KR20210009369A - Brake hydraulic pressure control device - Google Patents

Abstract

Provides a brake hydraulic pressure control device 10 that improves the vehicle mountability by eliminating the motor while at the same time aiming to suppress the vibration of the brake hydraulic pressure control device 10 by improving the balance of the center when mounted on a vehicle. do. A brake hydraulic pressure control device 10 that controls the hydraulic pressure of the brake hydraulic pressure unit 20, comprising a housing 110 and a plurality of electronic control valves 36, 34, 58, 54 for increasing, reducing, or maintaining the hydraulic pressure. Wow, an accumulator 70 temporarily storing the working fluid, and a plurality of solenoid pumps 44 capable of discharging the working fluid stored in the accumulator 70, and the housing 10 includes a plurality of electronic control valves ( A second side (110b) having a valve mounting bore (131, 133, 135, 137) on which 36, 34, 58, 54) is mounted, and a plurality of solenoid type pumps 44 are mounted against the second side It has a first side (110a) having a pump mounting bore (143).

Description

Brake hydraulic pressure control device

The present invention relates to a brake hydraulic pressure control device.

BACKGROUND ART [0002] Conventionally, there is known a brake hydraulic pressure control device that performs brake control by controlling the hydraulic pressure of brake fluid supplied to the brake unit by a hydraulic circuit. The brake hydraulic pressure control device has a hydraulic unit and an electronic control unit (ECU).

The hydraulic unit includes a plurality of electromagnetic control valves, a pump, a motor that drives the pump, and the like. Such a plurality of electromagnetic control valves and motors are controlled and operated by the ECU, and the braking force generated in the wheel is controlled by increasing or decreasing the hydraulic pressure in the brake hydraulic circuit (see, for example, Patent Document 1).

The plurality of electromagnetic control valves are mounted on a surface of the housing opposite to the surface on which the motor is mounted. Further, at least a part of the piping port to which the piping is connected is formed on a surface vertically continuous on both the mounting surface of the motor and the mounting surface of the plurality of electromagnetic control valves in the housing. The plurality of electromagnetic control valves are arranged in a plurality of rows from the side close to the side where the piping port is formed to the side farther away.

A brake hydraulic pressure control device mounted on a four-wheeled vehicle is usually provided with 12 electromagnetic control valves. In general, a plurality of electromagnetic control valves are mounted on one surface of a housing so that a maximum of four electromagnetic control valves are arranged in one row (for example, see Patent Document 2). In accordance with the arrangement of the plurality of electromagnetic control valves, the length in two directions of one surface of the housing in which the plurality of electromagnetic control valves are mounted is designed.

[Patent Document 1] Japanese Unexamined Patent Application Publication No. 2016-203880 [Patent Document 2] Japanese Unexamined Patent Application Publication No. 2005-145239

Here, the motor is used to give eccentric rotation to the motor shaft and drive the plunger of the pump, but since the housing of the motor is mounted to protrude from the housing of the hydraulic unit, the dimension in the depth direction of the hydraulic unit increases. For this reason, it is necessary to form a space corresponding to the depth direction when the brake hydraulic pressure control device is attached to the vehicle, and there is a problem in the mountability of the brake hydraulic pressure control device.

In addition, when the brake hydraulic pressure control device is mounted on a vehicle, the brake hydraulic pressure is controlled so that the mounting surface of the motor and the mounting surface of a plurality of electronic control valves face the side, and the surface on which at least some piping ports are formed faces upward. The device is installed. When the number of electromagnetic control valves arranged in one row is set to four as in the conventional brake hydraulic pressure control device, it is difficult to reduce the size of the housing in the height direction when the surface on which the piping port is formed is the upper surface. For this reason, the central position of the brake hydraulic pressure control device is increased, and the balance is liable to deteriorate when mounted on a vehicle. In addition, in the case of a structure in which the heavy motor is disposed on the front surface of the brake hydraulic pressure control device, the weight balance in the depth direction of the device is deteriorated, and the dimension in the depth direction increases. As a result, there is a fear that the brake hydraulic pressure control device is liable to vibrate, and the sound vibration property is lowered. In addition, although a yaw rate sensor or an acceleration sensor may be mounted in the ECU of the brake hydraulic pressure control device, if the brake hydraulic pressure control device is liable to vibrate, there is a concern that the sensing characteristics of these sensors may be deteriorated.

The present invention has been made in view of the above problems, and improves the mountability of the device to the vehicle by excluding the motor, and at the same time improves the balance of the center when mounted on the vehicle, thereby suppressing the vibration of the brake hydraulic pressure control device. It is possible to provide a brake hydraulic pressure control device.

According to one aspect of the present invention, as a brake hydraulic pressure control device for controlling the hydraulic pressure of the brake hydraulic pressure unit 20, a housing, a plurality of electronic control valves for increasing, reducing, or maintaining the hydraulic pressure, and a working fluid are temporarily stored And a plurality of solenoid type pumps capable of discharging the working fluid stored in the accumulator, and the housing has a first surface having a valve mounting portion on which a plurality of electronic control valves are mounted, and a plurality of A brake hydraulic pressure control device is provided having a second surface having a pump mount on which a solenoid type pump is mounted.

As described above, according to the present invention, it is possible to suppress vibration of the brake hydraulic pressure control device by improving the balance of the center when mounted on the vehicle while improving mountability on the vehicle.

1 is a circuit diagram showing a configuration example of a brake hydraulic circuit 1 to which a brake hydraulic pressure control device 10 according to an embodiment of the present invention is applicable.
Fig. 2 is a perspective view of the brake hydraulic pressure control device according to the embodiment as viewed from the mounting surface side of the solenoid type pump.
3 is an exploded perspective view of a brake hydraulic pressure control device according to the embodiment.
4 is a perspective view showing the internal configuration of the housing according to the embodiment in solid lines.
Fig. 5 is an explanatory view showing an internal configuration diagram of a solenoid type pump in the brake hydraulic pressure control device according to the embodiment.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the present specification and drawings, components having substantially the same functional configuration are denoted by the same reference numerals, and redundant descriptions are omitted.

Referring to Fig. 1, a brief description will be given of a brake hydraulic circuit 1 to which the brake hydraulic pressure control device 10 according to the present embodiment is applicable.

The brake hydraulic circuit 1 shown in Fig. 1 is a hydraulic circuit of a brake system for a four-wheeled vehicle. The brake hydraulic circuit 1 is applied to a brake system that amplifies the pedal effort of a brake pedal by a driver and transmits it to a wheel cylinder without using a booster. However, the brake system may be an example in which a booster is used.

The brake hydraulic circuit 1 includes a first hydraulic circuit 28 and a second hydraulic circuit 30 having the same configuration. Brake fluid is supplied from the master cylinder 14 to the first hydraulic circuit 28 and the second hydraulic circuit 30.

The brake hydraulic circuit 1 controls hydraulic pressure by pairing one front wheel and one rear wheel at a diagonal position of the vehicle, respectively, by a first hydraulic circuit 28 and a second hydraulic circuit 30, It is composed of the so-called X-type piping method. In addition, the brake system is not limited to the X-type piping system.

The second hydraulic circuit 30 has the same configuration as the first hydraulic circuit 28. Hereinafter, the first hydraulic circuit 28 will be briefly described, and the description of the second hydraulic circuit 30 will be omitted.

The first hydraulic circuit 28 is provided with a plurality of pumps 44aa, 44ba, 44ca. Fig. 1 shows an example in which three pumps are installed in each of the first hydraulic circuit and the second hydraulic circuit. Further, the first hydraulic circuit 28 is provided with an accumulator 70a and a damper 75a.

The pumps 44aa, 44ba, 44ca are solenoid type pumps, and drive the plunger 146 by energizing the pump coil 83 to discharge brake fluid (see FIG. 5). The energization of the pump coil 83 is controlled by an electronic control unit (ECU) 90. The number of solenoid type pumps installed in the first hydraulic circuit 28 is not limited to three. In addition, the details of the solenoid type pump will be described separately with reference to FIG. 5.

A first pressure sensor 24 is provided in the pipeline communicating with the master cylinder 14. The first pressure sensor 24 detects the internal pressure of the master cylinder 14.

A second pressure sensor 26a is provided in the pipeline communicating with the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel. The second pressure sensor 26a detects the internal pressure of the wheel cylinder 38a.

Further, the second pressure sensor 26a may be provided in a pipeline communicating with the wheel cylinder 38b of the hydraulic brake 22b of the left and rear wheels to detect the internal pressure of the wheel cylinder 38b. In addition, such a pressure sensor can function as a brake fluid pressure control device even if it is not installed in the circuit.

The first hydraulic circuit 28 is provided with a plurality of electromagnetic control valves. The plurality of electromagnetic control valves are normally open type and linearly controllable circuit control valve 36a, and normally closed type and on/off suction control valve 34a. ), upper-open type and linearly controllable pressure-increasing valves 58aa and 58ba, and upper-closed type pressure-reducing valves 54aa and 54ba that are controlled on and off.

The circuit control valve 36a is disposed in a flow path 33a connecting the master cylinder 14 and the discharge side of the solenoid type pumps 44a, 44ba, 44ca. The circuit control valve 36a is capable of linear control, and continuously adjusts the flow path area between the master cylinder 14 and the pressure boosting valves 58aa and 58ba.

The suction control valve 34a is disposed in a flow path 31a connecting the master cylinder 14 and the suction side of the solenoid pumps 44a, 44ba, 44ca. The suction control valve 34a communicates or blocks the master cylinder 14 and the suction side of the solenoid type pumps 44a, 44ba, 44ca.

The pressure boosting valves 58aa and 58ba are arranged in flow paths 51aa and 51ba connecting the circuit control valve 36a and the wheel cylinders 38a and 38b. The pressure boosting valves 58aa and 58ba are capable of linear control, and from the master cylinder 14 and circuit control valve 36a side to the wheel cylinder 38a side of the hydraulic brake 22a of the front right wheel and the hydraulic brake of the left rear wheel. The flow rate of the hydraulic oil to the wheel cylinder 38b of (22b) is continuously adjusted.

The pressure reducing valves 54aa and 54ba are disposed in flow paths 53aa and 53ba connecting the suction side of the solenoid pumps 44a, 44ba and 44ca and the wheel cylinders 38a and 38b. The pressure reducing valves 54aa, 54ba communicate or block the suction side of the solenoid type pumps 44aa, 44ba, 44ca and the wheel cylinders 38a, 38b. The pressure reducing valves 54aa and 54ba reduce pressure by supplying hydraulic oil supplied to the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel to the accumulator 71a in the valve open state. By intermittently repeating the opening and closing of the pressure reducing valves 54aa and 54ba, the flow rate of the hydraulic oil flowing from the wheel cylinders 38a and 38b to the accumulator 71a can be adjusted.

The driving of this electronic control valve is controlled by the ECU 90. In addition, each of the electromagnetic control valves is not capable of linear control, and may be of an normally closed type or an upper open type.

The second hydraulic circuit 30 controls the hydraulic brake 22c of the left front wheel and the hydraulic brake 22d of the right rear wheel. The second hydraulic circuit 30 replaces the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel in the description of the first hydraulic circuit 28 with the wheel cylinder 38c of the hydraulic brake 22c of the left front wheel. And, except for replacing the wheel cylinder 38b of the hydraulic brake 22b of the left rear wheel with the wheel cylinder 38d of the hydraulic brake 22d of the right rear wheel, it is configured in the same manner as the first hydraulic circuit 28.

Next, with reference to Figs. 2 and 3, the overall configuration of the brake hydraulic pressure control device 10 according to the present embodiment will be described.

Fig. 2 is a perspective view of the brake hydraulic pressure control device 10 as viewed from the side of the mounting surface of the solenoid type pumps 44aa, 44ba, 44ca, 44ab, 44bb, 44cb and accumulators 70a, 70b. 3 is an assembled exploded view of the brake hydraulic pressure control device 10. 2 and 3, the illustration of the ECU 90 is omitted.

The illustrated brake hydraulic pressure control device 10 is a device for controlling the braking force of each wheel of a four-wheeled vehicle. The brake hydraulic pressure control device 10 includes a hydraulic pressure unit 20 and an ECU 90. The hydraulic unit 20 is provided with a brake hydraulic circuit 1 shown in FIG. 1.

The hydraulic unit 20 has a housing 110.

Six solenoid pumps 44aa, 44ba, 44ca, 44ab, 44bb, 44cb and two accumulators 70a and 70b are mounted on the first surface 110a of the housing 110. The solenoid type pumps 44aa, 44ba, 44ca, 44ab, 44bb, 44cb are mounted such that the plunger 146 faces the second side opposite the first side of the housing 110. Hereinafter, four vertically continuous surfaces on both the first and second surfaces 110a and 110b are respectively referred to as the third surface 110c, the fourth surface 110d, the fifth surface 110e, and the fourth surface 110e. It is made into 6 sides (110f).

The accumulators 70a and 70b incorporate check valves 71a and 71b, pistons 72a and 72b, and elastic bodies 73a and 73b that pressurize the piston, and cover accumulator bores 139a and 139b formed in the housing ( 74a, 74b) closed by.

Further, pipe ports 121a and 121b connected to the master cylinder are formed on the first surface 110a.

Accumulators (70a, 70b), piping ports (121a, 121b), and solenoid type pumps (44aa, 44ba, 44ca, 44ab, 44bb, 44cb) are the first row (L1) from the side close to the third side (110c) to the far side. ) To the fourth row (L4). Accumulators 70a and 70b are disposed in the first row L1. In the second row, piping ports 121a and 121b are disposed outside the accumulators 70a and 70b in the width direction of the hydraulic unit. Solenoid type pumps 44aa, 44ba, 44ca provided in the first hydraulic circuit among six solenoid type pumps in the third row, and solenoid type pumps 44ab, 44bb, 44cb provided in the second hydraulic circuit in the fourth column Is placed.

The solenoid-type pump is divided into two rows, the third row and the fourth row, and the third row and the fourth row are disposed to be shifted from each other in a parallel direction. Specifically, a solenoid-type pump 44bb provided in the second hydraulic circuit is between the solenoid-type pumps 44aa and 44ba provided in the first hydraulic circuit, and a solenoid-type pump 44cb provided in the second hydraulic circuit Is disposed between the solenoid type pumps 44ba and 44ca provided in the first hydraulic circuit.

For this reason, the pump coils 83bb and 83cb corresponding to the solenoid type pumps 44bb and 44cb are respectively arranged in the third row, and the pump coils 83aa, 83ba, 83ca corresponding to the solenoid type pumps 44aa, 44ba, 44ca, respectively. Since it can be disposed in the valley of (see FIG. 3), the height H between the third surface 110c and the sixth surface 110f can be formed compactly.

In addition, six solenoid pumps are mounted on the housing 110 with the plunger protruding from the second surface 110b of the housing 110. The protruding plunger is accommodated in the inside of the pump coils 83aa, 83ba, 83ca, 83ab, 83bb, 83cb built into the ECU housing. Details will be described with reference to FIG. 5.

Twelve electronic control valves are mounted on the second surface 110b of the housing 110. In addition, the ECU housing 90b accommodates an electromagnetic valve coil for driving an electromagnetic control valve, a pump coil for driving six solenoid type pumps, an electronic control valve, and an ECU that controls the operation of the solenoid type pump, and the ECU housing ( It is attached to the second surface of the housing 110 by applying an adhesive or the like to the opening of 90b).

The twelve electronic control valves include two circuit control valves 36a and 36b, two intake control valves 34a and 34b, four pressure increase valves 58aa, 58ba, 58ab, 58bb, and four pressure reducing valves ( 54aa, 54ba, 54ab, 54bb). When the 12 electronic control valves have one end fixed to the second surface by caulking or the like, and the ECU housing 90b is fixed to the second surface, the bodies of the 12 electronic control valves are 12 corresponding solenoid valves formed in a sleeve shape. It is accommodated inside the coils 61a, 61b, 62aa, 62ba, 62ab, 62bb, 63a, 63b, 64aa, 64ba, 64ab, 64bb.

Accordingly, the 12 coils 61a, 61b, 62aa, 62ba, 62ab, 62bb, 63a, 63b, 64aa, 64ba, 64ab, 64bb are also arranged in two rows in the ECU housing 90b like the 12 electronic control valves.

Four piping ports 123a, 123b, 123c, 123d to which pipings connected to the wheel cylinders are connected are formed on the third surface 110c.

4 is an explanatory view showing an example of the configuration of the housing 110 of the hydraulic unit 20. 4 is a perspective view showing the internal configuration of the housing 110 by a solid line, and is a view viewed from the side to which a plurality of electromagnetic control valves are attached.

The housing 110 is made of, for example, a light metal or metal such as aluminum. In the housing 110, an internal flow path, which is a flow path for brake fluid, is formed. Further, the housing 110 has a solenoid type pump, an electromagnetic control valve, and a plurality of attachment portions on which an accumulator is disposed. Each of the attachment portions is a cylindrical or frustum-shaped recess formed in the housing 110 by, for example, drilling.

The housing 110 has piping ports 121a and 121b as attachment portions on a first surface 110a, and a piping connecting the master cylinder and the first hydraulic circuit 28 is connected to the piping port 121a, and piping A pipe connecting the master cylinder and the second hydraulic circuit 30 is connected to the port 121b. The third surface 110c has a plurality of piping ports 123a, 123b, 123c, 123d as attachment portions, and a piping connected to the wheel cylinder of the hydraulic brake of the right front wheel is connected to the piping port 123a. A pipe connected to the wheel cylinder of the hydraulic brake of the left rear wheel is connected to the pipe port 123b. A pipe connected to the wheel cylinder of the hydraulic brake of the left front wheel is connected to the pipe port 123c. The piping port 123d is connected to a piping connected to the wheel cylinder of the hydraulic brake of the right rear wheel.

The housing 110 has pump mounting portions 143aa, 143ba, 143ca, 143ab, 143bb, and 143cb as an attachment portion on the first surface 110a. A solenoid-type pump 44aa is mounted on the pump mounting portion 143aa of the first surface 110a, a solenoid-type pump 44ba is mounted on the pump mounting portion 143ba, and a solenoid-type pump 44ca is mounted on the pump mounting portion 143ca. , A solenoid-type pump 44ab is mounted on the pump mounting portion 143ab, a solenoid-type pump 44bb is mounted on the pump mounting portion 143bb, and a solenoid-type pump 44cb is mounted on the pump mounting portion 143cb.

The housing 110 has accumulator bores 139a and 139b as attachment portions to the first surface 110a. Accumulators 71a and 71b are assembled in the accumulator bore 139a and 139b, respectively. The accumulators 70a and 70b include check valves 71a and 71b that prevent reverse flow of the brake fluid, pistons 72a and 72b, elastic members 73a and 73b that pressurize the piston, and covers 74a and 74b. Consists of Check valves 71a, 71b, pistons 72a, 72b, and elastic members 73a, 73b are inserted into the accumulator bore 139a, 139b, and cover 74a, in the opening of the accumulator bore 139a, 139b, By attaching 74b), accumulators 70a and 70b are configured.

The housing 110 has valve mounting portions 131a to 131d, 133a to 133b, 135a to 135b, and 137a to 137d to which a plurality of electronic control valves are mounted as an attachment portion on the second surface 110b.

The valve mounting portion 131a is equipped with a pressure boosting valve 58aa for supplying brake fluid to the wheel cylinder of the hydraulic brake of the right front wheel. The valve mounting portion 131b is equipped with a pressure boosting valve 58ba that supplies brake fluid to the wheel cylinder of the hydraulic brake of the left and rear wheels. The valve mounting portion 131c is equipped with a pressure boosting valve 58ab that supplies brake fluid to the wheel cylinder of the hydraulic brake of the left front wheel. The valve mounting portion 131d is equipped with a pressure boosting valve 58bb for supplying brake fluid to the wheel cylinder of the hydraulic brake of the right and rear wheels.

The circuit control valve 36a of the first hydraulic circuit 28 is mounted on the valve mounting portion 133a. The circuit control valve 36b of the second hydraulic circuit 30 is mounted on the valve mounting portion 133b. The intake control valve 34a of the first hydraulic circuit 28 is mounted on the valve mounting portion 135a. The intake control valve 34b of the second hydraulic circuit 30 is mounted on the valve mounting portion 135b.

A pressure reducing valve 54aa for discharging brake fluid from the wheel cylinder of the hydraulic brake of the right front wheel is mounted on the valve mounting portion 137a. A pressure reducing valve 54ba for discharging brake fluid from the wheel cylinder of the hydraulic brake of the left rear wheel is mounted on the valve mounting portion 137b. A pressure reducing valve 54ab for discharging the brake fluid from the wheel cylinder of the hydraulic brake of the left front wheel is mounted on the valve mounting portion 137c. A pressure reducing valve 54bb for discharging the brake fluid from the wheel cylinder of the hydraulic brake of the right rear wheel is mounted on the valve mounting portion 137d.

The arrangement of a plurality of electromagnetic control valves in the brake hydraulic pressure control device 10 according to the present embodiment will be described with reference to FIGS. 3 and 4.

The plurality of electromagnetic control valves are arranged in a first row (L1') and a second row (L2') from the side closer to the third surface 110c on the second surface 110b to the side farther away. In the first row L1', a total of six electronic control valves, including four boosting valves 58aa, 58ba, 58ab, and 58bb, and two circuit control valves 36a and 36b, are disposed.

In the second row L2', a total of six electronic control valves, including four pressure reducing valves 54aa, 54ba, 54ab, and 54bb, and two intake control valves 34a and 34b, are arranged.

In the brake hydraulic pressure control device 10 according to the present embodiment, six electromagnetic control valves are arranged in the first row L1' of the housing 110, so that a total of 12 electromagnetic control valves are arranged in two rows. For this reason, the distance H between the third surface 110c and the sixth surface 110f is shorter than the distance W between the fourth surface 110d and the fifth surface 110e. In general, since the brake hydraulic pressure control device 10 is mounted on the vehicle so that the third surface 110c on which the piping port is formed is positioned upward, the height H is shorter than the width W of the brake hydraulic pressure control device 10. Lose.

In an ordinary brake hydraulic pressure control device, the center position of the brake hydraulic pressure control device in which a motor, an ECU, a pump, and the like are assembled is relatively low. For this reason, the support of the brake hydraulic pressure control device fixed to the bracket for mounting on the vehicle through the support member may become unstable, but in the brake hydraulic pressure control device 10 according to the present embodiment, a plunger pump driven by a motor is used. Instead of using a solenoid type pump, further arranging a plurality of solenoid valves on the upper side, and arranging a plurality of solenoid type pumps at the bottom thereof, thereby achieving a balance of the center, and as a result, the brake hydraulic pressure control device 10 Vibration is suppressed, and sound vibration is improved.

In addition, the ECU 90 of the brake hydraulic pressure control device 10 may be provided with a yaw rate sensor or an acceleration sensor used for brake control such as an ESP (Electronic Stability Program).

In the brake hydraulic pressure control device 10 according to the present embodiment, since vibration is suppressed, the sensing characteristics of such a yaw rate sensor or an acceleration sensor are improved.

Further, in the brake hydraulic pressure control device 10 according to the present embodiment, since the length in the width W direction is enlarged, the vibration stability at the time of attachment of the brake hydraulic pressure control device can be further improved.

In the brake hydraulic pressure control device 10 according to the present embodiment, the circuit control valves 36a, 36b arranged in the first row L1' of the second surface 110b are four boosting valves 58aa, 58ba, 58ab. , 58bb), that is, it is arranged so as to sandwich these intensifying valves.

Since the circuit control valves 36a, 36b and the pressure boosting valves 58aa, 58ba, 58ab, and 58bb are arranged in the same row, the height (H) dimension of the brake hydraulic pressure control device in the design of the pipeline formed in the hydraulic unit Can be further reduced. Further, since the circuit control valves 36a and 36b are located outside the two boosting valves 58aa, 58ba, 58ab, 58bb, the complexity of the hydraulic circuit formed inside the housing 110 is reduced. Thereby, the housing 110 is suppressed from being excessively large.

In addition, in the brake hydraulic pressure control device 10 according to the present embodiment, the intake control valves 34a and 34b disposed in the second row L2' of the second surface 110b are four pressure reducing valves 54aa and 54ba. , 54ab, 54bb). Similar to the first row L1', this arrangement also contributes to reducing the complexity of the hydraulic circuit formed inside the housing 110.

Referring to Fig. 5, the operation of the solenoid type pump of the present invention will be described.

In Fig. 5, a structure of one solenoid type pump 44 and a corresponding pump coil 83 is shown, but other solenoid type pumps and pump coils 83 have the same structure.

The solenoid type pump 44 has a pump body 145 and a plunger 146 engaged with the pump body 145. The pump coil 83 guides the plunger 146 to a fixed core 147 fixed to the opening of the pump coil, a movable core 148 disposed at a rear portion (bottom of the pump coil) of the fixed core 147, A bobbin 149 disposed so as to surround the movable core 148 and the fixed core 147 is provided.

The pump body 145, the pump housing 145a, the filter 145b installed to cover the opening of the pump housing 145a, the pump chamber 145c installed inside the pump housing, and the plunger 146 In contact with the pump element 145e, the suction valve 145d installed in the opening of the pump housing, the discharge valve 145f installed in the discharge port of the bottom of the pump housing 145a, and attached to the opening of the pump mounting portion 143 And a pump cover 144 that accommodates a valve spring 145fb that pressurizes the discharge valve 145f. Both the intake valve 145d and the discharge valve 145f are valves for preventing reverse flow, and the intake valve 145d is a spherical valve body 145da and a valve spring that presses the valve body 145da in the valve closing direction. (145db), and the discharge valve 145f is composed of a spherical valve body 145fa and a valve spring 145fb that presses the valve body 145fa in the valve closing direction.

The plunger 146 is maintained to be movable in the axial direction by a fixed core 147 formed in a sleeve shape and a seal ring 150 installed at an opening on the pump coil side of the pump mounting portion 143.

The bobbin 149 has a hollow bottom hole, and a movable core 148 is accommodated in the bottom of the bottom hole so as to be movable in the axial direction. The coil assembly 149a is housed in the bobbin 149.

When the coil assembly 149a is excited, a magnetic circuit is formed, and the movable core 148 is pulled downward in FIG. 5. Pressurized by the movable core 148, the plunger 146 moves toward the pump chamber 145c. At the same time as the volume of the pump chamber 145c is reduced, the pump chamber 145c is increased in pressure, the valve body 145fa of the discharge valve 145f moves outward, and the discharge valve 145f is opened. The working fluid in the pump chamber 145c flows to the discharge valve 145f and flows out to the brake duct connected to the pump discharge side.

Subsequently, when the coil assembly 149a is demagnetized, the plunger 146 and the movable core 148 are retracted by the pressing force of the plunger spring 146a. At the same time as the volume of the pump chamber 145c increases, the pump chamber 145c is depressurized, the valve body 145fa of the discharge valve 145f moves to the pump chamber 145c side, and the discharge valve 145f is closed. When the pump chamber 145c is further depressurized, the valve element 145da of the suction valve 145d moves to the pump chamber 145c side, and the suction valve 145d is opened. The working fluid flows from the suction side pipe of the pump to the suction valve 145d, and is further sucked into the pump chamber 145c. Subsequently, the valve body 145da of the intake valve 145d moves to the filter 145b side, and the intake valve 145d is closed. By repeating such an operation, suction and discharge of the working fluid are continuously performed.

The solenoid type pump is a pump operated by movement in the axial direction, and the diameter in the depth direction of the hydraulic pressure control unit can be made sufficiently smaller than a conventional pump using a rotary motor as a drive source. In addition, by moving the plunger in the axial direction, it is possible to reduce wear of the seal ring and improve the life of the unit as compared to a pump using a conventional rotary motor that drives the plunger by eccentric rotation. Further, since the rotary motor becomes unnecessary, it is possible to prevent the generation of noise caused by the rotation of the motor.

The solenoid type pump 44 is arranged so that the axis of the movable core 148 is in the same direction as the axis of the plunger 146, and thus can be arranged in a small space. For this reason, by using the solenoid type pump 44, compared with a pump that uses a motor as a drive source, for example, it is possible to achieve a reduction in size and weight while reducing the size. In addition, since it is not necessary to arrange the motor in a direction perpendicular to the axis of the pump as in the prior art, the degree of freedom in the layout of the hydraulic unit 20 can be increased, and the mountability of the brake hydraulic pressure control device 10 to the vehicle is improved. I can. In addition, by installing a plurality of solenoid-type pumps 44 and individually controlling the drive of the solenoid-type pumps 44 to cancel each other out of pulsations generated by the discharge pressure from the solenoid-type pumps 44, pulsation is generated. It is also possible to reduce significantly.

In the above, preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to these examples. It is clear that those of ordinary skill in the technical field to which the present invention pertains can conceive of various modifications or modifications within the scope of the technical idea described in the claims. Also, of course, it is understood that it belongs to the technical scope of the present invention.

For example, the brake hydraulic circuit 1 described in the above embodiment had dampers 75a and 75b in the first hydraulic circuit 28 and the second hydraulic circuit 30, respectively, but these dampers 75a , 75b) may be omitted.

In addition, the brake hydraulic pressure control device 10 described in the above embodiment was provided with second pressure sensors 26a and 26b for detecting the internal pressure of the wheel cylinder, but these second pressure sensors 26a and 26b are omitted. It may be done.

In addition, in the brake hydraulic pressure control device 10 described in the above embodiment, the piping ports 121a and 121b to which the pipes connected to the master cylinder are connected are connected to the first surface 110a, and the pipes connected to the wheel cylinders are connected. Although the piping ports 123a to 123d were formed on the third surface 110c, the present invention is not limited to this example. Some piping ports may be formed on the other side. For example, the piping ports 121a and 121b to which piping connected to the master cylinder is connected may be provided on the third surface 110c like the piping ports 123a to 123d.

10… Brake hydraulic pressure control device, 20... Hydraulic unit, 34a, 34b... Intake control valve, 36a, 36b... Circuit control valves, 44aa, 44ba, 44ca, 44ab, 44bb, 44cb... Solenoid type pump, 51aa, 51ba, 51ab, 51bb... Euro, 54aa, 54ba, 54ab, 54bb... Pressure reducing valve, 58aa, 58ba, 58ab, 58bb... Pressure boosting valve, 70a, 7Ob... Accumulator, 110... Housing, 110a... Page 1, 110b … Page 2, 110c... Page 3, 121a, 121b... Piping ports, 123a, 123b, 123c, 123d... Piping port

Claims (9)

As a brake hydraulic pressure control device 10 that controls the hydraulic pressure of the brake hydraulic pressure unit 20,
The housing 110,
A plurality of electronic control valves (34a, 34b, 36a, 36b, 54aa, 54ba, 54ab, 54bb, 58aa, 58ba, 58ab, 58bb) for increasing, reducing, or maintaining the hydraulic pressure, and
Accumulators (70a, 70b) for temporarily storing the working fluid,
A plurality of solenoid type pumps 44aa, 44ba, 44ca, 44ab, 44bb, 44cb capable of discharging the working fluid stored in the accumulators 70a and 70b are provided,
The housing 110 is:
The first surface having a valve mounting portion (131, 133, 135, 137) on which the plurality of electronic control valves (34a, 34b, 36a, 36b, 54aa, 54ba, 54ab, 54bb, 58aa, 58ba, 58ab, 58bb) are mounted and,
A second surface having a pump mounting portion (143aa, 143ba, 143ca, 143ab, 143bb, 143cb) on which the plurality of solenoid type pumps (44aa, 44ba, 44ca, 44ab, 44bb, 44cb) are mounted Having
Brake hydraulic pressure control device. The method of claim 1, wherein the valve mounting portions (131, 133, 135, 137) are arranged in two rows on the first surface,
Brake hydraulic pressure control device. The method of claim 1 or 2, wherein the pump mounting portions (143aa, 143ba, 143ca, 143ab, 143bb, 143cb) are arranged in two rows on the second side,
Brake hydraulic pressure control device. The pump mounting portion (143aa, 143ba, 143ca, 143ab, 143bb, 143cb) arranged in two rows is the pump mounting portion (143aa, 143ba, 143ca) arranged in the first row according to any one of claims 1 to 3 And the pump mounting portions (143ab, 143bb, 143cb) disposed in the second row are arranged to be offset from each other in the parallel direction,
Brake hydraulic pressure control device. The method according to any one of claims 1 to 4, wherein an accumulator bore (139a, 139b) for assembling the accumulator is formed on the second side,
Brake hydraulic pressure control device. The method according to any one of claims 1 to 5, wherein the plurality of solenoid valves are flow paths (33a, 121b) connecting pipe ports (121a, 121b) to which pipes connected to the master cylinder are connected, and the discharge side of the solenoid type pump (33a, 33b), and pipe ports 123a, 123b, 123c, 123d to which pipes connected to the circuit control valves 36a and 36b and the wheel cylinder are connected. Including four pressure boosting valves (58aa, 58ba, 58ab, 58bb) disposed in the flow paths (51aa, 51ba, 51ab, 51bb), the two circuit control valves and the four pressure boosting valves are arranged in the same row,
Brake hydraulic pressure control device. The brake hydraulic pressure control device according to claim 6, wherein the four pressure boosting valves are disposed between the two circuit control valves. The method according to any one of claims 1 to 7, wherein the plurality of electromagnetic valves are:
Two suction control valves (34a, 34b) disposed in the pipe ports (121a, 121b) to which the pipes connected to the master cylinder are connected and the flow paths (31a, 31b) connecting the suction side of the solenoid type pumps (44a, 44b) )Wow
4 arranged in flow paths 53aa, 53ba, 53ab, 53bb connecting pipe ports 123a, 123b, 123c, 123d to which pipes connected to the suction side of the solenoid pumps 44a and 44b and the wheel cylinders are connected Including four pressure reducing valves (54aa, 54ba, 54ab, 54bb),
The two intake control valves and the four pressure reducing valves are disposed in the same row,
Brake hydraulic pressure control device. 9. The brake hydraulic pressure control device according to claim 8, wherein the four pressure reducing valves are disposed between the two circuit intake valves.

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