JP2572583Y2 - Hydraulic pressure control device for anti-brake lock - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic pressure control device for an anti-brake lock, and more particularly, to a wheel cylinder using an electromagnetic control valve incorporated in a main fluid passage of an anti-brake lock system (ABS) for a vehicle. The present invention relates to a hydraulic pressure control device for controlling the hydraulic pressure of brake working fluid supplied to a hydraulic control device.

[0002]

2. Description of the Related Art Conventional hydraulic control devices for ABS include:
For example, Japanese Utility Model Application Laid-Open No. 61-24353 and Japanese Utility Model Application Laid-Open No.
The one described in US Pat. No. 15,885 is known.

In such a fluid pressure control device, a control solenoid valve is provided for increasing or decreasing or maintaining the fluid pressure of the brake working fluid supplied to the wheel cylinder.
FIG. 3 shows an example of the configuration according to the conventional example. Where 1
Is an upper body connected to the body 1, 2 is an electromagnetic coil held by the bodies 1 and 2,
Is a core, and 5 is a cylindrical member for interrupting the magnetic path.
Are integrated into the bodies 1 and 2 together with the core 4.

The core 4 is formed in a substantially cylindrical shape, and a valve rod portion 7A of a plunger 7 assembled integrally with an armature 6 in an inner cylindrical portion of the core 4 maintains a gap 8 serving as a liquid passage therebetween. It is loosely fitted. Reference numeral 9 denotes a spring which is provided in the gap 8 and maintains the valve body 7B of the plunger 7 through the armature 6 in an open state. Reference numeral 10 denotes a valve seat having a valve seat 10A. By keeping the valve body 7B formed at the distal end in a state of being pulled up from the valve seat 10A, the liquid passage 12 on the side of the armature 6 through the orifice 11 provided on the valve seat 10 side. And the circulation of the liquid is performed. When the electromagnetic coil 3 is "ON", that is, in the excited state, the armature 6 is attracted to the core 4 and the valve body 7B contacts the valve seat 10A to close the orifice 11 as shown in FIG. The gap C is maintained between the lower end (suction surface) 6A of the armature 6 and the upper end (suction surface) 4A of the core 4.

[0005] By the way, in the case where a conventional hydraulic valve for controlling hydraulic pressure according to a form earlier than the electromagnetic valve shown in FIG. 3 is used as a pressure-increasing-side electromagnetic valve of a general circulation type hydraulic control circuit used for vehicles, Hydraulic pressure holding state by "ON", "OFF"
If the pressure increase due to the hydraulic fluid flow is repeated continuously, surging occurs due to rapid fluctuations in the hydraulic pressure in the wheel cylinders due to high responsiveness. As a result, there is a problem that the vibration of the vehicle body is induced, which causes discomfort to the driver.

In order to prevent this, an electromagnetic valve as shown in FIG. 3 has been developed. That is, according to the present embodiment, the orifice 11 is provided on the valve seat 10 side so that the valve is opened. In other words, even when the hydraulic pressure is turned off, the brake hydraulic fluid is not suddenly supplied to the wheel cylinder, and the suppression of the surge pressure is expected.

[0007]

However, in the above-mentioned prior art, the orifice 11 is also provided on the main fluid passage because the solenoid valve is disposed in the main fluid passage of the brake working fluid. In addition, there is a problem that the responsiveness at the time of normal brake operation is impaired as a result of the liquid passage being constantly throttled when the valve is opened.

An object of the present invention is to focus on such a conventional problem, and to solve the problem, without impairing the responsiveness at the time of normal brake operation, and from increasing the pressure to holding and increasing the hydraulic pressure to the wheel cylinder. Anti-surge that can suppress the surge pressure that occurs even when
An object of the present invention is to provide a brake lock hydraulic pressure control device.

[0009]

In order to achieve this object, the present invention provides an electromagnetic control valve having an armature that is attracted to a core by excitation and disposed in a hydraulic fluid passage for braking to a wheel cylinder. In the anti-brake lock hydraulic pressure control device, the pressure is increased to the wheel cylinder by opening the valve due to demagnetization, and the hydraulic pressure is maintained to the wheel cylinder by closing the valve by excitation. The armature is brought into contact with the core by closing the valve by excitation, and the response operation of the valve opening at the time of the next demagnetization is delayed due to residual magnetism due to the contact. Is what you do.

[0010]

According to the present invention, the armature is kept in contact with the core when the valve is closed by excitation, whereby the hydraulic pressure of the brake hydraulic fluid supplied to the wheel cylinder is maintained. When the valve is opened due to demagnetization, the response to the opening of the valve is delayed due to the residual magnetism caused by the above-mentioned contact. Body vibration can be prevented.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings.

FIGS. 1 and 2 show an embodiment of the present invention. Hereinafter, members having the same functions as those shown in FIG. 3 are denoted by the same reference numerals, and detailed description thereof will be omitted.
FIG. 1 shows the "off" state of the control solenoid valve according to the present invention, that is, the state of increasing or decreasing the pressure by opening the valve. FIG. 2 shows the "on" state of the solenoid valve, that is, the state of closing the valve. It shows a wheel cylinder hydraulic pressure holding state. As is apparent from these figures, in the case of the present invention, the valve seat 10 is not provided with the orifice 11 as shown in FIG.

When the electromagnetic coil 3 is energized to close the valve as shown in FIG. 2 from the valve opening state as shown in FIG. 1, the lower end suction surface 6A of the armature 6 contacts the upper end suction surface 4A of the core 4. It is configured to touch. Therefore, the armature 6 and the core 4 are attracted by the armature lower end 6A and the core upper end 4A which serve as a suction surface during excitation.

Therefore, when the valve is closed as shown in FIG. 2, that is, when the electromagnetic coil 4 is turned off from the excited state to the valve open state shown in FIG.
A is applied to the armature 6 until the remnant magnetism disappears and the resilience of the spring 9 overcomes this.
Does not work with the plunger 7, and the valve opening can be delayed accordingly.

That is, in the conventional solenoid valve shown in FIG. 3, the suction surface 6A of the armature 6 and the suction surface 4
With the gap C provided between the armature A and the armature 6, the armature 6 is quickly separated from the core 4 only by the elastic force of the spring 9 without the influence of residual magnetism when the valve is opened by demagnetization. At times, the hydraulic fluid for braking for increasing the pressure was controlled to be restricted by the orifice 11. On the other hand, in the case of the present invention, as described above, the valve opening timing is delayed by the action of the residual magnetism between the armature 6 and the core 4, and the time lag reduces the surge pressure and suppresses surging. Things.

Hereinafter, a comparison of such phenomena occurring during the operation of the ABS will be described in detail with reference to FIG. Here,
(A), (B) and (C) show the elapsed time T
This indicates the surging of the hydraulic pressure generated in the master cylinder, the input signal, and the fluctuation of the hydraulic pressure in the wheel cylinder, that is, the fluctuation state of the surge pressure based on the master cylinder. Represents the fluctuation of the surge pressure according to the present embodiment.

Now, when the input signal to the solenoid valve is turned on,
If "off" is performed as shown in (B), whereby the brake fluid pressure is maintained, increased, and maintained continuously in a short time, then in the case of the conventional example, (C) t ₁
Surge pressure P ₂ as indicated by a solid line with a time lag, as shown as occurs in the wheel cylinder. Then, at the time of the next “off” to “on”, that is,
At the time when the pressure is switched from the pressure increase to the hold, the time lag indicated by t ₂ causes the surge pressure in the wheel cylinder to fall and the hydraulic pressure fluctuation due to surging to occur within the range indicated by P ₂ .
Incidentally, P ₁ denotes the normal pressure increase amount during the above operations in the wheel cylinders (slow pressure increase amount).

On the other hand, in the case of this embodiment, the timing of opening the valve is delayed by the action of the residual magnetism.
When the signal is switched from "on" to "off", a time lag as indicated by t ₁ 'is maintained. Since time lag t ₂ does not change at the time of the "on" from: "off", the wheel cylinder is performed pressure increase as shown by a broken line (C), the the slow pressure increase amount P ₁ ' And surge pressure P ₂ ′
Can be both reduced.

Since the surge pressure in the wheel cylinder and its surging phenomenon are also transmitted to the master cylinder through the main liquid passage, a surging of the hydraulic pressure as shown in FIG. This causes pipe vibration, which in turn causes vehicle body vibration, and gives the driver discomfort. However, according to the present embodiment, the fluctuation width as shown by the broken line can be suppressed against the waveform fluctuation as shown by the solid line in the conventional example, so that the influence of the vehicle body vibration can be suppressed to a lower level. An effect of improving stability and reliability during steering and improving reliability can be obtained.

[0020]

As described above, according to the present invention, there is provided an armature which is attracted to the core by excitation,
An electromagnetic control valve provided in a brake hydraulic fluid passage to the wheel cylinder is provided, and when the valve is opened by demagnetization, the pressure on the wheel cylinder is increased. When the valve is closed by the excitation, the hydraulic pressure is held on the wheel cylinder. In the anti-brake lock fluid pressure control device, the armature is brought into contact with the core by closing the valve by the excitation, so that the response operation of the valve opening at the time of the next demagnetization is performed. The delay is caused by the residual magnetism due to contact, so that the residual lag between the core and the armature during the contact delays the time lag from the valve-closed state to the valve-opened state and slowly increases the wheel cylinder. The surge pressure can be kept low together with the pressure, and the main fluid path is not restricted by the orifice as in the conventional example. Kicking without response such that impaired, it is possible to suppress noise such as discomfort to the driver, vibration. In addition, by suppressing the gradual pressure increase amount, the behavior of shifting from the pressure increase in the wheel cylinder at the time of maintaining the hydraulic pressure becomes smooth, and the controllability by the ABS can be expected to be improved.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a configuration of an electromagnetic control valve according to the present invention in an open state by demagnetization.

FIG. 2 is a sectional view showing the configuration of the electromagnetic control valve according to the present invention in a closed state by excitation.

FIG. 3 is a cross-sectional view showing an example of a configuration of a conventional electromagnetic control valve in a closed state by excitation.

FIG. 4 is a characteristic curve diagram relating to a fluctuation of a brake operating fluid pressure generated during the ABS control.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Body 2 Upper body 3 Electromagnetic coil 4 Core 4A, 6A Suction surface 6 Amateur 7 Plunger 7A Valve stem 7B Valve body 9 Spring 10 Valve seat

Claims (1)

(57) [Scope of request for utility model registration] 1. An electromagnetic control valve having an armature that is attracted to a core by excitation and disposed in a brake hydraulic fluid passage to a wheel cylinder, wherein the valve is opened by demagnetization to increase the pressure on the wheel cylinder. A hydraulic pressure control device for an anti-brake lock, wherein the valve closing by the excitation keeps the hydraulic pressure in the wheel cylinder, wherein the armature is brought into contact with the core by the valve closing by the excitation. The anti-brake lock hydraulic pressure control device is characterized in that the response operation of the valve opening at the time of the next demagnetization is delayed due to the residual magnetism due to the contact.