KR100594615B1 - Hydraulic brake system - Google Patents

Abstract

The present invention relates to a hydraulic brake system, and more particularly, to a hydraulic brake system having a function of a relief valve and an anti-rolling solenoid valve including an orifice in order to prevent the vehicle from being pushed back when the vehicle starts on a slope.

To this end, the present invention provides a solenoid valve having a sleeve, an armature, a magnet core and a plunger, comprising: a plunger guide member installed between an outer surface of the plunger and an inner surface of the magnet core; A valve seat provided below the hollow part of the magnet core and provided with a first orifice opened and closed by a plunger, and a second orifice having a diameter smaller than that of the first orifice; It is made of a configuration further comprising a lip seal provided on one side of the magnet core.

Description

Hydraulic brake system {HYDRAULIC BRAKE SYSTEM}

1 is a hydraulic circuit diagram of a hydraulic brake system according to an embodiment of the present invention.

2 is a cross-sectional view of a push-open solenoid valve applied to a hydraulic brake system according to an embodiment of the present invention.

3 is a cross-sectional view of a push-open solenoid valve in a state where a power applied to the hydraulic brake system according to an embodiment of the present invention is applied.

4 is a cross-sectional view of the push-open solenoid valve when the relief function is operated in the state that the power applied to the hydraulic brake system according to an embodiment of the present invention is applied.

* Description of the symbols for the main parts of the drawings *

30: master cylinder 50: NO solenoid valve

53: Amateur 54: Magnet Core

55: plunger 55a: relief spring

56 valve seat 57 plunger guide member

58: return spring 59: lip seal

The present invention relates to a hydraulic brake system, and more particularly, to a hydraulic brake system having a non-slip solenoid valve to prevent the vehicle from being pushed back when the vehicle stopped on the ramp starts again.

Even if the power is cut off while the car is running, the car does not stop but continues to some extent by inertia. The brake device is necessary for stopping such a running vehicle.

The brake device of a vehicle applies a method of braking by converting kinetic energy into thermal energy by friction. In general, a hydraulic brake system that generates friction by using hydraulic pressure is widely used.

In the hydraulic brake system, the braking force obtained by the operation of the brake pedal is amplified by the booster, and the master cylinder that receives the amplified braking force generates the braking hydraulic pressure, and the braking hydraulic pressure is a caliper or wheel installed at each wheel along the hydraulic line. It is delivered to the cylinder and the brake pads or lining exert direct braking force.

When a vehicle using the hydraulic brake system is stopped on a slope such as a hill, when the driver steps out of the brake pedal, the oil stored in the caliper or the wheel cylinder flows out to the master cylinder and the braking hydraulic pressure disappears. . At this time, due to the delay time of moving the foot from the brake pedal to the accelerator pedal, the vehicle could not be moved immediately, but pushed backward, causing a risk of a safety accident such as a contact accident with the rear vehicle.

In order to suppress the vehicle's maximum movement, the driver relies on the separate driver's operation to prevent the vehicle from being pushed, such as stepping on the accelerator pedal, using a hand brake, or simultaneously operating the accelerator pedal and the brake pedal.

In order to solve this problem, the registered patent (No. 10-0358894) installs an intermittent valve for opening and closing the hydraulic line in the middle of the brake hydraulic line and operates the brake in a ramp to operate the intermittent valve when the vehicle is stopped. In order to shut off the hydraulic line, and the clutch transmits power to the transmission, a technique has been proposed to prevent the rolling when the vehicle is restarted after the vehicle is stopped on the ramp by releasing the operation of the control valve to open the hydraulic line.

In such a technique, when the brake pedal is pressed, hydraulic pressure is stored on the brake side, and when the brake is applied with excessive force, excess braking hydraulic pressure is maintained on the brake side. Since the brake hydraulic pressure on the brake side is maintained until the accelerator pedal is pressed for the driver's start and the pedal is returned to the master cylinder after the accelerator pedal is pressed, the time interval between the brake pedal and the brake side is released after the accelerator pedal is released. Occurs. Due to this time interval, there was a problem that a quick and smooth start was difficult.

The present invention is to solve such a problem, it is an object of the present invention to provide a hydraulic brake system having a non-slip solenoid valve in order to prevent being pushed back when the vehicle stopped on the slope.

Hydraulic brake system including a solenoid valve of the present invention for achieving this object comprises a coil for forming an electromagnetic field by the applied electric signal; A cylindrical sleeve installed through the center of the coil and having a hollow portion; An armature which is installed inside the sleeve and moves up and down by an electromagnetic field formed by the coil; A magnet core installed at one end of the armature and fixed to one inner circumferential surface of the sleeve and having a hollow part; A plunger inserted to be slidable up and down at the hollow portion of the magnet core; A relief spring provided between the plunger and the armature; A first orifice installed below the hollow part formed in the magnet core and penetrating in the longitudinal direction to the center and opening and closing by the plunger, and a second orifice penetrating in the circumferential direction from the center to have a diameter smaller than the first orifice. Valve seat; And a return spring provided between the plunger and the valve seat.

In addition, it is characterized in that it further comprises a plunger guide member which extends a predetermined length from one end of the armature and is installed between the outer surface of the plunger and the inner surface of the magnet core.

In addition, the relief spring is wrapped between the outer surface of the plunger is inserted between the plunger and the plunger guide member is characterized in that the elastic modulus is larger than the return spring.

In addition, the relief spring is characterized in that the brake side is provided with an elastic modulus enough to maintain a predetermined hydraulic pressure setting value to prevent the vehicle from sliding when the hydraulic pressure of the brake.

In addition, the solenoid valve is installed on one side of the magnet core is characterized in that it further comprises a lip seal (Lip seal) for passing the oil in the direction of the brake wheel and prevent backflow.

In addition, the plunger is provided with a tapered diameter enlargement portion in a predetermined position, the plunger guide member is provided with a locking groove of a predetermined width on the inner circumferential surface, the diameter expansion portion is caught by the locking groove when the sliding of the plunger up the sliding section It is characterized in that it is limited.

Hereinafter, one preferred embodiment according to the present invention will be described in detail with reference to the accompanying drawings.

1 is a hydraulic circuit diagram of a hydraulic brake system according to an embodiment of the present invention.

The hydraulic brake system to which the present invention is applied includes a brake pedal 10 for providing a braking force to a vehicle, a booster device 20 connected to the brake pedal 10 to amplify the braking force, and a booster device 20. The master cylinder 30 for generating the braking hydraulic pressure by receiving the amplified braking force, the hydraulic brake 40 which is provided on the front wheel and the rear wheel to transmit the braking hydraulic pressure generated in the master cylinder 30, and the hydraulic brake 40 side When the braking oil returns to the master cylinder 30, the anti-rolling solenoid valve 50 for controlling the cracking and the sensor (not shown) detects the stop state of the vehicle and turns the solenoid valve 50 for the anti-rolling on. It consists of a configuration including a transmission control unit (hereinafter referred to as 'TCU') (60) to turn on / off. The anti-rolling solenoid valve is a normally open solenoid valve that maintains an open state when no power is applied.

The anti-rolling solenoid valve 50 of one embodiment applied to the hydraulic brake system according to the present invention is a coil 51 that forms an electromagnetic field, and a cylindrical shape installed in the center of the coil 51, as shown in FIG. A sleeve 52. Moreover, the armature 53 which moves up and down by the electromagnetic field formed by the coil 51 in the sleeve 52 is provided. In addition, a magnet core 54 fixed to an inner circumferential surface of the sleeve 52 and provided with a hollow portion 54a is provided at one end of the armature 53, and a plunger (up to down) is movable on the hollow portion 54a of the magnet core 54. 55). In addition, a valve seat 56 provided with a first orifice 56b and a second orifice 56c for inflow and outflow of oil is provided below the hollow portion 54a of the magnet core 54.

Here, the armature 53 is installed in the cylindrical sleeve 52 with the lower portion open, and the vertical movement is possible by the electromagnetic field of the coil 51 in the inner space formed by the lower end of the sleeve and the outside of the magnet core is fixedly coupled. do.

In addition, the plunger 55 is inserted into the hollow portion 54a of the magnet core 54, and a relief spring 55a is seated between one end thereof and the lower end of the armature 53, and the other end of the valve seat 56 The spherical opening and closing member 55b for directly opening and closing the first orifice 56a is press-fitted.

In the mounting structure of the plunger 55, the plunger guide is preferably provided with a locking groove 57b of a predetermined width around the inner circumferential surface of the hollow portion 57a in a hollow cylindrical shape with a hollow inside at the lower side of the armature 53. The member 57 is further included, and the plunger 55 is inserted into the hollow portion 57a of the plunger guide member 57, and a seating protrusion 55c is provided at a lower end thereof so as to have an upper surface of the seating protrusion 55c of the plunger 55. A relief spring 55a is inserted between the lower surfaces of the plunger guide member 57. In addition, a tapered diameter enlargement portion 55d is provided in the middle portion of the plunger 55 in the downward direction so that the diameter enlargement portion 55d is engaged with the locking groove 57b of the plunger guide member 57 when the plunger 55 slides upward. It will be caught by the role of limiting the sliding distance.

In addition, the valve seat 56 is installed below the plunger 55 installed in the hollow portion 54a of the magnet core 54, and has a through hole 56a formed therein and a diameter smaller than the through hole 56a in the upper portion thereof. A first orifice 56b is formed to contact the opening / closing member 55b of the plunger 55 to open and close the flow path. In addition, a second orifice 56c having a smaller diameter than the first orifice penetrated in the circumferential direction is formed at the end of the first orifice 56b. When the power is not applied to the coil 51 between the step portion 56d of the outer surface of the valve seat 56 and the bottom surface of the seating protrusion 55c of the plunger 55, the plunger 55 and the armature 53 are returned to their original state. A return spring 58 is installed to restore the first orifice 56b to maintain the open state.

In addition, the elastic modulus of the relief spring (55a) is set larger than the return spring (58), preferably the relief spring (55a) is a wheel cylinder (not shown) or a caliper (not shown) when the hydraulic pressure of the brake 40 is released It is provided with a modulus of elasticity to maintain a predetermined hydraulic pressure set value so as to prevent the rolling.

Also preferably, the lip seal 59 is further provided on the outer bottom of the magnet core 54. The lip seal 59 is provided as an elastic member and functions as a check valve for passing oil to the brake 40 side without preventing the valve seat 56 from the master cylinder 30 side and preventing backflow.

The following describes the operation of an embodiment of a hydraulic brake system including a slip prevention solenoid valve with reference to the drawings.

When the driver presses the brake pedal 10 while driving on a hill, the back pressure is generated by the pressure difference in the power booster 20, and the master cylinder 30 receives the amplified force from the power booster 20 to generate braking hydraulic pressure. The hydraulic pressure is transmitted to the brakes 40 installed on the front wheels and the rear wheels through the slide preventing solenoid valve 50 to exert a braking force to stop the vehicle.

At this time, if a stop state is detected when driving on a hill by a sensor (not shown), an electrical signal is applied to the TCU 60, and when the TCU 60 operates the solenoid valve 50 to close the flow path, a brake caliper (not shown) or The return of the braking oil of the wheel cylinder (not shown) may be blocked to maintain a state in which the brake 40 is operated. That is, when the driver stops the vehicle by stepping on the brake pedal 10 on the hill road, the anti-slip solenoid valve 50 operates to block the hydraulic line returning to the master cylinder 30 so that the brake 40 is operated. Keep it. In such a state, when the brake pedal 10 is further depressed, the braking oil of the master cylinder 30 flows into the brake 40 through the lip seal 59 provided in the solenoid valve 50, so that the hydraulic pressure may be increased. Braking force can be exerted.

In addition, when the vehicle releases the operation of the brake pedal 10 to start, since the TCU 60 does not turn off the anti-slip solenoid valve 50, the hydraulic pressure on the brake 40 side may be the elasticity of the relief spring 55a. After the pressure is reduced to a predetermined hydraulic pressure set value determined by the coefficient, it gradually flows out through the second orifice 56c to suppress the rolling of the vehicle. Then, when the clutch (not shown) transmits power, a sensor (not shown) detects this and applies a signal to the TCU 60. At this time, when the TCU 60 turns off the solenoid valve 50, the flow path is opened to return the braking oil acting on the brake 40 to the master cylinder 30. That is, when the driver returns the brake pedal 10 so that the vehicle starts, the clutch (not shown) is released and power of the engine is transmitted to the transmission (not shown). At this time, since the TCU 60 releases the braking hydraulic pressure by opening the solenoid valve 50, it is possible to prevent the sliding phenomenon at the start of the vehicle.

Such a solenoid valve can be used in a variety of hydraulic circuits that are configured to prevent slipping, of course.

With reference to Figures 2, 3, 4 will be described in detail the operation of the anti-sole solenoid valve according to an embodiment of the present invention.

2 is a cross-sectional view of a push-open solenoid valve applied to a hydraulic brake system according to an embodiment of the present invention.

3 is a cross-sectional view of a push-open solenoid valve in a state where a power applied to the hydraulic brake system according to an embodiment of the present invention is applied.

4 is a cross-sectional view of the push-open solenoid valve when the relief function is operated in the state that the power applied to the hydraulic brake system according to an embodiment of the present invention is applied.

As described above, when the stop state is detected during driving on the hill, an electrical signal is applied to the TCU 60, and the TCU 60 applies electricity to the coil 51 of the anti-rolling solenoid valve 50. At this time, when a magnetic field is formed in the magnet core 54 by the applied electricity, the armature 53 in the sleeve 52 moves downward and is connected to the armature 53 to connect the hollow portion 54a of the magnet core 54. Plunger guide member 57 is also provided to move downward. When the plunger guide member 57 moves downward, the opening and closing member 55b provided at the lower end of the plunger 55 moves downward by interlocking with the plunger 55 connected by the relief spring 55a. Blocks the first orifice 56b. At this time, since the elastic modulus of the relief spring 55a is larger than the elastic modulus of the return spring 58 provided between the plunger 55 and the valve seat 56, the return spring 58 is compressed while the relief spring 55a is Uncompressed, the relative position of the plunger 55 and the plunger guide member 57 does not change.

As shown in FIG. 3, the solenoid valve 50 operates to block the braking oil on the brake 40 from returning to the master cylinder 30, thereby maintaining the braking state of the brake 40. When the brake pedal 10 is further depressed in this state, the braking oil on the side of the master cylinder 30 flows into the brake 40 side through the lip chamber 59 to increase the braking hydraulic pressure on the brake 40 side.

On the other hand, when the vehicle is to return the brake pedal 10 to start as shown in Figure 4 the operation state of the anti-slip solenoid valve 50 is maintained as it is to return from the brake 40 side to the master cylinder 30 side The hydraulic pressure of the braking oil is increased. Due to the increase in the hydraulic pressure, the relief spring 55a is compressed and the plunger 55 slides upward with respect to the plunger guide member 57 so that the opening / closing member 55b at the bottom of the plunger 55 is pushed up so that the first orifice ( 56b) is opened. As a result, the braking oil on the brake 40 side is discharged to the master cylinder 30 through the first orifice 56b and the second orifice 56c which is normally open. At this time, the diameter expanding portion 55d of the plunger is caught by the locking groove 57b of the plunger guide member 57 to prevent excessive upward sliding of the plunger 55.

At this time, the relief spring 55a has an elastic modulus capable of maintaining a predetermined hydraulic pressure setting value such that the brake 40 side can prevent the vehicle from being pushed so that the hydraulic pressure of the brake 40 side is set to the predetermined hydraulic pressure setting value. When the pressure is reduced, the elasticity of the relief spring 55a becomes relatively larger than the hydraulic pressure on the brake 40 side, so that the compression of the relief spring 55a is released. In addition, the plunger 55 slides downward to open and close the opening and closing member 55b. The first orifice 56b of the seat 56 is closed. At this time as well, the hydraulic pressure on the brake 40 side gradually flows out through the second orifice 56c.

Then, when the driver presses the accelerator pedal (not shown) and the engine power is transmitted to the transmission (not shown), the sensor (not shown) detects this and applies a signal to the TCU 60. At this time, when the TCU 60 turns off the solenoid valve 50 and the first orifice 56b is opened, the braking oil acting on the brake 40 side is returned to the master cylinder 30 side.

By operating the solenoid valve in the same way as above, the vehicle can be prevented from moving and the relief function and the second orifice are added, so that the driver releases the brake pedal and sets the brake hydraulic pressure at the brake side while the accelerator pedal is pressed. The pressure is reduced to a value and then the braking oil is gradually discharged to the master cylinder 30 by the second orifice, so that the driver can quickly and smoothly start the vehicle when the driver presses the accelerator pedal.

As described in detail above, the hydraulic brake system including the anti-solenoid valve according to the present invention is provided by the orifice and lip seal in the anti-solenoid valve and includes a relief function to be pushed back when the vehicle stopped on the slope again starts It has the effect of preventing the damage and enabling a quick and smooth start.

In addition, it is possible to simplify the flow path by integrally forming a relief function in the anti-solenoid valve for preventing rolling, it is unnecessary to manufacture a separate relief valve, there is an effect to reduce the manufacturing cost and increase the efficiency of the installation space.

Claims (7)

A coil for forming an electromagnetic field by an applied electric signal; A cylindrical sleeve installed through the center of the coil and having a hollow portion; An armature which is installed inside the sleeve and moves up and down by an electromagnetic field formed by the coil; A magnet core installed at one end of the armature and fixed to one inner circumferential surface of the sleeve and having a hollow part; A plunger inserted to be slidable up and down at the hollow portion of the magnet core; A relief spring provided between the plunger and the armature; A valve seat provided below the hollow part formed in the magnet core and provided with a first orifice opened and closed by the plunger and a second orifice having a smaller diameter than the first orifice; Hydraulic brake system including a slip prevention solenoid valve having a return spring provided between the plunger and the valve seat. The method of claim 1, The hydraulic brake system further comprises a plunger guide member which extends a predetermined length from one end of the armature and is installed between the outer surface of the plunger and the inner surface of the magnet core. The method of claim 2, The relief spring is wrapped around the outer surface of the plunger, characterized in that the hydraulic brake system is inserted between the plunger and the plunger guide member. The method according to claim 1 or 3, The relief spring is a hydraulic brake system, characterized in that the elastic modulus is larger than the return spring The method according to claim 1 or 3, The relief spring is a hydraulic brake system, characterized in that the brake side has a modulus of elasticity such that the brake side maintains a predetermined hydraulic pressure setting value to prevent the vehicle from slipping when the hydraulic pressure of the brake is released. The method according to claim 1 or 3, Hydraulic brake system is installed on one side of the magnet core further comprises a lip seal (Lip seal) for passing the oil in the direction of the brake and preventing backflow The method of claim 2, The plunger is provided with a tapered diameter enlargement portion at a predetermined position, the plunger guide member is provided with a locking groove of a predetermined width on the inner circumferential surface, the diameter expansion portion is caught in the locking groove when the sliding of the plunger is the upward sliding section Hydraulic brake system, characterized in that to be limited.

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