JPH0643180B2 - Hydraulic control device for anti-skidding - Google Patents

Description

TECHNICAL FIELD The present invention relates to an antiskid hydraulic pressure control device used in a brake device of a vehicle or the like.

[Conventional technology]

The applicant has previously proposed, as this type of device, a cut valve arranged between a master cylinder and a wheel cylinder, a control piston movable to open and close the cut valve, and a control piston and a cut valve. A volume chamber formed between them and connected to the wheel cylinder, a pressure chamber formed on the side opposite to the volume chamber of the control piston, an electromagnetic pump whose discharge side is connected to the pressure chamber, and a discharge side of the electromagnetic pump. It has been proposed to have an electromagnetic valve that is provided between the suction side and the solenoid valve and can switch between a shut-off position and a communication position.

In these cases, the solenoid valve is turned off and the control piston is urged by the pressure contained in the pressure chamber that is shut off from the suction side of the electromagnetic pump to open the cut valve. When anti-skid control is performed after the pressure is supplied,
First, the solenoid valve is switched to the communication position to open the pressure in the pressure chamber to the suction side of the electromagnetic pump, thereby closing the cut valve by the pressure supplied to the wheel cylinder and increasing the volume of the volume chamber. The pressure on the wheel cylinder side, which is cut off from the master cylinder side, is reduced in accordance with the increase in the volume of the volume chamber. Then, after that, the solenoid valve is switched to the shut-off position to drive the electromagnetic pump to supply the discharge pressure liquid to the pressure chamber, thereby moving the control piston in the direction of decreasing the volume of the volume chamber and reducing the wheel cylinder. The side pressure is increased, and thereafter, similarly to the above, the decrease and increase of the wheel cylinder side pressure are appropriately repeated.

Then, when the pressure of the master cylinder is reduced and the anti-skid control is no longer performed, the control piston is moved back to the position where the cut valve is opened so that the master cylinder side and the wheel cylinder side communicate with each other. Has become.

[Problems to be Solved by the Invention]

The return movement of the control piston to the position where the cut valve is opened must be performed by driving the electromagnetic pump and supplying its discharge liquid into the pressure chamber that is blocked from the suction side of the electromagnetic pump by the electromagnetic valve. Therefore, the return movement is performed only at a speed corresponding to the discharge volume amount of the electromagnetic pump per unit time.

For this reason, when the control piston is in the position where the cut valve is closed and the volume of the volume chamber is increased, when the brake operation is performed to decrease the pressure of the master cylinder and immediately increase it again, the electromagnetic pump will Although the control piston may move back according to the pressure fluid discharge of
There is a problem that the cut valve cannot be opened in time for the re-increasing of the master cylinder pressure, and the pressure cannot be immediately supplied to the wheel cylinder.

The present invention has been made in view of the above problem, and provides an anti-skid hydraulic pressure control device capable of quickly communicating a master cylinder side and a wheel cylinder side in response to a decrease in master cylinder pressure. With the goal.

[Means for Solving the Problems]

In order to achieve the above object, the present invention provides an accumulator in communication with the pressure chamber, and an accumulator control valve that is closed by the pressure from the master cylinder between the pressure chamber and the accumulator. Is.

[Action]

When pressure is generated in the master cylinder to operate the brake, the accumulator and the pressure chamber are shut off, and the anti-skid control is performed by switching the solenoid valve and driving the solenoid pump as described above, and lowers the master cylinder pressure. Then, the accumulator control valve is opened, the pressure liquid stored in advance in the accumulator is supplied to the pressure chamber, and biases the control piston toward the open position of the cut valve.

〔The invention's effect〕

Even if the control piston is in the position to close the cut valve and increase the volume of the volume chamber, it will be instantly returned to the position to open the cut valve according to the decrease in master cylinder pressure, so the pressure in the master cylinder will drop immediately. Even if a brake operation is performed to increase the pressure to the wheel cylinder, the pressure can be quickly supplied to the wheel cylinders, and it is possible to prevent the brake operation from being delayed with respect to the pressure increase in the master cylinder. When pressure is generated in the master cylinder and anti-skid control is performed and the pressure on the wheel cylinder side rises, only the discharge pressure liquid of the electromagnetic pump is supplied to the pressure chamber, and the control piston reduces the volume of the volume chamber. Since it is moved in the decreasing direction, the stable pressure increase on the wheel cylinder side is not impaired.

〔Example〕

 An embodiment of the present invention shown in the drawings will be described below.

In the figure, the anti-skid hydraulic pressure control device of this embodiment is indicated by 1 as a whole, and hydraulic pressure is supplied from a master cylinder 2 with a vacuum booster. That is, the master cylinder 2 with vacuum booster comprises a known vacuum booster 3 and a master cylinder 4, and the vacuum booster 3 is driven by the brake pedal 5 and the master cylinder 4 is driven by its output. Master cylinder 4
One of the hydraulic pressure generating chambers is connected to the wheel cylinder of the front wheel via a pipe 6 and a device similar to the hydraulic pressure control device 1 shown in the drawing. The other hydraulic pressure generating chamber will be described later via the pipe 7. It is connected to the input port 16 of the pressure regulating device 8, the first output port 17 of this device 8 is connected to the wheel cylinders 12 and 13 of the rear wheels 10 and 11 via the pipe 9, and the second output port 19 is It is connected to the pipe 9 through the pipe 14.

The control port 18 of the pressure regulator 8 is connected to the discharge port 27 of the electromagnetic pump 26 via a pipe 24 provided with a check valve 25, and branches from the pipe 24 on the control port 18 side of the check valve 25. Piping 20,
It can be connected to a reservoir 23 via a solenoid valve 21 and a pipe 22. As is well known, the reservoir 23 is provided with a main body 40, a piston 45 which is slidable by mounting a seal ring in its inner hole, and a relatively weak spring 46 which urges the piston 45. The intake chamber is defined. The liquid chamber communicates with the pipe 22 through the above-mentioned through hole 47, and is further connected through the pipe 29 provided with the check valve 28 to the discharge port 27 which also serves as the suction port of the electromagnetic pump 26. Check valves 28 and 25 are respectively reservoir 23
From the electromagnetic pump 26 side to the electromagnetic pump 26 side and from the electromagnetic pump 26 side to the control port 18 side is allowed, but the opposite is prohibited. 70
Is a pressure switch provided on the control port 18 side of the check valve 25 of the pipe 24, and detects the pressure in the pressure chamber 39 of the pressure adjusting device 8 and the pressure accumulating chamber 78 of the accumulator device 72, which will be described later. It switches when a predetermined pressure is set in advance and outputs a signal when the pressure is equal to or lower than the predetermined pressure.

An input / output port 73 of an accumulator device 72 is connected to the discharge side of the electromagnetic pump 26 via a pipe 71 branched from the pipe 24 between the control port 18 and the check valve 25. The accumulator device 72 is one in which an accumulator 75 is integrally assembled with an accumulator control valve device 80 described later, and the accumulator 75 has a flexible membrane plate 77 in a spherical main body 76 as is known.
The film plate 77 defines a gas chamber in which high-pressure nitrogen gas is enclosed and a pressure accumulating chamber 78.
The accumulator chamber 78 is connected to the above-mentioned input / output port 73
It is possible to communicate with. The control port 81 of the accumulator device 72 is connected to the pipe 7 connected to the hydraulic pressure generation chamber of the master cylinder 4 via the pipe 89.

The solenoid valve 21 is a two-position valve that switches in response to the demagnetization of the solenoid 21b. When the solenoid 21b is demagnetized, the urging force of the spring 21a cuts off the communication between the control port 18 side and the reservoir 23 side. When A is taken and the solenoid 21b is excited, the position B for connecting the control port 18 side and the reservoir 23 side is taken.

The electromagnetic pump 26 has a bobbin 49 in the large diameter portion of the inner hole 53 of the main body 48.
A coil 50 wound around is fixedly arranged, and a main plunger 51 made of a magnetic material is slidably fitted into a center hole of a bobbin 49. The coil 50 is excited by the current from the control unit 57, but the drawing shows the non-excitation state, and the main plunger 51 is in contact with the bottom portion 48a of the main body 48.

A stepped sub-plunger 52 is slidably fitted to the small-diameter portion of the inner hole 53 of the main body 48 with a sail ring 54 interposed therebetween, and is urged toward the bottom portion 48a by a spring 55 to urge the main plunger.
It is in contact with 51. In the normal state shown, the secondary plunger
A liquid chamber 56 having a predetermined volume (for example, 0.1 cc) is formed between the end surface 52a of 52 and the inner wall end surface 48b of the main body 48, and the liquid chamber 56 communicates with the discharge port 27 described above. When the coil 50 is excited, the main plunger 51 is biased toward the discharge port 27 by the magnetic attraction force, and presses the sub-plunger 52 against the biasing force of the spring 55. The sub-plunger 52 stops when its end face 52a contacts the inner wall end face 48b of the main body 48, and a predetermined volume of hydraulic fluid is delivered to the pressure regulator 8 side via the check valve 25 and the pipe 24 by one stroke so far. Send in. Spring 55 when coil 50 is de-energized
The sub-plunger 52 and the main plunger 51 return to the positions shown in the drawing by the urging force of. By the return stroke at this time, the working fluid is sucked from the reservoir 23 through the check valve 28 by a predetermined volume. The main plunger 51 made of a magnetic material and a part of the main body 48 form a magnetic circuit.

The solenoid valve 21 and the solenoid pump 26 described above are controlled by receiving the outputs from the output terminals 59a and 59b of the control unit 57 by the solenoid 21b and the coil 50, respectively. The control unit 57 has its input terminal 58a connected to an output terminal of a wheel speed detector provided on each wheel (not shown),
Based on the outputs of these detectors, various calculations and judgments are performed to generate a brake slack signal and a brake re-injection signal. Further, the output terminal of the pressure switch 70 described above is connected to the input terminal 58b, and the electromagnetic pump 26 is driven based on the output of the pressure switch 70 generated when the pressures in the pressure chamber 39 and the accumulator chamber 78 are below a predetermined pressure. Generate a signal. However, while the anti-skid control is being performed on the basis of the brake slackening signal and the reloading signal, the output of the pressure switch 70 is invalid and the drive signal is not generated.

When the brake slack signal is generated, the output S ₁ at the output terminal 59a connected to the solenoid 21b has a high level of 1 ″, and the output S ₂ at the output terminal 59b connected to the coil 50 has a low level.
The output S ₁ is at a low level 0 ″, and the output S ₂ is at a high level 1 ″ and a low level at appropriate time intervals when a brake re-injection signal or a drive signal is generated.
The pulse output switches to 0 ″.

The pressure regulator 8 interposed between the master cylinder 4 and the wheel cylinders 12 and 13 has a stepped hole 30 formed inside the main body 15 and is connected to the input port 16 communicating with the master cylinder 4. A stepped cut valve body 32 is slidably fitted inside the diameter hole 30a. The cut valve main body 32 is formed with a plurality of grooves 32a for communicating both ends of the cut valve main body 32 on the outer circumference of the large diameter portion, and a control piston 36 described later.
An annular valve body 31 made of synthetic rubber is attached to the outer periphery of the end portion facing the
It can be attached to and detached from a valve seat 37 formed on 30c. The cut valve body 32 is stretched between the inner side portion of the lid body 60 attached to the opening of the large diameter hole 30a and provided with the second output port 19 and the large diameter portion of the cut valve body 32. It is biased toward the valve seat 37 by the first valve spring 40. Such cut valve body 32
Is formed with a stepped through hole that further extends in the axial direction, and the valve ball 35 is provided in the through hole on the end side where the valve body 31 is mounted.
Is provided with a tapered valve seat 32b that can be seated on and off.
A lid member 33 provided with a throttle hole 34 is integrally assembled to the opening of the through hole on the end side facing the lid body 60, and the first valve is provided between the lid member 33 and the valve ball 35. By tensioning the second valve spring 42, which has a weaker spring force than the spring 40, the valve ball 35 moves to the valve seat 32a.
Is urged towards.

A control piston 36 having a pair of sealing members 38 mounted on the outer circumference is slidably mounted on the small diameter hole portion 30b of the stepped hole 30 which is communicated with the large diameter hole portion 30a through a communication hole 30d provided on the inner wall 30c. The control piston 36 and the valve body 31 of the cut valve body 32 are fitted together.
A volume chamber 41, which is in constant communication with the wheel cylinders 12 and 13 via the first output port 17, is defined between the valve seat 37 and the valve seat 37, on which the control piston 36 faces the volume chamber 41. A pressure chamber 39 communicating with the control port 18 is defined on the opposite side of the pressure chamber 39. The end of the control piston 36 on the side of the volume chamber 41 penetrates the communication hole 30d and can abut against the cut valve body 32, and the shaft-like portion 43 integrally formed at the end of the control piston 36 has the cut valve. It can come into contact with the valve ball 35 inside the main body 32. In this way, the control piston 36 moves according to the pressure difference generated between the volume chamber 41 side and the pressure chamber 39 side, so that the cut valve body 32 is attached to or detached from the valve seat 37, and the valve ball 35 is seated. When the valve seat 31 is seated on the valve seat 37 and the valve ball 35 is seated on the valve seat 32b according to the movement of the control piston toward the pressure chamber 39,
The liquid communication from the input port 16 side to the first output port 17 side is cut off.

A large-diameter hole 63b is formed in the lid 60 attached to the opening of the large-diameter hole 30a of the main body 15 and extending inward thereof, and a stepped hole 63 is formed in which the large-diameter hole 63b opens to the cut valve main body 32 side. A stepped piston 64 is movably fitted in the hole 63. A cup seal 66 is attached to the outer periphery of the small diameter portion 64a of the stepped hole piston 64 that fits into the small diameter portion 63a of the stepped hole 63, with its lip portion facing the second output port 19 side. Hole 63b Large diameter part 6 to fit
A seal ring 67 is attached to the outer circumference of 4b. The stepped piston 64 is formed with a through hole 65 extending in the axial direction so that the inner side of the large diameter hole portion 30a in which the cut valve body 32 is disposed and the small diameter hole portion 63a side of the lid body 60 can be connected. . The tube sheet 61 having the conical surface 62 at the tip portion that is press-fitted into the lid body 60 from the second output port 19 side and projects into the small diameter hole portion 63a has a small diameter hole portion 6
A through hole 69 that connects the inside of 3a and the second output port 19 is formed, and the end surface of the small diameter portion 64a of the stepped piston 64 can receive the hydraulic pressure on the wheel cylinders 12 and 13 side and also has the small diameter hole. It receives the biasing force of the spring 68 arranged in the portion 63a. On the other hand, the end surface of the large diameter portion 64b of the stepped piston 64 is
The hydraulic pressure on the master cylinder 4 side can be received via the control cylinder 36, and the urging force corresponding to the pressure in the pressure chamber 39 is received via the cut valve main body 32 which is pressed by the control piston 36 and can come into contact with the end surface thereof. Is possible. In this way, the stepped piston 64 is configured so that the force applied to the end surface of the large diameter portion 64b is larger than the force applied to the end surface of the small diameter portion 64a.
A through hole to block communication between the 16 side and the second output port 19
When the peripheral edge of the opening of 65 is brought into pressure contact with the conical surface 62 of the cave seat 61, and when the force received by the end surface of the large diameter portion 64b becomes smaller than the force received by the small diameter portion 64a, it moves to the cut valve main body 32 side and the input port 16 side. Through hole 65 to communicate with the second output port 19 side
The peripheral edge of the opening is separated from the conical surface 62. As described above, the stepped piston 64 is the cut valve body 32.
When moved to the side, the portion of the large diameter portion 64b, to which the seal ring 67 is attached, comes out from the inside of the large diameter hole portion 63b to the tapered portion 63c having a diameter larger than that of the large diameter hole portion 63b.

The above-described accumulator 75 is attached to the main body 82 of the accumulator control valve device 80 by screwing the cylindrical portion 74 thereof to one end side of the stepped hole 83 via a seal ring, and the step facing the accumulator 75 is attached. A lid 84 having a control port 81 is screwed into a large-diameter hole portion on the other end side of the attaching hole 83. At the inner end of the lid body 84, a hole 85 is formed that opens toward a support member 87 fitted through a seal ring in the medium diameter hole portion of the stepped hole 83. A large-diameter piston 86 which receives the hydraulic pressure of the master cylinder 4 at one end side through the control port 81 and the pipe 89 is fitted with a seal ring. A small hole 88 that communicates with the pressure accumulator chamber 78 of the accumulator 75 via the passage 79 is opened in the small diameter hole portion of the stepped hole 83 that communicates with the input / output port 73 that communicates with the pressure chamber 39 of the pressure regulator 8. A tapered valve seat 90 is provided around the opening of the small hole 88. Then, a small-diameter piston 92 brazed with a valve ball 91 that can be seated on and separated from the valve seat 90 is slidably fitted with its shaft portion 93 into a through hole 94 in which a sealing member of a support member 87 is mounted. It is provided. The small diameter piston receives the urging force of the spring 95 and the valve ball
The 91 is urged in the direction to move it away from the valve seat 90, and the end of the shaft 93 is in contact with the other end of the large-diameter piston 86. In this way, the master cylinder 4 acting on the large-diameter piston 86
The acting force according to the side hydraulic pressure and the small-diameter piston facing it
The large-diameter piston 86 and the small-diameter piston 92 can be moved integrally by changing the magnitude relationship between the urging force of the spring 95 acting on 92 and the acting force corresponding to the pressure on the accumulator 75 side. When the force acting on the large-diameter piston 86 becomes larger than the force acting on the small-diameter piston 92, the pistons 86, 92 move to the small hole 88 side to seat the valve ball 91 on the valve seat 90, and the accumulator 75 The communication between the pressure accumulating chamber 78 and the input / output port 73 communicating with the pressure chamber 39 of the pressure regulator 8 is cut off.

Next, the operation of this embodiment described above will be described. The brake system for the front wheels (not shown) connected to the master cylinder 4 via the pipe 6 is also provided with the same device as the device 1 shown in the drawing. The operation will be described only for the system.

Now, it is assumed that the vehicle equipped with the hydraulic control device 1 and the master cylinder 2 with the vacuum booster is traveling at a constant speed. That is, the brake pedal 5 is not depressed, and the output signals S ₁ , S of the control unit 57 are
Both ₂ are 0 ″, and the device 1 is in the illustrated state.
At this time, the solenoid valve 21 blocks the pressure chamber 39 of the adjusting device 8 and the accumulator 75 side of the accumulator device 72 from the reservoir 23 side, and the pressure in the pressure chamber 36 is lower than the predetermined pressure at which the pressure switch 70 switches. While being kept at high pressure,
A pressure liquid of the same pressure is stored in the pressure storage chamber 78. In the pressure regulator 8, the control piston 36 receives the pressure in the pressure chamber 36 and presses the cut valve body 32 and the valve ball 35 against the spring force of the valve springs 40 and 42, and the valve body 31, Valve ball 35 together with valve seat 37,3
2b, the input port 16 and the first output port 17 are separated from each other by the volume chamber 41.
Through the. Further, the stepped piston 64 receives the urging force from the control piston 36 via the cut valve body 32 in the large diameter portion.
64b receives and presses the opening peripheral edge of the through hole 65 against the conical surface 62 of the tube sheet 61 against the spring force of the spring 68, and between the input port 16 and the second output port 19. It has been cut off. In the accumulator device 72, the small-diameter piston 92 of the accumulator control valve device 80 is urged by the spring 95 and the pressure in the accumulator chamber 78 is received to cause the valve ball 91 to move to the valve seat 90.
It is separated from the accumulator 75 side and the input / output port 73.
It is in communication with the side.

The brake pedal 5 is used to stop the vehicle in such a state.
When is strongly depressed, the hydraulic pressure generated in the master cylinder 4 is applied to the wheel cylinders 12 and 13 via the pipe 7, the input port 16 of the pressure regulator 8, the volume chamber 41, the first output port 17 and the pipe 9. Accumulator device supplied via pipe 89
It is supplied to 72 control ports 81. Then, the large-diameter piston 86 of the accumulator control valve device 80 receives the hydraulic pressure from the master cylinder 4, and moves the small-diameter piston 92 against the spring force of the spring force 95 and the urging force corresponding to the accumulated pressure of the accumulator 75,
The valve ball 91 is seated on the valve seat 90. As a result, the communication between the accumulator chamber 78 of the accumulator 75 and the pressure chamber 39 side of the pressure regulator 8 is cut off.

Due to the hydraulic pressure supplied from the master cylinder 4 to the wheel cylinders 12 and 13, braking is started on the rear wheels 10 and 11, and the wheel cylinders 12 and 13 are increased in response to the increase in hydraulic pressure of the master cylinder 4.
The hydraulic pressure inside also rises. And the control unit 57
If it is determined that the brake is overloaded, the output S ₁ of the output terminal 59a becomes 1 ″.
The solenoid valve 21 is excited by the solenoid 21b of the solenoid 21 and the solenoid valve 21 moves the pressure regulator 8
The position A where the pressure chamber 39 side and the reservoir 23 side are cut off is switched to the position B where they are communicated. The pressure liquid contained in the pressure chamber 39 of the pressure regulator 8 is discharged to the liquid chamber of the reservoir 23 through the pipes 20 and 22. When the pressure in the pressure chamber 39 decreases in this way, the control piston 36 is pressed by the hydraulic pressure of the master cylinder 4 supplied from the input port 16 and moves to the pressure chamber 39 side. As the control piston 36 moves, the cut valve main body 32 moves the inner wall 30c by the spring force of the first valve spring 40.
Side, the valve body 31 is seated on the valve seat 37, and then the valve ball 35 in the cut valve body 32 is moved by the spring force of the second valve spring 42.
Sitting on 2b, the communication between the input port 16 and the volume chamber 41 is cut off. The control piston 36 receives the hydraulic pressure on the wheel cylinders 12 and 13 side and further moves to the pressure chamber 39 side, and the volume of the volume chamber 41 increases accordingly, so that the volume chamber via the first output port 17 is increased. The hydraulic pressure in the wheel cylinders 12, 13 communicating with 41 decreases.

Stepped piston arranged between the input port 16 and the second output port 19
64 is a control piston due to the movement of the cut valve body 32 described above.
The urging force from the pressure chamber 39 side through 36 will not be received by the end surface of the large diameter portion 64b, and the end surface of the small diameter portion 64a will be subjected to the hydraulic pressure on the wheel cylinder 12, 13 side via the pipe 14. However, the end surface of the large diameter portion 64b receives hydraulic pressure on the master cylinder 4 side via the input port 16, and the large diameter portion 64b and the small diameter portion 64b
The acting force obtained by multiplying the difference in pressure receiving area with 64a by the hydraulic pressure is larger than the spring force of the spring 68. Therefore, the stepped piston 64
Continues to be pressed against the conical surface 62 of the tube sheet 61,
By pressing the peripheral edge of the through hole 65 and the conical surface 62, the input port
The 16 side and the second output port 19 side are kept in the cutoff state.

When the control unit 57 determines that the brake is excessively loosened because the brake is loosened in accordance with the decrease in the hydraulic pressure on the wheel cylinders 12 and 13 side, the output terminal 5
The output S _{1 of} 9a is switched from 1 ″ to 0 ″, the solenoid 21b of the solenoid valve 21 is demagnetized, and the solenoid valve 21 is moved to the position A where the pressure chamber 39 side and the reservoir 23 side are shut off by the spring force of the spring 21a. Can be switched. At this time, by stopping the liquid discharge from the pressure chamber 39 to the liquid chamber of the reservoir 23, the control piston 36
Stops and the volume of the volume chamber 41 does not change, and the hydraulic pressure on the wheel cylinders 12 and 13 side is kept constant. After that, the output S ₂ of the output terminal 59b of the control unit 57 becomes a pulse output which switches between 1 ″ and 0 ″ at an appropriate time interval, and this output is guided to the coil 50 of the electromagnetic pump 26. Then, in the electromagnetic pump 26, when the output S ₂ becomes 1 ″, the coil 50 is excited. The magnetic plunger attracts the main plunger.
The 51 and the sub-plunger 52 move against the spring force of the spring 55 to send the liquid in the liquid chamber 56 into the pressure chamber 39 of the pressure regulator 8 via the check valve 25. The sub-plunger 52 is the inner wall surface of the main body 48.
It stops by contact with 48b, and then output signal S
₁ moves to 0 ″ and moves back, but one stroke at the time of this forward movement causes the liquid of a constant volume in the liquid chamber 56 to move to the pressure chamber of the pressure regulator 8.
The liquid is fed into the chamber 39, whereby the control piston 36 moves to the volume chamber 41 side by this liquid amount, and the volume of the volume chamber 41 decreases. Then, the hydraulic pressure on the wheel cylinders 12 and 13 side increases due to this volume decrease.

When the output S ₂ becomes 0 ″, the coil 50 is demagnetized, so that the main plunger 51 and the sub-plunger 52 return by receiving the spring force of the spring 55. At this time, the reservoir is passed through the check valve 28. The liquid is sucked from 23 into the liquid chamber 56. Plunger
Since the liquid is not supplied to the pressure chamber 39 of the pressure regulator 8 during the backward movement of the pressure adjusting device 51, 52, the hydraulic pressure on the wheel cylinder 12, 13 side becomes constant.

When the output S ₂ becomes 1 ″ again and the coil 50 is excited, as described above, the main plunger 51 and the sub-plunger 52 are moved forward, so that a constant volume of liquid in the liquid chamber 56 enters the pressure chamber 39 of the pressure regulator 8. The control piston 36 is sent in, and the control piston 36 moves by the amount of the liquid, the volume of the volume chamber 41 decreases, and the hydraulic pressure on the wheel cylinders 12 and 13 side increases.

In this way, while the pulsed output S ₂ is being supplied from the control unit 57 to the coil 50 of the electromagnetic pump 26, the electromagnetic pump 26 discharges the liquid to the pressure chamber 39 side and the reservoir 23.
Control piston by repeating liquid suction from the side
36 moves while reducing the volume of the volume chamber 41, and accordingly, the hydraulic pressure on the wheel cylinders 12 and 13 side gradually increases. Then, when the shaft-like portion 43 provided at the end of the control piston 36 pushes the valve ball 35 and separates it from the valve seat 32b according to the movement of the control piston 36, the large-diameter hole portion 30a passes through the input port 16. The hydraulic pressure of the master cylinder 4 supplied into the wheel cylinders 12 and 13 from the throttle hole 34 of the lid member 33 through the cut valve body 32, the volume chamber 41 and the first output port 17. As a result, the hydraulic pressure on the wheel cylinders 12 and 13 side is further increased.

When the brakes of the rear wheels 10 and 11 are applied in this way and the control unit 57 determines that the brakes are applied too much, the output S ₁ of the output terminal 59a becomes 1 ″. At this time, the output S of the output terminal 59b has already been applied. The pulse output of ₂ has disappeared.

When the output S ₁ becomes 1 ″, the solenoid 21b of the solenoid valve 21 is excited and the solenoid valve 21 is switched to the position B where the pressure chamber 39 side and the reservoir 23 side communicate with each other.
When the pressure liquid inside is discharged to the liquid chamber of the reservoir 23 and the pressure inside the pressure chamber 39 drops, the control piston 36 moves to the wheel cylinder.
The wheel cylinders 12, 13 are pressed by the hydraulic pressure on the 12 and 13 side to move to the pressure chamber 39 side, and the volume of the volume chamber 41 increases.
Side hydraulic pressure drops.

Thereafter, similarly to the above, the operations of holding, raising and lowering the hydraulic pressures on the wheel cylinders 12 and 13 side are repeated based on the outputs S ₁ and S ₂ of the control unit 57, so that the anti-skid control is continued and the rear wheel. The vehicle slows down and stops without locking 10 and 11.

When the above-mentioned anti-skid control is completed, the pressure regulator 8
If the pressure in the pressure chamber 39 is lower than the predetermined pressure for urging the control piston 36 to keep the valve body 31 and the valve ball 35 separated from the valve seats 37 and 32b, Upon receiving the output of the switch 70, the control unit 57 generates a drive signal for the electromagnetic pump 26, and the output S ₂ at the output terminal 59b becomes a pulse output. As a result, the electromagnetic pump 26 is driven at the same time when the above-mentioned brake is reloaded, and the discharge pressure liquid is supplied to the pressure chamber 39. However, the desired brake operation is obtained by the anti-skid control, and the brake pedal 5 When the depression is released, the pressure liquid is supplied from the accumulator 75 to the pressure chamber 39 in response to the decrease in the hydraulic pressure on the master cylinder 4 side.

That is, when the hydraulic pressure of the master cylinder 4 is reduced, the hydraulic fluid supplied to the wheel cylinders 12 and 13 is released to the master cylinder 4 side through the first output port 17, the volume chamber 41, and the input port 16. At the same time, in the accumulator device 72, the large-diameter piston of the accumulator control valve device 80
In response to a decrease in master cylinder 4 hydraulic pressure that was pressing 86,
The acting force that urges the small-diameter piston 92 toward the valve seat 90 becomes smaller than the urging force of the spring 95 and the accumulator 75 that corresponds to the accumulated pressure. The valve ball 91 moves away from the valve seat 90, the accumulator chamber 78 of the accumulator 75 communicates with the input / output port 73 side, and the accumulator chamber 78
Of the pressure liquid is sent to the pressure chamber 39 of the pressure regulator 8.

Therefore, after the end of the anti-skid control, the control piston 36 of the pressure regulator 8 causes the valve element 31 and the valve ball 35 to be seated on the valve seats 37 and 32b, and the wheel cylinders 12 and 13 from the master cylinder 4 side.
The pressure chamber 39 is supplied with not only the discharge pressure liquid of the electromagnetic pump 26 but also the pressure liquid from the accumulator 75 even at the position where the liquid supply to the side is shut off and the volume of the volume chamber 41 is increased. As a result, the control piston 36 quickly returns to the volume chamber 41 side, and the cut valve body 32, the valve ball 35, and the valve spring 40,
It is pressed against the spring force of 42 to separate from the valve seats 37, 32b.

Then, when the pressure on the pressure chamber 39 side rises to a predetermined pressure by the liquid discharge of the electromagnetic pump 26 and the pressure liquid supply from the accumulator 75, the pressure switch 70 is switched and its output disappears, but the control unit. 57 is a pressure switch
The drive signal of the electromagnetic pump 26 is continuously generated for a predetermined time after the switching of 70, and the output S _{2 at} the output terminal 59b is a pulse output until the predetermined time elapses, and the discharge liquid of the electromagnetic pump 26 accumulates pressure in the accumulator 75. Replenished in chamber 78.

In this way, when the brake operation is released, the pressure in the pressure chamber 39 of the pressure regulator 8 and the pressure accumulation chamber 78 of the accumulator 75, which are shut off from the reservoir 23 side by the solenoid valve 21, are higher than a predetermined pressure. The control piston 36 of the pressure regulating device 8 receives the pressure of the pressure chamber 39, resists the spring force of the valve springs 40 and 42, and the hydraulic pressure of the master cylinder 4 acting from the volume chamber 41 side, and cut valve. The main body 32 is returned to the position shown in the figure and the communication between the master cylinder 4 side and the wheel cylinders 12 and 13 side is maintained via the first output port 17.

Although the case where the brake is released after the vehicle has stopped has been described, the brake pedal 5 is depressed while the hydraulic pressure on the wheel cylinders 12 and 13 side is being reduced by the above-described anti-skid control while the vehicle is traveling. Similarly, when released, the control piston 36 is rapidly returned by the supply of the pressure liquid from the accumulator 75 to the pressure chamber 39, and the valve bodies 31, 35 are separated from the valve seats 37, 32b.

That is, the output S ₁ of the control unit 57 becomes 1 ″ and the solenoid valve 21 is switched to the position B where the pressure chamber 39 communicates with the reservoir 23 side, and the control piston 36 causes the valve elements 31, 35 to move to the valve seat.
When the brake pedal 5 is released and the master cylinder 4 side hydraulic pressure is released while being moved to a position where the volume chamber 41 is increased by being seated on the 37, 32b, the wheel cylinders 12, 13 side The hydraulic pressure is released against the master cylinder 4 side while pressing the valve ball 35 against the spring force of the second valve spring 42 to separate it from the valve seat 32b. As a result, the brake release signal of the control unit 57 disappears and the output S ₁
Becomes 0 ″, and the solenoid valve 21 is switched to the position A where the pressure chamber 39 is shut off from the reservoir 23 side. Thus, anti-skid control is no longer performed, and at the same time, accumulator control is performed in response to the decrease in master cylinder 4 side hydraulic pressure. Both pistons 85, 95 of the valve device 80 move to the control port 81 side, the valve ball 91 separates from the valve seat 90, and the pressure regulator 8 is shut off from the accumulator 75 by the solenoid valve 21 from the reservoir 23 side. The pressure liquid is supplied to the pressure chamber 39 of the.

The normal case in which the pressure of the pressure chamber 39 of the pressure regulator 8 can be made higher than the predetermined pressure has been described above. The case where the pressure on the pressure chamber 39 side cannot be raised to a predetermined pressure or more due to the above circumstances will be described.

When the brake pedal 5 is not depressed and the brake is not operated, the pressure chamber 39 and the lid pressure chamber 78 are caused by the above-mentioned failure.
Is lower than a predetermined pressure, and the force of the control piston 36 urging the cut valve body 42 from the pressure chamber 36 side is the valve spring.
If it becomes smaller than the spring force of 40 and 42, the cut valve body 32 pushes the control piston 36 and moves to the valve seat 37 side. Then, the valve body 31 is seated on the valve seat 37, and the valve ball 35 is further moved by the spring force of the second valve spring 42 so that the shaft-like portion 43 of the control piston 36 is formed.
By pressing and moving to sit on the valve seat 32b, the communication between the input port 16 and the first output port 17 is cut off.

However, in this case, the input port 16 and the second output port 19
The stepped piston 64 provided between the control valve 36 and the stepped piston 64 transmits the biasing force transmitted from the control piston 36 via the cut valve body 32 that abuts the end surface of the large diameter portion 64b, that is, the force pressed to the tube seat 61 side. I will not receive it. Since the brake is inoperative at the large diameter portion 64b end surface and the small diameter portion 64a end surface of the stepped piston 64, the master cylinder 4, the wheel cylinder 1
Since the hydraulic pressure of 2 and 13 is not applied, the stepped piston 64
Is pressed by the spring force of the spring 68 acting on the end surface of the small diameter portion 64a, and is moved to the cut valve body 32 side. In response to this movement, the opening peripheral edge of the through hole 65 on the small diameter portion 64a side moves away from the conical surface 62 of the tube sheet 61, and the large diameter portion 64a
The portion where the seal ring 67 is attached comes out from the large diameter hole portion 63b to the tapered portion 63c. In this way, the input port 16 and the second output port 19 side communicate with each other through the through hole 65 of the stepped piston 64, the gap between the stepped piston 64 and the tube seat 61, the small diameter hole portion 63a, and the passage 69.

Therefore, even if the input port 16 and the first output port 17 are cut off, when the brake pedal 5 is stepped on to operate the brake, the hydraulic pressure generated in the master cylinder 4 is applied to the input port 16 and the second output port 17. It is supplied to the wheel cylinders 12 and 13 through the output port 19 and the pipe 14, and the rear wheels 10 and 11 are braked.

When hydraulic pressure is supplied from the master cylinder 4 to the wheel cylinders 12 and 13, the small diameter portion 64a end surface and the large diameter portion 64b end surface of the stepped piston 64 respectively receive the hydraulic pressure, but the large diameter portion 64b The part where the seal ring 67 is attached is the taper part 6
By escaping to 3c, hydraulic pressure also acts on the step portion connecting the small diameter portion 64a and the large diameter portion 64b, and the stepped piston 64 has the same hydraulic pressure on each of the opposing pressure receiving surfaces of substantially the same area. Will be received. Therefore, a failure such as a pressure leak on the pressure chamber 39 side is repaired, a predetermined pressure is supplied into the pressure chamber 39, and the cut valve body 32 is attached to the end surface of the large diameter portion 64b of the stepped piston 64.
The stepped piston 64 does not move to the tube seat 61 side until the biasing force from the control piston 36 comes to be applied via the control valve regardless of whether or not hydraulic pressure is generated. Communication with mouth 19 is maintained.

As is clear from the above description, in this embodiment,
An accumulator control valve device that connects the pressure chamber 39 of the pressure regulator 8 with an accumulator 75 and receives the hydraulic pressure from the master cylinder 4 between the pressure chamber 39 and the accumulator 75 by the large-diameter piston 86 to close the valve. By providing 82, when the hydraulic pressure is generated in the master cylinder 4 and the brake is operating, the pressure chamber 39 of the pressure regulator 8 is cut off from the accumulator chamber 78 of the accumulator 75 and lowered by the anti-skid control. When the hydraulic pressures on the wheel cylinders 12 and 13 side are to be increased again, the control piston 36 is moved to the volume chamber 41 side at a speed according to the discharge liquid amount of the electromagnetic pump 26. Then, when the hydraulic pressure in the master cylinder 4 is reduced and the brake operation is released, the pressure chamber 39 and the accumulator chamber 78 of the accumulator 75 communicate with each other, so that the control piston 36 causes the valve element 31 and the valve ball 35 to seat on the valve seat. 3
Even when the volume chamber 41 is seated on the seats 7, 32b and the volume of the volume chamber 41 is increased, the control piston 36 receives not only the discharge pressure liquid of the electromagnetic pump 26 but also the discharge liquid from the accumulator 75, and the volume chamber 41 The valve body 31 and the valve ball 35 are quickly separated from the valve seats 37 and 32b in the direction of decreasing the volume of the valve body.

Therefore, the rate of increase in hydraulic pressure during anti-skid control can be stabilized, and in addition, the master cylinder 4 side and the wheel cylinder 1 can be immediately responded to the decrease in hydraulic pressure of the master cylinder 4.
Since the 2nd and 13th sides are in communication with each other, even if a brake operation is performed in which the brake pedal 5 is stopped and immediately pressed again, it is possible to prevent the brake operation from being delayed with respect to the hydraulic pressure re-elevation of the master cylinder 4.

Although the embodiment shown in the drawings has been described above, the present invention is not limited to this, for example, instead of using the accumulator 75 filled with high-pressure nitrogen gas, it resists the biasing force of the high-preload spring. You may use the accumulator of the type which stores a pressure fluid. Also, accumulator control valve device
At 80, a large-diameter piston 86 that receives the hydraulic pressure of the master cylinder 4 and a valve ball 91 that is movably moved integrally with the large-diameter piston 86 in a direction away from the valve seat 90 by a spring 95.
Instead of providing the small-diameter piston 92 that fixes the valve, the valve provided between the accumulator 75 and the pressure chamber 39 has a structure in which the valve body is biased toward the valve seat by a spring, and the valve body is a master cylinder. A piston may be provided which is separated from the valve seat when not receiving hydraulic pressure and is seated on the valve seat when receiving master cylinder hydraulic pressure.

Further, in the illustrated embodiment, the pressure in the pressure chamber 39 is lower than the pressure capable of urging the control piston 36 to open the cut valve when the brake is not operated in which the hydraulic pressure is not generated in the master cylinder 4. In this case, the master cylinder 4 side and the wheel cylinders 12 and 13 side are directly connected according to the movement of the stepped piston 64. According to the present invention, the accumulator communicating with the pressure chamber 39 when the brake is not operated. Since 75 is provided, a piston that directly receives the pressure of the accumulator 75 is provided in place of the stepped piston 64 described above, and movement of this piston according to the pressure drop of the accumulator 75 causes the master cylinder 4 side and the wheel cylinder 12 to move. ,13
You may make it contact with the side directly.

[Brief description of drawings]

The drawing shows a cross-sectional view of an embodiment of the present invention together with a piping system of a brake device. 1 …… Hydraulic control device for anti-skid 21 …… Solenoid valve, 26 …… Electromagnetic pump 32 …… Cut valve body, 36 …… Control piston 39 …… Pressure chamber, 41 …… Volume chamber, 75 …… Accumulator 80 ...... Accumulator control valve device

Claims (1)

[Claims] 1. A cut valve disposed between a master cylinder and a wheel cylinder, a control piston movable to open and close the cut valve, and a wheel cylinder formed between the control piston and the cut valve. And a pressure chamber formed on the opposite side of the control piston from the volume chamber,
In an anti-skid hydraulic pressure control device having an electromagnetic pump whose discharge side is connected to a pressure chamber, and an electromagnetic valve which is provided between the discharge side and the suction side of the electromagnetic pump and which can switch between a blocking position and a communication position An anti-skid hydraulic pressure control device comprising an accumulator in communication with the pressure chamber, and an accumulator control valve that is closed by the pressure from the master cylinder between the pressure chamber and the accumulator.