JPH1120666A - Hydraulic brake device for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To quickly and easily fill brake fluid to a power chamber formed in a rear side of a master piston in a hydraulic brake device for vehicle with hydrauic boosting means. SOLUTION: In this device, a control piston 30 exposing its rear side to a pressure chamber R4 and forming a regulator chamber R6 in its front side is liquid-tightly and freely slidably stored in the front of a master piston 20 inside a cylinder body 1, being arranged to interlocking to the master piston 20. Brake fluid pressure outputted via a regulator RG is applied to a power chamber R1 to assist energization of the master piston. Sealing members 81, 82 are disposed in both sides of a drain chamber R7 communicating to a reservoir 4 as a unidirectional valve means allowing only a flow of brake fluid from a reservoir 4 side of a pressure-reducing valve means (sleeve valve mechanism 50) of the regulator RG to the power chamber R1.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic brake device for supplying brake hydraulic pressure to a wheel cylinder of a vehicle wheel, and more particularly to a vehicle hydraulic brake device provided with a hydraulic booster.

[0002]

2. Description of the Related Art Various types of hydraulic brake devices for automobiles are known, and a device provided with a hydraulic booster is disclosed in U.S. Pat. No. 3,928,970. . The publication discloses a master cylinder using the pressure of a pressurized fluid source, having a piston slidably housed in a cylinder bore, and forming a pressure chamber connected to a brake hydraulic circuit in front of the piston. A master cylinder device is disclosed in which a power chamber connected to a source of pressurized fluid is formed at the rear and a valve device for controlling supply of fluid from the source of pressurized fluid is disclosed. It is an object of the publication to provide a master cylinder having a source of pressurized fluid in which a piston is directly driven by a brake pedal operation, but does not require an inlet or an inlet seal that moves in a pressurized state. A first pressure chamber is formed between the first piston and the second piston and connected to a hydraulic circuit, and a second pressure chamber is formed in front of the second piston to form a first piston. , And an introduction valve for introducing the output hydraulic pressure of the pressurized fluid source into the second pressure chamber, and a discharge valve connecting the second pressure chamber to the reservoir. There has been proposed a master cylinder device configured to be driven in accordance with the operation of a piston.

In GB 2170874A, a servo chamber is formed on the back of the first piston, and a servo chamber is provided to the servo chamber from a source of pressurized fluid. Servo pressurization master cylinder devices configured to supply pressurized fluid via a valve have been proposed. In the device described in this publication, a spool valve is arranged vertically or parallel to a master cylinder.

[0004]

In the apparatus described in the above publication, the pressurized fluid after pressure adjustment through a valve device is supplied to a power chamber (servo chamber). I have. As for the pressure adjusting operation as a so-called regulator, the balance between the regulator hydraulic pressure and the master cylinder hydraulic pressure applied to the front and rear of the control piston is adjusted by a valve device.

In the apparatus described in the above-mentioned US Patent and British Patent, when the brake pedal is stroked, the power chamber is shut off from the reservoir by the valve device and communicates with the source of pressurized fluid. Therefore, when the pressurized fluid source fails (for example, when the pump is stuck), the piston moves forward and the power chamber becomes negative pressure, and the fluid in the reservoir is supplied to the power chamber via the pressurized fluid source. You. As a result, the supply of the fluid from the reservoir to the power chamber is delayed, particularly when the pressurized fluid source is located away from the hydraulic booster due to space restrictions. For this reason, the negative pressure in the power chamber is not easily released, and a force for urging the piston rearward due to the negative pressure acts, and the output is reduced accordingly.

When the piston is moved forward from the power chamber side in a state where the power hydraulic pressure of the pressurized fluid source does not exist, the power chamber becomes a negative pressure. At this time, the fluid in the reservoir is also pressurized. The power is supplied to the power chamber via a fluid source. Therefore, it is not possible to immediately fill the power chamber with the fluid (that is, the brake fluid).

In view of the above, the present invention provides a vehicle hydraulic brake device having a hydraulic booster, which is capable of quickly and easily filling a power chamber formed behind a master piston with brake fluid. The task is to

[0008]

In order to achieve the above object, a vehicle hydraulic brake device according to the present invention comprises a reservoir for storing brake fluid, and a master piston slidably and slidably in a cylinder body. A pressure chamber is formed in front of the master piston and a power chamber is formed behind the master piston. Brake fluid in the reservoir is introduced into the pressure chamber, and a brake is applied from the pressure chamber in accordance with sliding of the master piston. At least one master cylinder that outputs hydraulic pressure, an auxiliary hydraulic pressure source that boosts the brake fluid in the reservoir to a predetermined pressure and outputs power hydraulic pressure, and a front of the master piston in the cylinder body. A control piston that is liquid-tightly slidably housed and disposed so as to interlock with the master piston, and that exposes the rear to the pressure chamber and forms a regulator chamber in the front; A pressure increasing valve means in conjunction with the control piston communicating or blocking the auxiliary pressure source to the power chamber,
Pressure reducing valve means for communicating or shutting off the power chamber with the reservoir via the regulator chamber in conjunction with the control piston, and permitting only a flow of brake fluid from the reservoir side of the pressure reducing valve means to the power chamber. And one-way valve means.

In the hydraulic brake device for a vehicle, a drain chamber communicating with the reservoir is formed in the cylinder body so as to be adjacent to the regulator chamber via the pressure reducing valve means, and the one-way valve means is provided. And a seal member interposed between the drain chamber and the regulator chamber to allow only the flow of the brake fluid from the drain chamber to the regulator chamber. Alternatively, the one-way valve means is interposed between the drain chamber and the regulator chamber, and is constituted by a check valve that allows only the flow of brake fluid from the drain chamber to the regulator chamber. Is also good.

Further, in the hydraulic brake system for a vehicle, the master cylinder, the control piston, the pressure reducing valve means, and the pressure increasing valve means are disposed coaxially within the cylinder body, and the control piston and the pressure reducing valve are disposed. The pressure chamber may be formed between the pressure reducing valve means and the pressure increasing valve means, and the drain chamber may be formed between the pressure reducing valve means and the pressure increasing valve means.

Further, a first position where the pressure reducing valve means communicates with the reservoir and a communication between the reservoir side of the pressure reducing valve means and the auxiliary hydraulic pressure source is interrupted, and the reservoir side of the pressure reducing valve means is connected. Switching valve means communicating with the auxiliary hydraulic pressure source and selectively switching between a pressure reducing valve means and a second position at which communication with the reservoir is interrupted; The means may be configured to be the first position, and to switch to the second position according to a brake operation state. The switching valve means can be constituted by one 3-port 2-position electromagnetic switching valve, but can also be constituted by two 2-port 2-position electromagnetic switching valves.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a hydraulic brake device according to an embodiment of the present invention. A master cylinder MC and a regulator RG are formed in a cylinder body 1. The master cylinder MC of this embodiment has two pressure chambers R.
A so-called diagonal pipe is constituted by a tandem master cylinder on which R2 and R4 are formed. That is, when a pedaling force is applied to a brake pedal 2 which is a brake operating member provided on the rear side of the vehicle (the right side in FIG. 1), the pedaling force is transmitted as a brake operating force via a push rod 3 and the master is accordingly actuated. Two pressure chambers R2, R of cylinder MC
The output brake fluid pressure from the wheel cylinders Wfr and Wr of the front right and rear left wheels FR and RL, respectively, of the vehicle
l, and output to the wheel cylinders Wfl, Wrr of the front left and rear right wheels FL, RR. At this time, a regulator hydraulic pressure is output from the regulator RG in accordance with the operation of the brake pedal 2, and the master cylinder MC is assisted in accordance with the operation of the regulator RG as described later.

The cylinder body 1 has holes 1 having different inner diameters.
a, 1b, 1c and the like are formed with stepped holes, in which master pistons 10, 20 and control piston 30 are formed.
Is housed, and a pressure chamber R is provided between the master pistons 10 and 20.
2, the master piston 20 and the control piston 30
And a pressure chamber R4 is formed. The rear end of the hole 1a communicates with a power chamber R1 having a larger inner diameter. The smallest hole 1b and the larger hole 1
Both ends of the control piston 30 are slidably fitted in both liquid-tight manners.

As shown in FIG. 2, the master piston 10 has a land portion 11 formed on the outer surface of a front end portion thereof, and an annular seal member 12 and an annular seal member 13 having a cup-shaped cross section. The master piston 20 is mounted so as to be slidably fitted to the hole 1 a in a liquid-tight manner, with the front end face facing the rear end face of the master piston 20. Therefore, the sealing member 1
The power chamber R1 and the pressure chamber R2 are separated by 2 and 13. The main body 14 of the master piston 10 is supported by a cylindrical sleeve 15. This sleeve 15
An annular groove is formed on the inner surface and the outer surface, and an annular groove is also formed on the inner surface separated from the inner surface by a predetermined distance in the axial direction. Each of these grooves has an annular sealing member 16,
17 and an annular seal member 18 having a cup-shaped cross section are accommodated, and the sealing performance with respect to the power chamber R1 is ensured. Further, a concave portion 10a is formed in the axial direction from the distal end surface of the master piston 10, and a retainer 1 is formed at the distal end portion.
9 is mounted.

A land 21 is formed on the outer periphery of the master piston 20 at the rear end, and a land 22 having the same diameter as the land 21 is formed on the front side at a predetermined distance in the axial direction. The land portions 21 and 22 are provided with annular sealing members 23 and 24 each having a cup-shaped cross section, and are slidably fitted in the hole 1a in a liquid-tight manner. Also,
Recesses 20a, 2 in the axial direction from both ends of master piston 20
0b is formed, and a hole 20c is formed in the radial direction of the master piston 20, and the bottom thereof communicates with the recess 20a through the communication hole 20d. The annular liquid supply chamber R3 formed between the lands 21 and 22 communicates with the reservoir 4 via the port 1e, and the liquid supply chamber R3 is connected to the pressure chamber R2 via the hole 20c, the communication hole 20d and the recess 20a. Can communicate with Further, a retainer 2 is provided at the tip of the master piston 20.
9 is mounted.

A retainer 25 is mounted on the rear end side of the master piston 20, and a valve element 26 is locked to the retainer 25.
In the direction of the master piston 10 is restricted.
An elastic member such as rubber is attached to the tip of the valve body 26, and is configured to abut on the communication hole 20d to seal it. A rod 27 is integrally formed on the other end side of the valve body 26, and a locking portion 28 is formed at a rear end of the rod 27. The locking portion 28 is movably arranged in the recess 10a, and the retainer 1
9, the movement in the direction of the master piston 20 is restricted. And, the retainer 1 of the master piston 10
The spring 5 is stretched between the retainer 9 and the retainer 25 of the master piston 20, and is urged in a direction separating the two. The retracted position of the master piston 20 is regulated by a locking pin 7 fixed to the cylinder body 1.

As shown in an enlarged view in FIG. 3, a large-diameter land portion 31 is formed at the rear end of the outer periphery of the control piston 30, and a small-diameter land is formed at a predetermined distance in the axial direction on the front side. A land portion 32 is formed, and an annular seal member 33 having a cup-shaped cross section is disposed on the land portion 31 so as to be slidably fitted in the hole 1a in a liquid-tight manner, and the land portion 32 slides in the hole 1b. They are freely fitted. Thus, the pressure chamber R4 and the liquid supply chamber R5 are separated by the seal member 33, and the liquid supply chamber R5 and a regulator chamber R6 described later are separated by the seal member.
Are separated. That is, the liquid supply chamber R5 is formed between the seal member 33 and the seal member 34, and the liquid supply chamber R5 is connected to the reservoir 4 through the port 1t.

The control piston 30 has a recess 30a and a stepped recess 30b at both ends in the axial direction, and a communication hole 30c penetrating in the radial direction. The communication hole 30c communicates with the bottom of the recess 30a via the communication hole 30d. A retainer 35 is mounted on the rear end side of the control piston 30, and a valve body 36 having the same configuration as the above-described valve body 26 is locked to the retainer 35, thereby restricting the movement of the valve body 36 in the direction of the master piston 10. . A rod 37 is integrally formed on the other end side of the valve body 36, and a locking portion 38 is formed at a rear end thereof. The locking portion 38 is movably disposed in the concave portion 20b and engages with the retainer 29. Control piston 30 stopped
Movement in the direction is regulated. On the other hand, control piston 3
In the bottom of the stepped concave portion 30b, a spool 53 described later is provided.
The rear end is held. Also, the master piston 20
The spring 6 is stretched between the retainer 29 of the control piston 30 and the retainer 35 of the control piston 30, and is urged in a direction separating the two.

As shown in FIG. 1, a regulator RG is formed in front of the cylinder body 1, and an auxiliary hydraulic pressure source 40 is connected to the regulator RG, and its output power hydraulic pressure is appropriately controlled, for example, as shown in FIG. The regulator hydraulic pressure is output to the hydraulic pressure control device PC indicated by a two-dot chain line in FIG. The hydraulic pressure control device PC includes, for example, a solenoid valve, a controller, and the like for performing anti-skid control and the like, and is configured such that the regulator hydraulic pressure supplied to the wheel cylinder Wfr and the like is appropriately controlled according to the driving state of the vehicle. Have been. The auxiliary hydraulic pressure source 40 includes a hydraulic pump 42 driven by an electric motor 41. The input side is connected to the reservoir 4 and the output side is connected to the accumulator 43. The regulator RG is connected to the accumulator 43 via the port 1p.
Is configured to be supplied with power hydraulic pressure.

As shown in the enlarged view of FIG. 3, the regulator RG has a stepped cylindrical sleeve 51 fitted in a stepped hole 1c communicating with the hole 1b. A plurality of annular grooves are formed on the outer periphery of the sleeve 51, and an annular seal member is fitted to each. In addition, communication holes 51e and 51f are formed between the adjacent seal members in the radial direction of the sleeve 51, and the hollow portions of the sleeve 51 are connected to the port 1s and the hydraulic path P1 via these holes. . A regulator chamber R6 is formed between the rear end surface of the sleeve 51 and the front end surface of the control piston 30, and is connected to the power chamber R1 (FIGS. 1 and 2) via a hydraulic pressure path P2. Holes 51a, 51b, 51 are formed in the hollow portion of the sleeve 51.
The inside of the hole 51b having the smallest diameter is a drain chamber R7 that communicates with the reservoir 4 via the communication hole 51e and the port 1s.

A sleeve 52 is further housed in the hole 51a, and a stepped hole 52a is formed in a hollow portion thereof, and a communication hole 52b communicating with the regulator chamber R6 is formed in a radial direction orthogonal to the hole. Have been. A spool 53 is slidably received in the stepped hole 52 a of the sleeve 52. A plunger 54 is accommodated in the hole 51b. A base 54a of the plunger 54 is slidably supported by the hole 51b. A rear end face of the plunger 54 is disposed so that a distal end face of the spool 53 of the spool valve mechanism 50 abuts. I have.

Further, a cylindrical elastic member 70 made of rubber, for example, is fitted into the hole 51c, and the plunger 54 penetrates through the hole 51c and the tip of the plunger 54 extends into the poppet valve mechanism 60. . An annular transmission member 71 is interposed between the base portion 54a of the plunger 54 and the elastic member 70, and an annular concave portion is formed on the surface of the elastic member 70 opposite to the surface in contact therewith. . Further, a plate 72 is disposed on the front end surface of the elastic member 70, and is configured so that the hydraulic pressure is uniformly applied to the entire surface of the elastic member 70. A power output chamber R8 is formed between the elastic member 70 in the hole 51c and the poppet valve mechanism 60, and communicates with the hydraulic pressure path P1 via the communication hole 51f of the sleeve 51. This hydraulic path P1 is connected to the power chamber R as shown in FIG.
1 and the power chamber R1 is connected to the regulator chamber R6 via a hydraulic path P2. In other words, the power output chamber R8, the hydraulic path P1, the power chamber R1, the hydraulic path P2, and the regulator chamber R6 constitute a pressure regulation chamber.

The sleeve 5 forming the above-described drain chamber R7
1 is provided with an annular sealing member 8 having a cup-shaped cross section.
1, 82 are provided. The seal members 81 and 82 constitute one-way valve means of the present invention, and are arranged so as to permit only the flow of the brake fluid from the reservoir 4 side to the power chamber R1. That is, the seal member 81 is arranged so as to allow the flow of the brake fluid from the drain chamber R7 to the power output chamber R8 (therefore, the power chamber R1 via the hydraulic pressure path P1) and prevent the flow in the reverse direction. The seal member 82 is arranged so as to allow the flow of the brake fluid from the drain chamber R7 to the regulator chamber R6 (therefore, the power chamber R1 via the hydraulic pressure path P2) and to prevent the flow in the reverse direction.

The spool valve mechanism 50 constitutes the pressure reducing valve means of the present invention. As shown in FIG. 4, the spool valve mechanism 50 has a stepped cylindrical spool 53 having a plurality of labyrinth grooves formed in a large diameter portion thereof. ing. A retainer 54 is supported at an intermediate portion of the spool 53, and the retainer 54 is supported within the stepped recess 30 b of the control piston 30. And
A spring 55 is provided between the retainer 54 and the sleeve 52.
And the spool 53 is urged to abut the bottom surface of the stepped recess 30b of the control piston 30.

In the fitting portion of the spool 53 to the sleeve 52, the communication hole 52b is always open to the regulator chamber R6 and communicates with the drain chamber R7 at the initial position of the spool 53. The flow path area is limited by the large diameter portion, and the communication hole 52b is finally shielded. As shown in FIG. 3, the drain chamber R7 is provided with the communication hole 51e of the sleeve 51 and the port 1
s is connected to the reservoir 4 (FIG. 1). Therefore, at the initial position of the spool 53, the inside of the regulator chamber R6 also communicates with the reservoir 4, and is filled with the brake fluid at atmospheric pressure. Note that the pressure reducing valve means is not limited to the spool valve mechanism 50, and may be another mode, and may be arranged not in the regulator RG but in the vicinity of, for example, the power chamber R1.

The poppet valve mechanism 60 constitutes the pressure increasing valve means of the present invention, and is constructed as shown in FIG.
The sleeve 61 is a cylindrical body having a bottom and has a hollow portion 61a formed in the axial direction and a radial communication hole 61 communicating with the hollow portion 61a.
b is formed, and a sleeve 61 is formed in parallel with the hollow portion 61a.
The communication hole 61c which penetrates is formed. A communication hole 61d is formed in the center of the bottom of the sleeve 61 in the axial direction, and a valve seat 61e is formed on the hollow portion 61a side. A plurality of annular grooves are formed on the outer periphery of the sleeve 61, and annular seal members are respectively fitted therein, and a communication hole 61b is formed between adjacent seal members, and a hollow is formed through the communication hole 61b. The portion 61a is connected to the port 1p shown in FIGS.

In the hollow portion 61a of the sleeve 61, a valve member 63, a retainer 64, a spring 65 and a filter 66 are provided.
Is accommodated, and a stepped cylindrical sleeve 62 is provided in the hollow portion 61a.
When the small diameter portion is fitted, the hollow portion 61a of the sleeve 61
A power input chamber R9 is formed therein. The power input chamber R9 can communicate with the power output chamber R8 (FIG. 3) through the communication hole 61d. A hole 62a is formed in the sleeve 62 in the axial direction.
Are formed, and a communication hole 62b is formed in a radial direction orthogonal to the hole 62a. The valve member 63 has a valve body 63a formed at the tip, and a large-diameter portion 63 through a flange portion 63b.
c, a stepped cylindrical body including a middle diameter portion 63d and a small diameter portion 63e is formed, and the middle diameter portion 63d is slidably supported by the hole 62a of the sleeve 62. The opening area of the hole 62a is set to be substantially equal to the seat area of the valve body 63a on the valve seat 61e.

The valve member 63 is housed in the hollow portion 61a of the sleeve 61 together with the filter 66. When the spring 65 is stretched between the flange 63b of the valve member 63 and the retainer 64, the valve body 63a is moved to the valve seat. It is urged in the direction of sitting on 61e. In this state, the middle diameter portion 63d of the valve member 63
The small-diameter portion of the sleeve 62 is fitted into the hollow portion 61a of the sleeve 61 so as to be supported by a. At this time, a gap 62c is formed between the front end face of the sleeve 61 and the rear end face of the sleeve 62, and the hole 62a is formed in the communication hole 62b and the gap 6b.
Through the communication hole 2c and the communication hole 61c of the sleeve 61, it communicates with the power output chamber R8, that is, the top surface side of the valve body 63a of the valve member 63 seated on the valve seat 61e. As a result, substantially equal pressure is applied to the valve member 63 from both ends in the axial direction, so that the load on the valve member 63 is extremely small. Although the plunger 54 is disposed so as to face the valve body 63a of the valve member 63, a slight clearance is formed between the valve body 63a and the tip of the plunger 54 at the initial position shown in FIG.

In the initial position shown in FIGS. 1 and 3, the inside of the regulator chamber R6 is provided with the communication hole 52 of the sleeve 52.
a, 52b, the communication hole 51e of the sleeve 51, and the port 1s, which communicate with the reservoir 4 and are at atmospheric pressure. When the control piston 30 moves forward, the spool 53 moves forward. Sleeve 5 as shown
The second communication hole 52b is blocked by the outer peripheral surface of the spool 53, and the valve member 63 of the poppet valve mechanism 60 opens instead, as shown in FIG. As a result, the power hydraulic pressure of the auxiliary hydraulic pressure source 40 is first supplied to the power chamber R1 via the hydraulic pressure path P1, and further supplied to the regulator chamber R6 via the hydraulic pressure path P2 to increase the pressure in each chamber. You. When the force of the regulator hydraulic pressure applied to the front land portion 32 of the control piston 30 exceeds the force of the master cylinder hydraulic pressure applied to the rear land portion 31, the control piston 30 moves rearward, and the valve member of the poppet valve mechanism 60. Since the valve 63 is closed and the spool 53 of the spool valve mechanism 50 is opened, the pressure in the regulator chamber R6 (and the power chamber R1, the power output chamber R8, and the hydraulic paths P1, P2) is reduced. By repeating such operations, the pressure in the same chamber is adjusted to a predetermined regulator hydraulic pressure.

Next, the overall operation of the hydraulic brake device having the above configuration will be described. FIGS. 1 to 3 show a state in which the brake pedal 2 is not operated. From this state, the brake pedal 2 is operated, and the master piston 10 is moved forward (to the left in FIG. 1) via the push rod 3. When pressed, the valve body 26 comes into contact with the master piston 20 and the valve body 26
The communication hole 20d is closed by the elastic member of the pressure chamber R.
The communication between the liquid supply chamber R3 and the liquid supply chamber R3 is interrupted, and a closed state is established. Further, the valve body 36 comes into contact with the control piston 30, and the communication hole 30d is closed by the elastic member of the valve body 36, so that the pressure chamber R4
The communication between the liquid supply chamber R5 and the liquid supply chamber R5 is interrupted, and a closed state is established. Thus, the communication between the pressure chamber R2 and the liquid supply chamber R3 and the pressure chamber R
When the master piston 10 is driven by the operating force of the brake pedal 2 in a state where the communication between the master piston 10 and the liquid supply chamber R5 is interrupted, the master pistons 10 and 20 are connected via the spring 5 to the master piston 20 and the control piston. Since 30 is held in the state shown in FIGS. 2 and 3 via the spring 6, respectively, they advance together.

Therefore, the communication hole 52b is closed by the spool 53 supported by the control piston 30, and the communication with the reservoir 4 is cut off. At the same time, the power hydraulic pressure of the auxiliary hydraulic pressure source 40 is supplied to the power chamber R1 via the hydraulic pressure path P1. As a result, the master pistons 10 and 20 move forward, and the pressure chambers R2 and R4 are further compressed, and the ports 1x,
The master cylinder pressure is output from 1y. At this time,
Since the seal diameter of the land part 31 of the control piston 30 is larger than the seal diameter of the land part 32, the control piston 30 is controlled such that a regulator hydraulic pressure larger than the master cylinder hydraulic pressure is generated as the control piston 30 moves. Thus, the movement of the master piston 10 is assisted by the power hydraulic pressure (ie, the regulator hydraulic pressure) supplied from the power output chamber R8 to the power chamber R1 via the hydraulic pressure path P1 in response to the operation of the brake pedal 2. The Rukoto.

During this time, the force applied to the control piston 30 by the regulator fluid pressure in the regulator chamber R6 is:
If the force applied to the control piston 30 by the master cylinder hydraulic pressure in the pressure chambers R2 and R4 is larger than the force applied to the control piston 30, the spool 53 of the spool valve mechanism 50 opens and the poppet valve mechanism 60
The control piston 30 moves in the direction in which the valve member 63 of (3) closes, and the pressure in the regulator chamber R6 is reduced. When the relationship of the force applied to the control piston 30 is reversed, the control piston 30 moves in the direction in which the spool 53 of the spool valve mechanism 50 closes and the valve member 63 of the poppet valve mechanism 60 opens.
Moves, and the pressure inside the regulator chamber R6 is increased. The regulator hydraulic pressure is adjusted to a pressure higher than the master cylinder hydraulic pressure by a predetermined value or more by repeating the movement of the control piston 30 and the accompanying opening and closing operations of the spool valve mechanism 50 and the poppet valve mechanism 60.

Specifically, the force by the regulator hydraulic pressure applied to the pressure receiving area of the small diameter land portion 32 of the control piston 30 and the force by the master cylinder hydraulic pressure applied to the pressure receiving area of the large diameter land portion 31 Is controlled to be equal to or higher than the master cylinder hydraulic pressure by a predetermined value or more, and a regulator hydraulic pressure that is substantially proportional to the master cylinder hydraulic pressure is output. Brake fluid pressure characteristics are obtained. Further, when the elastic member 70 is deformed by the power hydraulic pressure in the power output chamber R8, the elastic member 70 comes into contact with the transmission member 71, and the valve member 63 is pressed in a direction in which the valve member 63 is seated on the valve seat 61e. Is pressed in the direction in which the opening area to the communication hole 52b increases. As a result, the regulator hydraulic pressure is reduced, and a second brake hydraulic pressure characteristic having a pressure increasing gradient that is gentler than the pressure increasing gradient of the first brake hydraulic pressure characteristic between the brake pedal input and the master cylinder hydraulic pressure is obtained. Can be

In the hydraulic brake device according to the present embodiment,
When the power chamber R1 is filled with the brake fluid in a state where the power hydraulic pressure does not exist in the auxiliary hydraulic pressure source 40, it can be quickly performed by moving the master piston 10 forward. That is, since the power chamber R1 becomes negative pressure in accordance with the advance of the master piston 10, the brake fluid flows from the reservoir 4 to the port 1s, the drain chamber R7, the seal member 81, the power output chamber R8, the hydraulic pressure path P1, or the port 1s. ,
The power is immediately supplied to the power chamber R1 via the drain chamber R7, the seal member 82, the regulator chamber R6, and the hydraulic path P2. As a result, the power chamber R1 is quickly and easily filled with the brake fluid. Next, when the master piston 10 is moved backward, the regulator chamber R6 is communicated with the reservoir 4 by the spool valve mechanism 50, so that the brake fluid including air in the power chamber R1 and the like is discharged to the reservoir 4. As described above, air bleeding in the power chamber R1 is also easily performed.

FIG. 8 shows a part of a hydraulic brake device according to another embodiment of the present invention, and the remaining structure is the same as that of FIG. FIG. 8 shows a three-port two-position electromagnetic switching valve 90 as switching valve means of the present invention interposed in a hydraulic passage P3 that connects and connects the reservoir 4 and the port 1p. The electromagnetic switching valve 90 is controlled by the electronic control unit ECU in accordance with the brake operation state, and communicates a drain chamber R7 formed between the spool valve mechanism 50 as the pressure reducing valve means and the reservoir 4 with the reservoir 4, and the drain chamber R7. Select a first position at which communication between R7 and the auxiliary hydraulic pressure source 40 is interrupted, and a second position at which communication between the drain chamber R7 and the auxiliary hydraulic pressure source 40 is interrupted and communication between the drain chamber R7 and the reservoir 4 is interrupted. The first position is set during normal brake operation, and is switched to the second position in accordance with the brake operation state.

As shown in FIG. 8, for example, a stroke sensor 91 is provided in the brake pedal 2, and the operation speed of the brake pedal 2 is calculated in the electronic control unit ECU based on the detection signal. It is determined whether or not the pedal 2 has been rapidly operated, that is, whether or not so-called emergency braking has been performed. Although not shown, two 2-port 2-position solenoid valves may be used instead of the electromagnetic switching valve 90.

Thus, according to the embodiment of FIG. 8, it is possible to obtain the brake fluid pressure characteristics as shown in FIG. That is, when the electromagnetic switching valve 90 is switched to the second position when the brake pedal 2 is not operated, the communication between the drain chamber R7 and the reservoir 4 is cut off, and the drain chamber R7 communicates with the auxiliary hydraulic pressure source 40. Thereby, the spool valve mechanism 50 and the seal member 82, the regulator chamber R6, and the hydraulic pressure path P in which the power hydraulic pressure output from the auxiliary hydraulic pressure source 40 is open
2 and into the power chamber R1 via the seal member 81, the power output chamber R8 and the hydraulic path P1. Accordingly, the brake fluid pressure in the power chamber R1 rapidly increases, and the characteristic K indicated by a dashed line in FIG.
a, and can be used for automatic braking.

When the electronic control unit ECU determines that the emergency brake is applied when the brake pedal 2 is operated, the electromagnetic switching valve 90 is switched to the second position, and the output from the auxiliary hydraulic pressure source 40 is output. The power hydraulic pressure is introduced into the power chamber R1 through the seal member 82, the regulator chamber R6, and the hydraulic pressure path P2, and the seal member 8
1. Introduced into the power chamber R1 via the power output chamber R8 and the hydraulic path P1. Thus, the characteristic Kb indicated by a broken line in FIG.
, And brake assist is performed. in this way,
According to the embodiment of FIG. 8, in addition to the characteristic Kn at the time of the normal brake operation shown by the solid line in FIG. 9, it has characteristics Ka and Kb, and can exhibit both the automatic braking function and the brake assist function. it can.

It should be noted that the seal members 81, 8 of the above-described embodiment are used.
Instead of 2, a check valve may be used as the one-way valve means of the present invention. That is, a hydraulic pressure path (not shown) that connects the drain chamber R7 and the regulator chamber R6 in FIG. 3 is provided,
The first hydraulic fluid passage allows the flow of the brake fluid from the drain chamber R7 to the regulator chamber R6 and prevents the flow in the reverse direction.
And a check valve (not shown) of the drain chamber R7
A hydraulic passage (not shown) is provided for communicating the brake fluid from the drain chamber R7 to the power output chamber R8 and blocking the flow in the reverse direction. (Not shown) may be arranged.
Further, only one of the first and second check valves may be provided.

[0040]

Since the present invention is configured as described above, the following effects can be obtained. That is, the vehicle hydraulic brake device according to the first aspect is provided with a one-way valve means that allows only the flow of the brake fluid from the reservoir side of the pressure reducing valve means to the power chamber. In the event of a failure, the brake fluid in the reservoir is immediately supplied to the power chamber via the one-way valve even if the master piston is driven forward and the power chamber becomes negative pressure. As a result, the negative pressure in the power chamber is immediately released, and the force for urging the master piston rearward due to the negative pressure is reduced, so that the output is increased as compared with the conventional device. Further, even when the master piston is driven forward in a state where the power hydraulic pressure of the auxiliary hydraulic pressure source does not exist, the power chamber becomes a negative pressure. At this time, the brake fluid in the reservoir passes through the one-way valve means. Supplied to the power room. Therefore, even when the power hydraulic pressure of the auxiliary hydraulic pressure source does not exist, the filling of the brake fluid into the power chamber can be performed quickly and easily. in this way,
According to the present invention, when the pressure in the power chamber becomes negative, the brake fluid in the reservoir can be immediately supplied to the power chamber.

According to a second aspect of the present invention, a drain chamber communicating with the reservoir is formed in the cylinder body so as to be adjacent to the regulator chamber via the pressure reducing valve means, and the one-way valve means is provided between the drain chamber and the regulator. If it is configured with a seal member that is interposed between the chamber and allows only the flow of brake fluid from the drain chamber side to the regulator chamber side, it can be easily assembled with a simple configuration, and it is an inexpensive device. be able to. Alternatively, the one-way valve means may be constituted by a check valve, in which case the seal member may be a general one, and the brake member can be easily braked by adding a check valve. A configuration capable of filling a liquid can be employed.

According to a third aspect of the present invention, in the hydraulic brake device, the master cylinder, the control piston, the pressure reducing valve means and the pressure increasing valve means are disposed coaxially in the cylinder body, and the master cylinder, the control piston and the pressure reducing valve means are provided between the control piston and the pressure reducing valve means. And a drain chamber is formed between the pressure reducing valve means and the pressure increasing valve means, so that the hydraulic brake device is reduced in size.

In the hydraulic brake device according to the fifth aspect, the pressure reducing valve means communicates with the reservoir, and the first position at which the communication between the reservoir side of the pressure reducing valve means and the auxiliary hydraulic pressure source is interrupted; Normal brakes are provided with switching valve means for connecting the reservoir side of the pressure reducing valve means to an auxiliary hydraulic pressure source and selectively switching between a pressure reducing valve means and a second position at which communication between the pressure reducing valve means and the reservoir is interrupted. In operation, the switching valve means is set to the first position, and is switched to the second position in accordance with the brake operation state, so that both the automatic braking function and the brake assist function can be exhibited with a simple configuration. Can be.

[Brief description of the drawings]

FIG. 1 is a sectional view of a vehicle hydraulic brake device according to an embodiment of the present invention.

FIG. 2 is an enlarged sectional view showing a master cylinder portion in the vehicle hydraulic brake device according to one embodiment of the present invention.

FIG. 3 is an enlarged sectional view showing a regulator portion in the vehicle hydraulic brake device according to one embodiment of the present invention.

FIG. 4 is an enlarged sectional view showing a spool valve mechanism in the vehicle hydraulic brake device according to one embodiment of the present invention.

FIG. 5 is an enlarged sectional view showing a poppet valve mechanism in the vehicle hydraulic brake device according to one embodiment of the present invention.

FIG. 6 is an enlarged sectional view showing an operation state of a spool valve mechanism according to the embodiment of the present invention.

FIG. 7 is an enlarged sectional view showing an operating state of the poppet valve mechanism according to the embodiment of the present invention.

FIG. 8 is a cross-sectional view showing a part of a vehicle hydraulic brake device according to another embodiment of the present invention.

FIG. 9 is a graph showing brake hydraulic pressure characteristics of a vehicle hydraulic brake device according to another embodiment of the present invention.

[Explanation of symbols]

1 cylinder body, 2 brake pedal, 4 reservoir 10, 20 master piston, 30 control piston,
40 auxiliary hydraulic pressure source 50 spool valve mechanism, 60 poppet valve mechanism, 7
0 Elastic member 81, 82 Seal member MC master cylinder, RG regulator R1 power room R2, R4 pressure room, R3, R5 liquid supply room R6 regulator room, R7 drain room R8 power input room, R9 power output room P1, P2 hydraulic pressure Road

Claims (5)

[Claims] A reservoir for storing brake fluid, a master piston slidably housed in a cylinder body in a fluid-tight manner, and a pressure chamber formed in front of the master piston and a power chamber formed rearward. At least one master cylinder for introducing brake fluid in the reservoir into the pressure chamber and outputting brake fluid pressure from the pressure chamber in response to sliding of the master piston, and applying a predetermined pressure to the brake fluid in the reservoir; An auxiliary hydraulic pressure source that outputs power hydraulic pressure by increasing the pressure in the cylinder body, and is disposed in the cylinder body so as to be slidably accommodated in front of the master piston in a liquid-tight manner and interlocked with the master piston. A control piston exposed to the pressure chamber and forming a regulator chamber in front thereof; and a pressure-intensifying valve for communicating or shutting off the auxiliary hydraulic pressure source with the power chamber in conjunction with the control piston. Means, pressure reducing valve means for communicating or shutting off the power chamber with the reservoir through the regulator chamber in conjunction with the control piston, and a flow of brake fluid from the reservoir side of the pressure reducing valve means to the power chamber. And a one-way valve means for permitting only the hydraulic fluid. 2. A drain chamber communicating with the reservoir is formed in the cylinder body so as to be adjacent to the regulator chamber via the pressure reducing valve means, and the one-way valve means is provided between the drain chamber and the regulator. 2. The hydraulic brake device for a vehicle according to claim 1, further comprising a seal member interposed between the drain chamber and the regulator chamber to allow only a flow of the brake fluid from the drain chamber to the regulator chamber. 3. The regulator chamber, wherein the master cylinder, the control piston, the pressure reducing valve means, and the pressure increasing valve means are coaxially disposed within the cylinder body, and wherein the regulator chamber is provided between the control piston and the pressure reducing valve means. 3. The hydraulic brake device for a vehicle according to claim 2, wherein the drain chamber is formed between the pressure reducing valve means and the pressure increasing valve means. 4. A drain chamber communicating with the reservoir is formed in the cylinder body so as to be adjacent to the regulator chamber via the pressure reducing valve means, and the one-way valve means is provided between the drain chamber and the regulator. 2. The hydraulic brake device for a vehicle according to claim 1, wherein the check valve is provided between the drain chamber and the regulator chamber to allow only a flow of the brake fluid from the drain chamber to the regulator chamber. . 5. A first position in which the pressure reducing valve means is communicated with the reservoir to interrupt communication between the reservoir side of the pressure reducing valve means and the auxiliary hydraulic pressure source, and the reservoir side of the pressure reducing valve means. Switching valve means communicating with the auxiliary hydraulic pressure source and capable of selectively switching between the pressure reducing valve means and a second position for interrupting communication with the reservoir, wherein the switching valve means is provided during normal brake operation. 2. The hydraulic brake system for a vehicle according to claim 1, wherein the first position is set and the second position is switched to the second position according to a brake operation state.