JPS592961A - Anti-skid device for automoble - Google Patents

Abstract

PURPOSE:To set a power liquid pressure to a back pressure value when the pressure in a master cylinder is zero and enable to increase the power liquid pressure stepwise in accordance with a rise in the pressure in the master cylinder, by providing a valve body for a regulator with a spring. CONSTITUTION:A regulating valve 22 provided with a piston 5 for receiving a brake pressure from the master cylinder 12 comprises the first valve body 49 and the second valve body 50 larger than the first valve body 49 in diameter. The spring 56 acts on the first valve body 49, and the force thereof is set to be equal to the sliding resistance of the valve body and the piston. By this, when the pressure in the master cylinder is zero, the power liquid pressure is set to be a back pressure value, and concurrently with a rise in the pressure in the master cylinder, the first valve body 49 is operated to rapidly increase the power liquid pressure. When the pressure in the master cylinder exceeds a predetermined value, the second valve body 50 pushed by the spring 55 is operated, whereby the power liquid pressure is raised with a low rising ratio.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an anti-skid device for a motor vehicle. especially,
A brake fluid pressure adjusting piston is installed in the brake fluid pressure circuit from the brake master cylinder to the brake boil cylinder, and moves forward and backward depending on the brake fluid pressure and power fluid pressure to increase and decrease the volume of the brake fluid pressure circuit. ,
A cut valve is provided in the brake fluid pressure circuit leading from the brake fluid pressure regulating piston to the brake mask cylinder, and is closed when the brake fluid pressure regulating piston reciprocates, and a cut valve is driven by the engine and is connected to the brake fluid pressure regulating piston. A hydraulic pump that generates the power hydraulic pressure to be supplied, a regulator valve that adjusts the pressure to a value according to the generated hydraulic pressure by this hydraulic pump, and the power hydraulic pressure regulated by this regulator valve to the skid state of the car. A power fluid pressure supply/discharge valve supplies and discharges the brake fluid pressure to the brake fluid pressure regulating piston in response to the power fluid pressure being regulated by the regulator valve. The present invention relates to an anti-skid device for an automobile, which includes a slip bypass valve that communicates with a brake wheel cylinder without a cut valve.

In this conventional glaze device, the regulator valve is configured to regulate the power hydraulic pressure at a constant ratio to the brake mask cylinder hydraulic pressure. In order to prevent the bypass valve from erroneously operating, the power hydraulic pressure is regulated to a relatively high set value even when the hydraulic pressure in the brake mask cylinder is zero. As a result, there were drawbacks such as poor engine fuel efficiency and low durability of seal members in the power hydraulic circuit.

The purpose of the present invention is to maintain the power hydraulic pressure at the back pressure value when the brake mask cylinder hydraulic pressure is zero, and to maintain the power hydraulic pressure at the back pressure value when the hydraulic pressure of the brake mask cylinder increases, by controlling the regulation characteristics of the regulator valve. The first mask cylinder has low hydraulic pressure.
While rising to the set value, the power hydraulic pressure is rapidly increased at the first setting ratio to the first crotch constant pressure that does not cause malfunction of the bypass valve.
By further increasing the hydraulic pressure in the brake mask cylinder, the power hydraulic pressure is increased at a second setting ratio that is smaller than the first setting ratio, thereby reducing the fuel consumption of the engine and the sealing member in the power hydraulic circuit. The aim is to improve durability than conventional equipment.

In order to achieve this object, in the present invention, a first valve body and an annular second valve body are disposed coaxially with each other in the body of a regulator valve, and either one of the opposing parts of these two valve bodies is disposed coaxially with the other. The formed small-diameter annular throttle part and the flat surface formed on the other side form a first variable throttle that closes when the second valve body is displaced toward the first valve body. A second variable throttle that is parallel to the first variable throttle and is opened by displacement of the second valve body toward the first valve body, with a large-diameter annular throttle formed on one side and a flat surface formed on the other side. to form the first
The valve body is urged toward the second valve body side by the hydraulic pressure of the brake mask cylinder, and the displacement of the second valve body toward the first valve body side is prevented by the power hydraulic pressure until the power hydraulic pressure reaches a set value. Another method that includes a spring and urges the first valve element toward the second valve element with a force equivalent to the sum of the urging force applied to the first valve element by the lowest power hydraulic pressure and the sliding resistance related to the first valve element. Install a spring.

With the above configuration, when the hydraulic pressure in the brake mask cylinder is zero, the throttling effect of the first variable throttle disappears, so the power hydraulic pressure is the back pressure value. Since a large proportion of the time is spent when the hydraulic pressure is zero, the fuel efficiency of the engine is significantly improved compared to conventional devices, and the durability of the sealing member in the power hydraulic circuit is improved. When the hydraulic pressure of the brake master cylinder is increased, the power is increased by the throttling action of the first variable throttle caused by the displacement of the first valve body until the hydraulic pressure of the brake mask cylinder reaches its first set pressure. The hydraulic pressure rises rapidly to the first set pressure at the [1st] set ratio, and then the hydraulic pressure in the brake mask cylinder further increases, causing the second valve body to displace integrally with the first valve body, and to open the second variable throttle. Due to the throttling action, the power hydraulic pressure increases at a second setting ratio that is smaller than the first setting ratio. This prevents malfunction of the bypass valve due to a delay in the increase in power hydraulic pressure relative to the increase in hydraulic pressure in the brake mask cylinder.

Furthermore, with the above-mentioned configuration, misalignment between the first valve body and the second valve body does not affect the accuracy of the first variable throttle and the second variable throttle, so there is little variation in pressure regulating characteristics. Both variable throttles are switched by the displacement of the valve body, and brake fluid is not consumed when switching between both variable throttles, so the feeling of brake pedal operation is not reduced when switching between both variable throttles, and the first valve during braking is Since there is no disabled stroker in the body, the power hydraulic pressure rises quickly and the brake fluid consumption of the monitor regulator valve is low.

Hereinafter, one embodiment of the present invention will be described based on the drawings.

In FIG. 1, 10 is a brake pedal, 11 is a brake booster, and 12 is a tandem brake mask cylinder. When the brake pedal 10 is depressed, the tandem brake mask cylinder 12 generates a hydraulic pressure according to the brake pedal depression force, and this fluid The pressure is applied to the front wheel 1 by the brake fluid pressure circuit 18.
While being supplied to the brake wheel cylinder 15 of 4.
The brake fluid pressure circuit 16 supplies the brake fluid to the brake wheel cylinder 18 of the rear wheel 17 .

The anti-skid device that prevents the rear wheels 17 from locking during braking and thus from falling into a skid state is a hydraulic pump 20 driven by the engine.
This hydraulic pump 20 has a regulator valve 22 interposed in the middle of a circuit that supplies discharged fluid to the power steering cylinder 21, and an actuator 23 interposed in the middle of the brake hydraulic pressure circuit 16. ing.

The actuator 23 includes a brake fluid pressure adjusting piston 25. Cut valve 26. A power hydraulic supply/discharge valve 27 and a bypass valve 28 are housed therein. Bow) 24a, 24b, 24c, 24d
and 24e are tandem brake mask cylinders 12. Brake wheel cylinder 18. regulator + 22,
+I Server 2 g and regulator valve 22 are connected to each other.

The brake fluid pressure adjusting piston 25 consists of a small diameter piston 25a and a large diameter piston 25b, and has a brake fluid pressure chamber 30. A power hydraulic chamber 81 and an atmospheric chamber 32 are formed. Brake fluid pressure chamber 8° is hole 38 - chamber 84 - passage 35
The passageway 86 communicates with the boat 24a through the hole 3.
7 - communicates with boat 24b via chamber 88;

c) The valve 26 is provided in the chamber 84, is biased by a spring to close the hole 38, and has a rond portion that protrudes into the brake fluid pressure chamber 8o through the hole 88 and comes into contact with the small diameter piston 25m. ing. As a result, when the small diameter piston 25a is positioned as shown in the figure, the cut valve 26
opens the hole 88 and connects the brake fluid pressure chamber 80 and the boat 24a.
The small diameter piston 25a communicates with the cut valve 26 through the hole 33, but the small diameter piston 25a slides leftward from the position shown in the figure.
closes the hole 33, and communication between the brake fluid pressure chamber 30 and the boat 248 via the hole 33 is cut off.

The power hydraulic supply/discharge valve 27 includes a first valve plunger 27B biased downward by a spring, a 24th plunger 27b biased downward by a spring, and a first valve plunger 27B biased downward by a spring.
Valve plunger 2? The first solenoid 27e has a first solenoid 27e for moving the second valve plunger 27b upward against the spring, and a first solenoid 27e for moving the second valve plunger 27b upward against the spring. ing. When the first valve plunger 27C is de-energized, the first valve plunger 27
a communicates the chamber 89 with the upper power hydraulic pressure introduction hole 40 and blocks it from the lower power hydraulic discharge hole 41, and when the first solenoid 27e is energized, the first valve plunger 27B communicates with the chamber 39. 7.Cut off from power hydraulic pressure introduction hole 4.0 and communicate with power hydraulic pressure discharge hole Φl. When the second solenoid 27d is not energized, the second valve plunger 2
7b communicates the chamber 42 that communicates with the chamber 39 with the power hydraulic pressure chamber 81 only through the eleventh frame 43, and when the second solenoid 27d is energized, the chamber 42 communicates with the power hydraulic pressure chamber 81 through the hole 44. It communicates with room 81.

The computer 45 that controls the energization of the first solenoid 27c and the second solenoid 27d is operated by the sensor +J-45a.
detects the rotation of the output shaft of the automobile transmission and detects the rotation status of the rear wheel 17. If it is necessary to reduce the brake fluid pressure, both solenoids 27e and 27d are energized, and then the brake fluid pressure is reduced. When pressure recovery is required, at least the first solenoid 27c is de-energized and the rear @17
The second solenoid 27d is selectively de-energized depending on the rotation status of the second solenoid 27d.

The bypass valve 28 is biased leftward by a spring in the chamber 88, and the swinging valve body 28a and the small diameter screw diameter piston 28
A power hydraulic pressure chamber 46 is formed in the body 24 and communicated with the hydraulic pressure chamber 24.0 (c is baud), and is biased to the right by the power hydraulic pressure. When the power hydraulic pressure is normal, the valve body 28a, the small diameter piston 28b, and the large diameter piston 28e occupy the positions shown in the figure, and the valve body 28a is connected to the right hole 1.7 communicating with the bow) 24n.
is closed, and the left hole 87 is opened. Further, when the power hydraulic pressure becomes zero, the valve body 28g, the small diameter piston 28b, and the large diameter piston 28e are moved leftward from the position shown in the figure by the spring that biases the valve body 28a, and the valve body 28B is moved from the position in the hole 47. The boat 24B is opened and the hole 37 is closed, thereby allowing the boat 24B to pass through the hole 4I7-chamber 88 to the boat 2.
Connects with 4b.

The body 48 of the regulator valve 22 has an inlet 488 into which the discharged liquid of the hydraulic pump 20 flows, an outlet 48b which supplies the discharged liquid that has flowed into the inlet 48a to the steering wheel 21, and a bow of the actuator 28. The body 48 has a power hydraulic pressure output port 480 that communicates with the boat 24e and a valve 488 that receives the pressure of the brake mask cylinder 12 from the boat 24Ie of the actuator 23.The body 48 has a first valve body 49 and a central hole. An annular second valve body 5 having a diameter of 50a.
0 and the piston 51 are arranged coaxially. The right side of the second valve body 50 is provided with a small-diameter annular throttle portion 50b that forms a first variable throttle with the flat surface 498 at the left end of the first valve body 49, and the left side of the body 48 is provided with a small diameter annular constriction portion 50b. flat surface 486
A large-diameter annular constriction portion 50e that forms a second variable aperture is provided. The first variable aperture and the second variable aperture are in a parallel relationship with each other. Further, the right end portion of the first valve body is in contact with the left end of the shite piston 51 that protrudes into the air chamber 52. The piston 51 has a chamber 58 in the body 48 at its right end that communicates with the opening 48d, and the first valve body 49 is biased to the left by the hydraulic pressure of the brake mask cylinder supplied to the chamber 58. . Spring 5 in chamber 54 communicating with outlet 48
5 urges the second valve body 50 to the left, and the power hydraulic pressure
The rightward displacement of the whistle 2 valve body 50 is prevented until the set pressure is reached. A spring 56 is provided within the air chamber 5z to bias the piston 51 to the left. The force of this spring 56 is the urging force applied to the first valve body 49 by the lowest power hydraulic pressure and the sliding resistance related to the first valve body 49 (sliding resistance of the first valve body 49 and sliding resistance of the piston 51). is set equal to the sum of

The pressure regulating characteristics of the regulator valve 22 are as shown by the solid line in FIG. When the brake master cylinder hydraulic pressure supplied to the chamber 58 is zero, the urging force that urges the tenth body 49 to the left is zero, and the throttling effect of the first variable throttle disappears. Therefore, the liquid supplied from the hydraulic pump 20 to the inlet 4.8a passes through the central hole 50a of the second valve body 50 - the first variable throttle chamber 54 without resistance, and then passes through the outlet 4.8.
The power hydraulic pressure flows from the outlet 48b to the power steering 21, and becomes a back pressure caused by the resistance of the circuit from the outlet 48b to the reservoir 29. Here, to poXAl++bird-F
t (At is the area of the right part of the first valve body 49,
The sliding resistance of the valve body 49, R2 is the sliding resistance of the piston 51,
Fl is the initial load of the spring). When the brake mask cylinder hydraulic pressure is increased, while the brake mask cylinder hydraulic pressure increases to Pl,
Due to the throttling action of the first variable throttle caused by the displacement of the first valve body 49, the power hydraulic pressure rapidly rises to the peak. Here, the ratio of the power hydraulic pressure to the mask cylinder hydraulic pressure is Ai/As (A is the cross-sectional area of the piston 51 + Aa is the effective diameter inner area of the first variable throttle), and P + X (A4 A3)
-F2 (A4 is the effective diameter inner area of the second variable diaphragm, F2 is the initial load of the spring 55).

While the brake mask cylinder hydraulic pressure rises from Pl to F2, the force of the power hydraulic pressure urging the second valve body 50 in the right direction overcomes the urging force of the spring 55, so that the second valve body 50 moves to the right. 1 valve body 49 side, the first variable throttle closes, the second variable throttle opens, and the first valve body 4
9 and the second valve body 50 are integrally displaced, and the power hydraulic pressure is increased by the throttling action of the second variable throttle. Here, the ratio of power hydraulic pressure to brake master cylinder and hydraulic pressure is AI
/A4. In FIG. 2, the chest is the relief pressure of the hydraulic pump 20.

The relationship between the power hydraulic pressure and the brake mask cylinder hydraulic pressure for bypass operation (opening the hole 47 and closing the hole 87) is shown.

The operation in the above configuration is substantially the same as that in the conventional V position except for the value of the power hydraulic pressure regulated by the regulator valve 22, and will be easily understood by those skilled in the art from the above explanation. Since this seems to be the case, I will omit it.

In one embodiment, nothing is interposed in the brake hydraulic pressure circuit from the actuator 28 to the brake mask cylinder, but as is well known, a blobbing valve is interposed in this brake hydraulic pressure circuit. In this case, the output/hydraulic pressure of the blotting valve is the brake mask cylinder hydraulic pressure supplied to the regulator valve.

Further, in one embodiment, the cut valve 26 is opened and closed mechanically in conjunction with the brake fluid pressure regulating piston, but as is known in the art, an actuating means such as a solenoid exclusively for the cut valve is provided, and this actuating means The cut valve may be closed while the brake fluid pressure adjusting piston is in operation.

[Brief explanation of the drawing]

FIG. 1 is a diagram showing an example of the present invention, and FIG. 2 is a diagram showing the pressure regulating characteristics of a regulator valve. 12... Brake mask cylinder, 16... Brake fluid pressure circuit, 18... Brake wheel cylinder, 20
...Hydraulic pump, 22...Regulator valve, 25@
...Brake fluid pressure adjustment piston, 26...Cut valve,
27...Power hydraulic supply/drain valve, 28...Bypass valve,
48...Body, 48e...Flat surface, 49-m5 first valve body 4, 911 m/11 flat surface, 5 Q s *
*Second valve body 950b-50c... annular throttle part, 55
...Spring, 56...Spring patent applicant Reio Nakai, representative of Aisin Seiki Co., Ltd.

Claims (1)

[Claims] It is provided in the brake fluid pressure circuit from the brake mask cylinder to the brake wheel cylinder, and moves forward and backward by brake fluid pressure and power fluid pressure to increase and decrease the volume of the brake fluid pressure circuit. A brake fluid pressure adjustment piston, a cut valve that is provided in the brake fluid pressure circuit from the brake fluid pressure adjustment piston to the brake master cylinder and that is closed when the brake fluid pressure adjustment piston reciprocates; A hydraulic pump that generates power hydraulic pressure to be supplied to the brake hydraulic Ni piston; a regulator valve that regulates the power hydraulic pressure generated by the hydraulic pump to a value that corresponds to the hydraulic pressure of the brake mask cylinder; There is a power fluid pressure supply/discharge valve that supplies and discharges the power fluid pressure regulated by the regulator valve to the brake fluid pressure adjustment piston according to the skid condition of the vehicle, and the power fluid pressure regulated by the overnight valve to the regulator. An anti-skid device for an automobile comprising a bypass valve that communicates the brake mask cylinder and the brake wheel cylinder without a cut valve in response to the hydraulic pressure of the brake mask cylinder being lower than a set value, the regulator valve. has a first valve body and an annular second valve body located coaxially with each other in its body, and a small diameter annular constriction portion formed on either one of the opposing parts of the two valve bodies, and the like. A first variable throttle which is closed by displacement of the second valve body toward the first valve body is formed by the flat surface 1 formed on the side;
A large-diameter annular constriction portion formed on either one of the second valve body and the body and a flat surface formed on the other side are in parallel with the first variable constriction and toward the first valve body side of the second valve body. A second variable throttle is formed which is opened by the displacement of , and the first ff body is urged toward the second valve body by the hydraulic pressure of the brake mask cylinder, and the power fluid pressure pushes the second valve body toward the tenth body side. ) A spring is provided to prevent displacement until the power hydraulic pressure reaches a set pressure, and the force is equal to the sum of the urging force applied to the first valve body by the lowest power hydraulic pressure and the sliding resistance related to the first valve body. An anti-skid device for an automobile is provided with a valve spring that urges a first valve body toward a second valve body with a force of .