阅读说明：本技术 制动液压控制装置 (Brake fluid pressure control device ) 是由 仁张勉 于 2020-03-27 设计创作，主要内容包括：本发明涉及控制多个系统的液压回路(28,30)的液压的制动液压控制装置(20),该制动液压控制装置具备压力供给单元(90)和液压块(130),前述压力供给单元(90)具备马达(96)及泵元件(80),前述液压块(130)具备控制阀(34,36,54,58),前述控制阀(34,36,54,58)调节与压力供给单元(90)连接的液路及多个系统的液压回路(28,30)的液压,压力供给单元(90)具备马达(96)、斜板(127)、泵元件(80),前述马达(96)具有定子(97)及转子(98),前述斜板(127)被相对于转子(98)的旋转轴的轴线方向倾斜配置,前述泵元件(80)具有被通过马达(96)的旋转而驱动的多个泵部(44),泵元件(80)的至少一部分被配置于转子(98)的内部。(The present invention relates to a brake fluid pressure control device (20) for controlling the fluid pressure of a plurality of hydraulic circuits (28, 30), the brake fluid pressure control device comprising a pressure supply unit (90) and a hydraulic block (130), the pressure supply unit (90) comprising a motor (96) and a pump element (80), the hydraulic block (130) comprising control valves (34, 36, 54, 58), the control valves (34, 36, 54, 58) adjusting the fluid pressure of a fluid passage connected to the pressure supply unit (90) and the fluid pressure of the plurality of hydraulic circuits (28, 30), the pressure supply unit (90) comprising a motor (96), a swash plate (127), and a pump element (80), the motor (96) comprising a stator (97) and a rotor (98), the swash plate (127) being disposed so as to be inclined with respect to the axial direction of the rotation shaft of the rotor (98), the pump element (80) comprising a plurality of pump sections (44) driven by the rotation of the motor (96), at least a part of the pump element (80) is disposed inside the rotor (98).)

1. A brake hydraulic pressure control apparatus (20) that controls hydraulic pressures of hydraulic circuits (28, 30) of a plurality of systems,

comprises a pressure supply unit (90) and a hydraulic block (130),

the pressure supply unit (90) includes a motor (96) and a pump element (80),

the hydraulic block (130) includes a fluid path connected to the pressure supply unit (90) and control valves (34, 36, 54, 58) for adjusting the hydraulic pressures of the hydraulic circuits (28, 30) of the plurality of systems,

the pressure supply unit (90) is provided with the motor (96), a swash plate (125), and the pump element (80),

the motor (96) has a stator (97) and a rotor (98),

the swash plate (125) is disposed so as to be inclined with respect to the axial direction of the rotating shaft of the rotor (98),

the pump element (80) has a plurality of pump sections (44) driven by the rotation of the motor (96),

at least a part of the pump element (80) is disposed inside the rotor (98).

2. The brake hydraulic control device according to claim 1,

the pump element (80) is assembled by being inserted into a recess (98a) or a hole provided in the rotor (98) from the hydraulic block (130) side,

the piston (151) of the pump section (44) abuts the swash plate (125) disposed in the recess (98a) or hole.

3. The brake hydraulic pressure control apparatus according to claim 1 or 2,

the pressure supply unit (90) is mounted on one side surface (130a) of the hydraulic block (130),

the pump element (80) has an introduction path (169) into which the working fluid is introduced and a discharge path (179) from which the working fluid is discharged,

the introduction passage (169) and the discharge passage (179) open to a surface facing the one side surface (130a) of the hydraulic block (130).

4. The brake hydraulic pressure control device according to claim 3,

sealing rings (202a, 202b) are provided around the connection between the introduction passage (169) of the pressure supply unit (90) and the fluid path of the hydraulic block (130), and around the connection between the discharge passage (179) of the pressure supply unit (90) and the fluid path of the hydraulic block (130), respectively.

5. The brake hydraulic pressure control device according to any one of claims 1 to 4,

a damper component (200) is located between the pressure supply unit (90) and the hydraulic block (130).

6. The brake hydraulic pressure control device according to any one of claims 1 to 5,

each of the pump sections (44) has a piston (151), a housing chamber (153), and a discharge valve (180),

the piston (151) reciprocates substantially in parallel to the axial direction of the rotary shaft in accordance with the rotation of the motor (96),

the housing chamber (153) houses a part of the piston (151) and receives brake fluid,

the discharge valve (180) discharges brake fluid from the housing chamber (153).

Technical Field

The present invention relates to a brake hydraulic pressure control device that controls hydraulic pressures of hydraulic circuits of a plurality of systems.

Background

Conventionally, there is known a brake fluid pressure control device that performs brake control by controlling a fluid pressure of brake fluid supplied to a brake unit via a fluid pressure circuit. The brake hydraulic pressure control device is a hydraulic circuit including two systems for front wheels and two systems for rear wheels in the case of a two-wheeled vehicle, two systems for front wheels and two systems for rear wheels in the case of a four-wheeled vehicle, or two systems for grouping front wheels and rear wheels located at opposite corners, respectively.

The brake fluid pressure control device includes a regulating valve that can be opened and closed freely, a pump element that operates in conjunction with the regulating valve, an electric motor that drives the pump element, and the like. The brake hydraulic pressure control device is electronically controlled and automatically operated to increase or decrease the hydraulic pressure in the brake hydraulic circuit, thereby controlling the braking force generated at the wheels.

For example, the pump element has a piston that contacts an eccentric cam provided on the motor shaft and reciprocates by rotation of the eccentric cam. The pump element sucks in the brake fluid through the suction valve and discharges the brake fluid through the discharge valve in accordance with the reciprocating movement of the piston (see, for example, patent document 1).

Patent document 1: japanese patent laid-open publication No. 2015-205686.

Here, in the conventional brake fluid pressure control device, all components such as the control valve, the pump element, and the electric motor are individually assembled to the hydraulic block in which the fluid passage is formed. Since these components are individually subjected to generation of Noise Vibration (NVH), it is necessary to take measures against noise vibration such as providing a damper for each component. Further, when the components are assembled to the hydraulic block, the outer shape of the brake hydraulic pressure control device may become large, and mountability to the vehicle may be reduced.

Disclosure of Invention

The present invention has been made in view of the above problems, and provides a brake fluid pressure control device that can simplify measures against sound vibration and can reduce the size of the outer shape.

According to an aspect of the present invention, there is provided a brake fluid pressure control device that controls fluid pressures in a plurality of hydraulic circuits, the brake fluid pressure control device including a pressure supply unit and a hydraulic block, the pressure supply unit including a motor and a pump element, the hydraulic block including a fluid passage connected to the pressure supply unit and a control valve that adjusts the fluid pressures in the plurality of hydraulic circuits, the pressure supply unit including a motor, a swash plate, and a pump element, the motor including a stator and a rotor, the swash plate being disposed obliquely with respect to an axial direction of a rotating shaft of the rotor, the pump element including a plurality of pump portions driven by rotation of the motor, and at least a part of the pump element being disposed inside the rotor.

Effects of the invention

As described above, according to the present invention, it is possible to simplify the sound vibration countermeasure of the brake fluid pressure control device and to reduce the size of the outer shape.

Drawings

Fig. 1 is a circuit diagram showing a brake hydraulic circuit according to an embodiment of the present invention.

Fig. 2 is a schematic diagram showing the brake hydraulic pressure control device of the embodiment.

Fig. 3 is a sectional view showing the pressure supply module of this embodiment.

Fig. 4 is a perspective view showing an external appearance of the pump element of the embodiment.

Fig. 5 is a sectional view showing a configuration example of the pump element of the embodiment.

Detailed Description

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

< 1. Hydraulic Circuit for braking

A configuration example of a brake hydraulic pressure circuit 1 to which the brake hydraulic pressure control device 20 of the present embodiment can be applied will be described with reference to fig. 1.

The brake hydraulic circuit 1 according to the present embodiment is applied to a brake system that amplifies the depression force of the brake pedal 10 by the driver and transmits the amplified depression force to the wheel cylinders without using a booster. The brake system shown in fig. 1 is a brake system for a four-wheeled vehicle. However, the brake hydraulic circuit 1 may be applied to a brake system in which the depression force of the brake pedal 10 by the driver is amplified by the booster and transmitted to the wheel cylinders.

The brake pedal 10 is depressed by the driver when braking the vehicle. If the element is an element that can input the braking request of the driver, the element may be replaced with an operation element of the brake pedal 10.

The brake pedal 10 is connected to a piston rod 11. The piston rod 11 is provided with a stroke sensor 8 for detecting an axial displacement amount, i.e., a stroke amount, of the piston rod 11.

The reservoir tank 16 holds a working fluid as a fluid for generating hydraulic pressure. The reservoir tank 16 is connected to the master cylinder 14, and supplies the working fluid into the master cylinder 14.

The master cylinder 14 holds the first piston 12a and the second piston 12b so as to be movable forward and backward. The master cylinder 14 shown in fig. 1 is a tandem type master cylinder 14, and has two pressure chambers 13a, 13b partitioned by a first piston 12a and a second piston 12 b.

The first piston 12a is provided at the end of the piston rod 11. The second piston 12b is connected to the first piston 12a via a spring 15a disposed in the pressure chamber 13 a. A spring 15b connected to the second piston 12b is disposed in the pressure chamber 13 b. For example, the spring forces of the two springs 15a, 15b are the same.

The respective capacities of the two pressure chambers 13a, 13b vary in accordance with the stroke amount of the piston rod 11. The two pressure chambers 13a, 13b are connected to hydraulic circuits 28, 30, respectively. By the operation of the brake pedal 10, the first piston 12a and the second piston 12b are pressed via the piston rod 11, and the hydraulic fluid is moved to the hydraulic circuits 28, 30.

The brake hydraulic control device 20 includes two hydraulic circuits 28, 30 having the same structure. The hydraulic fluid is supplied from one of the pressure chambers 13a of the master cylinder 14 to one of the hydraulic circuits 28. The hydraulic fluid is supplied from the other pressure chamber 13b of the master cylinder 14 to the other hydraulic circuit 30.

The brake hydraulic circuit 1 of the present embodiment is configured in a so-called X-pipe system in which hydraulic pressure is controlled in groups of one front wheel and one rear wheel located diagonally with respect to the vehicle by the respective hydraulic circuits 28 and 30.

In the example shown in fig. 1, the hydraulic fluid is supplied to the wheel cylinder 38a of the hydraulic brake 22a of the front right wheel (FR) and the wheel cylinder 38b of the hydraulic brake 22b of the rear left wheel (RL) via the hydraulic circuit 28. The hydraulic fluid is supplied to the wheel cylinder 38c of the hydraulic brake 22c of the front left wheel (FL) and the wheel cylinder 38d of the hydraulic brake 22d of the rear right wheel (RR) via the hydraulic circuit 30.

The brake system is not limited to the X-pipe system. The brake system is not limited to the brake system for a four-wheel vehicle, and may be a brake system for a two-wheel vehicle or other vehicles.

In the brake hydraulic pressure circuit 1 of the present embodiment, the hydraulic pressure circuit 30 has the same configuration as the hydraulic pressure circuit 28. The hydraulic circuit 28 will be described below, and the hydraulic circuit 30 will not be described.

The hydraulic circuit 28 to which the hydraulic fluid is supplied from the pressure chamber 13a of the master cylinder 14 includes a plurality of solenoid valves. The solenoid valves include a normally closed and linearly controllable circuit control valve 36, a normally closed and open/close controllable suction control valve 34, normally open and linearly controllable pressure increase valves 58a, 58b (hereinafter, collectively referred to as pressure increase valves 58 unless otherwise specified), and normally closed and open/close controllable pressure decrease valves 54a, 54b (hereinafter, collectively referred to as pressure decrease valves 54 unless otherwise specified).

The hydraulic circuit 28 includes a pump section 44 driven by a motor 96. The hydraulic circuit 28 includes an accumulator 71 and a damper 73.

The circuit control valve 36 connects or disconnects the master cylinder 14 and the pressure increasing valves 58a, 58 b. The suction control valve 34 communicates or shuts off between the master cylinder 14 and the suction side of the pump section 44. The driving of the circuit Control valve 36 and the suction Control valve 34 is controlled by an Electronic Control Unit (ECU) not shown in the figure.

The circuit control valve 36 has a bypass flow path 41 provided with a check valve 40. The check valve 40 can move the hydraulic fluid through a bypass passage 41 from the master cylinder 14 side to the hydraulic brake 22a for the right front wheel and the hydraulic brake 22b for the left rear wheel. On the other hand, the check valve 40 prevents the hydraulic fluid from moving to the bypass passage 41 on the master cylinder 14 side from the hydraulic brake 22a of the right front wheel and the hydraulic brake 22b of the left rear wheel.

The check valve 40 secures the movement of the hydraulic fluid from the master cylinder 14 side to the hydraulic brake 22a of the right front wheel and the hydraulic brake 22b of the left rear wheel when the circuit control valve 36 is in the closed state due to, for example, a failure of the circuit control valve 36.

The pressure increasing valve 58a and the pressure reducing valve 54a are provided on a conduit that communicates with the wheel cylinder 38a of the hydraulic brake 22a for the front right wheel. The pressure increasing valve 58a and the pressure reducing valve 54a are used for controlling the hydraulic brake 22a for the front right wheel. The pressure increasing valve 58b and the pressure reducing valve 54b are provided in a fluid path that communicates with the wheel cylinder 38b of the hydraulic brake 22 for the rear left wheel. The pressure increasing valve 58b and the pressure reducing valve 54b are used for control of the hydraulic brake 22b for the rear left wheel. The driving of the pressure-increasing valves 58a, 58b and the pressure-decreasing valves 54a, 54b is controlled by an ECU not shown in the drawings.

The pressure increasing valve 58a is provided between the circuit control valve 36 and the hydraulic brake 22a of the right front wheel. The pressure increase valve 58a can be linearly controlled, and continuously adjusts the flow rate of the hydraulic fluid from the master cylinder 14 and the circuit control valve 36 side to the wheel cylinder 38a side of the hydraulic brake 22a for the front right wheel.

The pressure increasing valve 58a has a bypass flow path 61a provided with a check valve 60 a. The check valve 60a allows the hydraulic fluid to move through a bypass passage 61a from the hydraulic brake 22a side of the right front wheel to the master cylinder 14 and the circuit control valve 36. On the other hand, the check valve 60a prevents the hydraulic fluid from moving through the bypass passage 61a from the master cylinder 14 and the circuit control valve 36 side to the hydraulic brake 22a side of the right front wheel.

The check valve 60 secures the movement of the hydraulic fluid through the bypass flow path 61a from the hydraulic brake 22a side of the right front wheel to the master cylinder 14 and the circuit control valve 36 side when the pressure increasing valve 58a is in the closed state due to, for example, a failure of the pressure increasing valve 58 a.

The pressure reducing valve 54a is an electromagnetic valve that can be switched only between fully open and fully closed. The pressure reducing valve 54 is provided between the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel and the accumulator 71. The pressure reducing valve 54a reduces the pressure by supplying the operating fluid supplied to the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel to the accumulator 71 in the open state. The accumulator 71 accumulates or discharges the working fluid while changing the volume in accordance with the pressure of the working fluid supplied through the pressure reducing valves 54a and 54 b.

The pressure reducing valve 54a is opened and closed repeatedly intermittently, so that the flow rate of the hydraulic fluid flowing from the wheel cylinder 38a of the hydraulic brake 22a of the right front wheel to the accumulator 71 can be adjusted.

The pressure-increasing valve 58b is provided between the line connecting the circuit control valve 36 and the pressure-increasing valve 58a and the wheel cylinder 38b of the hydraulic brake 22b of the rear left wheel. The pressure increasing valve 58b can be linearly controlled, and the flow rate of the working fluid from the master cylinder 14, the circuit control valve 36, the pressure increasing valve 58a, and the wheel cylinder 38a side of the hydraulic brake 22a for the front right wheel to the wheel cylinder 38b side of the hydraulic brake 22b for the rear left wheel is continuously adjusted.

The pressure increasing valve 58b has a bypass flow path 61b provided with a check valve 60 b. The check valve 60b allows the hydraulic fluid to move through a bypass passage 61b from the hydraulic brake 22b side of the left rear wheel to the master cylinder 14 and the circuit control valve 36 side. On the other hand, the check valve 60b prevents the hydraulic fluid from moving through the bypass passage 61b on the hydraulic brake 22b side of the left rear wheel from the master cylinder 14 and the circuit control valve 36 side.

The check valve 60b secures the movement of the hydraulic fluid through the bypass flow path 61b from the side of the hydraulic brake 22b of the left rear wheel to the side of the master cylinder 14 and the circuit control valve 36, for example, when the pressure increasing valve 58b is in the closed state due to a failure of the pressure increasing valve 58 b.

The pressure reducing valve 54b is an electromagnetic valve that can be switched only between fully open and fully closed. The pressure reducing valve 54b is provided between the wheel cylinder 38b of the hydraulic brake 22b of the rear left wheel and the accumulator 71. The pressure reducing valve 54b reduces the pressure by supplying the operating fluid supplied to the wheel cylinder 38b of the hydraulic brake 22b of the rear left wheel to the accumulator 71 in the open state.

The pressure reducing valve 54b can be opened and closed repeatedly intermittently to adjust the flow rate of the working fluid flowing from the wheel cylinder 38b of the hydraulic brake 22b of the rear left wheel to the accumulator 71.

The pump section 44 is driven by a motor 96 to discharge the working fluid. The driving of the motor 96 is controlled by an ECU not shown in the figure. In addition, the number of pump sections 44 is not limited to one.

The discharge side of the pump section 44 is connected to a conduit connecting the circuit control valve 36 and the pressure increasing valves 58a, 58 b. A damper 73 is provided on the discharge side of the pump section 44. The damper 73 has a function of reducing vibration or vibration sound accompanying a change in the flow rate of the working fluid in the hydraulic circuit 28.

A variable throttle valve 31 and a check valve 32 are provided between a line connecting the circuit control valve 36 and the pressure increasing valves 58a, 58b and the shock absorber 73. The variable throttle valve 31 adjusts the flow rate of the working fluid supplied through the damper 73. The check valve 32 can move the working fluid from the damper 73 side to the line side connecting the circuit control valve 36 and the pressure increasing valves 58a, 58b, but cannot move the working fluid in the opposite direction.

A check valve 69 is provided at a pipe connecting the pressure reducing valves 54a, 54b and the suction side of the pump section 44. The check valve 69 can move the working fluid from the pressure reducing valves 54a and 54b to the suction side of the pump section 44, but cannot move the working fluid in the opposite direction.

A 1 st pressure sensor 24 is provided in a pipe line communicating with the pressure chamber 13a of the master cylinder 14. The 1 st pressure sensor 24 detects the pressure (master cylinder pressure) in the pressure chamber 13. The 2 nd pressure sensor 26 is provided in a conduit that communicates with the wheel cylinder 38a of the hydraulic brake 22a for the right front wheel. The 2 nd pressure sensor 26 detects the wheel cylinder pressure. The 2 nd pressure sensor 26 may be provided on a conduit that communicates with the wheel cylinder 38b of the hydraulic brake 22b of the left rear wheel.

The other hydraulic circuit 30, to which the hydraulic fluid is supplied from the pressure chamber 13b of the master cylinder 14, controls the hydraulic brake 22c for the left front wheel and the hydraulic brake 22d for the right rear wheel. The hydraulic circuit 30 is configured similarly to the hydraulic circuit 28 except that the wheel cylinder 38a of the hydraulic brake 22a for the right front wheel is replaced with the wheel cylinder 38c of the hydraulic brake 22c for the left front wheel and the wheel cylinder 38b of the hydraulic brake 22b for the left rear wheel is replaced with the wheel cylinder 38d of the hydraulic brake 22d for the right rear wheel in the description of the hydraulic circuit 28.

<2 > the overall configuration of the brake fluid pressure control device >

As shown in fig. 2, the brake fluid pressure control device 20 of the present embodiment includes a pressure supply unit 90 and a fluid pressure block 130. The hydraulic block 130 includes a circuit control valve, a suction control valve, a pressure increasing valve, a pressure reducing valve, a pressure sensor, an accumulator, a damper, and the like, which are not shown in the figure, and forms a hydraulic circuit having two systems of a plurality of fluid paths connecting these components. The pressure supply unit 90 includes a motor 96 and a pump element 80 having two pump sections 44, and is attached to one side surface 130a of the hydraulic block 130.

The motor 96 and the two pump sections 44 operate at high speeds, respectively, and thus become sources of sound vibration. The brake fluid pressure control device 20 is configured such that a pressure supply unit 90, which integrates a motor 96 and a pump element 80 as a sound vibration generation source, is attached to a hydraulic block 130. The damper member 200 made of elastic rubber, for example, in an annular shape, is located between the pressure supply unit 90 and the hydraulic block 130, and vibration generated at the pressure supply unit 90 is difficult to be transmitted to the hydraulic block 130. That is, in the brake fluid pressure control device 20 of the present embodiment, measures against sound vibration of the motor 96 and the two pump portions 44 are implemented by one damper member 200.

<3. pressure supply Module >

Referring to fig. 3 to 5, a configuration example of the pressure supply unit 90 will be specifically described. Fig. 3 is a sectional view of the pressure supply unit 90. Fig. 4 is a perspective view of the pump member 80, and fig. 5 is a sectional view of the pump member 80. Fig. 5 is a sectional view of the pump element 80 shown in fig. 4 taken along the line I-I, and fig. 3 is a sectional view of the pressure supply unit 90 at a corresponding position.

As shown in fig. 3, the pressure supply unit 90 is mounted to a side surface 130a of the hydraulic block 130. The method of fixing the pressure feed unit 90 to the hydraulic block 130 is not particularly limited as long as it is a method of damping vibration generated in the pressure feed unit 90. For example, it is also possible to provide a flange portion at the case 91 of the pressure supply unit 90 with an elastic rubber as a damper therebetween, and fix the bolt to the hydraulic block 130 through the flange portion.

The pressure supply unit 90 includes a housing 91, a motor 96, and a pump element 80. The housing 91 has a cylindrical inner space, i.e., a housing portion 91a, and the motor 96 and the pump element 80 are housed in the housing portion 91 a.

The motor 96 includes a stator 97 and a rotor 98. The stator 97 is formed in an annular shape and attached along the inner peripheral surface of the housing 91a of the housing 91. The rotor 98 is disposed on the inner diameter side of the stator 97 and is axially supported to be rotatable around the axis. The rotor 98 has a recess 98a that opens to at least the hydraulic block 130 side. Hereinafter, the extending direction of the rotating shaft is referred to as an axial direction.

A shaft member 101 is provided on one end side (upper side in fig. 3) in the axial direction of the rotor 98, and the shaft member 101 is supported in the protruding portion 92 of the housing 91 via a bearing (not shown). The other end side (lower side in fig. 3) in the axial direction of the rotor 98 is supported by the case 91 via a bearing 94. The shaft member 101 extends into the recess 98a of the rotor 98, and a rotary member 123 is fixed to the distal end side of the shaft member 101 in the recess 98 a. The surface of the rotating member 123 facing the pump element 80 is formed to be inclined with respect to the axial direction. The rotary member 123 rotates coaxially with the rotor 98. The rotating member 123 may be directly fixed to the rotor 98 without being fixed to the shaft member 101.

A swash plate 125 is disposed on a surface of the rotary member 123 facing the pump element 80 via a bearing 125. The surface of the swash plate 125 on the side opposite to the rotary member 123 is supported by the two pistons 151 of the pump element 80. Swash plate 125 does not rotate with the rotation of the shaft of rotor 98, but changes its inclination direction with respect to the surface of rotary member 123 inclined with respect to the axial direction as the shaft of rotary member 123 rotates. The swash plate 125 itself may be configured to rotate in accordance with the rotation of the rotor 98, but in the brake hydraulic pressure control device 20 according to the present embodiment, the swash plate 125 itself does not rotate, and therefore, the wear of the swash plate 125 or the pistons 151 due to the friction between the swash plate 125 and the pistons 151 can be reduced.

The pump element 80 is assembled by being inserted into a recess 98a provided in the rotor 98 from the hydraulic block 130 side through a central hole 93a formed in the housing 93. The pump element 80 is fixed to the housing and does not rotate with the rotor 98. At least a part of the pump element 80 may be disposed in the recess 98a, or the entire pump element 80 may be disposed in the recess 98 a. The pump element 80 has two pump sections 44 arranged at 180 degree intervals around the shaft.

As shown in fig. 4 and 5, the pump element 80 has two pump portions 44 assembled to a pump body 159. The two pump sections 44 have the same structure. Hereinafter, one pump section 44 will be described.

The pump 159 includes an introduction passage 169 and a discharge passage 179 as a fluid passage through which the working fluid flows. The pump 159 includes a housing chamber 153 into which the working fluid is introduced via an introduction passage 169, and the piston 151 is disposed in the housing chamber 153 so as to be axially reciprocated. The piston 151 is biased by a piston spring 155 in a direction to enlarge the volume of the housing chamber 153.

An intake valve 161 is provided midway in the introduction passage 169. The suction valve 161 includes a valve body 165, a valve seat member 163, and a valve spring 167. The valve seat member 163 has a passage hole 163a for the working fluid, and the passage hole 163a is opened and closed by a valve body 165. The valve body 165 is urged toward the valve seat member 163 by a valve spring 167. The suction valve 161 is configured to allow the working fluid to pass through the check valve from the hydraulic block 130 side to the accommodation chamber 153 side.

A discharge valve 171 is provided midway in the discharge passage 179. The discharge valve 171 includes a valve body 175, a valve seat member 173, and a valve spring 177. The valve seat member 173 has a passage hole 173a for the working fluid, and the passage hole 173a is opened and closed by a valve body 175. The valve body 175 is urged toward the valve seat member 173 by a valve spring 177. The discharge valve 171 is configured as a check valve that allows the working fluid to pass from the reservoir chamber 153 side to the hydraulic block 130 side.

The introduction passage 169 and the discharge passage 179 have openings 169a and 179a, respectively, on a surface facing the side surface 130a of the hydraulic block 130. The introduction passage 169 and the discharge passage 179 communicate with a fluid passage formed in the hydraulic block 130 (see fig. 3). Grooves 157a, 157b in which seal rings are disposed are formed around the openings 169a, 179 a. As shown in fig. 3, the pressure supply unit 90 is sandwiched between the pump element 80 and the hydraulic block 130 in a state of being mounted on the hydraulic block 130. This prevents the working fluid flowing through the introduction passage 169 and the discharge passage 179 from leaking out of the fluid passage. Grooves defining the positions of the seal rings 202a and 202b may be provided on the hydraulic block 130 side.

<4. operation example >

An example of the operation of the brake fluid pressure control device 20 of the present embodiment will be described.

When an operation command of the ESP or ABS is input to the electronic control unit, the electronic control unit drives the motor 96. When the motor 96 is driven, the rotor 98 rotates around the shaft. With this, the inclination direction of the swash plate 127 changes. Therefore, the piston 151 of each pump section 44 included in the pump element 80 reciprocates once in the housing chamber 153 while the rotor 98 rotates once.

At this time, the piston 151 is urged by the piston spring 155 to move to the distal end side with a change in the inclination direction of the swash plate 127, and the volume of the housing chamber 153 is enlarged. Accordingly, the hydraulic pressure in the housing chamber 153 decreases, the discharge valve 171 closes, the intake valve 161 opens, and the working fluid is introduced into the housing chamber 153.

Further, when the inclination direction of the swash plate 127 changes and the piston 151 is pushed against the biasing force of the piston spring 155, the volume of the housing chamber 153 decreases. Accordingly, the hydraulic pressure in the housing chamber 153 rises, the suction valve 161 closes, the discharge valve 171 opens, and the working fluid is discharged from the housing chamber 153.

The pump section 44 repeats suction and discharge of the working fluid as the motor 96 rotates. Since the stroke amount of the piston 151 changes in accordance with the inclination angle of the swash plate 125, the discharge amount of the working fluid from the pump unit 44 can be set by adjusting the inclination angle of the swash plate 125. Since the two pump sections 44 are disposed at 180-degree intervals, the suction and discharge of the working fluid are in opposite phases.

The electronic control unit discharges the working fluid from the pump section 44 in this manner, controls the pressure increasing valve 58, the pressure reducing valve 54, and the like, and controls the brake fluid pressure generated in each wheel 38.

<5. Effect >

The brake hydraulic pressure control device 20 of the present embodiment described above is configured such that the motor 96 and the pump element 80, which are sources of sound vibration, are integrally attached to the hydraulic block 130 as the pressure supply unit 90. Therefore, the common damper member 200 can be used to provide measures against the sound vibration of the motor 96 and the pump element 80.

The brake hydraulic control device 20 is configured such that at least a part of the pump element 80 is inserted into a recess 98a formed in the rotor 98 of the motor 96. Therefore, when the motor 96 and the pump element 80 are unitized, the hydraulic block 130 can be downsized by an amount that does not provide the pump element 80 to the hydraulic block 130 while suppressing an increase in the axial dimension. Therefore, the overall outer shape of the brake hydraulic pressure control device 20 can be reduced in size.

While preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, the present invention is not limited to such examples. It will be apparent to those skilled in the art having a general knowledge of the technical field to which the present invention pertains that various modifications and variations can be made within the scope of the technical idea described in the claims, and they are also apparent to be within the technical scope of the present invention.

In the above-described embodiment, the brake fluid pressure control device mounted on a four-wheeled vehicle has been described as an example, but the present invention is not limited to this example, and may be a brake fluid pressure control device mounted on another vehicle such as a two-wheeled vehicle such as a motorcycle. In the above embodiment, the brake fluid pressure control device including the two-line fluid pressure circuit has been described as an example, but the brake fluid pressure circuit may include three or more fluid pressure circuits.

Description of the reference numerals

20 … brake hydraulic pressure control means, 28, 30 … hydraulic circuit, 34 … suction control valve, 36 … circuit control valve, 44 … pump section, 54 … pressure reducing valve, 58 … pressure increasing valve, 80 … pump element, 90 … pressure supply unit, 96 … motor, 97 … stator, 98 … rotor, 130 … hydraulic block, 200 … damper component, 202a, 202b … sealing ring.