JPS6325165A - Hydraulic pressure control device for antiskid - Google Patents

Abstract

PURPOSE:To raise again pressure of a master cylinder, stably, by setting a cut valve between the master cylinder and wheel cylinder, as this but valve confronts a part between a displacement chamber and a pressure chamber, and connecting an accumulator to the pressure chamber through a control valve. CONSTITUTION:A cut valve 32 is set between a master cylinder 4 and wheel cylinders 12, 13, and a control piston 36 adapted to open/close the cut valve 32, is set between a displacement chamber 41 and a pressure chamber 39. An electromagnetic pump 26 and a solenoid controlled valve 21 are connected to the pressure chamber 39, and at the same time, an accumulator 72 is also connected to the pressure chamber 39, through an accumulator control valve 80 adapted to be closed by the pressure from the master cylinder 4. Anti-skid control is performed by switching the solenoid controlled valve 21, and the control valve 80 is opened when the pressure of the master cylinder 4 becomes lower, to feed pressed liquid in the accumulator 72 to the pressure chamber 39, and open the cut valve 32 through the control piston 36, and consequently, pressure of the master cylinder 4 can be raised again stably.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an anti-skid hydraulic pressure control device used in a brake device of a vehicle or the like.

[Prior art]

The present applicant previously proposed a device of this type that includes a cut valve disposed between a master cylinder and a wheel cylinder, a control piston that is movable to open and close the cut valve, and a control piston and a cut valve that are movable to open and close the cut valve. A volume chamber formed in between and connected to the wheel cylinder, a pressure chamber formed on the opposite side from the volume chamber of the control piston, an electromagnetic pump whose discharge side is connected to the pressure chamber, and the discharge side of the electromagnetic pump. We have proposed a solenoid valve that is provided between the suction side and the solenoid valve that can be switched between a blocking position and a communicating position.

In such a device, the solenoid valve is set to the cutoff position, the control piston is energized by the pressure contained in the suction side of the solenoid pump, and the cutoff valve is opened, and the master cylinder is connected to the wheel cylinder. When anti-skid control is performed after pressure is supplied, the control piston is connected to the wheel cylinder by first switching the solenoid valve to the appropriate position and releasing the pressure in the pressure chamber to the suction example of the solenoid pump. The supplied pressure closes the cut valve and moves it in a direction to increase the volume of the volume chamber, and the pressure on the wheel cylinder side, which is cut off from the master cylinder side, is reduced in accordance with the increase in volume of the volume chamber. Then, by switching the solenoid valve to the cutoff position and driving the solenoid pump to supply its discharge pressure fluid to the pressure chamber, the control piston is moved in the direction of decreasing the volume of the volume chamber, and the wheel cylinder is lowered. The side pressure is increased, and thereafter, similarly to the above, the decrease and increase of the wheel cylinder side pressure is repeated as appropriate.

When the pressure in the master cylinder decreases and anti-skid control is no longer performed, the control piston is moved back to the position where the cut valve is opened in order to communicate between the master cylinder side and the wheel cylinder side. There is.

[Problems to be solved by the present invention]

Return movement of the control piston to the position where the cut valve is opened must be done by driving the electromagnetic pump and supplying its discharge liquid into the pressure chamber that is isolated 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 capacity per unit time of the electromagnetic pump.

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, if a brake operation is performed that lowers the master cylinder pressure and immediately raises it again, the electromagnetic pump will Although the control piston is moved back in response to the discharge of pressurized fluid,
A problem arises in that the cut valve is not opened in time for the master cylinder pressure to rise again, and the pressure cannot be immediately supplied to the wheel cylinders.

The present invention has been made in view of the above problems, and provides an anti-skid hydraulic pressure control device that can communicate the master cylinder side and the wheel cylinder side in immediate response to a decrease in master cylinder pressure. With the goal.

[Means of the present invention]

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

[Effect of means]

When pressure is generated in the master cylinder to operate the brake, the accumulator and the pressure chamber are cut off, and anti-skid control is performed by switching the solenoid valve and driving the solenoid pump as described above, reducing the pressure in the master cylinder. , the accumulator control valve opens, and the pressure fluid previously stored in the accumulator is supplied to the pressure chamber, biasing the control piston toward the open position of the cut valve.

[Effects of the present invention]

Even if the control piston is in the position where the cut valve is closed and the volume of the volume chamber is increased, it is instantly returned to the position where the cut valve is opened in response to a decrease in master cylinder pressure, thereby reducing the master cylinder pressure. Even if a brake operation is performed to immediately raise the pressure again, the pressure can be quickly supplied to the wheel cylinders, and it is possible to prevent the brake operation from being delayed in response 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 is increased, only the pressure fluid discharged from the electromagnetic pump is supplied to the pressure chamber, and the control piston controls the volume of the volume chamber. Since the pressure is moved in the decreasing direction, the stable pressure increase on the wheel cylinder side is not impaired.

〔Example〕

Hereinafter, one embodiment of the present invention illustrated in the drawings will be described.

In the figure, the anti-skid hydraulic pressure control device of this embodiment is indicated as a whole by 1, and hydraulic pressure is supplied from a master cylinder 2 with a vacuum booster.

That is, the vacuum booster-equipped master cylinder 2 consists of a known vacuum booster 3 and a master cylinder 4. The vacuum booster 3 is driven by a brake cylinder 5, and the master cylinder 4 is driven by its output. It is assumed that one of the hydraulic pressure generating chambers in the master cylinder 4 is connected to the wheel cylinder of the front wheel via a piping 6 and a device similar to the hydraulic pressure control device 1 shown in the figure.

The other hydraulic pressure generating chamber will be described later via piping 7. connected to the input port 16 of the pressure regulating device 8;
7 is connected to the wheel cylinder 12.13 of the rear wheel 10.11 via pipe 9, and the second output lo 19 is connected to pipe 1
It is connected to piping 9 via 4.

The control port 18 of the pressure regulator 8 is connected to a pipe 2 provided with a check valve 25.
A pipe 20.4 is connected to the discharge port 27 of the tMi pump 26 through a pipe 20. It can be connected to a reservoir 23 via a solenoid valve 21 and piping 22. As is well known, the reservoir 23 includes a main body 40, a slidable piston 45 with a seal ring attached to its inner hole, and a relatively weak spring 46 that biases the piston 45. An air chamber is defined. The liquid chamber communicates with the piping 22 through the above-mentioned through hole 47, and further through the piping 29 provided with the check valve 28! It is connected to a discharge port 27 that also serves as a suction port of the magnetic pump 26 . The check valves 28 and 25 allow flow from the reservoir 23 to the electromagnetic pump 26 side and from the electromagnetic pump 26 side to the control port 18 side, respectively, but prohibit the opposite flow. 70 is connected to the control port 1 from the check valve 25 of the pipe 24.
8 side, the pressure chamber 39 of the pressure regulator 8, which will be described later. Accumulator chamber 78 of accumulator device 72
The pressure is detected, and when the pressure reaches a predetermined pressure, the switch is switched, and a signal is output when the pressure is below the predetermined pressure.

A control port 18 and a check valve 25 are provided on the discharge side of the electromagnetic pump 26.
An input/output port 73 of an accumulator device 72 is connected to the accumulator device 72 via a pipe 71 branched from the pipe 24. The accumulator device 72 has an accumulator 75 integrally assembled with an accumulator control valve device 80 to be described later, and the accumulator 75 has a flexible membrane plate 77 disposed within a spherical main body 76 as is well known. The membrane plate 77 defines a gas chamber in which high-pressure nitrogen gas is sealed in the main body 76 and a pressure accumulation chamber 78 . And the pressure storage chamber 7
8 can communicate with the above-mentioned input/output port 73 via a passage 79. The control port 81 of the accumulator device 72 is
The piping 7 is connected to the hydraulic pressure generating chamber of the master cylinder 4 via a piping 89 .

The solenoid valve 21 is a two-position valve that switches in response to de-energization of the solenoid 21b, and when the solenoid 21b is de-energized, communication between the control port 18 side and the reservoir 23 side is cut off by the biasing force of the spring 21a. When the solenoid 21b is energized, the control port 18 side and the reservoir 23
Take position B that communicates with the side.

In the electromagnetic pump 26, a coil 50 wound around a bobbin 49 is arranged and fixed in the large diameter part of the inner hole 53 of the main body 48, and a main plunger 51 made of a magnetic material is slidably fitted into the center hole of the bobbin 49. It matches. The coil 50 is excited by a current from the control unit 57, but is shown in a non-energized state, and the main plunger 51 is in contact with the bottom 48a of the main body 48.

A stepped-shaped sub-plunger 52 is slidably fitted into the small diameter portion of the inner hole 53 of the main body 48 with a seal ring 54 interposed therebetween, and is biased toward the bottom portion 48a by a spring 55 so that the main plunger It is in contact with 51. In the illustrated normal state, a liquid chamber 5 with a predetermined volume (for example, O, Ice) is located between the end surface 52a of the sub-plunger 52 and the inner wall end surface 48b of the main body 48.
6 is formed, which communicates with the above-mentioned discharge port 27. When the coil 50 is excited, the main plunger 51 is urged toward the discharge port 27 by magnetic attraction, and presses the sub-plunger 52 against the urging force of the spring 55. Sub-plunger 5
2 stops when its end surface 52a comes into contact with the inner wall end surface 48b of the main body 48, and the previous stroke sends a predetermined volume of hydraulic fluid to the pressure regulator 8 side via the check valve 25 and the piping 24.

When the coil 50 is de-energized, the auxiliary plunger 52 and the main plunger 51 move back due to the biasing force of the spring 55 and assume the illustrated position. Due to the return stroke at this time, a predetermined volume of hydraulic fluid is sucked from the reservoir 23 via the check valve 28. Note that a magnetic circuit is constituted by the main plunger 51 and a portion of the main body 48 made of a magnetic material.

The above-mentioned solenoid valve 21. The electromagnetic pumps 26 are controlled by receiving outputs from the output terminals 59a and 59b of the control unit $7 through the solenoid 21b and the coil 50, respectively. The control unit 57 has its input terminal 5
Although not shown in the figure, output terminals of wheel speed detectors provided on each wheel are connected to 8a, and various calculations and judgments are made based on the outputs of these detectors to generate a brake release signal and a brake resend signal. . Further, the output terminal of the pressure switch 70 described above is connected to the input terminal 58b, and the pressure chamber 39. A drive signal for the electromagnetic pump 26 is generated based on the output of the pressure switch 70, which is issued when the pressure in the pressure accumulation chamber 78 is below a predetermined pressure.

However, while the anti-skid control is being performed based on the brake release signal and reload signal, the output of the pressure switch 70 is disabled and the above drive signal is not generated.

When the brake release signal is generated, the output of the control unit 57 is such that the output S1 at the output terminal 59a connected to the solenoid 21b is at a high level 1', and the output S2 at the output terminal 59b connected to the coil 50 is at a low level O'. bawl. In addition, when a brake resending signal is generated or a drive signal light is generated, the output S1 is at a low level O", and the output S2 is at a high level L" at an appropriate time interval.
This is a pulse output that switches between low level and low level 0''.

The pressure regulating device 8 interposed between the master cylinder 4 and the wheel cylinders 12.13 has a stepped hole 30 inside the main body 15.
A stepped cut valve main body 32 is slidably fitted inside a large diameter hole 30a communicating with an input port 16 connected to the master cylinder 4. The cut valve body 32 has a plurality of grooves 32a formed on the outer periphery of its large diameter portion to communicate both ends of the cut valve body 32, and a synthetic rubber groove 32a on the outer periphery of the end facing a control piston 36, which will be described later. An annular valve body 31 is attached, and the valve seat 3 formed on the inner wall 30c according to the movement of the cut valve body 32.
It is possible to take up and take off the seat at 7. And the cut valve body 32
is attached to the opening of the large diameter hole 30a and the second output lo 1
The first valve spring 40, which is stretched between the inner end of the lid body 60 provided with
It is biased toward 7. Such a cut valve body 32
Further, a stepped through hole extending in the axial direction is formed, and a tapered valve seat 32b in which the valve ball 35 can be seated and removed is provided in the through hole on the end side where the valve body 31 is attached. It is provided. A lid member 33 having an aperture hole 34 is integrally assembled into the opening of the through hole on the end side facing the lid body 60.
A first valve spring 4 is provided between this lid member 33 and the above-mentioned valve ball 35.
By tensioning the second valve spring 42 whose spring force is weaker than zero, the valve ball 35 is urged toward the valve seat 32b.

Large diameter hole 30 through communication hole 30d provided in inner wall 30c
A control piston 36 having a pair of sealing members 38 attached to its outer periphery is slidably fitted into the small diameter hole 30b of the stepped hole 30 that communicates with the cut valve body 32. The wheel cylinder 12.13 is connected via the first output rod 17 between the valve body 31 and the valve seat 37 which can be seated and taken off.
A volume chamber 41 is defined which is always in communication with the volume chamber 41.
A pressure chamber 39 communicating with the control port 18 is defined on the opposite side of the control piston 36 .

The end of the control piston 36 on the volume chamber 41 side is connected to the communication hole 30.
d so that it can come into contact with the cut valve main body 32, and furthermore, the shaft-like part 43 formed integrally at the end can come into contact with the valve ball 35 inside the cut valve main body 32. .

In this way, the movement of the control piston 36 in accordance with the pressure difference generated between the volume chamber 41 side and the pressure chamber 39 side causes the valve body 32 of the valve body 32 to be seated and unseated with respect to the valve seat 37, and the valve ball 3
The seating and unseating of the valve body 31 with respect to the valve seat 32b is controlled, and the valve body 31 is moved against the valve seat 32b in accordance with the movement of the control piston toward the pressure chamber 39 side.
7, when the valve ball 35 is seated on the valve seat 32b, liquid communication from the input port 16 side to the first output port 17 side is cut off.

A lid 60 that is attached to the opening of the large diameter hole 30a of the main body 15 and extends inward is formed with a stepped hole 63 in which the large diameter hole 63b opens toward the cut valve main body 32. A stepped piston 64 is movably fitted into the provided 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 hole 63a of the stepped hole 63, with its lip portion facing the second output rotor 19 side.
A seal ring 67 is attached to the outer periphery of the large diameter portion 64b that fits into the large diameter hole 63b. And cart/cart valve body 3
2 and the inner side of the large diameter hole 30a with the lid 6
The stepped piston 64 can communicate with the small diameter hole 63a side of 0.
A through hole 65 extending in the axial direction is formed therein. The tube sheet 61 is press-fitted into the lid body 60 from the second output hole 19 side and has a conical surface 62 at the tip that projects into the small diameter hole 63a, which connects the inside of the small diameter hole 63a and the second output hole 19. A through hole 69 is formed so that the end surface of the small diameter portion 64a of the stepped piston 64 can receive the hydraulic pressure on the wheel cylinder 12.13 side, and the spring 68 disposed in the small diameter hole 63a can is receiving force. On the other hand, the end surface of the large diameter portion 64b of the stepped piston 64 can receive the hydraulic pressure on the master cylinder 4 side via the input port 16, and can also be pressed by the control piston 36 and come into contact with the end surface thereof. It is possible to receive an urging force depending on the pressure in the pressure chamber 39 via the cut valve main body 32. In this way, the stepped piston 64 is configured to:
In order to cut off communication between the input port 16 side and the second output port 19, the opening periphery of the through hole 65 is brought into pressure contact with the conical surface 62 of the tube sheet 61, so that the force received by the end surface of the large diameter portion 64b is transferred to the small diameter portion 64a. When the force becomes smaller than the force received, it moves toward the cut valve main body 32 side, and the opening periphery of the through hole 65 is separated from the conical surface 62 in order to communicate the input port 16 side and the second output port 19 side. There is. Note that when the stepped piston 64 moves toward the cuff valve main body 32 as described above, the portion of the large diameter portion 64b where the seal ring 67 is attached expands from inside the large diameter hole 63b to a larger diameter than the large diameter hole 63b. The opening is designed to come out at the tapered portion 63c.

The accumulator 75 described above is attached to the main body 82 of the accumulator control valve device 80 by screwing its cylindrical portion 74 to one end side of a stepped hole 83 via a seal ring. A lid body 84 in which a control port 81 is provided in the large diameter hole on the other end side of the attached hole 83
is screwed on. A hole 85 is formed at the inner end of the lid 84 and opens toward a support member 87 fitted into the medium diameter hole of the stepped hole 83 via a seal ring.
A large-diameter piston 86, which receives the hydraulic pressure of the master cylinder 4 at one end through the control port 81 and piping 89, is fitted into the hole 85 with a seal ring attached thereto. A small hole 88 that communicates with the pressure storage chamber 78 of the accumulator 75 via a 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 this small hole 88.

Then, a small-diameter piston 92 with a valve ball 91 that can be placed on and taken off from the valve seat 90 is brazed, and the shaft portion 93 is attached to the support member 87.
It is slidably fitted into a through hole 94 fitted with a sealing member. The small diameter piston is biased in a direction to move the valve ball 91 away from the valve seat 90 under the biasing force of the spring 95.
An end of the shaft portion 93 is in contact with the other end of the large diameter piston 86. In this way, the force acting on the large-diameter piston 86 is responsive to the hydraulic pressure on the master cylinder 4 side, the biasing force of the spring 95 acting on the small-diameter piston 92, and the pressure on the accumulator 75 side The large-diameter piston 86 and the small-diameter piston 92 can move integrally by changing the magnitude relationship with the applied force. Then, 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 and 92 move toward the small hole 88 and seat the valve ball 91 on the valve seat 90.
Communication between the pressure storage chamber 78 of the accumulator 75 and the input/output port 73 connected to the pressure chamber 39 of the pressure regulator 8 is cut off.

Next, the operation of the above-mentioned embodiment will be explained. It is assumed that the brake system for the front wheels (not shown) connected to the master cylinder 4 via piping 6 is also provided with a device similar to the device 1 shown in the drawings. The operation will be explained only for the system.

It is now assumed that a vehicle equipped with the present hydraulic pressure control device 1 and the master cylinder 2 with a vacuum booster is traveling at a constant speed. That is, the brake pedal 5 is not depressed, and the output signal S of the control unit 57 is
Both S2 are 0", and the device I is in the state shown in the figure. At this time, the solenoid valve 21 isolates the pressure chamber 39 of the regulating device 8 and the accumulator 75 side of the accumulator device 72 from the reservoir 23 side, The pressure within the pressure chamber 36 is maintained at a higher pressure than the predetermined pressure at which the pressure cass isothia 0 switches, and a pressure liquid of the same pressure is stored in the pressure accumulation chamber 78.In the pressure regulator 8, control piston 3
6 receives the pressure of the pressure chamber 39 and presses the cut valve body 32 and the valve ball 35 against the spring force of each valve spring 40, 42,
Valve body 31. Both the valve balls 35 are removed from the valve seats 37 and 32b, and the input port 16 and the first output port 17 communicate with each other via the volume chamber 41. Further, the stepped piston 64 receives the biasing force from the control piston 36 via the cut valve main body 32 on the large diameter portion 64b, and resists the spring force of the spring 68 to
The opening periphery of the tube sheet 61 is pressed to a position where it comes into pressure contact with the conical surface 62 of the tube sheet 61, and the input port 16 and the second output port 19 are
It is cut off between. In the accumulator device 72, the small-diameter piston 92 of the accumulator control valve device 80 is biased by a spring 95 and receives pressure from the pressure accumulation chamber 78 to displace the valve ball 91 from the valve seat 90.
The accumulator 75 side and the input/output row 73 side are in communication.

In order to stop the vehicle in this condition, the brake pedal 5
When ``is strongly depressed'', the hydraulic pressure generated in the master cylinder 4 is transferred to the pipe 7. Input port 16 of pressure regulator 8, volume chamber 41. The wheel cylinder 12 is connected via the first output rotor 17 and the pipe 9.
．． 13 and is also supplied to the control port 81 of the accumulator device 72 via piping 89. 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 95 and the urging force according to the accumulated pressure of the accumulator 75, and the valve The ball 91 is seated on the valve seat 90. As a result, the pressure accumulation chamber 78 of the accumulator 75
Communication between the pressure regulator 8 and the pressure chamber 39 side is cut off.

The hydraulic pressure supplied from the master cylinder 4 to the wheel cylinder 12.13 begins to brake the rear wheel 10.11, and as the hydraulic pressure in the master cylinder 4 increases, the hydraulic pressure in the wheel cylinder 12.13 also increases. When the control unit 57 determines that the brake has been applied too much, the output SI of the output terminal 59a becomes 1''.

As a result, the solenoid 21b of the solenoid valve 21 is energized, and the solenoid valve 21 is connected to the pressure chamber 39 side of the pressure regulator 8 and the reservoir 23.
It is possible to switch from position A, which blocks the two sides, to position B, which communicates the two. The pressure liquid contained in the pressure chamber 39 of the pressure regulator 8 is discharged to the liquid chamber of the reservoir 23 via the piping 20.22.

When the pressure in the pressure chamber 39 decreases in this way, the control piston 36 is pushed by the hydraulic pressure of the master cylinder 4 supplied from the input port 16 and moves toward the pressure chamber 39. Along with this movement of the control piston 36, the cut valve body 32 moves toward the inner wall 30c due to the spring force of the first valve spring 40, and the valve body 31 seats on the valve seat 37.
The inner valve ball 35 is pressed against the valve seat 32 by the spring force of the second valve spring 42.
b, communication between the input port 16 and the volume chamber 41 is cut off. The control piston 36 is connected to the wheel cylinder 12.1
In response to the hydraulic pressure on the third side, the first liquid moves further toward the pressure chamber 39 side, and the volume of the volume chamber 41 increases accordingly.
The hydraulic pressure in the wheel cylinders 12, 13, which communicate with the volume chamber 41 via the output I7, decreases.

A stepped piston 64 disposed between the input port 16 and the second output port 19 transfers the biasing force from the pressure chamber 39 side via the control piston 36 to its large diameter portion by the movement of the cut valve body 32 described above. 64b is no longer received by the end face, and the small diameter portion 64a
Wheel cylinder 12.13 via pipe 14 on the end face of
However, the end face of the large diameter portion 64b receives the hydraulic pressure from the master cylinder 4 side through the input port 16, and the difference in pressure receiving area between the large diameter portion 64b and the small diameter portion 64a The acting force obtained by multiplying the hydraulic pressure by the hydraulic pressure is greater 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, and the pressure contact between the opening periphery of the through hole 65 and the conical surface 62 blocks the input port 16 side and the second output port 19 side. kept in condition.

The brake is released in response to the decrease in the hydraulic pressure on the wheel cylinder 12, 13 side described above, and the control unit 57
When it is determined that the brake is too loose, the output Sl of the output terminal 59a is switched from 1" to O", the solenoid 21b of the solenoid valve 21 is demagnetized, and the solenoid valve 21 is activated by the spring force of the spring 21a. It is switched to position A which blocks off the pressure chamber 39 side and the reservoir 23 side. At this time, by stopping the liquid discharge from the pressure chamber 39 to the liquid chamber of the reservoir 23, the movement of the control piston 36 is stopped and the volume chamber 44 is stopped.
The volume of 1 does not change.

The hydraulic pressure on the wheel cylinder 12, 13 side is kept constant. After that, the output S2 of the output terminal 59b of the control unit 57 becomes 1'' and 0'' at an appropriate time interval.
This output is a pulse output that switches between the two, and this output is guided to the coil 50 of the electromagnetic pump 26. Then, when the output S2 of the tit pump 26 becomes 1'', the coil 50 is excited.The main plunger 51 and the sub plunger 52 move against the spring force of the spring 55 due to the magnetic attraction force, and the liquid chamber 56
The liquid inside is sent into the pressure chamber 39 of the pressure regulator 8 via the check valve 25. The sub-plunger 52 is attached to the inner end wall surface 4 of the main body 48.
8b and stops, and after this, the output signal S
, becomes O'' and moves backward, but one stroke during this forward movement sends a certain volume of liquid in the liquid chamber 56 into the pressure chamber 39 of the pressure regulating device 8, and the control piston 36 moves this liquid. The wheel cylinder 1 moves toward the volume chamber 41 by the same amount, and the volume of the volume chamber 41 decreases.
2. The hydraulic pressure on the 13 side increases.

When the output S2 becomes O'', the coil 50 is demagnetized, and the main plunger 51 and the sub plunger 52 are activated by the spring 55.
It moves backward in response to the spring force, and at this time, liquid is sucked from the reservoir 23 into the liquid chamber 56 via the check valve 28. During the backward movement of the plungers 51 and 52, no liquid is supplied to the pressure chamber 39 of the pressure regulator 8, so the wheel cylinder 1
2. The hydraulic pressure on the 13 side remains constant.

When the output S2 becomes 1'' again and the coil 50 is excited,
As described above, by the forward movement of the main plunger 51 and the sub-plunger 52, a fixed volume of liquid in the liquid chamber 56 is sent into the pressure chamber 39 of the pressure regulating device 8, and the liquid volume control piston 36 moves to fill the volume chamber. 41 decreases, and the hydraulic pressure on the wheel cylinder 12.13 side increases.

In this way, while the pulsed output sz is supplied from the control unit 57 to the coil 50 of the electromagnetic pump 26, the electromagnetic pump 26 discharges liquid to the pressure chamber 39 side and sucks liquid from the reservoir 23 side. By repeating this, the control piston 36 moves while decreasing the volume of the volume chamber 41, and the hydraulic pressure on the wheel cylinder 12, 13 side gradually increases accordingly. When the shaft-like part 43 provided at the end of the control piston 36 presses the valve ball 35 to separate it from the valve seat 32b, the large-diameter hole 30a passes through the input port 16. The hydraulic pressure of the master cylinder 4, which is supplied inside the cant valve body 32, passes through the throttle hole 34 of the lid member 33 and into the volume chamber 41. It is supplied to the wheel cylinder 12.13 via the first output 17, thereby further increasing the hydraulic pressure on the wheel cylinder 12.13 side.

In this way, the brakes of the rear wheels 10.11 are applied, and when the control unit 57 determines that the brakes are applied too much, the output S1 of the output terminal 59a becomes 1''.At this time, the output S2 of the output terminal 59b has already been applied. The pulse output has disappeared.

When the output S1 becomes 1", the solenoid 21 of the solenoid valve 21
b is excited, and the solenoid valve 21 is connected to the pressure chamber 39 side and the reservoir 2.
It is switched to position B, which communicates with the third side.

In this way, the pressure fluid in the pressure chamber 39 is again discharged into the fluid chamber of the reservoir 23, and when the pressure in the pressure chamber 39 decreases, the control piston 36 is pushed by the fluid pressure on the wheel cylinder 12, 13 side, and the control piston 36 is pushed toward the pressure chamber 39. , the volume of the volume chamber 41 increases, and the hydraulic pressure on the wheel cylinder 12.13 side decreases.

Thereafter, in the same way as described above, the output S of the control unit 57
By repeating the operation of maintaining, increasing, and decreasing the hydraulic pressure on the wheel cylinder 12.13 side based on 1 and S2,
The anti-skid control continues and the vehicle is decelerated to a stop without locking the rear wheels 10.11.

When the anti-skid control described above is completed, the pressure regulator 8
The pressure in the pressure chamber 39 of the valve body 31. Place the valve ball 35 on each valve seat 3.
If the pressure is lower than a predetermined pressure that urges the control piston 36 to keep it separated from the pressure switch 70, the control unit 57 receives the output from the pressure switch 70.
generates a drive signal for the electromagnetic pump 26, and the output terminal 59b
The output S2 at is a pulse output. As a result, the electromagnetic pump 26 is driven in the same way as when re-feeding the brakes described above, and its discharged pressure fluid is supplied to the pressure chamber 39, but the anti-skid control allows the desired brake operation to be obtained and the brake pedal 5. When the depression is released, pressure fluid is also supplied from the accumulator 75 to the pressure chamber 39 in response to the decrease in the master cylinder 4 side hydraulic pressure.

That is, as the hydraulic pressure in the master cylinder 4 is reduced, the pressurized liquid that was being supplied to the wheel cylinders 12.13 is transferred to the first output port 17. Volume chamber 41. At the same time when the fluid is released to the master cylinder 4 side through the input port 16, in the accumulator device 72, in response to the drop in master cylinder 4 fluid pressure that was pressing the large diameter piston 86 of the accumulator control valve device 80, the small diameter piston is released. The acting force that was biasing the valve 92 toward the valve seat 90 becomes smaller than the biasing force depending on the spring force of the spring 95 and the accumulated pressure of the accumulator 75, and both pistons 86 and 92 move toward the control port 81. And Bentama 91
is removed from the valve seat 90, and the pressure accumulation chamber 7 of the accumulator 75
8 communicates with the input/output lo 73 side, and the pressure liquid in the pressure accumulating chamber 78 is sent to the pressure chamber 39 of the pressure regulating device 8 .

Therefore, after the anti-skid control is completed, the control piston 36 of the pressure regulating device 8 moves the valve body 31. Place the valve ball 35 on each valve seat 37.3
2b, the fluid supply from the master cylinder 4 side to the wheel cylinder 12.13 side is cut off, and even if the volume of the volume chamber 41 is increased, the pressure chamber 39
By supplying not only the discharge pressure fluid of the electromagnetic pump 26 but also the pressure fluid from the accumulator 75 to the control piston 36, the control piston 36 quickly returns to the volume chamber 41 side, and the cut valve body 32. The valve ball 35 is pushed against the spring force of the valve springs 40, 42 and is removed from each valve seat 37, 32b.

Then, the liquid discharge of the electromagnetic pump 26 and the accumulator 75
When the pressure on the pressure chamber 39 side rises due to the supply of pressure fluid from the pressure chamber 39 and reaches a predetermined pressure, the pressure switch 70 switches and its output disappears. Continuing to generate a drive signal for the electromagnetic pump 26 for a time, the output S at the output terminal 59b
2 is a pulse output until a predetermined time elapses,
The pressure fluid discharged from the electromagnetic pump 26 is replenished into the pressure storage chamber 78 of the accumulator 75 .

In this way, when the brake operation is released, the pressure regulator 8 is isolated from the reservoir 23 by the solenoid valve 21.
A pressure higher than a predetermined pressure is contained in the pressure chamber 39 of the accumulator 75 and the pressure accumulation chamber 78 of the accumulator 75, and the pressure regulating device 8
The control piston 36 receives the pressure in 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 moves the cut valve body 32 to the illustrated position. The master cylinder 4 side and the wheel cylinder 12.13 side are maintained in communication via the first output rotor 17.

Although we have described the case where the brake is released after the vehicle has stopped, if the brake pedal 5 is depressed while the vehicle is running and the hydraulic pressure on the wheel cylinder 12, 13 side is being lowered by the anti-skid control described above. Similarly, when it is released, the pressure chamber 39 is removed from the accumulator 75.
By supplying pressurized fluid to the control piston 36, the control piston 36 is quickly moved back and the valve body 31.35 is removed from the valve seat 37, 32b.

That is, the output S1 of the control unit 57 is 1''
Then, the solenoid valve 21 is switched to position B which communicates the pressure chamber 39 with the reservoir 23 side, and the control piston 36
1.35 is seated on the valve seats 37, 32b and moved to a position where the volume of the volume chamber 41 is increased, when the brake pedal 5 is released and the master cylinder 4 side hydraulic pressure is released, The hydraulic pressure on the wheel cylinder 12, 13 side presses the valve ball 35 against the spring force of the second valve spring 42, causing it to move away from the valve seat 32b and being released toward the master cylinder 4 side. As a result, the control unit 57
The brake release signal disappears, the output S becomes O'', and the solenoid valve 21 is switched to position A, which isolates the pressure chamber 39 from the reservoir 23 side.

In this way, anti-skid control is no longer performed, and at the same time, both pistons 85 and 92 of the accumulator control valve device 80 move toward the control port 81 side in response to a decrease in the hydraulic pressure on the master cylinder 4 side, and the valve ball 91 moves toward the valve seat. Pressure liquid is supplied from the accumulator 75 to the pressure chamber 39 of the pressure regulating device 8 which is isolated from the reservoir 23 side by the electromagnetic valve 21 .

Above, we have described the normal case where the pressure in the pressure chamber 39 of the pressure regulator 8 can be made higher than a predetermined pressure.
Next, a case where the pressure on the pressure chamber 39 side cannot be increased above a predetermined pressure due to damage to the piping connected to the control port 18, failure of the electromagnetic pump 26, etc. will be described.

When the brake pedal 5 is not depressed and the brake pedal is not activated, the pressure chamber 39. Suppose that the pressure in the pressure accumulation chamber 78 drops below a predetermined pressure and the force with which the control piston 36 biases the cut valve body 42 from the pressure chamber 36 side becomes smaller than the spring force of the valve spring 40, 42. The cut valve body 32 presses the control piston 36 and moves toward the valve seat 37. Then, the valve body 31 is seated on the valve seat 37, and further, the valve ball 35 is moved by pressing the annular portion 43 of the control piston 36 by the spring force of the second valve spring 42, and is seated on the valve seat 32b. Communication between the port 16 and the first output hole 17 is cut off.

However, in this case, the stepped piston 64 provided between the input port 16 and the second output port 19 is
The biasing force transmitted from the control piston 36 via the cut valve body 32 that contacts the end surface of the tube sheet 4b, that is, the force that presses the tube sheet 61 side, is no longer received. Since the brake is not activated, the large diameter part 64b end face and the small diameter part 64a end face of the stepped piston 64 are connected to the master cylinder 4.
．． Since it is not receiving the hydraulic pressure of the wheel cylinders 12, 13, the stepped piston 64 is eventually pressed by the spring force of the spring 68 acting on the end face of the small diameter portion 64a, and is moved toward the cut valve main body 32. According to this movement, the small diameter portion 6
As the opening periphery of the through hole 65 on the side 4a moves away from the conical surface 62 of the tube sheet 61, the portion of the large diameter portion 64a where the seal ring 67 is attached comes out from the inside of the large diameter hole 63b to the tapered portion 63c. In this way, the input port 16 and the second output port 19 side are connected to the through hole 651 of the stepped piston 64, the gap between the stepped piston 64 and the tube sheet 61, and the small diameter hole portion 6.
3a and through a passage 69.

Therefore, even if the input port 16 and the first output port 17 are cut off, the brake pedal 5 is in order to operate the brake.
is depressed, the hydraulic pressure generated in the master cylinder 4 is transferred to the input port 16. Second output port 19. It is supplied through the line 14 to the wheel cylinder 12.13, which brakes the rear wheel 10.11.

When hydraulic pressure is supplied from the master cylinder 4 to the wheel cylinders 12.13, the small diameter section 64a and large diameter section 64b end surfaces of the stepped piston 64 each receive the hydraulic pressure, but the large diameter section 64b receives the hydraulic pressure. The part where the seal ring 67 is attached is exposed to the tapered part 63c, so that the small diameter part 64
Hydraulic pressure also acts on the stepped portion connecting a and the large diameter portion 64b,
The stepped piston 64 will experience equal hydraulic pressure on each of its opposing pressure receiving surfaces of substantially equal area. Therefore,
After repairing malfunctions such as pressure leaks in 39 pressure chambers, pressure chamber 3
9 until a predetermined pressure is supplied to the large diameter portion 64b of the stepped piston 64 and the biasing force from the control piston 3G acts on the end face of the large diameter portion 64b of the stepped piston 64 via the cut valve body 32. Regardless, the stepped piston 64 does not move toward the tube seat 1-61, and the input port 16 and the second output port 1-61
Communication with 9 is maintained.

As is clear from the above explanation, in this example,
The accumulator 75 is connected to the pressure chamber 39 of the pressure regulator 8.
At the same time, the hydraulic pressure from the master cylinder 4 is transferred between the pressure chamber 39 and the accumulator 75 by a large diameter piston 86.
By providing an accumulator control valve device 82 that closes in response to the pressure, when hydraulic pressure is generated in the master cylinder 4 and the brake is operating, the pressure chamber 39 of the pressure regulator 8 is
is cut off from the pressure accumulation chamber 78 of the accumulator 75, and the wheel cylinder 12 is lowered by anti-skid control.
．． When increasing the liquid pressure on the 13 side again, the control piston 36 is moved toward the volume chamber 41 at a speed corresponding to the amount of liquid discharged from the electromagnetic pump 26. Then, when the hydraulic pressure in the master cylinder 4 decreases and the brake operation is released, the pressure chamber 39 and the pressure accumulation chamber 78 of the accumulator 75 are communicated with each other, so that the control piston 36 moves to the valve body 31. Even in the position where the valve ball 35 is seated on the valve seat 37.32b 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 pressure from the accumulator '15. Upon receiving the liquid, the valve body 31 is rapidly returned in a direction that reduces the volume of the volume chamber 41. Immediately move the valve ball 35 to each valve seat 37.
．． Take it off the '32b.

Therefore, the hydraulic pressure upper limit speed during anti-skid control can be stabilized, and in addition, in immediate response to a decrease in the hydraulic pressure of the master cylinder 4, the master cylinder 4 side and the wheel cylinder 1
Since the 2.13 side is in communication, even if a brake operation is performed in which the brake pedal 5 is stopped being depressed and then immediately depressed again, it is possible to prevent the brake operation from being delayed in response to a re-increase in the hydraulic pressure in the master cylinder 4.

Although the illustrated embodiment has been described above, the present invention is not limited thereto, and instead of using the accumulator 75 filled with high-pressure nitrogen gas, for example, the present invention resists the biasing force of the spring of the high-speed load. An accumulator that stores pressurized liquid may also be used.

Further, in the accumulator control valve device 80, a large-diameter piston 86 receives hydraulic pressure from the master cylinder 4, and a spring 95 urges the large-diameter piston 86 to move away from the valve seat 90 so as to be movable integrally with the large-diameter piston 86. Instead of providing a small-diameter piston 92 to which a valve ball 91 is fixed, the valve provided between the accumulator 75 and the pressure chamber 39 has a structure in which the valve body is urged toward the valve seat by a spring, and the valve body is biased toward the valve seat by a spring. A piston may be provided that moves the body away from the valve seat when not receiving master cylinder hydraulic pressure and seats it on the valve seat when receiving master cylinder hydraulic pressure.

Further, in the illustrated embodiment, when the brake is not activated and no hydraulic pressure is generated in the master cylinder 4, the pressure in the pressure chamber 39 is lower than the pressure that can bias the control piston 36 to open the cut valve. When the stepped piston 64 moves, the master cylinder 4 side and the wheel cylinder 12.
However, according to the present invention, an accumulator 75 that communicates with the pressure chamber 39 when the brake is not activated is provided, so the accumulator 75 is connected in place of the stepped piston 64 described above. A piston that directly receives pressure may be provided, and the movement of this piston in accordance with the decrease in pressure in the accumulator 75 may cause direct communication between the master cylinder 4 side and the wheel cylinder 12, 13 side.

[Brief explanation of the drawing]

The figure shows a sectional view of an embodiment of the present invention together with a piping system of a hook device.

Claims (1)

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