KR102273572B1 - Integrated type solenoid valve and brake system using the same - Google Patents

Abstract

Disclosed are an integrated solenoid valve and a brake system using the same. The integrated solenoid valve according to this embodiment is an integrated solenoid valve for controlling the flow rate of a flow path connecting the first port and the second port, it is disposed inside the sleeve, ascends and descends along the axial direction, and opens and closes the orifice formed on the lower side amateur; an elastic member providing an elastic force to the armature in a direction for closing the orifice; a magnet core providing a driving force to the armature in a direction opposite to the elastic member; a sheet having a first flow path, a second flow path, and an orifice disposed therein; a filter member provided on the outer circumferential surface of the sheet to prevent the inflow of foreign substances, the filter member having a gap passage recessed along the axial direction on the inner circumferential surface in contact with the sheet; It includes; a lip seal provided between the gap flow path and the second flow path and having an inclined protrusion formed to be inclined toward the second port, and a bidirectional flow path that is opened and closed by the lift of the armature and passes through the first flow path and the orifice, and a gap; It may be provided by providing a one-way flow path that sequentially passes through the flow path, the inclined protrusion, and the second flow path.

Description

Integrated solenoid valve and brake system using same {INTEGRATED TYPE SOLENOID VALVE AND BRAKE SYSTEM USING THE SAME}

The present invention relates to an electronic brake system that generates a braking force using an electric signal corresponding to a displacement of an integrated solenoid valve and a brake pedal.

A vehicle is necessarily equipped with a hydraulic brake system for braking. Recently, various types of systems for obtaining a more powerful and stable braking force have been proposed. An example of a hydraulic brake system is an anti-lock brake system (ABS) that prevents wheel slipping during braking, and a brake traction control system (BTCS) that prevents slipping of the driving wheels when the vehicle starts or accelerates rapidly. Brake Traction Control System), and an Electronic Stability System (ESC) that maintains the driving state of the vehicle stably by controlling the brake fluid pressure by combining the anti-lock brake system and traction control.

On the other hand, in the case of a vehicle attitude control system, a certain level of flow rate is required to operate and release the brake, and a plurality of electronically controlled simulator valves are installed in the modulator block to implement such a system.

The simulator valve used in the above-described brake system is generally installed by being inserted into the bore of the modulator block and has a hollow valve housing having an inlet and an outlet communicating with the modulator block, and a hollow inserted from the upper part of the valve housing and joined by welding. It has a cylindrical sleeve, a valve seat press-fitted and fixed inside the valve housing and having an orifice, a magnetic core coupled to the sleeve opposite the valve housing by welding, and an armature installed in the sleeve to move forward and backward.

Republic of Korea Patent Publication No. 10-1276072

An object of the present invention is to provide an integrated solenoid valve and an electronic brake system that is easily manufactured and operated efficiently at low cost using the same.

According to an aspect of the present invention, in the integrated solenoid valve for controlling the flow rate of the flow path connecting the first port and the second port, the armature is disposed inside the sleeve, ascends and descends along the axial direction, and opens and closes the orifice formed at the lower side. ; an elastic member for providing an elastic force to the armature in a direction for closing the orifice; a magnet core providing a driving force to the armature in a direction opposite to the elastic member; a sheet having a first flow path, a second flow path, and the orifice disposed therein; a filter member provided on the outer circumferential surface of the sheet to prevent inflow of foreign substances, the filter member having a crevice flow path recessed along the axial direction on the inner circumferential surface in contact with the sheet; and a lip seal provided between the gap passage and the second passage and having an inclined protrusion formed to be inclined toward the second port, which is opened and closed by lifting and lowering of the armature and passes through the first passage and the orifice. and a one-way flow path sequentially passing through the gap flow path, the inclined protrusion, and the second flow path.

The gap flow path may be provided on the filter member on the side of the second flow path.

The first flow path may be formed on the sheet on the armature side, the second flow path may be formed on the seat side on the second port side, and the orifice may be formed through an inner side of the sheet in an axial direction.

The armature may include a ball provided on a surface in contact with the orifice.

A plurality of the gap flow passages may be provided on an inner circumferential surface of the filter member at predetermined intervals in a radial direction.

The lip seal may be provided between the outer circumferential surface of the seat and the modulator block, and the inclined protrusion may be formed on the inner circumferential surface to be in contact with the outer circumferential surface of the seat.

The inclined protrusion is provided to be deformable by hydraulic pressure, and is deformed in a narrowing direction when the pressure of the first port is greater than the pressure of the second port to allow the one-way flow path, and the pressure of the first port is the second port. When the pressure of the two ports is less than the pressure, it can be deformed in an open direction to block the one-way flow path.

Integrated solenoid valve according to any one embodiment; a master cylinder provided with a cylinder chamber whose volume is changed by pedal operation; a pedal simulator connected to the cylinder chamber to provide a reaction force according to a pedal effort; a hydraulic pressure supply device for providing hydraulic pressure to at least one of the first hydraulic circuit and the second hydraulic circuit; an electronic control unit operating the hydraulic pressure supply device; and a circuit balance valve provided for regulating the pressure difference between the first hydraulic circuit and the second hydraulic circuit, wherein the integrated solenoid valve is in a hydraulic flow path connecting the pressure chamber of the hydraulic pressure supply device and the circuit balance valve. can be installed.

The electromagnetic brake system according to the present invention operates efficiently using an integrated solenoid valve having a check valve function, and there is no need to install a check valve, so it can be easily manufactured at low cost.

1 is a hydraulic circuit diagram of an integrated solenoid valve and an electromagnetic brake system having the same according to a first embodiment of the present invention.
2 is a side cross-sectional view of the integrated solenoid valve according to the first embodiment of the present invention.
3 is (a) a plan view and (b) a bottom view of the orifice unit of the integrated solenoid valve according to the first embodiment of the present invention.
4 is a side cross-sectional view of an integrated solenoid valve according to a second embodiment of the present invention.
5 shows (a) an upper surface, (b) a side cross-section, and (c) a lower surface of an integrated solenoid valve seat according to a second embodiment of the present invention.
6 is (a) a side cross-sectional view and (b) a bottom view of an integrated solenoid valve filter member according to a second embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The following examples are presented in order to sufficiently convey the spirit of the present invention to those of ordinary skill in the art to which the present invention pertains. The present invention is not limited to the embodiments presented herein and may be embodied in other forms. The drawings may omit the illustration of parts irrelevant to the description in order to clarify the present invention, and may slightly exaggerate the size of the components to help understanding.

1 is a hydraulic circuit diagram showing a non-braking state of an integrated solenoid valve and a brake system including the same according to a first embodiment of the present invention. Referring to FIG. 1 , the electronic brake system 1 typically includes a master cylinder 20 generating hydraulic pressure, a reservoir 30 coupled to the upper portion of the master cylinder 20 to store oil, and a brake pedal ( 10) the input rod 12 for pressing the master cylinder 20 according to the pedal effort, the wheel cylinder 40 for braking each wheel RR, RL, FR, FL by receiving hydraulic pressure, and a brake pedal A pedal displacement sensor 11 for detecting the displacement of (10) and a pedal simulator 50 for providing a reaction force according to the pedal effort of the brake pedal 10 are provided.

The master cylinder 20 may be configured to include at least one cylinder chamber to generate hydraulic pressure. For example, the master cylinder 20 is configured to include two cylinder chambers, one cylinder chamber is provided in front of the second piston 22a and the other cylinder chamber is a first piston 21a and a second piston It is provided between the (22a), the first piston (21a) may be connected to the input rod (12). In addition, the master cylinder 20 may form first and second hydraulic ports 24a and 24b from which hydraulic pressure is discharged from the two cylinder chambers, respectively.

On the other hand, the master cylinder 20 can secure safety in case of failure by having two cylinder chambers. For example, one cylinder chamber of the two cylinder chambers may be connected to the right front wheel FR and the left rear wheel RL of the vehicle, and the other cylinder chamber may be connected to the left front wheel FL and the right rear wheel RR. . In this way, by independently configuring the two cylinder chambers, it is possible to make it possible to brake the vehicle even if one cylinder chamber fails.

Alternatively, unlike shown in the drawings, one cylinder chamber of the two cylinder chambers may be connected to the two front wheels FR and FL, and the other cylinder chamber may be connected to the two rear wheels RR and RL. In addition, one of the two cylinder chambers may be connected to the left front wheel FL and the left rear wheel RL, and the other cylinder chamber may be connected to the right rear wheel RR and the right front wheel FR. That is, the position of the wheel connected to the cylinder chamber of the master cylinder 20 may be variously configured.

A first spring 21b is provided between the first piston 21a and the second piston 22a of the master cylinder 20, and a second spring is provided between the second piston 22a and the end of the master cylinder 20. (22b) may be provided.

The first spring 21b and the second spring 22b are respectively provided in the two cylinder chambers, and as the displacement of the brake pedal 10 changes, the first piston 21a and the second piston 22a are compressed while the first spring 21b and the second spring 22b are compressed. An elastic force is stored in the first spring 21b and the second spring 22b. And when the force pushing the first piston 21a is smaller than the elastic force, the first and second pistons 21a and 22a are pushed back to their original state by using the stored elastic force of the first spring 21b and the second spring 22b. can

On the other hand, the input rod 12 for pressing the first piston 21a of the master cylinder 20 is in close contact with the first piston 21a, and when the brake pedal 10 is pressed, the master cylinder directly without a pedal invalid stroke section (20) can be pressurized.

The pedal simulator 50 may be connected to a first backup flow path 251 to be described later to provide a reaction force according to the pedal effort of the brake pedal 10 . By providing a reaction force that compensates for the pedal force provided by the driver, the driver can fine-tune the braking force as intended.

Referring to FIG. 1 , the pedal simulator 50 includes a simulation chamber 51 provided to store oil flowing out from the first hydraulic port 24a of the master cylinder 20 and a reaction force piston provided in the simulation chamber 51 ( 52 ) and a reaction force spring 53 for elastically supporting it, and a simulator valve 54 and a check valve 55 may be provided in parallel between the pedal simulator 50 and the reservoir 30 .

The reaction force spring 53 shown in the drawing is only one embodiment capable of providing an elastic force to the reaction force piston 52 , and may include various embodiments capable of storing the elastic force by shape deformation. For example, it includes various members capable of storing elastic force by being provided with a material such as rubber, or having a coil or plate shape.

On the other hand, several reservoirs 30 are shown in the drawing, and each of the reservoirs 30 uses the same reference numerals. However, these reservoirs may be provided with the same part or may be provided with different parts. For example, the reservoir 30 connected to the pedal simulator 50 may be the same as the reservoir 30 connected to the master cylinder 20 or may store oil separately from the reservoir 30 connected to the master cylinder 20 . It can be a repository in

An operation state of the pedal simulator 50 will be described. First, when the driver applies a pedal force to the brake pedal 10 , the driver is provided with a pedal feeling while the reaction force spring 53 is compressed. And when the pedal 10 is released, the reaction force spring 53 pushes the reaction force piston 52 back to its original state. In the process described above, since the inside of the simulation chamber 51 is always filled with oil, friction of the reaction force piston 52 is minimized when the pedal simulator 50 is operated, so that the durability of the pedal simulator 50 is improved, as well as from the outside. Ingress of foreign substances may be blocked.

The electronic brake system 1 according to the embodiment of the present invention is a hydraulic pressure supply device 100 that receives the driver's braking intention as an electrical signal from the pedal displacement sensor 11 that detects the displacement of the brake pedal 10 and operates mechanically. ) and first and second hydraulic circuits 201 and 202 for controlling the flow of hydraulic pressure delivered to the wheel cylinders 40 provided on the two wheels RR, RL, FR, and FL, respectively. 200 and a first cut valve 261 provided in the first backup flow path 251 connecting the first hydraulic port 24a and the first hydraulic circuit 201 to control the flow of hydraulic pressure, and the second A second cut valve 262 provided in the second backup flow path 252 connecting the hydraulic port 24b and the second hydraulic circuit 202 to control the flow of hydraulic pressure, hydraulic pressure information and pedal displacement information based on hydraulic pressure information It may include an electronic control unit (ECU, not shown) for controlling the supply device 100 and the valves.

The hydraulic pressure supply device 100 includes a hydraulic pressure supply unit 110 that provides oil pressure transmitted to the wheel cylinder 40 , a motor 120 that generates a rotational force by an electrical signal from the pedal displacement sensor 11 , and a motor It may include a power conversion unit 130 that converts the rotational motion of the 120 into a linear motion and transmits it to the hydraulic pressure providing unit 110 . Alternatively, the hydraulic pressure providing unit 110 may be operated by the pressure provided from the high-pressure accumulator instead of the driving force supplied from the motor 120 .

The hydraulic pressure providing unit 110 includes a cylinder block 111 in which a pressure chamber to receive and store oil is formed, a hydraulic piston 114 accommodated in the cylinder block 111 , a hydraulic piston 114 and a cylinder block 111 . ) provided between the sealing member 115 for sealing the pressure chamber, and the driving shaft 133 connected to the rear end of the hydraulic piston 114 and transmitting the power output from the power conversion unit 130 to the hydraulic piston 114 . include

The pressure chamber is a first pressure chamber 112 located in front of the hydraulic piston 114 (forward direction, left direction in the drawing), and a rear (reverse direction, right direction in the drawing) of the hydraulic piston 114 (reverse direction, right direction in the drawing). A second pressure chamber 113 may be included. That is, the first pressure chamber 112 is partitioned by the front end of the cylinder block 111 and the hydraulic piston 114 , and is provided to have a different volume according to the movement of the hydraulic piston 114 , and the second pressure chamber 113 . ) is partitioned by the rear end of the cylinder block 111 and the hydraulic piston 114 , and the volume is provided to vary according to the movement of the hydraulic piston 114 .

The pressure chambers 112 and 113 are connected to the first hydraulic oil passage 211 and the fourth hydraulic oil passage 214 . The first hydraulic flow path 211 connects the first pressure chamber 112 and the first and second hydraulic circuits 201 and 202 . And the first hydraulic oil passage 211 is branched into a second hydraulic oil passage 212 communicating with the first hydraulic circuit 201 and a third hydraulic oil passage 212 communicating with the second hydraulic circuit 202 . The fourth hydraulic flow path 214 connects the second pressure chamber 113 and the first and second hydraulic circuits 201 and 202 . And the fourth hydraulic oil passage 214 is branched into a fifth hydraulic oil passage 215 communicating with the first hydraulic circuit 201 and a sixth hydraulic oil passage 216 communicating with the second hydraulic circuit 202 .

The sealing member 115 is provided between the hydraulic piston 114 and the cylinder block 111 to seal between the first pressure chamber 112 and the second pressure chamber 113 . The hydraulic pressure or negative pressure of the first pressure chamber 112 generated by the forward or backward movement of the hydraulic piston 114 is blocked by the piston sealing member 115 and does not leak into the second pressure chamber 113. 4 may be transmitted to the hydraulic flow paths (211, 214).

The first and second pressure chambers 112 and 113 are respectively connected to the reservoir 30 by the dump passages 116 and 117, and receive and store oil from the reservoir 30, or the first or second pressure chamber ( Oils 112 and 113 may be transferred to the reservoir 30 . For example, the dump passages 116 and 117 are branched from the first pressure chamber 112 and connected to the reservoir 30 , and the dump passages 116 are branched from the second pressure chamber 113 and connected to the reservoir 30 . ) may include a second dump flow path 117 connected to the.

The second hydraulic oil passage 212 may communicate with the first hydraulic circuit 201 , and the third hydraulic oil passage 213 may communicate with the second hydraulic circuit 202 . Accordingly, hydraulic pressure may be transmitted to the first hydraulic circuit 201 and the second hydraulic circuit 202 by the advance of the hydraulic piston 114 .

In addition, the electromagnetic brake system 1 according to the embodiment of the present invention is provided in the second and third hydraulic flow passages 212 and 213, respectively, to control the flow of oil. A first control valve 231 and a second control valve ( 232) may be included.

The first and second control valves 231 and 232 allow only the oil flow in the direction from the first pressure chamber 112 to the first or second hydraulic circuit 201, 202, and the oil flow in the opposite direction is It may be a shut-off check valve. That is, the first or second control valves 231 and 232 allow the hydraulic pressure of the first pressure chamber 112 to be transferred to the first or second hydraulic circuits 201 and 202 while allowing the first or second hydraulic pressure to be transferred. It is possible to prevent the hydraulic pressure of the circuits 201 and 202 from leaking into the first pressure chamber 112 through the second or third hydraulic passages 212 and 213 .

The fourth hydraulic oil passage 213 may be branched into a fifth hydraulic oil passage 215 and a sixth hydraulic oil passage 216 to communicate with both the first hydraulic circuit 201 and the second hydraulic circuit 202 . The fifth hydraulic oil passage 215 branched from the fourth hydraulic oil passage 214 communicates with the first hydraulic circuit 201 , and the sixth hydraulic oil passage 216 branched from the fourth hydraulic oil passage 214 is a second hydraulic pressure passage. It may be in communication with the circuit 202 . Accordingly, hydraulic pressure may be transmitted to both the first hydraulic circuit 201 and the second hydraulic circuit 202 by the backward movement of the hydraulic piston 114 .

The integrated solenoid valve 300 may be provided in the fifth hydraulic flow path 215 to control the flow of oil. The integrated solenoid valve 300 is a control valve including a bidirectional flow path and a unidirectional flow path F for controlling the oil flow between the second pressure chamber 113 and the circuit balance valve 235 or the first hydraulic circuit 201 . can In addition, the integrated solenoid valve 300 may be provided as a normally closed solenoid valve that is normally closed and operates to open the valve when an open signal is received from the electronic control unit.

Here, the one-way flow path F is provided in the integrated solenoid valve 300 to allow only the oil flow in the direction from the second pressure chamber 113 to the first hydraulic circuit 201, and check that the oil flow in the opposite direction is blocked. It can perform a valve function. That is, the one-way flow path can prevent the hydraulic pressure of the first hydraulic circuit 201 from leaking to the second pressure chamber 113 through the sixth hydraulic flow path 216 and the fourth hydraulic flow path 214 .

In addition, the electromagnetic brake system 1 according to the embodiment of the present invention is provided in the seventh hydraulic oil passage 217 connecting the second hydraulic oil passage 212 and the third hydraulic oil passage 213 to the first hydraulic circuit 201 . and a circuit balance valve 235 for regulating the pressure difference between the oil and the second hydraulic circuit 202, provided in the eighth hydraulic passage 218 connecting the second hydraulic passage 212 and the seventh hydraulic passage 217. It may include a sixth control valve 236 for controlling the flow of.

The circuit balance valve 235 and the sixth control valve 236 may be normally closed solenoid valves that operate to open when an open signal is received from the electronic control unit.

When an abnormality occurs in the first control valve 231 or the second control valve 232 , the circuit balance valve 235 and the sixth control valve 236 operate to open the hydraulic pressure of the first pressure chamber 112 . The first hydraulic circuit 201 and the second hydraulic circuit 202 are directed.

In addition, the circuit balance valve 235 and the sixth control valve 236 may be opened when the hydraulic pressure of the wheel cylinder 40 is taken out and sent to the first pressure chamber 112 . This is because the first control valve 231 and the second control valve 232 provided in the second hydraulic passage 212 and the third hydraulic passage 213 are provided as check valves allowing only one-way oil flow.

In addition, the electromagnetic brake system 1 according to the embodiment of the present invention is provided in the first and second dump passages 116 and 117, respectively, and a first dump valve 241 and a second dump valve 241 and second dump valves ( 242) may be included. The dump valves 241 and 242 may be check valves that open only a direction from the reservoir 30 to the first or second pressure chambers 112 and 113 and close in the opposite direction.

That is, the first dump valve 241 allows oil to flow from the reservoir 30 to the first pressure chamber 112 , but blocks the flow of oil from the first pressure chamber 112 to the reservoir 30 . It may be a check valve, and the second dump valve 242 allows oil to flow from the reservoir 30 to the second pressure chamber 113 , but the oil flows from the second pressure chamber 113 to the reservoir 30 . It may be a check valve that shuts off the flow.

In addition, the second dump flow path 117 may include a bypass flow path, and the bypass flow path includes a third dump valve 243 for controlling the oil flow between the second pressure chamber 113 and the reservoir 30 . can be installed.

The third dump valve 243 may be provided as a solenoid valve capable of controlling bidirectional flow, and is open in a normal state and operates to close the valve when a closing signal is received from the electronic control unit (Normal Open) type) solenoid valve.

The hydraulic pressure providing unit 110 may operate in a double acting type. That is, the hydraulic pressure generated in the first pressure chamber 112 as the hydraulic piston 114 moves forward is transmitted to the first hydraulic circuit 201 through the first hydraulic oil passage 211 and the second hydraulic oil passage 212 to the right side. The wheel cylinder 40 installed on the front wheel FR and the left rear wheel LR can act, and it is transmitted to the second hydraulic circuit 202 through the first hydraulic oil passage 211 and the third hydraulic oil passage 213 . to operate the wheel cylinder 40 installed on the right rear wheel RR and the left front wheel FL.

In addition, the negative pressure generated in the first pressure chamber 112 while the hydraulic piston 114 moves backward sucks the oil of the wheel cylinder 40 installed in the right front wheel FR and the left rear wheel LR to form the first pressure chamber. It can be transferred to 112 , and the oil of the wheel cylinder 40 installed on the right rear wheel RR and the left front wheel FL can be sucked and transferred to the first pressure chamber 112 .

Next, the motor 120 and the power conversion unit 130 of the hydraulic pressure supply device 100 will be described.

The motor 120 is a device for generating a rotational force by a signal output from an electronic control unit (ECU, not shown), and may generate a rotational force in a forward or reverse direction. The rotation angular speed and rotation angle of the motor 120 may be precisely controlled. Since the motor 120 is a well-known technology, a detailed description thereof will be omitted.

On the other hand, the electronic control unit controls the valves included in the electronic brake system 1 of the present invention to be described later, including the motor 120 .

The driving force of the motor 120 generates displacement of the hydraulic piston 114 through the power conversion unit 130, and the hydraulic pressure generated while the hydraulic piston 114 slides within the pressure chamber is transferred to the first and second hydraulic flow paths. It is transmitted to the wheel cylinder 40 installed in each wheel (RR, RL, FR, FL) through (211, 212).

The power conversion unit 130 is a device that converts rotational force into linear motion, and may include, for example, a worm shaft 131 , a worm wheel 132 , and a drive shaft 133 .

The worm shaft 131 may be integrally formed with the rotation shaft of the motor 120 , and a worm is formed on the outer circumferential surface to engage the worm wheel 132 to rotate the worm wheel 132 . The worm wheel 132 is connected to engage the drive shaft 133 to linearly move the drive shaft 133 , and the drive shaft 133 is connected to the hydraulic piston 114 to slide the hydraulic piston 114 in the cylinder block 111 . move it

When the above operations are described again, a signal sensed by the pedal displacement sensor 11 while displacement occurs in the brake pedal 10 is transmitted to an electronic control unit (ECU, not shown), and the electronic control unit is a motor 120 . is driven in one direction to rotate the worm shaft 131 in one direction. The rotational force of the worm shaft 131 is transmitted to the drive shaft 133 via the worm wheel 132 , and the hydraulic piston 114 connected to the drive shaft 133 moves forward to generate hydraulic pressure in the first pressure chamber 112 .

Conversely, when the pedal force is removed from the brake pedal 10 , the electronic control unit drives the motor 120 in the opposite direction to rotate the worm shaft 131 in the opposite direction. Accordingly, the worm wheel 132 also rotates in the opposite direction and the hydraulic piston 114 connected to the drive shaft 133 returns (moves backward) to generate negative pressure in the first pressure chamber 112 . As such, the hydraulic pressure supply device 100 serves to transmit the hydraulic pressure to the wheel cylinder 40 or suck the hydraulic pressure to the reservoir 30 according to the rotational direction of the rotational force generated from the motor 120 .

On the other hand, when the motor 120 rotates in one direction, hydraulic pressure may be generated in the first pressure chamber 112 or negative pressure may be generated in the second pressure chamber 113 . Whether to brake using hydraulic pressure, or negative pressure Whether or not to release the brake by using can be determined by controlling each solenoid valve.

The power conversion unit 130 may be configured as a ball screw nut assembly. For example, it is composed of a screw formed integrally with the rotation shaft of the motor 120 or connected to rotate with the rotation shaft of the motor 120, and a ball nut that is screwed with the screw in a state of limited rotation and moves linearly according to the rotation of the screw. can be The hydraulic piston 114 is connected to the ball nut of the power conversion unit 130 to press the pressure chamber by the linear motion of the ball nut. The structure of such a ball screw nut assembly is a well-known technique as a device for converting a rotational motion into a linear motion, so a detailed description thereof will be omitted.

The first and second backup passages 251 and 252 may directly supply oil discharged from the master cylinder 20 to the wheel cylinder 40 when the electromagnetic brake system 1 operates abnormally. A first cut valve 261 for controlling the flow of oil may be provided in the first backup passage 251 , and a second cut valve 262 for controlling the flow of oil may be provided in the second backup passage 252 . have. In addition, the first backup passage 251 connects the first hydraulic port 24a and the first hydraulic circuit 201, and the second backup passage 252 is connected to the second hydraulic port 24b and the second hydraulic circuit ( 202) can be connected.

In addition, the first and second cut valves 261 and 262 may be normally open type solenoid valves that are opened in a normal state and operate to close the valves when a closing signal is received from the electronic control unit.

The hydraulic control unit 200 may include a first hydraulic circuit 201 and a second hydraulic circuit 202 that receive hydraulic pressure to control two wheels, respectively. For example, the first hydraulic circuit 201 may control the right front wheel FR and the left rear wheel RL, and the second hydraulic circuit 202 may control the left front wheel FL and the right rear wheel RR. . In addition, a wheel cylinder 40 is installed on each of the wheels FR, FL, RR, and RL to receive hydraulic pressure to perform braking.

The hydraulic circuits 201 and 202 may include a plurality of inlet valves 221 (221a, 221b, 221c, 221d) to control the flow of hydraulic pressure. The first hydraulic circuit 201 is provided with two inlet valves 221a and 221b that are connected to the first hydraulic passage 211 and control the hydraulic pressure transmitted to the two wheel cylinders 40, respectively, and the second hydraulic circuit At 202 , two inlet valves 221c and 221d that are connected to the second hydraulic flow path 212 and respectively control hydraulic pressure transmitted to the wheel cylinder 40 may be provided.

The inlet valve 221 is disposed on the upstream side of the wheel cylinder 40 and is a normally open type solenoid valve that is open in a normal state and operates to close the valve when a closing signal is received from the electronic control unit. can

The hydraulic circuits 201 and 202 may include check valves 223a, 223b, 223c, and 223d provided in a bypass passage connecting the front and rear of each of the inlet valves 221a, 221b, 221c, and 221d. . The check valves 223a, 223b, 223c, and 223d allow only the flow of oil from the wheel cylinder 40 to the hydraulic pressure providing unit 110 in the direction, and from the hydraulic pressure providing unit 110 to the wheel cylinder 40 direction. flow can be restricted. The check valves 223a, 223b, 223c, and 223d quickly release the braking pressure of the wheel cylinder 40 or when the inlet valves 221a, 221b, 221c, and 221d do not operate normally. The hydraulic pressure may be introduced into the hydraulic pressure providing unit 110 .

The hydraulic circuits 201 and 202 may further include a plurality of outlet valves 222 (222a, 222b, 222c, 222d) connected to the reservoir 30 to improve performance when braking is released. The outlet valves 222 are respectively connected to the wheel cylinders 40 to control the hydraulic pressure to escape from the respective wheels RR, RL, FR, and FL. That is, the outlet valve 222 detects the braking pressure of each of the wheels RR, RL, FR, and FL and selectively opens when pressure reduction braking is required to control the pressure.

The outlet valve 222 may be a normally closed type solenoid valve that is normally closed and operates to open when an open signal is received from the electronic control unit.

The hydraulic control unit 200 may be connected to the backup passages 251 and 252 . For example, the first hydraulic circuit 201 is connected to the first backup passage 251 to receive hydraulic pressure from the master cylinder 20 , and the second hydraulic circuit 202 is connected to the second backup passage 252 , Hydraulic pressure may be provided from the master cylinder 20 .

The first backup flow path 251 may join the first hydraulic circuit 201 upstream of the first and second inlet valves 221a and 221b. Similarly, the second backup flow path 252 may join the second hydraulic circuit 202 upstream of the third and fourth inlet valves 221c and 221d. Therefore, when the first and second cut valves 261 and 262 are closed, the hydraulic pressure provided from the hydraulic pressure supply device 100 is supplied to the wheel cylinder 40 through the first and second hydraulic circuits 201 and 202. When the first and second cut valves 261 and 262 are opened, the hydraulic pressure provided from the master cylinder 20 is supplied to the wheel cylinder 40 through the first and second backup passages 251 and 252. can At this time, since the plurality of inlet valves 221a, 221b, 221c, and 221d are in an open state, it is not necessary to change the operating state.

On the other hand, unexplained reference numeral “PS1” is a hydraulic oil pressure sensor for sensing the hydraulic pressure of the hydraulic circuits 201 and 202 , and “PS2” is a backup passage pressure sensor for measuring the oil pressure of the master cylinder 20 . And “MPS” is a motor control sensor that controls the rotation angle of the motor 120 or the current of the motor.

2 is a side cross-sectional view of the integrated solenoid valve according to the first embodiment of the present invention, and FIG. 3 is (a) a plan view and (b) a bottom view of the orifice unit 370 .

Referring to the drawings, the integrated solenoid valve 300 according to the first embodiment of the present invention is disposed inside the sleeve 320, and the orifice 360a of the seat 360 is raised and lowered along the axial direction. The armature 350 that opens and closes the orifice 360a, the elastic member 340 for providing an elastic force to the armature 350 in the direction of closing the orifice 360a, and the elastic member 340 in the opposite direction to the armature 350 providing a driving force The magnet core 330, the orifice unit 370 coupled to the lower side of the seat 360, and having a hollow hole 370a and a flow path hole 370b communicating with the orifice 360a of the seat 360, preventing the inflow of foreign substances It includes a filter member 380 and a lip seal 390 fitted between the orifice unit 370 and the filter member 380 and having an inclined protrusion 390a, and opens and closes by lifting of the armature 350 It may include a bidirectional flow path and a one-way flow path F passing through the flow path hole 370b and the outer surface of the inclined protrusion 390a.

The integrated solenoid valve 300 opens and closes the orifice 360a with the armature 350 that is lifted by the magnet core 330, the first port 301A of the pressure chamber 112,113 side and the circuit balance valve 235 side Controls the flow rate of the bidirectional flow path connecting the second port 301B of This integrated solenoid valve 300 is installed in the bore of the modulator block 301 . In this case, the modulator block 301 may be a rectangular block for compactly embedding each of the above-described elements including the simulator valve in the brake system.

The sleeve 320 may be press-fitted or welded to the integral solenoid valve 300 , and a magnet core 330 may be installed on the upper side of the sleeve 320 . And the sleeve 320 accommodates the armature 350 therein and restricts the movement in the width direction of the armature 350 to guide the armature 350 to ascend and descend only in the longitudinal direction.

The magnet core 330 is coupled to the upper side of the sleeve 320 to close the open upper portion of the sleeve 320 . For a more intimate coupling between the magnet core 330 and the sleeve 320 , a coupling groove is formed in the magnet core 330 , and the sleeve 320 may be assembled by pressing the coupling groove to engage the sleeve 320 . This coupling structure facilitates the coupling of the sleeve 320 and the magnet core 330 compared to the conventional welding method and may simplify the coupling process.

The armature 350 is installed so as to move forward and backward in the sleeve 320 , and a ball is fastened to the lower end thereof to contact the seat 360 having an orifice 360a. The upper groove of the armature 350 is provided on the opposite surface of the magnet core 330 to form a space in which the elastic member 340, which will be described later, is fitted.

The elastic member 340 may be installed so that one end is in contact with the upper groove of the armature 350 and the other end is in contact with the magnet core 330 . The elastic member 340 can maintain the normally closed state of the integrated solenoid valve 300 by applying an elastic force to the armature 350 . If magnetic force is not normally generated in the magnet core 330 , the armature 350 maintains a state pressed downward by the elastic member 340 , and when the magnet core 330 generates a magnetic force, the armature 350 rises. To open the bidirectional flow path through the orifice (360a).

The orifice unit 370 is provided with a hollow hole 370a for flow control, and is press-fitted to the lower side of the seat 360 , on the other side of the seat 360 , a large diameter portion corresponding to the inner diameter size of the filter member 370 and a lip seal 390 . ) The inner step, which is a small diameter part, for assembly is provided. The orifice unit 370 may have a flow path hole 370b for the fluid flow of the one-way flow path F.

The lip seal 390 is installed between the inner surface of the filter member 370 and the outer surface of the orifice unit 370, the inclined protrusion 390a is provided inside the lip seal 390, and the one-way flow path F is the orifice unit ( It may be provided to pass through the passage hole 370b provided in the 370 and the inclined protrusion 390a.

The lip seal 390 is accommodated in the filter member 370 so that the inclined protrusion 390a is in contact with the outer circumferential surface of the small-diameter portion of the orifice unit 370, is deformed by the pressure difference and protrudes inwardly inclined ) to allow only one-way transfer of the fluid. The inclined protrusion 390a is bent in a narrowing direction when the pressure of the first port 301A is greater than the pressure of the second port 301B to form a one-way flow path F, but on the contrary, the pressure of the second port 301B is When the pressure of the first port 301A is less than the pressure, the one-way flow path F is not formed by bending in the open direction.

The filter member 380 is positioned on the opposite surface of the first port 301A to prevent the inflow of the first filter 380a and the second port 301B to prevent the inflow of foreign substances. It maintains a distance between the 380b and the modulator block 301 and includes a support portion 380c protruding from the lower side to secure a flow path. And it is assembled under the orifice unit 370, and restricts the lip seal 390 together with the orifice unit 370 to limit the movement of the lip seal 390 when pressure is applied.

4 is a side cross-sectional view of the integrated solenoid valve 400 according to a second embodiment of the present invention, and FIG. 5 is a (a) upper surface, (b) side cross-section and (c) lower surface of the seat 460, and FIG. 6 shows (a) a side cross-sectional view and (b) a bottom view of the filter member 480 .

Referring to the drawings, the integrated solenoid valve 400 according to the second embodiment of the present invention replaces the integrated solenoid valve 300 in the first embodiment, and the first port ( 401A) and the second port 402A may be an integrated solenoid valve 400 for controlling the flow rate of the flow path. At this time, the first port 401A communicates with the pressure chambers 112 and 113 of the hydraulic pressure supply device 100, and the second port 401B is connected to the circuit balance valve 235 side, so the integrated solenoid valve 400 is the pressure chamber. It is possible to control the fluid flow between the (112, 113) and the circuit balance valve (235).

This integrated solenoid valve 400 is disposed inside the sleeve 420, and the armature 450 that opens and closes the orifice 460a of the seat 460 disposed on the lower side while ascending and descending along the axial direction, the orifice 460a is closed. The elastic member 440 for providing an elastic force to the armature 450 in the direction of the magnet core 430 for providing a driving force to the armature 450 in the opposite direction to the elastic member 440, the first flow path (460b) second A flow path 460c is provided and the seat 460 having an orifice 460a is sandwiched between the modulator block 401 and the seat 460, and has an inclined protrusion 490a to allow only one-way transfer of the fluid. A bidirectional flow path including a lip seal 490, opened and closed by the elevation of the armature 450 and passing through the first flow path 460b, and a second flow path 460c and a one-way flow path passing through the outer surface of the inclined protrusion 490a ( F) may be included.

The seat 460 is formed along the axial direction on the inside, and an orifice 460a provided to be opened and closed by a ball of the armature 450, and a first flow path 460b concavely formed at both ends of the upper portion on the side of the armature 450 ), and a second flow path 460c provided in a stepwise manner at both ends of the lower portion of the second port 401B at a position in contact with the modulator block 401 .

The filter member 480 may be provided on the outer circumferential surface of the sheet to prevent the inflow of foreign substances. The filter member 480 may include a gap flow path 480b recessed along the axial direction on the inner circumferential surface in contact with the sheet 460 . The gap flow path 480b is formed on the inner circumferential surface of the filter member 480 close to the second flow path 460c side of the sheet 460, and a plurality of gap flow paths 480b are provided at regular intervals in the radial direction so that the one-way flow path F passes through. can

The lip seal 490 is provided between the outer peripheral surface of the seat 460 and the modulator block 401, and may be disposed between the gap passage 480b of the filter member 480 and the second passage 460c of the seat 460. have. In addition, the inclined protrusion 490a may be formed on the inner circumferential surface of the lip seal 390 to contact the outer circumferential surface of the seat 460 . The inclined protrusion 490a is formed to protrude obliquely toward the lower side of the second port 401B, and is deformed by a pressure difference to allow only one-way transfer of the fluid. Specifically, the inclined protrusion 390a is deformed in a narrowing direction when the pressure of the first port 401A is greater than the pressure of the second port 401B to open the one-way flow path F, but on the contrary, the first port ( When the pressure of the 401A is smaller than the pressure of the second port 401, it is deformed in an open direction to block and close the one-way flow path F. Accordingly, the one-way flow path F flows from the first port 401A to the second port 401B through the gap flow path 480b, the inclined protrusion 490a, and the second flow path 460c sequentially in one direction. It can perform the function of a check valve to allow only the flow of the fluid in the opposite direction and block the flow of the fluid in the opposite direction.

Although the present invention has been described with reference to an embodiment shown in the accompanying drawings, this is merely an example, and it is understood that various modifications and equivalent other embodiments are possible by those skilled in the art. You will understand. Accordingly, the true scope of the invention should be defined only by the appended claims.

10: brake pedal 11: pedal displacement sensor
20: master cylinder 30: reservoir
31: first reservoir chamber 32: second reservoir chamber
33: third reservoir chamber 34: bulkhead
35: bulkhead 40: wheel cylinder
50: simulation device 54: simulator valve
55: check valve 100: hydraulic supply
110: hydraulic pressure providing unit 112: first pressure chamber
113: second pressure chamber 120: motor
130: power conversion unit 200: hydraulic control unit
201: first hydraulic circuit 202: second hydraulic circuit
211: first hydraulic flow path 212: second hydraulic flow path
213: third hydraulic oil passage 214: fourth hydraulic oil passage
215: fifth hydraulic oil passage 216: sixth hydraulic oil passage
217: seventh hydraulic flow path 218: eighth hydraulic flow path
221: inlet valve 222: outlet valve
223: check valve 231: first control valve
232: second control valve 235: circuit balance valve
236: sixth control valve 241: first dump valve
242: second dump valve 243: third dump valve
251: first backup flow path 252: second backup flow path
261: first cut valve 262: second cut valve
271: third control valve 272: fourth control valve
273: fifth control valve 300: integrated solenoid valve
301: modulator block 301A: first port
301B: second port 320: sleeve
330: magnet core 340: elastic member
350: amateur 360: sheet
360a: orifice 370: orifice unit
370a: hollow hole 370b: euro hole
380: filter member 380a: first filter
380b: second filter 380c: support
390: lip seal 390a: inclined protrusion
400: integral solenoid valve 401: modulator block
401A: first port 401B: second port
410: valve housing 420: sleeve
430: magnet core 440: elastic member
450: amateur 460: sheet
460a: orifice 460b: first flow path
460c: second flow path 480: filter member
480a: filter 480b: crevice flow path
490: lip seal 490a: inclined protrusion

Claims (8)

In the integrated solenoid valve for controlling the flow rate of the flow path connecting the first port and the second port,
an armature disposed inside the sleeve, ascending and descending along the axial direction, and opening and closing the orifice formed at the lower side;
an elastic member for providing an elastic force to the armature in a direction for closing the orifice;
a magnet core providing a driving force to the armature in a direction opposite to the elastic member;
a sheet having a first flow path, a second flow path, and the orifice disposed therein;
a filter member provided on the outer circumferential surface of the sheet to prevent inflow of foreign substances, the filter member having a gap passage recessed along the axial direction on the inner circumferential surface in contact with the outer circumferential surface of the sheet;
a lip seal provided between the gap passage and the second passage and having an inclined protrusion inclined toward the second port; and
An integrated solenoid valve comprising: a bidirectional flow path that is opened and closed by lifting and lowering of the armature and passes through the first flow path and the orifice; According to claim 1,
The gap flow
An integrated solenoid valve provided on the filter member on the side of the second flow path. 3. The method of claim 2,
The first flow path is formed on the armature side on the seat,
The second flow path is formed on the seat on the side of the second port,
The orifice is an integral solenoid valve that is formed through the inner side of the seat along the axial direction. 4. The method of claim 3,
the amateur
An integrated solenoid valve including a ball provided on a surface in contact with the orifice. 3. The method of claim 2,
The gap flow
An integral solenoid valve provided with a plurality of radially spaced apart from the inner circumferential surface of the filter member. According to claim 1,
The lip seal is provided between the outer peripheral surface of the seat and the modulator block,
The inclined protrusion is formed on the inner peripheral surface of the integral solenoid valve provided to be in contact with the outer peripheral surface of the seat. 7. The method of claim 6,
The inclined protrusion is provided to be deformable by hydraulic pressure,
When the pressure of the first port is greater than the pressure of the second port, it is deformed in a narrowing direction to allow the one-way flow path,
When the pressure of the first port is less than the pressure of the second port, the integrated solenoid valve is deformed in an open direction to block the one-way flow path. An integrated solenoid valve according to any one of claims 1 to 7;
a master cylinder provided with a cylinder chamber whose volume is changed by pedal operation;
a pedal simulator connected to the cylinder chamber to provide a reaction force according to a pedal effort;
a hydraulic pressure supply device for providing hydraulic pressure to at least one of the first hydraulic circuit and the second hydraulic circuit;
an electronic control unit operating the hydraulic pressure supply device; and
Includes; circuit balance valve provided for regulating the pressure difference between the first hydraulic circuit and the second hydraulic circuit;
The integrated solenoid valve is installed in a hydraulic flow path connecting the pressure chamber of the hydraulic pressure supply device and the circuit balance valve.

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