An internal space surrounded by the seat member23-6and the body member23-7is a flow passage (internal oil passage)23-13through which the brake fluid flows. A valve part23-14is formed of the seat member23-6and the body member23-7.

The first filter member23-8is provided in the flow passage23-13. The first filter member23-8is configured to filter the brake fluid flowing from the second communication hole23-7einto the first communication hole23-6e, to thereby prevent contamination and the like in the brake fluid from being transmitted to the armature23-4and the valve seat23-6f. The first filter member23-8engages with the first step part23-6dof the seat member23-6and the second step part23-7dof the body member23-7, to thereby maintain a position in the Y axis-direction. The first filter member23-8is provided so as to face an inner peripheral surface23-6hof the large-diameter part23-6cof the seat member23-6. A gap smaller than coarseness of a mesh part23-8adescribed later is provided between the inner peripheral surface23-6hof the seat member23-6and the outer peripheral surface23-8cof the first filter member23-8. The shape of the first filter member23-8is the same as that of the first filter member21-8illustrated inFIGS. 7, and a description thereof is therefore omitted. The first filter23-8is arranged in a state in which a recessed portion faces the negative side in the Y axis-direction.

A second filter member23-9is injection-molded of a resin material. The second filter member23-9is arranged at a position outside the body member23-7, and overlaps the first filter member23-8in the Y-axis direction. The second filter member23-9is configured to filter the brake fluid flowing from the sixth hole88-26into the circulation holes23-7f, to thereby prevent contamination and the like in the brake fluid from being transmitted to the armature23-4and the valve seat23-6f.

The seal member23-10is an O ring, and is mounted on an outer periphery of the small-diameter part23-7bof the body member23-7, to thereby seal a gap between an outer peripheral surface of the small-diameter part23-7band an inner peripheral surface of the communication valve accommodating hole843.

A description is now given of an operation of the communication valve23.

When the current is not supplied to the coil23-1, the armature23-4is urged by an urging force of the coil spring23-12toward the positive side in the Y-axis direction, and the tip part23-4bof the armature23-4thus abuts against the valve seat23-6f. Therefore, the sixth hole88-26and the eleventh hole88-311are shut off from each other.

When a predetermined current is supplied to the coil23-1, a magnetic path is formed in the yoke23-11, the body center23-3, and the armature23-4, and an attraction force is generated between the body center23-3and the armature23-4. The armature23-4moves toward the negative side in the Y-axis direction by the attraction force, and when the tip part23-4bof the armature23-4separates from the valve seat23-6f, the sixth hole88-26and the eleventh hole88-311communicate with each other via the circulation holes23-7f, the axial oil passage23-5g, the first communication hole23-6e, and the second communication hole23-7e.

Structures of the SS/V IN27and the SS/V OUT28are the same, and a description is only given of the SS/V IN27.

FIG. 12is a longitudinal sectional view of the SS/V IN27.FIGS. 13are exploded perspective views of the SS/V IN27.FIG. 13(a)is a view as viewed from the positive side in the Y-axis direction, andFIG. 13(b)is a view as viewed from the negative side in the Y-axis direction.

The SS/V IN27includes a coil27-1, a cylinder27-2, a body center27-3, an armature27-4, a flange ring27-5, a seat member27-6, a body member27-7, a first filter member27-8, a second filter member27-9, and a seal member27-10. An electromagnetic drive part27-15is formed of the coil27-1, the cylinder27-2, and the armature27-4.

The coil27-1is configured to generate an electromagnetic force through a current supply. The coil27-1is accommodated in a yoke27-11made of a magnetic material.

The cylinder27-2is made of a non-magnetic material formed into a tubular shape opened at both ends.

The body center27-3is made of a magnetic material. An end on the positive side in the Y-axis direction of the body center27-3is welded to an end on the negative side in the Y-axis direction of the cylinder27-2. The body center27-3is configured to attract the armature27-4by the electromagnetic force generated by the coil27-1when the current is supplied to the coil27-1.

The armature27-4is made of a magnetic material. The armature27-4is arranged along the Y-axis direction inside the cylinder27-2. A recessed part27-4aextending toward the positive side in the Y-axis direction is formed at an end on the negative side in the Y-axis direction of the armature27-4. A coil spring27-12is provided in a compressed state between a bottom portion of the recessed part27-4aand the body center27-3. The coil spring27-12is configured to urge the armature27-4toward the positive side in the Y-axis direction. When a current is not supplied to the coil27-1, a predetermined gap is provided between an end on the positive side in the Y-axis direction of the cylinder27-2and an end on the negative side in the Y-axis direction of the armature27-4. A spherical valve body27-4bis fixed to an end on the positive side in the Y-axis direction of the armature27-4.

The flange ring27-5is made of a magnetic material formed into a tubular shape opened at both ends, and is arranged in the SS/V IN accommodating hole847. The flange ring27-5includes a crimped part27-5aincreased in diameter, and fixed to the housing8through crimping.

The seat member27-6is arranged in the SS/V IN accommodating hole847. The seat member27-6includes a bottom part27-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape having an opening27-6iopened at an end on the positive side in the Y-axis direction. The seat member27-6includes a small-diameter part27-6b, a large-diameter part27-6c, and a first step part27-6d. The small-diameter part27-6bincludes a bottom part27-6a, and is provided on the negative side in the Y-axis direction. A first communication hole27-6eis formed in the bottom part27-6a. A valve seat27-6fagainst which the valve body27-4bof the armature27-4abuts is formed around the first communication hole27-6e. The large-diameter part27-6cis provided on the positive side in the Y-axis direction with respect to the small-diameter part27-6b, and is formed so as to be larger in diameter than the small-diameter part27-6b. The first step part27-6dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part27-6band the large-diameter part27-6cto each other.

The body member27-7is arranged in the SS/V IN accommodating hole847, and is provided at a position outside the seat member27-6. The body member27-7includes a bottom part27-7aat an end on the positive side in the Y-axis direction, and is formed into a tubular shape having an opening27-7hopened at an end on the positive side in the Y-axis direction. The body member27-7includes a small-diameter part27-7b, a large-diameter part27-7c, and a second step part27-7d. The small-diameter part27-7bincludes a bottom part27-7a, and is provided on the positive side in the Y-axis direction. A second communication hole27-7eis formed in the bottom part27-7a. The second communication hole27-7eis connected to the fifth hole88-55. The large-diameter part27-7cis provided on the negative side in the Y-axis direction with respect to the small-diameter part27-7b, and is formed so as to be larger in diameter than the small-diameter part27-7b. The large-diameter part27-6cof the seat member27-6is fitted to the large-diameter part27-7c. The large-diameter part27-7cis inserted in an inner periphery of an end on the positive side in the Y-axis direction of the cylinder27-2. A tip end of the large-diameter part27-7cis inserted to a position of abutment against a side surface on the positive side in the Y-axis direction of the crimped part27-5avia the cylinder27-2. The large-diameter part27-7cis fixed by crimping an end on the positive side in the Y-axis direction of the cylinder27-2along an outer peripheral surface of the large-diameter part27-7c. An inner abutment surface27-7gthat abuts against an outer peripheral surface27-6gof the large-diameter part27-6cof the seat member27-6ais provided on an inner peripheral surface of the large-diameter part27-7c. A plurality of circulation holes27-7fare formed in the large-diameter part27-7con the negative side in the Y-axis direction with respect to the inner abutment surface27-7g. The circulation holes27-7fare connected to the eighth hole88-28. The second step part27-7dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part27-7band the large-diameter part27-7cto each other. An internal space surrounded by the seat member27-6and the body member27-7is a flow passage (internal oil passage)27-13through which the brake fluid flows. A valve part27-14is formed of the seat member27-6and the body member27-7.

The first filter member27-8is provided in the flow passage27-13. The first filter member27-8is configured to filter the brake fluid flowing from the second communication hole27-7einto the first communication hole27-6e, to thereby prevent contamination and the like in the brake fluid from being transmitted to the armature27-4and the valve seat27-6f. The first filter member27-8engages with the first step part27-6dof the seat member27-6and the second step part27-7dof the body member27-7, to thereby maintain a position in the Y axis-direction. The first filter member27-8is provided so as to face an inner peripheral surface27-6hof the large-diameter part27-6cof the seat member27-6. A gap smaller than coarseness of a mesh part27-8adescribed later is provided between the inner peripheral surface27-6hof the seat member27-6and the outer peripheral surface27-8cof the first filter member27-8. The shape of the first filter member27-8is the same as that of the first filter member21-8illustrated inFIGS. 7, and a description thereof is therefore omitted. The first filter27-8is arranged in a state in which a recessed portion faces the positive side in the Y axis-direction.

A second filter member27-9is injection-molded of a resin material. The second filter member27-9is arranged at a position outside the body member27-7, and overlaps the first filter member27-8in the Y-axis direction. The second filter member27-9is configured to filter the brake fluid flowing from the eighth hole88-28into the circulation holes27-7f, to thereby prevent contamination and the like in the brake fluid from being transmitted to the armature27-4and the valve seat27-6f.

The seal member27-10is a cup seal, and is mounted on an outer periphery of the small-diameter part27-7bof the body member27-7. The seal member22-10is configured to function as the check valve270by sealing a leak of the brake fluid from the eighth hole88-28to the fifth hole88-55when (hydraulic pressure in eighth hole88-28>hydraulic pressure in fifth hole88-55), and permitting a flow of the brake fluid from the fifth hole88-55to the eighth hole88-28when (hydraulic pressure in eighth hole88-28<hydraulic pressure in oil passage hole880).

A description is now given of an operation of the SS/V IN27.

When the current is not supplied to the coil27-1, the armature27-4is urged by an urging force of the coil spring27-12toward the positive side in the Y-axis direction, and the valve body27-4bof the armature27-4thus abuts against the valve seat27-6f. Therefore, the fifth hole88-55and the eighth hole88-28are shut off from each other.

When a predetermined current is supplied to the coil27-1, a magnetic path is formed in the yoke27-11, the body center27-3, and the armature27-4, and an attraction force is generated between the body center27-3and the armature27-4. The armature27-4moves toward the negative side in the Y-axis direction by the attraction force, and when the valve body27-4bof the armature27-4separates from the valve seat27-6f, the fifth hole88-55and the eighth hole88-28communicate with each other via the circulation holes27-7f, the axial oil passage27-5g, the first communication hole27-6e, and the second communication hole23-7e.

In the following description, reference numeral of each component of the SS/V OUT28is obtained by replacing27of the reference numeral of the same component of the SS/V IN27with28.

FIG. 13is a longitudinal sectional view of the SOL/V OUT25.

The SOL/V OUT25includes a coil25-.1, a cylinder25-2, a body center25-3, an armature25-4, a flange ring25-5, a seat member25-6, a body member25-7, a first filter member25-8, a second filter member25-9, and a seal member25-10. An electromagnetic drive part25-15is formed of the coil25-1, the cylinder25-2, and the armature25-4.

The coil25-1is configured to generate an electromagnetic force through a current supply. The coil25-1is accommodated in a yoke25-11made of a magnetic material.

The cylinder25-2is made of a non-magnetic material formed into a tubular shape opened at both ends.

The body center25-3is made of a magnetic material. An end on the positive side in the Y-axis direction of the body center25-3is welded to an end on the negative side in the Y-axis direction of the cylinder25-2. The body center25-3is configured to attract the armature25-4by the electromagnetic force generated by the coil25-1when the current is supplied to the coil25-1.

The armature25-4is made of a magnetic material. The armature25-4is arranged along the Y-axis direction inside the cylinder25-2. A recessed part25-4aextending toward the positive side in the Y-axis direction is formed at an end on the negative side in the Y-axis direction of the armature25-4. A coil spring25-12is provided in a compressed state between a bottom portion of the recessed part25-4aand the body center25-3. The coil spring25-12is configured to urge the armature25-4toward the positive side in the Y-axis direction. When a current is not supplied to the coil25-1, a predetermined gap is provided between an end on the positive side in the Y-axis direction of the cylinder25-2and an end on the negative side in the Y-axis direction of the armature25-4. A spherical valve body25-4bis fixed to an end on the positive side in the Y-axis direction of the armature25-4.

The flange ring25-5is made of a magnetic material formed into a tubular shape opened at both ends, and is arranged in the communication valve accommodating hole843. The flange ring25-5includes a crimped part25-5aincreased in diameter, and fixed to the housing8through crimping.

The seat member25-6is arranged in the SOLN OUT accommodating hole845. The seat member25-6includes a bottom part25-6aat an end on the negative side in the Y-axis direction, and is formed into a tubular shape having an opening25-6iopened at an end on the positive side in the Y-axis direction. The seat member25-6includes a small-diameter part25-6b, a large-diameter part25-6c, and a first step part25-6d. The small-diameter part25-6bincludes a bottom part25-6a, and is provided on the negative side in the Y-axis direction. A first communication hole25-6eis formed in the bottom part25-6a. A valve seat25-6fagainst which the tip part25-4bof the armature25-4abuts is formed around the first communication hole25-6e. The large-diameter part25-6cis provided on the positive side in the Y-axis direction with respect to the small-diameter part25-6b, and is formed so as to be larger in diameter than the small-diameter part25-6b. The first step part25-6dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part25-6band the large-diameter part25-6cto each other.

The body member25-7is arranged in the SOL/V OUT accommodating hole845, and is provided at a position outside the seat member25-6. The body member25-7includes a bottom part25-7aat an end on the positive side in the Y-axis direction, and is formed into a tubular shape having an opening25-7hopened at an end on the positive side in the Y-axis direction. The body member25-7includes a small-diameter part25-7b, a large-diameter part25-7c, and a second step part25-7d. The small-diameter part25-7bincludes a bottom part25-7a, and is provided on the positive side in the Y-axis direction. A second communication hole25-7eis formed in the bottom part25-7a. The second communication hole25-7eis connected to the first hole88-41. The large-diameter part25-7cis provided on the negative side in the Y-axis direction with respect to the small-diameter part25-7b, and is formed so as to be larger in diameter than the small-diameter part25-7b. The large-diameter part25-6cof the seat member25-6is fitted to the large-diameter part25-7c. The large-diameter part25-7cis inserted in an inner periphery of an end on the positive side in the Y-axis direction of the cylinder25-2. A tip end of the large-diameter part25-7cis inserted to a position of abutment against a side surface on the positive side in the Y-axis direction of the crimped part25-5avia the cylinder25-2. The large-diameter part25-7cis fixed by crimping an end on the positive side in the Y-axis direction of the cylinder25-2along an outer peripheral surface of the large-diameter part25-7c. An inner abutment surface25-7gthat abuts against an outer peripheral surface25-6gof the large-diameter part25-6cof the seat member25-6ais provided on an inner peripheral surface of the large-diameter part25-7c. A plurality of circulation holes25-7fare formed in the large-diameter part25-7con the negative side in the Y-axis direction with respect to the inner abutment surface25-7g. The circulation holes25-7fare connected to the sixth hole88-26. The second step part25-7dextends in a direction approximately orthogonal to the Y-axis direction, and connects the small-diameter part25-7band the large-diameter part25-7cto each other. An internal space surrounded by the seat member25-6and the body member25-7is a flow passage (internal oil passage)25-13through which the brake fluid flows. A valve part25-14is formed of the seat member25-6and the body member25-7.

A second filter member25-9is injection-molded of a resin material. The second filter member25-9is arranged at a position outside the body member25-7. The second filter member25-9is configured to filter the brake fluid flowing from the oil passage hole880into the circulation holes25-7f, to thereby prevent contamination and the like in the brake fluid from being transmitted to the armature25-4and the valve seat25-6f.

The seal member25-10is an O ring, and is mounted on an outer periphery of the small-diameter part25-7bof the body member25-7, to thereby seal a gap between an outer peripheral surface of the small-diameter part25-7band an inner peripheral surface of the SOL/V OUT accommodating hole845.

A description is now given of an operation of the SOL/V OUT25.

When the current is not supplied to the coil25-1, the armature25-4is urged by an urging force of the coil spring25-12toward the positive side in the Y-axis direction, and the tip part25-4bof the armature25-4thus abuts against the valve seat25-6f. Therefore, the oil passage hole880and the first hole88-41are shut off from each other.

When a predetermined current is supplied to the coil25-1, a magnetic path is formed in the yoke25-1l, the body center25-3, and the armature25-4, and an attraction force is generated between the body center25-3and the armature25-4. The armature25-4moves toward the negative side in the Y-axis direction by the attraction force, and when the tip part25-4bof the armature25-4separates from the valve seat25-6f, the oil passage hole880and the first hole88-41communicate with each other via the circulation holes25-7f, the axial oil passage25-5g, the first communication hole25-6e, and the second communication hole25-7e.

[Formation of Seat Members and Body Members]

The seat members and the body members of the normally-closed electromagnetic valve and the normally-open electromagnetic valve are different in diameter between the first communication hole and the second communication hole, but the other portions are common portions.FIGS. 15are views for illustrating a formation method for the seat member.FIG. 16are views for illustrating a formation method for the body member.

As illustrated inFIGS. 15andFIGS. 16, each of the seat member and the body member is formed into a rough shape by blanking (pressing) a sheet material. The, shaping is carried out by deburring, chamfering, and the like. Finally, the first communication hole and the second communication hole having diameters different depending on the electromagnetic valves are bored, and the forming is completed.

[Common Heights of Top Portion and Bottom Portion]

FIG. 17is a view for illustrating comparison of heights of the respective electromagnetic valves when valve ends (tips of the body members) of the respective electromagnetic valves are aligned on the same line.

As illustrated inFIG. 17, heights of the respective electromagnetic valves from the valve ends to surfaces on the positive side in the Y-axis direction of the crimped parts are equal to one another. The height (bottom-portion height) from the valve end to the surface on the positive side in the Y-axis direction of each of the electromagnetic valves is determined by the abutment of the body member of the normally-closed electromagnetic valve against the crimped part of the flange ring across the cylinder. A press-in amount of the seat member into the valve body of the normally-open electromagnetic valve is adjusted in accordance with the bottom-portion height determined by the normally-closed electromagnetic valve. Depths of the accommodating holes of the respective electromagnetic valves of the housing8can be set to be constant by equalizing the bottom-portion heights of the respective electromagnetic valves to one another.

Moreover, as illustrated inFIG. 17, heights from a plane of the housing8to the ends of the coils of the respective electromagnetic valves are equal to one another. The heights (top-portion heights) from the plane of the housing8to the ends of the coils of the respective electromagnetic valves are determined by heights of the coils. Heights of the yokes of the electromagnetic valves can be set to be constant.

Hitherto, the normally-closed electromagnetic valve and the normally-open electromagnetic valve have structures different from each other, and dedicated components are thus specified respectively therefor. The productivity may thus be degraded due to an increase in number of the components and working steps.

Thus, in the first embodiment, the valve part27-14of the normally-closed electromagnetic valve (such as the SS/V IN27) and the valve part21-14of the normally-open electromagnetic valve (such as the shutoff valve21) are caused to have the common portions. As a result, the valve part of the normally-closed electromagnetic valve and the valve part of the normally-open electromagnetic valve have the common portions, and most portions of both the valve parts can be common. Thus, the productivity of the electromagnetic valves can be improved.

Moreover, in the first embodiment, in the seat member27-6forming the valve part27-14of the normally-closed electromagnetic valve (such as the SS/V IN27) and the seat member21-6forming the valve part21-14of the normally-open electromagnetic valve (such as the shutoff valve21), the common portions having common shapes correspond to a portion other than the first communication hole27-6eof the seat member27-6and a portion other than the first communication hole21-6eof the seat member21-6. As a result, while the first communication holes are set in accordance with characteristics of the respective electromagnetic valves, the other portions of the seat members can be the common portions, and the productivity of the electromagnetic valves can thus be improved.

Moreover, in the first embodiment, in the body member27-7forming the valve part27-14of the normally-closed electromagnetic valve (such as the SS/V IN27) and the body member21-7forming the valve part21-14of the normally-open electromagnetic valve (such as the shutoff valve21), the common portions having common shapes correspond to a portion other than the second communication hole27-7eof the body member27-7and a portion other than the second communication hole21-7eof the body member21-7. As a result, while the second communication holes are set in accordance with characteristics of the respective electromagnetic valves, the other portions of the body members can be the common portions, and the productivity of the electromagnetic valves thus be improved.

Moreover, in the first embodiment, the normally-closed electromagnetic valve (such as the SS/V IN27) includes the electromagnetic drive part27-15formed of the coil27-1, the cylinder27-2, and the armature27-4, and the normally-open electromagnetic valve (such as the shutoff valve21) includes the electromagnetic drive part21-15formed of the coil21-1, the cylinder21-2, the armature21-3, and the valve body21-5. As a result, the valve parts having the common portions can be mounted in the normally-closed electromagnetic valve and the normally-open electromagnetic valve including the components different from each other.

Moreover, in the first embodiment, an axial length of the valve part21-14of the normally-open electromagnetic valve (such as the shutoff valve21) is set to be equal to the axial length of the valve part27-14of the normally-closed electromagnetic valve (such as the SS/V IN27). As a result, the depths of the accommodating holes of the housing8configured to accommodate the respective electromagnetic valves can be set to be equal, thereby being capable of increasing a degree of freedom in layout of an oil passage in the housing8.

Moreover, in the first embodiment, the depths from the surface of the housing8of the SS/V IN accommodating hole847of the housing8in which the valve part21-14of the normally-open electromagnetic valve (such as the shutoff valve21) is arranged and the shutoff valve accommodating hole841of the housing8in which the valve part27-14of the normally-closed electromagnetic valve (such as the SS/V IN27) is arranged are set to be equal. As a result, a thickness and a size of the housing8can be decreased, and an amount of machining when the accommodating holes are machined can be suppressed.

Moreover, in the first embodiment, the seat member27-6and the body member27-7of the normally-closed electromagnetic valve (such as the SS/V N27) and the seat member21-6and the body member21-7of the normally-open electromagnetic valve (such as the shutoff valve21) are formed through the press forming. As a result, the productivity of the seat member and the body member can be improved.

Moreover, in the first embodiment, both the SS/V IN accommodating hole847configured to accommodate the normally-closed electromagnetic valve (such as the SS/V IN27) and the shutoff valve accommodating hole841configured to accommodate the normally-open electromagnetic valve (such as the shutoff valve21) are formed so as to extend from the one surface of the housing8to the inside of the housing8. As a result, the thickness and the size of the housing8can be decreased. Moreover, ease of machining of the accommodating holes can be improved. Moreover, the electromagnetic valves can be mounted from one side surface of the housing8, and workability can thus be improved.

Moreover, in the first embodiment, the SOL/V OUT accommodating hole845and the SOL/V IN accommodating hole842of the housing8are arranged so as to be adjacent to each other, and the oil passage hole880configured to connect the SOL/V OUT accommodating hole845and the SOL/V IN accommodating hole842to each other of the oil passages to each other is formed along the one surface of the housing8. As a result, the oil passage hole880does not need to be formed so as to be inclined with respect to the surface of the housing8, and the size of the housing8can thus be decreased.

Moreover, in the first embodiment, the axial lengths of the coil27-1of the normally-closed electromagnetic valve (such as the SS/V IN27) and the coil27-1of the normally-open electromagnetic valve (such as the shutoff valve21) are set to be equal. As a result, the yokes can be common. Moreover, a size of the entire second unit1B can be decreased.

A description is given of effects in a case in which the SS/V IN27is applied as the normally-closed electromagnetic valve, and the shutoff valve21is applied as the normally-open electromagnetic valve. The same effects can be provided in a case in which the communication valve23, the SOL/V OUT25, and the SS/V OUT28are applied as the normally-closed electromagnetic valves, and the SOL/V IN22is applied as the normally-open electromagnetic valve (except for (9).

(1) The hydraulic pressure control device includes: the housing8, which internally includes the oil passage; the SS/V IN27(normally-closed electromagnetic valve), which includes the valve part27-14(first valve part) arranged so as to extend from the surface of the housing8to the inside of the housing8, and is configured to close the oil passage when a current is not supplied; and the shutoff valve21(normally-open electromagnetic valve), which includes the valve portion21-14(second valve part) being arranged so as to extend from the surface of the housing8to the inside of the housing8, and including the common portion having a shape common to the valve part27-14, and is configured to open the oil passage when a current is not supplied.

Thus, the valve part of the normally-closed electromagnetic valve and the valve part of the normally-open electromagnetic valve have the common portions, and most portions of both the valve parts can be common, and the productivity of the electromagnetic valves can thus be improved.

(2) The valve part27-14(first valve part) includes: the seat member27-6(first member), which is formed into a bottomed tubular shape having the opening27-6i(first opening) opened at one end, and has the first communication hole27-6e(first passage hole) formed in a bottom wall along an axial direction, and used to open/close the oil passage; and the body member27-7(second member), which is formed into the bottomed tubular shape having the opening27-7h(second opening) opened at one end, is fixed from the opening27-7h(second opening) side to the opening27-6i(first opening) in the axial direction, and has the second communication hole27-7e(second passage hole) being formed in the bottom wall, and communicating with the first communication hole27-6e(first passage hole) in the axial direction, and at least one circulation hole27-7f(first through hole) formed in the peripheral wall along the radial direction. The valve portion21-14(second valve part) includes: the seat member21-6(third member), which is formed into a bottomed tubular shape having the opening21-6i(third opening) opened at one end, and has the first communication hole21-6e(third passage hole) formed in the bottom wall along the axial direction, and used to open/close the oil passage; and the body member21-7(fourth member), which is formed into a bottomed tubular shape having the opening21-7h(fourth opening) opened at one end, is fixed from the opening21-7h(fourth opening) side to the opening21-6i(third opening) in the axial direction, and has the second communication hole21-7e(fourth passage hole) being formed in the bottom wall, and communicating with the first communication hole27-6e(first passage hole) in the axial direction, and at least one circulation hole21-7f(second through hole) formed in a peripheral wall along a radial direction. The common portions having common shapes correspond to the portion of the seat member27-6(first member) other than the first communication hole27-6e(first passage hole) and the portion of the seat member21-6(third member) other than the first communication hole21-6e(third passage hole).

Thus, while the first communication holes are set in accordance with the characteristics of the respective electromagnetic valves, the other portions of the seat members can be the common portions, and the productivity of the electromagnetic valves can thus be improved.

(3) The common portions having common shapes correspond to the portion of the body member27-7(second member) other than the second communication hole27-7e(second passage hole) and the portion of the body member21-7(fourth member) other than the second communication hole21-7e(fourth passage hole).

Thus, while the second communication holes are set in accordance with the characteristics of the respective electromagnetic valves, the other portions of the body members can be the common portions, and the productivity of the electromagnetic valves can thus be improved.

(4) The SS/V1N27(normally-closed electromagnetic valve) includes the electromagnetic drive part27-15(first electromagnetic drive part) including: the coil27-1(first electromagnetic coil), which is provided so as to extend from the surface of the housing8to the outside of the housing8, and is configured to generate an electromagnetic force when a current is supplied; the cylinder27-2(tubular member), which is made of a non-magnetic material, is arranged on the inner periphery of the coil27-1(first electromagnetic coil), and is connected to the opening27-7h(second opening) side of the body member27-7(second member) at the valve part27-14(first valve part); and the armature27-4(first movable member), which is formed of a magnetic body, is movably provided on the inner periphery of the cylinder27-2(tubular member), moves in the axial direction through the attraction force of the coil27-1(first electromagnetic coil), and includes the valve body27-4b(first valve body) used to open/close the first communication hole27-6e(first passage hole) on the tip side.

The shutoff valve21(normally-open electromagnetic valve) includes the electromagnetic drive part21-15(second electromagnetic drive part) including: the coil21-1(second electromagnetic coil), which is provided so as to extend from the surface of the housing8to the outside of the housing8, and is configured to generate an electromagnetic force when a current is supplied; the valve body21-5(fixed member), which is made of a magnetic material, is arranged on the inner periphery of the coil21-1(second electromagnetic coil), and is connected to the bottom wall side of the seat member21-6(third member) at the valve part21-14(second valve part); the cylinder21-2(cup-shaped member), which is made of a non-magnetic material, is arranged on the inner periphery of the coil21-1(second electromagnetic coil), and accommodates one end of the valve body21-5(fixed member); and the plunger21-4(second movable member), which is formed of a magnetic body, is movably provided on the inner periphery of the cylinder21-2(cup-shaped member), moves in the axial direction through the attraction force of the coil21-1(second electromagnetic coil), and includes the tip part21-4b(second valve body) used to open/close the first communication hole21-6e(third passage hole) on the tip side.

Thus, the valve parts having the common portions can be mounted in the normally-closed electromagnetic valve and the normally-open electromagnetic valve including the components different from each other.

(5) The axial length of the valve part21-14(second valve part) is set to be equal to the axial length of the valve part27-14(first valve part).

Thus, the depths of the accommodating holes of the housing8configured to accommodate the respective electromagnetic valves can be set to be equal to each other, thereby being capable of increasing the degree of freedom in layout of the oil passage in the housing8.

(6) The housing8has the SS/V IN accommodating hole847(first hole part), in which the valve part27-14(first valve part) is arranged, and the shutoff valve accommodating hole841(second hole part), which is equal to the SS/V N accommodating hole847(first hole part) in depth from the surface of the housing8, and in which the valve part21-14(second valve part) is arranged.

Thus, the thickness and the size of the housing8can be decreased, and the amount of machining when the accommodating holes are machined can thus be suppressed.

(7) The seat member27-6(first member), the body member27-7(second member), the seat member21-6(third member), and the body member21-7(fourth member) are formed through press forming.

Thus, the productivity of the seat member and the body member can be improved.

(10) Both the SS/V IN accommodating hole847(first hole part) and the shutoff valve accommodating hole841(second hole part) are formed so as to extend from the one surface of the housing8to the inside of the housing8.

Thus, the thickness and the size of the housing8can be decreased. Moreover, the ease of machining of the accommodating holes can be improved. Moreover, the electromagnetic valves can be mounted from the one side surface of the housing8, and the workability can thus be improved.

(11) The SOL/V OUT accommodating hole845(first hole part) and the SOL/V IN accommodating hole842(second hole part) are arranged so as to be adjacent to each other, and the oil passage hole880configured to connect the SOL/V OUT accommodating hole845(first hole part) and the SOL/V IN accommodating hole842(second hole part) to each other of the oil passage is formed along the one surface of the housing8.

Thus, the oil passage hole880does not need to be formed so as to be inclined with respect to the surface of the housing8, and the size of the housing8can thus be decreased.

(12) The SS/V IN27(normally-closed electromagnetic valve) includes the electromagnetic drive part27-15(first electromagnetic drive part) including the coil27-1(first electromagnetic coil), which is provided so as to extend from the surface of the housing8to the outside of the housing8, and is configured to generate an electromagnetic force through a current supply. The shutoff valve21(normally-open electromagnetic valve) includes the electromagnetic drive part21-15(second electromagnetic drive part) including the coil21-1(second electromagnetic coil), which is provided so as to extend from the surface of the housing8to the outside of the housing8, is configured to generate an electromagnetic force through a current supply, and has the axial length set to be equal to the axial length of the coil27-1(first electromagnetic coil).

Thus, the yokes can be common. Moreover, the size of the entire second unit1B can be decreased.

(13) The hydraulic pressure control device includes: the housing8, which internally includes the oil passage; the SS/V1N27(normally-closed electromagnetic valve), which includes the valve part27-14(first valve part) arranged from the surface of the housing8to the inside of the housing8, and is configured to close the oil passage when a current is not supplied; and the shutoff valve21(normally-open electromagnetic valve), which includes the valve part21-14(second valve part) being arranged from the surface of the housing8to the inside of the housing8, having the axial length set to be equal to the axial length of the valve part27-14(first valve part), and including the common portion having the shape common to the valve part27-14(first valve part), and is configured to open the oil passage when a current is not supplied.

Thus, the valve part of the normally-closed electromagnetic valve and the valve part of the normally-open electromagnetic valve have the common portions, and hence most portions of both the valve parts can be common. Thus, the productivity of the electromagnetic valves can be improved.

(17) The brake system includes: the first unit1A including: the master cylinder5, which is configured to generate the brake hydraulic pressure through the brake operation of a driver; and the stroke simulator6, into which the brake fluid having flowed out from the master cylinder5flows, and which is configured to generate a simulated operation reaction force of the brake pedal100(brake operation member); and the second unit1B integrally including: the housing8, which is connected to the first unit1A, and internally includes the oil passage; the pump3(hydraulic pressure source), which is provided to the inside of the housing8, and is configured to generate an operation hydraulic pressure for the wheel cylinder W/C provided to a wheel via the oil passage; the SS/V27(electromagnetic switching valve), which is a normally-closed electromagnetic valve including the valve part27-14(first valve part) arranged from the surface of the housing8to the inside of the housing8, and being configured to close when a current is not supplied, and is configured to permit an inflow of the brake fluid into the stroke simulator6; the shutoff valve21(electromagnetic shutoff valve), which is a normally-open electromagnetic valve including the valve part21-14(second valve part) being arranged from the surface of the housing8to the inside of the housing8, including the common portion having the shape common to the valve part27-14(first valve part), and being configured to open when a current is not supplied, and is configured to switch the communication state of the oil passage between the master cylinder8and the wheel cylinder W/C; and the ECU90(control unit), which is configured to drive the pump3(hydraulic pressure source), the shutoff valve21(electromagnetic shutoff valve), and the SS/V IN27(electromagnetic switching valve).

Thus, the valve part of the normally-closed electromagnetic valve and the valve part of the normally-open electromagnetic valve have the common portions, and hence most portions of both the valve parts can be common. Thus, the productivity of the electromagnetic valves can be improved.

Other Embodiments

The present invention have been described above based on the first embodiment. However, the specific configuration of the present invention is not limited to the first embodiment. A change in design without departing from the scope of the gist of the invention is encompassed in the present invention.

Now, technical ideas based on the embodiment are exemplified.

(8) In the hydraulic pressure control device described in the above-mentioned item (1),

an axial length of the second valve part may be set to be equal to an axial length of the first valve part

(9) In the hydraulic pressure control device described in the above-mentioned item (8),

the housing may have:

a first hole part, in which the first valve part is arranged; and

a second hole part, which is equal to the first hole part in depth from the surface of the housing, and in which the second valve part is arranged.

(14) In the hydraulic pressure control device described in the above-mentioned item (13),

the first valve part includes:a first member, which is formed into a bottomed tubular shape having a first opening opened at one end, and has a first passage hole formed in a bottom wall along an axial direction, and used to open/close the oil passage; anda second member, which is formed into a bottomed tubular shape having a second opening opened at one end, is fixed from the second opening side to the first opening in the axial direction, and has a second passage hole being formed in a bottom wall, and communicating with the first passage hole in the axial direction, and at least one first through hole formed in a peripheral wall along a radial direction,

the second valve part includes:a third member, which is formed into a bottomed tubular shape having a third opening opened at one end, and has a third passage hole formed in a bottom wall along an axial direction, and used to open/close the oil passage; anda fourth member, which is formed into a bottomed tubular shape having a fourth opening opened at one end, is fixed from the fourth opening side to the third opening in the axial direction, and has a fourth passage hole being formed in a bottom wall, and communicating with the third passage hole in the axial direction, and at least one second through hole formed in a peripheral wall along a radial direction, and

the common portions having common shapes correspond to a portion of the first member other than the first passage hole and a portion of the third member other than the third passage hole.

(15) In the hydraulic pressure control device described in the above-mentioned item (14),

the common portions having common shapes correspond to a portion of the second member other than the second opening and a portion of the fourth member other than the fourth opening.

(16) In the hydraulic pressure control device described in the above-mentioned item (15),

the normally-closed electromagnetic valve includes a first electromagnetic drive part including:a first electromagnetic coil, which is provided so as to extend from one surface of the housing to an outside of the housing, and is configured to generate an electromagnetic force when a current is supplied;a tubular member, which is made of a non-magnetic material, is arranged on an inner periphery of the first electromagnetic coil, and is connected to the second opening side of the second member at the first valve part; anda first movable member, which is formed of a magnetic body, is movably provided on an inner periphery of the tubular member, moves in the axial direction through an attraction force of the first electromagnetic coil, and includes a first valve body used to open/close the first passage hole on a tip side, and

the normally-open electromagnetic valve includes a second electromagnetic drive part including:a second electromagnetic coil, which is provided so as to extend from the one surface of the housing to the outside of the housing, and is configured to generate an electromagnetic force when a current is supplied;a fixed member, which is made of a magnetic material, is arranged on an inner periphery of the second electromagnetic coil, and is connected to a bottom wall side of the third member at the second valve part;a cup-shaped member, which is made of a non-magnetic material, is arranged on the inner periphery of the second electromagnetic coil, and accommodates one end of the fixed member; anda second movable member, which is formed of a magnetic body, is movably provided on an inner periphery of the cup-shaped member, moves in the axial direction through an attraction force of the second electromagnetic coil, and includes a second valve body used to open/close the third passage hole on a tip side.

(18) In the braking system described in the above-mentioned item (17),

the first valve part includes:a first member, which is formed into a bottomed tubular shape having a first opening opened at one end, and has a first passage hole formed in a bottom wall along an axial direction, and used to open/close the oil passage; anda second member, which is formed into a bottomed tubular shape having a second opening opened at one end, is fixed from the second opening side to the first opening in the axial direction, and has a second passage hole being formed in a bottom wall, and communicating with the first passage hole in the axial direction, and at least one first through hole formed in a peripheral wall along a radial direction,

the second valve part includes:a third member, which is formed into a bottomed tubular shape having a third opening opened at one end, and has a third passage hole formed in a bottom wall along an axial direction, and used to open/close the oil passage; anda fourth member, which is formed into a bottomed tubular shape having a fourth opening opened at one end, is fixed from the fourth opening side to the third opening in the axial direction, and has a fourth passage hole being formed in a bottom wall, and communicating with the third passage hole in the axial direction, and at least one second through hole formed in a peripheral wall along a radial direction, and

the common portions having common shapes correspond to a portion of the first member other than the first passage hole and a portion of the third member other than the third passage hole.

(19) In the braking system described in the above-mentioned item (18),

the common portions having common shapes correspond to a portion of the second member other than the second passage hole and a portion of the fourth member other than the fourth passage hole.

(20) In the braking system described in the above-mentioned item (19),

the normally-closed electromagnetic valve includes a first electromagnetic drive part including:a first electromagnetic coil, which is provided so as to extend from one surface of the housing to an outside of the housing, and is configured to generate an electromagnetic force when a current is supplied;a tubular member, which is made of a non-magnetic material, is arranged on an inner periphery of the first electromagnetic coil, and is connected to the second opening side of the second member at the first valve part; anda first movable member, which is formed of a magnetic body, is movably provided on an inner periphery of the tubular member, moves in the axial direction through an attraction force of the first electromagnetic coil, and includes a first valve body used to open/close the first passage hole on a tip side, and

the normally-open electromagnetic valve includes a second electromagnetic drive part including:a second electromagnetic coil, which is provided so as to extend from the one surface of the housing to the outside of the housing, and is configured to generate an electromagnetic force when a current is supplied;a fixed member, which is formed of a magnetic material, is arranged on an inner periphery of the second electromagnetic coil, and is connected to a bottom wall side of the third member at the second valve part;a cup-shaped member, which is made of a non-magnetic material, is arranged on the inner periphery of the second electromagnetic coil, and accommodates one end of the fixed member; anda second movable member, which is formed of a magnetic body, is movably provided on an inner periphery of the cup-shaped member, moves in the axial direction through an attraction force of the second electromagnetic coil, and includes a second valve body used to open/close the third passage hole on a tip side.

a coil, which forms a magnetic field when a current is supplied,

a yoke, which is made of a magnetic material, and is configured to accommodate the coil,

an armature, which is formed of a magnetic body, is arranged on an inner peripheral side of the yoke, and moves in an axial direction of the coil when a current is supplied to the coil,

a plunger, which is formed of a non-magnetic body, and moves along with the movement of the armature,

a valve body, which is formed into a tubular shape, and internally accommodates the plunger so as to be movable in the axial direction,

a valve part, which includes a first member being formed into a bottomed tubular shape having a first opening opened at one end, and having a first passage hole opened/closed by a tip part of the plunger on a bottom wall, and a second member being formed into a bottomed tubular shape having a second opening opened at one end, being fixed from the second opening side to the first opening in the axial direction, and having a second passage hole being formed in a bottom wall, and communicating with the first passage hole, and at least one first through hole formed in a peripheral wall along a radial direction, and

a coil spring, which is arranged between a reception part formed in the plunger and a reception part formed in the valve body so as to surround the plunger, and is configured to urge the plunger in a direction departing from the first communication hole.

A bottom wall side of the first member is inserted inside the valve body, thereby fixing the valve to the valve body.

A description has been given of only some embodiments of the present invention, but it is readily understood by a person skilled in the art that various changes and improvements can be made to the exemplified embodiments without practically departing from the novel teachings and advantages of the present invention. Thus, forms to which such changes and improvements are made are also intended to be included in the technical scope of the present invention. The above-mentioned embodiments may be arbitrarily combined.

The present application claims priority from the Japanese Patent Application No. 2015-207114 filed on Oct. 21, 2015. The entire disclosure including Specification, Scope of Claims, Drawings, and Abstract of Japanese Patent Application No. 2015-207114 filed on Oct. 21, 2015 is incorporated herein in its entirety by reference.

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