KR20220001306A - Electric brake system and Operating method of thereof - Google Patents

Abstract

Disclosed is an electronic brake system. The electronic brake system according to an embodiment of the present invention comprises: a reservoir for storing a pressurizing medium; a master cylinder including a first master piston connected to a brake pedal, a first master chamber having a volume varied by the displacement of the first master piston, a second master piston arranged to be able to be displaced by the displacement of the first master piston or the pressurizing medium accommodated in the first master chamber, and a second master chamber having a volume varied by the displacement of the second master piston; a reservoir flow path connected to the reservoir and the first master chamber; a hydraulic pressure supply device for generating hydraulic pressure by operating a hydraulic piston according to electric signals outputted in response to the displacement of the brake pedal; a first hydraulic circuit for controlling the hydraulic pressure of a first wheel cylinder and a second wheel cylinder; a second hydraulic circuit for controlling the hydraulic pressure of a third wheel cylinder and a fourth wheel cylinder; a backup flow path for connecting the second master chamber and the second hydraulic circuit; a cut valve arranged on the backup flow path to control the flow of the pressurizing medium; a dump flow path for connecting the first master chamber and the first hydraulic circuit; and a flow path orifice arranged on the dump flow path to generate the congestion of the pressurizing medium on the dump flow path to correspond to the congestion of the pressurizing medium generated while the pressurizing medium on the backup flow path passes the cut valve. Therefore, provided is an electronic brake system for realizing effective braking in various operating situations.

Description

Electronic brake system and Operating method of thereof

The present invention relates to an electronic brake system, and more particularly, to an electronic brake system that generates a braking force using an electrical signal corresponding to a displacement of a brake pedal.

A brake system for performing braking is essential to a vehicle, and various types of brake systems have been proposed for the safety of drivers and passengers.

The conventional brake system mainly uses a method of supplying hydraulic pressure required for braking to wheel cylinders using a mechanically connected booster when a driver presses a brake pedal. However, as the market demand to implement various braking functions in detail in response to the operating environment of the vehicle increases, recently, when the driver steps on the brake pedal, the driver's braking intention is electrically controlled from the pedal displacement sensor that detects the displacement of the brake pedal. An electronic brake system that receives a signal and operates a hydraulic pressure supply device based on the signal to supply hydraulic pressure required for braking to the wheel cylinders is widely used.

Such an electronic brake system generates and provides an electric signal for the driver's brake pedal operation in the normal operation mode or the braking judgment during autonomous driving of the vehicle, and based on this, the hydraulic pressure supply device is electrically operated and controlled to reduce the hydraulic pressure required for braking. formed and transferred to the wheel cylinder. As described above, the electronic brake system and operation method are electrically operated and controlled, and although complex and diverse braking actions can be implemented, when a technical problem occurs in the electrical components, the hydraulic pressure required for braking is not stably formed. There is a risk of jeopardizing the safety of passengers.

Therefore, the electronic brake system enters an abnormal operation mode when one component element is broken or falls out of control. In this case, a mechanism in which the driver's brake pedal operation is directly interlocked with the wheel cylinder is required. That is, in the abnormal operation mode of the electronic brake system, the hydraulic pressure required for braking should be directly formed as the driver applies a pedal force to the brake pedal, and this should be directly transmitted to the wheel cylinders. Furthermore, there is a need for a method capable of accurately and quickly inspecting whether the electronic brake system is malfunctioning so as to quickly enter an abnormal operation mode in an emergency to promote passenger safety.

EP 2 520 473 A1 (Honda Motor Co., Ltd.) 2012. 11. 7.

An object of the present embodiment is to provide an electronic brake system that can effectively implement braking in various operating situations.

An object of the present embodiment is to provide an electronic brake system capable of suppressing a hydraulic pressure deviation of a pressurized medium between a plurality of wheel cylinders and achieving a hydraulic pressure balance.

An object of the present embodiment is to provide an electronic brake system capable of uniformly supplying hydraulic pressure of a pressurized medium to a plurality of wheel cylinders.

An object of the present embodiment is to provide an electronic brake system capable of uniformly discharging hydraulic pressure of a pressurized medium from a plurality of wheel cylinders during active braking.

An object of the present embodiment is to provide an electronic brake system with improved braking performance and operational reliability.

This embodiment is intended to provide an electronic brake system with improved durability of the product by reducing the load applied to the component elements.

An object of the present embodiment is to provide an electronic brake system capable of implementing a stable braking operation with a simple structure.

According to one aspect of the present invention, a reservoir in which the pressurized medium is stored; A first master piston connected to a brake pedal, a first master chamber whose volume is changed by displacement of the first master piston, and displacement by a displacement of the first master piston or a pressurized medium accommodated in the first master chamber a master cylinder including a second master piston that is operably provided and a second master chamber whose volume is changed by displacement of the second master piston; a reservoir passage connecting the reservoir and the first master chamber; a hydraulic pressure supply device for generating hydraulic pressure by operating a hydraulic piston according to an electrical signal output in response to the displacement of the brake pedal; a first hydraulic circuit for controlling hydraulic pressures of the first wheel cylinder and the second wheel cylinder; a second hydraulic circuit for controlling hydraulic pressures of the third wheel cylinder and the fourth wheel cylinder; a backup passage connecting the second master chamber and the second hydraulic circuit; a cut valve provided in the backup passage to control the flow of the pressurized medium; a dump passage connecting the first master chamber and the first hydraulic circuit; and a flow path orifice provided in the dump flow path to generate stagnation of the pressurized medium on the dump flow path corresponding to the stagnation of the pressurized medium generated while the pressurized medium on the backup flow passage passes through the cut valve. .

The diameter or cross-sectional area of the flow passage orifice may be provided to correspond to the diameter or cross-sectional area of the orifice provided in the cut valve.

The dump passage further includes a bypass dump passage having one end connected to the front end of the passage orifice on the dump passage and the other end connected to the rear end of the passage orifice on the dump passage, and to the bypass dump passage It may be provided to further include an outlet check valve that allows only the flow of the pressurized medium from the first hydraulic circuit to the first master chamber.

The first hydraulic circuit forms an exhaust passage by connecting the first and second wheel cylinders to the reservoir via the dump passage, the bypass dump passage, the first master chamber, and the reservoir passage, 2 hydraulic circuit forms a discharge flow path by first and second outlet flow paths directly connecting the third and fourth wheel cylinders to the reservoir, respectively, and the cross-sectional area of an orifice provided in the outlet check valve and the flow path orifice The sum of the cross-sectional areas may be provided to correspond to a flow passage cross-sectional area of the first outlet flow passage or a flow passage cross-sectional area of the second outlet flow passage.

It may be provided by further comprising at least one dump valve provided in the dump passage to control the flow of the pressurized medium.

The dump valve includes a first dump valve for controlling the flow of the pressurized medium between the first wheel cylinder and the dump flow path, and a second dump valve for controlling the flow of the pressurized medium between the second wheel cylinder and the dump flow path can be provided.

Any one of the first dump valve and the second dump valve may be provided as a normally closed type solenoid valve that is normally closed and opened when receiving an electrical signal from the electronic control unit. .

The diameter or cross-sectional area of the orifice provided in the dump valve may be greater than the diameter or cross-sectional area of the flow passage orifice.

The electronic brake system according to the present embodiment can stably and effectively implement braking in various operating situations of the vehicle.

The electronic brake system according to the present embodiment can suppress the hydraulic pressure deviation of the pressurized medium between the plurality of wheel cylinders and achieve a hydraulic pressure balance.

In the electronic brake system according to the present embodiment, the hydraulic pressure of the pressurized medium may be uniformly supplied to the plurality of wheel cylinders.

The electronic brake system according to the present embodiment may uniformly discharge the hydraulic pressure of the pressurized medium from the plurality of wheel cylinders during active braking.

In the electronic brake system according to the present embodiment, braking performance and operational reliability may be improved.

The electronic brake system according to the present embodiment may reduce the load applied to the component elements to improve the durability of the product.

The electronic brake system according to the present embodiment may implement a stable braking operation with a simple structure.

1 is a hydraulic circuit diagram showing an electronic brake system according to the present embodiment.
2 is an inlet circuit diagram illustrating a state in which the electronic brake system according to the present embodiment performs a fallback mode.
3 is a hydraulic circuit diagram illustrating a state in which the electronic brake system according to the present embodiment performs active braking.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The following examples are presented 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 not related to the description in order to clarify the present invention, and slightly exaggerate the size of the components to help understanding.

1 is a hydraulic circuit diagram showing an electronic brake system 1000 according to the present embodiment.

Referring to FIG. 1 , the electronic brake system 1000 according to an embodiment of the present invention provides a reservoir 1100 in which a pressurized medium is stored and a reaction force according to the pedal effort of the brake pedal 10 to the driver and, at the same time, The master cylinder 1200 for pressurizing and discharging the pressurized medium such as brake oil received and the pedal displacement sensor 11 for detecting the displacement of the brake pedal 10 receive the driver's braking intention as an electrical signal to operate mechanically The hydraulic pressure supply device 1300 for generating the hydraulic pressure of the pressurized medium through Hydraulic circuits 1510 and 1520 having wheel cylinders 20 for braking RL, FR, and FL, and hydraulic pressure provided between the hydraulic pressure supply device 1300 and the reservoir 1100 to control the flow of the pressurized medium The dump unit 1800, the dump flow path 1610 that hydraulically connects the first hydraulic circuit 1510 with the master cylinder 1200 side, and the master cylinder 1200 and the second hydraulic circuit 1520 are hydraulically connected. A backup flow path 1620 for connecting, a cut valve 1621 provided in the backup flow path 1620 to control the flow of the pressurized medium, a flow path orifice 1615 provided in the dump flow path 1610, and both ends of the dump flow path ( 1610) A bypass dump flow path 1630 connecting the front and rear ends of the upper flow passage orifice 1615, an outlet check valve 1631 provided in the bypass dump flow path to control the flow of pressurized medium, and a reservoir 1100 A reservoir flow path 1700 that hydraulically connects the master cylinder 1200, an inspection flow path 1900 connected to the master chamber of the master cylinder 1200, and a hydraulic pressure supply device 1300 based on hydraulic pressure information and pedal displacement information ) and an electronic control unit (ECU, not shown) for controlling various valves.

When the driver applies a pedaling force to the brake pedal 10 for braking operation, the master cylinder 1200 provides a reaction force to the driver to provide a stable pedal feeling, and at the same time, when the driver applies a pedaling force to the brake pedal 10 , it is received inside by the operation of the brake pedal 10 . It is provided to pressurize and discharge the pressurizing medium.

Specifically, the master cylinder 1200 includes a first master chamber 1220a formed on the inlet side of a cylinder body 1210 forming a chamber therein, and a cylinder body 1210 to which the brake pedal 10 is connected, A first master piston 1220 provided in the first master chamber 1220a and connected to the brake pedal 10 to be displaceable by the operation of the brake pedal 10, and the first master piston 1220 on the cylinder body 1210 The second master chamber 1230a formed on the inner side or the front side (the left side with respect to FIG. 1) than the master chamber 1220a, and the second master chamber 1230a provided in the first master piston 1220 displacement or The second master piston 1230 is provided to be displaceable by the hydraulic pressure of the pressurized medium accommodated in the first master chamber 1220a, and is disposed between the first master piston 1220 and the second master piston 1230 when compressed A pedal simulator 1240 that provides a feeling of pedaling through the generated elastic restoring force may be included.

The first master chamber 1220a and the second master chamber 1230a are formed on the cylinder body 1210 of the master cylinder 1200 from the brake pedal 10 side (the right side with respect to FIG. 1 ) from the inside (with reference to FIG. 1 ). left) may be sequentially formed. In addition, the first master piston 1220 and the second master piston 1230 are provided in the first master chamber 1220a and the second master chamber 1230a, respectively, and hydraulic pressure is applied to the pressurized medium accommodated in each chamber according to the forward and backward movement. may be formed or a negative pressure may be formed.

The cylinder body 1210 has a first master chamber 1220a formed therein, a large diameter portion 1211 having a relatively large inner diameter, and a second master chamber 1230a formed inside the large diameter portion 1211. A small-diameter portion 1212 having a relatively small inner diameter may be included. The large-diameter portion 1211 and the small-diameter portion 1212 of the cylinder body 1210 may be integrally formed.

The first master chamber 1220a may be formed inside the large-diameter portion 1211 that is the inlet side or the rear side (the right side with respect to FIG. 1) of the cylinder body 1210, and the input to the first master chamber 1220a The first master piston 1220 connected to the brake pedal 10 via the rod 12 may be accommodated in a reciprocating manner.

In the first master chamber 1220a, the pressurized medium may be introduced and discharged through the first hydraulic port 1280a, the second hydraulic port 1280b, the third hydraulic port 1280c, and the fourth hydraulic port 1280d. . The first hydraulic port 1280a is connected to a first reservoir flow path 1710 to be described later to introduce a pressurized medium from the reservoir 1100 to the first master chamber 1220a or pressurized medium accommodated in the first master chamber 1220a. may be discharged to the reservoir 1100 , and the second hydraulic port 1280b is connected to a dump flow path 1610 to be described later so that the pressurized medium is discharged from the first master chamber 1220a to the dump flow path 1610 side or dumped in reverse. A pressurized medium may be introduced from the flow path 1610 toward the first master chamber 1220a.

In addition, the first master chamber 1220a is connected to the first and second branch passages 1910 and 1920 of the inspection passage 1900 to be described later through the third hydraulic port 1280c and the fourth hydraulic port 1280d, respectively. As a result, the pressurized medium accommodated in the first master chamber 1220a may be discharged toward the inspection passage 1900 , or the pressurized medium may be introduced into the first master chamber 1220a from the inspection passage 1900 .

The first master piston 1220 is provided to be accommodated in the first master chamber 1220a, and pressurizes the pressurizing medium accommodated in the first master chamber 1220a by advancing (left direction with reference to FIG. 1) to form hydraulic pressure or , it is possible to form a negative pressure in the interior of the first master chamber 1220a by moving backward (right direction with respect to FIG. 1 ). The first master piston 1220 includes a first body 1221 formed in a cylindrical shape so as to be in close contact with the inner circumferential surface of the first master chamber 1220a, and a rear end of the first body 1221 (a right end in reference to FIG. 1 ). ) is formed to expand in the radial direction and may include a first flange 1222 to which the input rod 12 is connected. The first master piston 1220 may be elastically supported by the first piston spring 1220b, and the first piston spring 1220b has one end of the front surface of the first flange 1222 (the left side with reference to FIG. 1 ). ), and the other end may be provided by being supported on the outer surface of the cylinder body 1210 .

The first master piston 1220 communicates with the first master chamber 1220a and communicates with the fourth hydraulic port 1280d and the second branch flow path 1920 in a non-operational state, that is, in a ready state before displacement occurs. A first cut-off hole 1220d is provided. Also, a first sealing member 1290a for sealing the first master chamber 1220a from the outside may be provided between the outer circumferential surface of the first master piston 1220 and the cylinder body 1210 . The first sealing member 1290a may be provided to be seated in a receiving groove recessed on the inner circumferential surface of the cylinder body 1210 to be in contact with the outer circumferential surface of the first master piston 1220, and to the first sealing member 1290a. Accordingly, it is possible to prevent the pressurized medium accommodated in the first master chamber 1220a from leaking to the outside and to prevent foreign substances from being introduced into the first master chamber 1220a. The first sealing member 1290a is the outermost on the inner circumferential surface of the cylinder body 1210, that is, the rear side of the fourth hydraulic port 1280d to which a second branch flow path 1920 to be described later is connected (right side with reference to FIG. 1 ). ) can be provided.

Between the outer circumferential surface of the first master piston 1220 and the cylinder body 1210, the flow of the pressurized medium flowing into the first master chamber 1220a from the first branch passage 1910 connected to the third hydraulic port 1280c is controlled. A third sealing member 1290c for blocking may be provided. The third sealing member 1290c is seated in a pair of receiving grooves respectively recessed at the front and rear of the third hydraulic port 1280c on the inner circumferential surface of the cylinder body 1210 to respectively seat the outer circumferential surface of the first master piston 1220 . can come into contact with The pair of third sealing members 1290c may be provided in front (left side with reference to FIG. 1) of the first sealing member 1290a, and the pressurizing medium accommodated in the first master chamber 1220a is the third hydraulic port The flow transferred to the first branch passage 1910 through the 1280c may be allowed, but the flow of the pressurized medium flowing from the first branch passage 1910 into the first master chamber 1220a may be blocked.

The second master chamber 1230a may be formed on the inside of the small diameter portion 1212 on the inner side or the front side (the left side with respect to FIG. 1 ) on the cylinder body 1210 , and the second master chamber 1230a has a second The master piston 1230 may be accommodated reciprocally.

In the second master chamber 1230a, the pressurized medium may be introduced and discharged through the fifth hydraulic port 1280e and the sixth hydraulic port 1280f. The fifth hydraulic port 1280e is connected to a second reservoir flow path 1720 to be described later so that the pressurized medium accommodated in the reservoir 1100 may flow into the second master chamber 1230a. In addition, the sixth hydraulic port 1280d is connected to a backup flow path 1620 to be described later so that the pressurized medium accommodated in the second master chamber 1230a can be discharged toward the backup flow path 1620 , and vice versa from the backup flow path 1620 . A pressurized medium may be introduced into the second master chamber 1230a.

The second master piston 1230 is accommodated in the second master chamber 1230a, and may form hydraulic pressure of the pressurized medium accommodated in the second master chamber 1230a by moving forward, and moving backward by moving the second master chamber 1230a ) can form a negative pressure. The second master piston 1230 includes a second body 1231 formed in a cylindrical shape so as to be in close contact with the inner circumferential surface of the second master chamber 1230a, and the rear end of the second body 1231 (the right end in reference to FIG. 1 ). ) extending in the radial direction and may include a second flange 1232 disposed inside the first master chamber 1220a. The diameter of the second flange 1232 may be larger than the diameter of the inner peripheral surface of the second master chamber 1230a. The second master piston 1230 may be elastically supported by a second piston spring 1230b, and the second piston spring 1230b has one end of the front surface of the second body 1231 (a left surface with reference to FIG. 1 ). ), and the other end may be provided by being supported on the inner surface of the cylinder body 1210 .

A second sealing member 1290b for sealing the first master chamber 1220a to the second master chamber 1230a may be provided between the outer circumferential surface of the second master piston 1230 and the cylinder body 1210 . The second sealing member 1290b may be provided to be seated in a receiving groove recessed on the inner circumferential surface of the cylinder body 1210 to be in contact with the outer circumferential surface of the second master piston 1230, and to the second sealing member 1290b. Accordingly, it is possible to prevent the pressurized medium accommodated in the first master chamber 1220a from leaking into the second master chamber 1230a.

The second master piston 1230 communicates with the second master chamber 1230a and communicates with the fifth hydraulic port 1280e and the second reservoir flow path 1720 in a non-operational state, that is, in a ready state before displacement occurs. A second cut-off hole 1230d is provided. In addition, between the outer peripheral surface of the second master piston 1230 and the cylinder body 1210, the flow of the pressurized medium discharged from the second master chamber 1230a to the second reservoir flow path 1720 connected to the fifth hydraulic port 1280e. A fourth sealing member (1290d) to block may be provided. The fourth sealing member 1290d is seated in a receiving groove that is recessed in the front (left side with reference to FIG. 1) of the fifth hydraulic port 1280e on the inner circumferential surface of the cylinder body 1210, the second master piston 1230 of It can be in contact with the outer periphery. The fourth sealing member 1290d may be provided in front of the second sealing member 1290b (left side with reference to FIG. 1 ), and a second from the second reservoir flow path 1720 connected to the fifth hydraulic port 1280e. The flow of the pressurized medium transferred to the master chamber 1230a is allowed, but the flow of the pressurized medium transferred from the second master chamber 1230a to the fifth hydraulic port 1280e and the second reservoir flow path 1720 may be blocked. .

The master cylinder 1200 can ensure safety in the event of a component element failure by independently providing the first master chamber 1220a and the second master chamber 1230a, respectively. For example, the first master chamber 1220a may have any two wheel cylinders 21 among a right front wheel FR, a left front wheel FL, a left rear wheel RL, and a right rear wheel RR through a dump flow path 1610 to be described later. , 22), and the second master chamber 1230a may be connected to the other two wheel cylinders 23 and 24 through a backup flow path 1620 to be described later, and thus leak in any one chamber. It may be possible to brake the vehicle even when such a problem occurs.

The pedal simulator 1240 is provided between the first master piston 1220 and the second master piston 1230 , and may provide a feeling of pedaling of the brake pedal 10 to the driver by its own elastic restoring force. Specifically, the pedal simulator 1240 may be interposed between the front surface of the first master piston 1220 and the rear surface of the second master piston 1230, and may be made of an elastic material such as compressible and expandable rubber. . The pedal simulator 1240 includes a cylindrical body portion 1241 at least partially inserted and supported on the front surface of the first master piston 1220, and at least a portion inserted and supported on the rear surface of the second master piston 1230. It is supported and may include a tapered portion 1242 whose diameter is gradually expanded toward the front (left with reference to FIG. 1 ). At least a portion of both ends of the pedal simulator 1240 may be stably supported by being inserted into the first master piston 1220 , respectively. Furthermore, a stable and familiar pedal feeling may be provided to the driver by changing the elastic restoring force according to the degree of the pedaling force of the brake pedal 10 by the tapered portion 1241 .

A simulator valve 1711 may be provided in the first reservoir flow path 1710 to be described later to control the flow of the pressurized medium between the reservoir 1100 and the first master chamber 1220a. The simulator valve 1711 may be provided as a normally closed type solenoid valve that is normally closed and operates to open the valve when receiving an electrical signal from the electronic control unit, and the electronic brake system 1000 can be opened in the normal operating mode of

When the pedal simulation operation by the master cylinder 1200 is described, the driver operates the brake pedal 10 in the normal operation mode and at the same time dump valves are provided in the dump passage 1610 and the backup passage 1620, which will be described later, respectively. 1611 and the cut valve 1621 are closed, while the simulator valve 1711 of the first reservoir flow path 1710 is open. As the operation of the brake pedal 10 progresses, the first master piston 1220 moves forward, but as the cut valve 1621 closes, the second master chamber 1230a is sealed and the second master piston 1230 is closed. no displacement occurs. At this time, the pressurized medium accommodated in the first master chamber 1220a is introduced along the first reservoir flow path 1710 by the closing operation of the dump valve 1611 and the opening operation of the simulator valve 1711 . While the second master piston 1230 does not advance, the first master piston 1220 compresses the pedal simulator 1240 as the forward movement continues, and the elastic restoring force of the pedal simulator 1240 gives the pedal to the driver. It can be served as a persimmon. After that, when the driver releases the pedaling force of the brake pedal 10 , the first and second master pistons 1220 and 1230 are generated by the elastic restoring force of the first and second piston springs 1220b and 1230b and the pedal simulator 1240 . The pedal simulator 1240 may return to its original shape and position, and the first master chamber 1220a may be filled by supplying a pressurized medium from the reservoir 1100 through the first reservoir flow path 1710 .

As such, since the inside of the first master chamber 1220a and the second master chamber 1230a is always filled with a pressurized medium, friction between the first master piston 1220 and the second master piston 1230 during pedal simulation operation As this is minimized, the durability of the master cylinder 1200 can be improved, and the inflow of foreign substances from the outside can be blocked.

On the other hand, the master cylinder 1200 described in this embodiment is an example for helping understanding of the present invention, and is not limited to the corresponding structure, and includes two master chambers 1220a and 1230a, and each master chamber 1220a and 1230a are respectively connected to a dump flow path 1610 and a backup flow path 1620 to be described later, and during active braking such as ABS mode and TCS mode of the first hydraulic circuit 1510, the dump flow path 1610 and the first master As long as the hydraulic pressure of the pressurized medium can be discharged to the reservoir 1100 through the chamber 1220a, the same may be applied to the case of devices having various shapes and structures.

The reservoir 1100 may accommodate and store the pressurized medium therein. The reservoir 1100 may be connected to each component element such as the master cylinder 1200, a hydraulic pressure supply device 1300 to be described later, and a hydraulic circuit to be described later to supply or receive a pressurized medium. Although a plurality of reservoirs 1100 are shown with the same reference numerals in the drawings, this is an example for better understanding of the invention, and the reservoir 1100 is provided as a single component or as a plurality of separate and independent components can

The reservoir flow path 1700 is provided to connect the master cylinder 1200 and the reservoir 1100 .

The reservoir flow path 1700 includes a first reservoir flow path 1710 connecting the first master chamber 1220a and the reservoir 1100 and a second reservoir flow path connecting the second master chamber 1230a and the reservoir 1100 ( 1720) may be included. For this, one end of the first reservoir flow path 1710 communicates with the first master chamber 1220a by the first hydraulic port 1280a of the master cylinder 1200, and the other end communicates with the reservoir 1100, One end of the second reservoir flow path 1720 may communicate with the second master chamber 1230a through the fifth hydraulic port 1280e of the master cylinder 1200 , and the other end may communicate with the reservoir 1100 . In addition, as described above, the first reservoir flow path 1710 is provided with a simulator valve 1711 that opens and operates in the normal operation mode, and the reservoir 1100 and the first master chamber 1220a through the first reservoir flow path 1710 are provided. ), the flow of the pressurized medium can be controlled.

The hydraulic pressure supply device 1300 is provided to generate hydraulic pressure of the pressurized medium through mechanical operation by receiving the driver's braking intention as an electrical signal from the pedal displacement sensor 11 that detects the displacement of the brake pedal 10 .

The hydraulic pressure supply device 1300 includes a hydraulic pressure supply unit that provides the pressurized medium pressure transmitted to the wheel cylinder 20 , a motor (not shown) that generates a rotational force by an electrical signal of the pedal displacement sensor 11 , and the motor It may include a power conversion unit (not shown) that converts the rotational motion into a linear motion and transmits it to the hydraulic pressure providing unit.

The hydraulic pressure providing unit includes a cylinder block 1310 in which a pressurized medium is accommodated, a hydraulic piston 1320 accommodated in the cylinder block 1310, and a pressure chamber provided between the hydraulic piston 1320 and the cylinder block 1310 . It includes a sealing member 1350 for sealing the parts 1330 and 1340 and a driving shaft 1390 for transmitting the power output from the power conversion unit to the hydraulic piston 1320 .

The pressure chambers 1330 and 1340 are a first pressure chamber 1330 located in the front (left direction of the hydraulic piston 1320 with reference to FIG. 1) of the hydraulic piston 1320, and the rear of the hydraulic piston 1320 ( A second pressure chamber 1340 positioned in the right direction of the hydraulic piston 1320 with reference to FIG. 1 may be included. That is, the first pressure chamber 1330 is partitioned by the front surface of the cylinder block 1310 and the hydraulic piston 1320 and is provided so that the volume varies according to the movement of the hydraulic piston 1320 , and the second pressure chamber 1340 . ) is partitioned by the rear surface of the cylinder block 1310 and the hydraulic piston 1320 so that the volume varies according to the movement of the hydraulic piston 1320 .

A motor (not shown) is provided to generate a driving force of the hydraulic piston 1320 by an electrical signal output from the electronic control unit (ECU). The motor may be provided including a stator and a rotor, and may provide power for generating displacement of the hydraulic piston 1320 by rotating in a forward or reverse direction through this. The rotation angular speed and rotation angle of the motor can be precisely controlled by a motor control sensor (not shown), and the motor control sensor includes a motor and a hydraulic piston ( 1320) can be controlled. Since the motor is a well-known technology, a detailed description thereof will be omitted.

The power conversion unit (not shown) is provided to convert the rotational force of the motor into linear motion. The power conversion unit may be provided in a structure including, for example, a worm shaft (not shown), a worm wheel (not shown), and a drive shaft 1390 . The worm shaft may be integrally formed with the rotation shaft of the motor, and a worm may be formed on the outer circumferential surface to rotate the worm wheel by engaging with the worm wheel. The worm wheel is connected to engage the drive shaft 1390 to move the drive shaft 1390 in a straight line, and the drive shaft 1390 is connected to the hydraulic piston 1320, through which the hydraulic piston 1320 is the cylinder block 1310. It can be moved by sliding within.

In describing the above operations again, when a displacement of the brake pedal 10 is detected by the pedal displacement sensor 11, the detected signal is transmitted to the electronic control unit, and the electronic control unit drives the motor to move the worm shaft in one direction. rotate to The rotational force of the worm shaft is transmitted to the drive shaft 1390 via the worm wheel, and the hydraulic piston 1320 connected to the drive shaft 1390 advances in the cylinder block 1310 to generate hydraulic pressure in the first pressure chamber 1330. have.

Conversely, when the pedal effort of the brake pedal 10 is released, the electronic control unit drives the motor to rotate the worm shaft in the opposite direction. Accordingly, the worm wheel may also rotate in the opposite direction and the hydraulic piston 1320 connected to the drive shaft 1390 may generate negative pressure in the first pressure chamber 1330 while moving backward in the cylinder block 1310 .

The generation of hydraulic pressure and negative pressure in the second pressure chamber 1340 may be implemented by operating in opposite directions. That is, when displacement of the brake pedal 10 is detected by the pedal displacement sensor 11, the sensed signal is transmitted to the electronic control unit, and the electronic control unit drives the motor to rotate the worm shaft in the opposite direction. The rotational force of the worm shaft is transmitted to the drive shaft 1390 via the worm wheel, and the hydraulic piston 1320 connected to the drive shaft 1390 moves backward in the cylinder block 1310 to generate hydraulic pressure in the second pressure chamber 1340. have.

Conversely, when the pedal effort of the brake pedal 10 is released, the electronic control unit drives the motor in one direction to rotate the worm shaft in one direction. Accordingly, the worm wheel also rotates in the opposite direction and the hydraulic piston 1320 connected to the drive shaft 1390 advances in the cylinder block 1310 to generate negative pressure in the second pressure chamber 1340 .

As such, the hydraulic pressure supply device 1300 may generate hydraulic pressure or negative pressure in the first pressure chamber 1330 and the second pressure chamber 1340, respectively, depending on the rotation direction of the worm shaft by driving the motor. It can be determined by controlling the valves whether to implement the braking by using a negative pressure or to release the braking by using the negative pressure.

On the other hand, the power conversion unit according to an embodiment of the present invention is not limited to any one structure as long as it can convert the rotational motion of the motor into the linear motion of the hydraulic piston 1320, and the same applies even if it consists of devices of various structures and methods. will have to be understood

The hydraulic pressure supply device 1300 may be hydraulically connected to the reservoir 1100 by the hydraulic pressure dump unit 1800 . The hydraulic dump unit 1800 may control the flow of the pressurized medium between the first and second pressure chambers 1330 and 1340 and the reservoir 1100, respectively, and pressurize the hydraulic pressure supply device 1300 and the reservoir 1100. It may include a plurality of flow paths and various solenoid valves to control the flow of the medium. In addition, the hydraulic dump unit 1800 is connected to one end of an inspection flow path 1900 to be described later, and transfers the pressurized medium flowing from the inspection flow path 1900 to the reservoir 1100 or discharges it from the second pressure chamber 1340 . The pressurized medium may be transferred to the inspection flow path 1900 .

The hydraulic control unit 1400 may be provided to control the hydraulic pressure transmitted to each wheel cylinder 20 , and the electronic control unit (ECU) is configured to operate with the hydraulic pressure supply device 1300 and various types based on the hydraulic pressure information and the pedal displacement information. provided to control the valves.

The hydraulic control unit 1400 includes a first hydraulic circuit 1510 for controlling the flow of hydraulic pressure transmitted to the first and second wheel cylinders 21 and 22 among the four wheel cylinders 20, and the third and third A second hydraulic circuit 1520 for controlling the flow of hydraulic pressure transferred to the four wheel cylinders 23 and 24 may be provided, and a plurality of hydraulic pressures to control the hydraulic pressure transferred from the hydraulic pressure supply device 1300 to the wheel cylinder 20 of flow paths and valves.

The hydraulic control unit 1400 adjusts and controls the hydraulic pressure in the first pressure chamber 1330 formed by the forward movement of the hydraulic piston 1320 or the hydraulic pressure in the second pressure chamber 134 formed by the backward movement of the hydraulic piston 1320 . Thus, the first hydraulic circuit 1510 and the second hydraulic circuit 1520 may be provided. In addition, the hydraulic control unit 1400 is a negative pressure in the first pressure chamber 1330 formed by the backward movement of the hydraulic piston 1320 or the negative pressure of the second pressure chamber 134 formed by the forward movement of the hydraulic piston 1320. The pressurized medium provided to the first hydraulic circuit 1510 and the second hydraulic circuit 1520 may be recovered.

The first hydraulic circuit 1510 controls the hydraulic pressure applied to the first and second wheel cylinders 21 and 22, which are two wheel cylinders 20 among the four wheels RR, RL, FR, and FL, and The second hydraulic circuit 1520 may control hydraulic pressure applied to the third and fourth wheel cylinders 23 and 24 that are the other two wheel cylinders 20 .

The first hydraulic circuit 1510 supplies the hydraulic pressure provided from the hydraulic pressure supply device 1300 through the hydraulic control unit 1400 to the first wheel cylinder 21 and the second wheel cylinder 22, the first wheel cylinder It may be provided by branching into two inlet passages connected to (21) and the second wheel cylinder (22). Similarly, the second hydraulic circuit 1520 supplies the hydraulic pressure provided from the hydraulic pressure supply device 1300 through the hydraulic control unit 1400 to the third wheel cylinder 23 and the fourth wheel cylinder 24, the third It may be provided by branching into two inlet passages connected to the wheel cylinder 24 and the fourth wheel cylinder 24 .

The first and second hydraulic circuits 1510 and 1520 are provided with the first to fourth inlet valves 1511a to control the flow and hydraulic pressure of the pressurized medium delivered to the first to fourth wheel cylinders 21, 22, 23, and 24. , 1511b, 1521a, 1521b) may be provided, respectively. The first to fourth inlet valves 1511a, 1511b, 1521a, and 1521b are disposed in respective inlet passages connected to the upstream side of the first to fourth wheel cylinders 21, 22, 23, 24, and are normally open It may be provided as a solenoid valve of a normally open type that operates to close the valve when receiving an electrical signal from the electronic control unit.

The first inlet valve 1511a and the second inlet valve 1511b may be controlled to be open in an inspection mode to be described later. It is required to enlarge the volume in which the pressurized medium is accommodated in order to perform detailed control of the motor (not shown) even at a low target pressure when the hydraulic pressure of the hydraulic pressure supply device 1300 for performing the inspection mode is generated. Therefore, in the first inspection mode of the electromagnetic brake system 1000 to be described later, at least one of the first inlet valve 1511a and the second inlet valve 1511b is controlled to an open state and provided from the hydraulic pressure supply device 1300 . It is possible to increase the volume of the pressurized medium. On the other hand, the third inlet valve 1521a and the fourth inlet valve 1521b are controlled to be closed in the first inspection mode to prevent the hydraulic pressure provided from the hydraulic pressure supply device 1300 from leaking to the backup flow path 1620 side. , the speed and accuracy of the inspection mode can be promoted. A detailed description thereof will be provided later.

The first and second hydraulic circuits 1510 and 1520 are provided with first to fourth check valves 1513a, 1513b, and 1523a connected in parallel with respect to the first to fourth inlet valves 1511a, 1511b, 1521a, 1521b. , 1523b) may include. The check valves 1513a, 1513b, 1523a, 1523b are bypasses connecting the front and rear of the first to fourth inlet valves 1511a, 1511b, 1521a, 1521b on the first and second hydraulic circuits 1510 and 1520 It may be provided in the flow path, and allows only the flow of the pressurized medium from each wheel cylinder 20 to the hydraulic pressure supply device 1300 or the hydraulic control unit 1400 side, and from the hydraulic pressure supply device 1300 or the hydraulic control unit 1400 . The flow of the pressurized medium to the wheel cylinder 20 may be blocked. The first to fourth check valves 1513a, 1513b, 1523a, and 1523b can quickly release the hydraulic pressure of the pressurized medium applied to each wheel cylinder 20, and the first to fourth inlet valves 1511a, 1511b, Even when 1521a and 1521b do not operate normally, the hydraulic pressure of the pressurized medium applied to the wheel cylinder 20 may be smoothly recovered to the hydraulic pressure supply device 1300 .

The second hydraulic circuit 1520 directly applies the pressurized medium from the third and fourth wheel cylinders 23 and 24 to the reservoir 1100 to improve performance when the third and fourth wheel cylinders 23 and 24 are released. It may be provided with first and second outlet flow paths 1525 and 1526 for discharging to the . The first outlet flow path 1525 has an upstream end connected to the third wheel cylinder 23 and a downstream end directly connected to the reservoir 1100, so that the pressurized medium applied to the third wheel cylinder 23 when braking is released. may be directly discharged to the reservoir 1100 . Similarly, the upstream end of the second outlet flow path 1526 is connected to the fourth wheel cylinder 24 and the downstream end is directly connected to the reservoir 1100, so that when braking is released, the The pressurized medium may be directly discharged to the reservoir 1100 .

First and second outlet valves 1522a and 1522b for controlling the flow of the pressurized medium may be provided in the first and second outlet passages 1525 and 1526, respectively. The first and second outlet valves 1522a and 1522b control the flow of the pressurized medium transferred from the third and fourth wheel cylinders 23 and 24 to the reservoir 1100, respectively. The first and second outlet valves 1522a and 1522b may be provided as normally closed type solenoid valves that are normally closed and operate to open the valves when receiving an electrical signal from the electronic control unit. .

The first and second outlet valves 1522a and 1522b are the third wheel cylinder 23 and the fourth wheel cylinder when active braking is performed such as in an anti-lock brake system (ABS) mode or a traction control system (TCS) mode of the vehicle. The opening operation can be selectively controlled to individually reduce the hydraulic pressure of the pressurized medium applied to (24). That is, during active braking, the third wheel cylinder 23 of the second hydraulic circuit 1520 forms a discharge passage to the reservoir 1100 by the first outlet passage 1525 provided with the first outlet valve 1522a, and , the fourth wheel cylinder 24 of the second hydraulic circuit 1520 may form a discharge passage to the reservoir 1100 by the second outlet passage 1525 provided with the second outlet valve 1522b.

On the other hand, the first hydraulic circuit 1510 includes a dump flow path 1610 from the first and second wheel cylinders 21 and 22 to improve performance when the brakes of the first and second wheel cylinders 21 and 22 are released, A discharge flow path to the reservoir 1100 may be formed via a bypass dump flow path 1630 to be described later, and a first master chamber 1220a and a first reservoir flow path 1710 .

The dump flow path 1610 has one end connected to the first master chamber 1220a, and the other end connected to the downstream side of the first and second inlet valves 1511a and 1511b on the first hydraulic circuit 1510 by being branched and connected. , whereby the pressurized medium applied to the first wheel cylinder 21 during active braking is applied to a dump flow path 1610 , a bypass dump flow path 1630 to be described later, a first master chamber 1220a and a first reservoir flow path 1710 . ) may be sequentially discharged to the reservoir 1100 . Similarly, when active braking is performed, the pressurized medium applied to the second wheel cylinder 22 includes a dump flow path 1610 , a bypass dump flow path 1630 to be described later, a first master chamber 1220a and a first reservoir flow path 1710 . may be sequentially discharged to the reservoir 1100 . In addition, the dump passage 1610 may perform emergency braking by transferring the pressurized medium accommodated in the first master chamber 1220a to the first and second wheel cylinders 21 and 22 in a fallback mode to be described later.

At least one dump valve 1611 for controlling the flow of the pressurized medium in both directions may be provided in the dump passage 1610 . Specifically, the other end of the dump flow path 1610 is branched and connected to the downstream sides of the first and second inlet valves 1511a and 1511b, respectively, and the first dump valve 1611 is connected to the first wheel cylinder 21 and the dump The first dump valve 1611a for controlling the flow of the pressurized medium between the flow passages 1610 and the second dump valve 1611b for controlling the flow of the pressurized medium between the second wheel cylinder 22 and the dump passage 1610 are provided. may include

At least one dump valve 1611a, 1611b of the first dump valve 1611a and the second dump valve 1611b normally operates to open when receiving an electrical signal from the electronic control unit after being normally closed. It may be provided as a normally closed type solenoid valve. For example, as shown in FIG. 1 , the second dump valve 1611b is provided as a normally closed type solenoid valve, and maintains a closed state in the normal operation mode of the electronic brake system 1000, but the vehicle's ABS (Anti -lock Brake System) mode, TCS (Traction Control System) mode, etc., when performing active braking, may be opened to independently reduce the hydraulic pressure of the pressurized medium applied to the second wheel cylinder 22 .

On the other hand, when the electronic brake system 1000 cannot operate normally due to a malfunction of the device, the pressurized medium discharged from the master cylinder 1200 is directly supplied to the first hydraulic circuit 1510 to implement braking. This is called an abnormal operation mode, that is, a fallback mode. 2 is an inlet circuit diagram showing a state in which the electronic brake system according to the present embodiment performs a fallback mode. Referring to FIG. 2 , the pressurized medium accommodated in the first master chamber 1220a in the fallback mode is the first Since it must be able to be supplied to the hydraulic circuit 1510 side, the first dump valve 1611a is normally open and operates to close the valve when it receives a closing signal from the electronic control unit. It may be provided as a solenoid valve. As the first dump valve 1611a is provided as a normally open type solenoid valve, it is switched to a closed state in the normal operation mode of the electronic brake system 1000, but can maintain an open state in the fallback mode, and also performs active braking The opening operation may be performed to independently reduce the hydraulic pressure of the pressurizing medium applied to the first wheel cylinder 21 .

Accordingly, during active braking, the first wheel cylinder 21 of the first hydraulic circuit 1510 includes a dump flow path 1610 provided with a first dump valve 1611a, a bypass dump flow path 1630 to be described later, and a first master A discharge flow path to the reservoir 1100 is formed by sequentially passing through the chamber 1220a and the first reservoir flow path 1710 , and the second wheel cylinder 22 of the first hydraulic circuit 1510 has a second dump valve 1611b ) provided with a dump flow path 1610, a bypass dump flow path 1630 to be described later, and a first master chamber 1220a and a first reservoir flow path 1710 sequentially to form an exhaust flow path to the reservoir 1100. can

A flow passage orifice 1615 to be described later may be provided in the dump passage 1610 , and a bypass dump passage 1630 connecting the front and rear ends thereof may be provided. A detailed description thereof will be provided later.

As described above, when normal operation of the electronic brake system 1000 is impossible due to a device failure, etc., the pressurized medium discharged from the master cylinder 1200 is directly supplied to the second hydraulic circuit 1520 to perform emergency braking. should be able to To this end, a backup flow path 1620 for transferring the pressurized medium discharged from the master cylinder 1200 to the second hydraulic circuit may be provided.

The backup flow path 1620 may be provided to connect the second master chamber 1230a of the master cylinder 1200 and the second hydraulic circuit 1520 . The backup flow path 1620 may have one end connected to the second master chamber 1230a and the other end connected between the fourth inlet valve 1521b and the second outlet valve 1522b on the second hydraulic circuit 1520 . However, the connection position is not limited thereto, and the other end of the backup flow path 1620 may be branched and connected to at least one of the upstream sides of the first outlet valve 1522a and the second outlet valve 1522b.

A cut valve 1621 for controlling the flow of the pressurized medium in both directions may be provided in the backup flow path 1620 . The cut valve 1621 may be provided as a normal open type solenoid valve that is normally open and operates to close when a closing signal is received from the electronic control unit. When the cut valve 1621 is closed, the pressurized medium of the master cylinder 1200 is prevented from being directly transmitted to the second hydraulic circuit 1520, and at the same time, the hydraulic pressure provided from the hydraulic pressure supply device 1300 is applied to the master cylinder ( 1200) to prevent leakage to the side.

Meanwhile, referring to FIGS. 1 and 2 , in the fallback mode, the first hydraulic circuit 1510 receives the pressurized medium accommodated in the first master chamber 1220a through the dump passage 1610 to perform emergency braking, and the second The hydraulic circuit 1520 receives the pressurized medium accommodated in the second master chamber 1230a through the backup flow path 1620 to perform emergency braking. At this time, in the case of the dump flow path 1610, the pressurized medium is transmitted from the first master chamber 1220a to the first hydraulic circuit 1510 along a pipe having a constant diameter or flow path cross-sectional area, while the backup flow path 1620 is cut As the valve 1621 is provided, the pressurized medium is transferred from the second master chamber 1230a to the second hydraulic circuit 1520 via the orifice inside the cut valve 1621 . Accordingly, when the orifice diameter or cross-sectional area of the cut valve 1621 is smaller than the diameter or cross-sectional area of the dump passage 1610, the flow of the pressurized medium is stagnated by the reduced cross-sectional area of the passage and applied to the second hydraulic circuit 1520. There is a fear that the hydraulic pressure value is smaller than the hydraulic pressure value applied to the first hydraulic circuit 1510 or that the hydraulic pressure for braking is relatively delayed. This causes an imbalance in hydraulic pressure between the wheel cylinders 21 , 22 , 23 , and 24 to impair the safety of the vehicle's behavior and reduce operability, thereby causing a safety accident.

Accordingly, the electronic brake system 1000 according to the present embodiment prevents the hydraulic pressure deviation between the first hydraulic circuit 1510 and the second hydraulic circuit 1520 in the fallback mode, and the plurality of wheel cylinders 21, 22, 23, 24 ) includes a flow path orifice 1615 for balancing the braking pressure between them.

The flow path orifice 1615 may be provided in the dump flow path 1610 connecting the first master chamber 1220a and the first hydraulic circuit 1510, and the diameter or cross-sectional area of the flow path orifice 1615 is the cut valve 1621. It may be provided to correspond to the diameter or cross-sectional area of the orifice provided in the . As a result, the flow of the pressurized medium transferred from the second master chamber 1230a to the second hydraulic circuit 1520 through the backup passage 1620 passes through the orifice of the cut valve 1620 and stagnates as much as the first hydraulic pressure level. The flow of the pressurized medium transferred from the master chamber 1220a to the first hydraulic circuit 1510 through the dump passage 1610 also passes through the passage orifice 1615 and causes stagnation or delay, thereby causing the first hydraulic circuit 1510 and It is possible to suppress and compensate for the hydraulic pressure deviation of the second hydraulic circuit 1520 .

In this case, the first and second dump valves 1611a and 1611a so that the flow of the pressurized medium is not stagnated by the orifices provided in the first dump valve 1611a and the second dump valve 1611b provided in the dump flow path 1610; The diameter or cross-sectional area of the orifice provided in 1611b) may correspond to or larger than the diameter or cross-sectional area of the flow passage orifice 1615 .

In addition, when the fallback mode operates while the second dump valve 1611b is closed, the hydraulic pressure of the pressurized medium passes through the first inlet valve 1511a and the second inlet valve 1511b to the second wheel cylinder 22 ), the diameter or cross-sectional area of the orifices provided in the first and second inlet valves 1511a and 1511b may also correspond to or be larger than the diameter or cross-sectional area of the flow passage orifice 1615 . In the same technical context, even in the case of the second hydraulic circuit 1520, the hydraulic pressure of the pressurized medium is transmitted to the third wheel cylinder 23 via the fourth inlet valve 1521b and the third inlet valve 1521a, The diameter or cross-sectional area of the orifices provided in the third and fourth inlet valves 1521a and 1521b is the cut valve so that additional stagnation of the pressurized medium flow does not occur due to the orifices provided in the third and fourth inlet valves 1521a and 1521b. It may be provided corresponding to or larger than the diameter or cross-sectional area of the orifice provided in 1620 .

On the other hand, as described above, the dump flow path 1610 supplies the pressurized medium accommodated in the first master chamber 1220a to the first hydraulic circuit 1510 in the fallback mode to perform emergency braking while performing emergency braking. During active braking, such as in ABS mode and TCS mode, it also serves as a discharge flow path for the pressurized medium applied to the first hydraulic circuit 1510 . In the second hydraulic circuit 1520, as the third and fourth wheel cylinders 23 and 24 are directly connected to the reservoir 1100 by the first and second outlet passages 1525 and 1526, the hydraulic pressure of the pressurized medium is Although it can be smoothly discharged and decompressed, in the case of the first hydraulic circuit 1520, as described above, some of the flow of the pressurized medium is intentionally stagnated or There may be a delay, and accordingly, there is a risk that a hydraulic pressure deviation between the first hydraulic circuit 1510 and the second hydraulic circuit 1520 may occur during active braking.

Accordingly, the electromagnetic brake system 1000 according to the present embodiment prevents hydraulic pressure deviation between the first hydraulic circuit 1510 and the second hydraulic circuit 1520 during active braking, and includes a plurality of wheel cylinders 21, 22, 23, 24) A bypass dump flow path 1630 and an outlet check valve 1631 are included for balancing the braking pressure between them.

3 is a hydraulic circuit diagram illustrating a state in which the electronic brake system according to the present embodiment performs active braking.

1 to 3 , the dump flow path 1630 includes a bypass dump flow path 1630 to more smoothly discharge the pressurized medium from the first hydraulic circuit 1510 to the first master chamber 1220a. include The bypass dump flow path 1630 has one end branched from the front end of the flow path orifice 1615 on the dump flow path 1610 , and the other end joins the rear end of the flow path orifice 1615 on the dump flow path 1610 . ) can be bypassed. In addition, an outlet check valve 1631 may be provided in the bypass dump flow path 1630 , and the outlet check valve 1631 is the flow of the pressurized medium from the first hydraulic circuit 1510 to the first master chamber 1220a. only, the flow of the pressurized medium from the first master chamber 1220a to the first hydraulic circuit 1510 may be blocked.

The sum of the cross-sectional area of the orifice provided in the outlet check valve 1631 and the cross-sectional area of the flow passage orifice 1615 may be provided to correspond to the flow passage cross-sectional area of the first outlet flow passage 1525 or the flow passage cross-sectional area of the second outlet flow passage 1526 have. In other words, since the cross-sectional area of the discharge passage of the first hydraulic circuit 1510 is smaller than the cross-sectional area of the discharge passage of the second hydraulic circuit 1520 by the passage orifice 1615 , the difference in the cross-sectional area is calculated as the orifice of the outlet check valve 1631 . to compensate, the orifice cross-sectional area of the outlet check valve 1631 is the flow passage cross-sectional area of the first outlet passage 1525 that is the discharge passage of the second hydraulic circuit 1520 or the passage orifice in the passage cross-sectional area of the second outlet passage 1526 (1615) minus the cross-sectional area. Accordingly, it is possible to suppress the hydraulic pressure deviation between the first hydraulic circuit 1510 and the second hydraulic circuit 1520 during active braking.

For example, as shown in FIG. 3 , when selective pressure reduction of the first wheel cylinder 21 and the third wheel cylinder 23 is required for active braking, the third wheel cylinder 23 is connected to the first outlet flow path. At least a portion of the hydraulic pressure of the pressurized medium may be discharged to the reservoir 1100 through 1525 , and the first wheel cylinder 21 may pass through the dump passage 1630 and the bypass dump passage 1631 to provide hydraulic pressure of the pressurized medium. At least a part of it may be discharged to the reservoir 1100, and in this case, the flow passage cross-sectional area of the first outlet passage 1525 corresponds to the sum of the cross-sectional area of the orifice of the outlet check valve 1631 and the cross-sectional area of the passage orifice 1611, so that the first The hydraulic pressure difference between the hydraulic circuit 1510 and the second hydraulic circuit 1520 can be suppressed, and hydraulic pressure can be balanced.

In this case, the orifices provided in the first and second outlet valves 1522a and 1522b so that the flow of the pressurized medium is not stagnated or delayed by the orifices provided in the first outlet valve 1522a and the second outlet valve 1522b. The diameter or cross-sectional area of the ? may be provided to correspond to or larger than the flow passage cross-sectional area of the first and second outlet passages 1525 and 1526 . In addition, the first reservoir so that the flow of the pressurized medium is not stagnated or delayed by the orifice provided in the first reservoir flow path 1710 forming the discharge flow path of the first hydraulic circuit 1510 and the simulator valve 1711 provided thereto. The flow passage cross-sectional area of the flow passage 1710 and the orifice cross-sectional area of the simulator valve 1711 may correspond to or larger than the flow passage cross-sectional areas of the first and second outlet passages 1525 and 1526 .

The inspection flow path 1900 is provided to connect the master cylinder 1200 and the hydraulic pressure supply device 1300 , and is provided to inspect whether various components mounted on the master cylinder 1200 and the simulator valve 1711 leak.

The inspection flow path 1900 has one end connected to the hydraulic pressure supply device 1300 through the hydraulic dump unit 1800, and the other end connected to the first master chamber 1220a, a first branch flow path 1910 and a second branch flow path. Branched to 1920, it may be respectively connected to the third hydraulic port 1280c and the fourth hydraulic port 1280d. A check valve 1901 for controlling the flow of the pressurized medium in both directions may be provided in the first branch flow path 1910 , and the hydraulic pressure dump unit 1800 from the first master chamber 1220a in the second branch flow path 1920 . A check check valve 1921 that allows only the flow of the pressurized medium to and blocks the flow of the pressurized medium in the opposite direction may be provided. The inspection valve 1901 may be provided as a normally closed type solenoid valve that is normally closed and operates to open when an electrical signal is received from the electronic control unit. Opening and closing operations of the inspection valve 1901 may be controlled according to the inspection mode of the electronic brake system 1000 .

The electromagnetic brake system 1000 includes a first pressure sensor PS1 for detecting the hydraulic pressure of the pressurized medium provided by the hydraulic pressure supply device 1300 and a second pressure sensor for detecting the hydraulic pressure in the second master chamber 1230a ( PS2). The first pressure sensor PS1 is provided on the side of the first hydraulic circuit 1510 to detect the hydraulic pressure of the pressurized medium generated and provided from the hydraulic pressure supply device 1300 in the inspection mode and delivered to the first hydraulic circuit 1510. The second pressure sensor PS2 is provided between the second master chamber 1230a and the cut valve 1621 on the backup flow path 1620 to detect the hydraulic pressure of the pressurized medium accommodated in the second master chamber 1230a. have. In the inspection mode, the information on the pressure value of the pressurized medium sensed by the first pressure sensor PS1 and the second pressure sensor PS2 may be transmitted to the electronic control unit, and the electronic control unit operates from the first pressure sensor PS1. Whether the master cylinder 1200 or the simulator valve 1711 is leaking may be determined by comparing the detected hydraulic pressure value and the hydraulic pressure value detected by the second pressure sensor PS2. In addition, the electronic brake system 1000 may include a stroke sensor (not shown) for measuring the displacement amount of the hydraulic piston 1320 of the hydraulic pressure supply device 1300, and the stroke sensor includes information on the displacement amount of the hydraulic piston 1320 in the inspection mode. It is possible to inspect whether the master cylinder 1200 is leaking based on the .

1000: electronic brake system
1100: reservoir 1200: master cylinder
1220: first master piston 1220a: first master chamber
1230: second master piston 1230a: second master chamber
1240: pedal simulator 1300: hydraulic supply
1400: hydraulic control unit 1510: first hydraulic circuit
1520: second hydraulic circuit 1610: dump passage
1611: dump valve 1620: backup flow path
1621: cut valve 1630: bypass dump flow path
1631: outlet check valve 1900: inspection flow path

Claims (8)

a reservoir in which the pressurized medium is stored;
A first master piston connected to a brake pedal, a first master chamber whose volume is changed by displacement of the first master piston, and displacement by a displacement of the first master piston or a pressurizing medium accommodated in the first master chamber a master cylinder including a second master piston that is operably provided, and a second master chamber whose volume is changed by displacement of the second master piston;
a reservoir passage connecting the reservoir and the first master chamber;
a hydraulic pressure supply device for generating hydraulic pressure by operating a hydraulic piston according to an electrical signal output in response to the displacement of the brake pedal;
a first hydraulic circuit for controlling hydraulic pressures of the first wheel cylinder and the second wheel cylinder;
a second hydraulic circuit for controlling hydraulic pressures of the third wheel cylinder and the fourth wheel cylinder;
a backup passage connecting the second master chamber and the second hydraulic circuit;
a cut valve provided in the backup passage to control the flow of the pressurized medium;
a dump passage connecting the first master chamber and the first hydraulic circuit; and
and a flow path orifice provided in the dump flow path to generate stagnation of the pressurized medium on the dump flow path corresponding to the stagnation of the pressurized medium generated while the pressurized medium on the backup flow passage passes through the cut valve. According to claim 1,
The diameter or cross-sectional area of the flow path orifice is
An electromagnetic brake system corresponding to a diameter or cross-sectional area of an orifice provided in the cut valve. According to claim 1,
The dump path
A bypass dump passage having one end connected to the front end of the passage orifice on the dump passage and the other end connected to the rear end of the passage orifice on the dump passage,
The electronic brake system further comprising an outlet check valve provided in the bypass dump passage and allowing only the flow of the pressurized medium from the first hydraulic circuit to the first master chamber. 4. The method of claim 3,
The first hydraulic circuit is
forming an exhaust passage by connecting the first and second wheel cylinders to the reservoir via the dump passage, the bypass dump passage, the first master chamber, and the reservoir passage;
The second hydraulic circuit is
A discharge flow path is formed by first and second outlet flow paths that directly connect the third and fourth wheel cylinders to the reservoir, respectively,
The sum of the cross-sectional area of the orifice provided in the outlet check valve and the cross-sectional area of the flow passage orifice is
An electromagnetic brake system corresponding to a flow passage cross-sectional area of the first outlet flow passage or a flow passage cross-sectional area of the second outlet flow passage. 5. The method of claim 2 or 4,
The electronic brake system further comprising at least one dump valve provided in the dump passage to control the flow of the pressurized medium. 6. The method of claim 5,
The dump valve is
a first dump valve for controlling the flow of the pressurized medium between the first wheel cylinder and the dump flow path;
and a second dump valve for controlling a flow of the pressurized medium between the second wheel cylinder and the dump passage. 7. The method of claim 6,
Any one of the first dump valve and the second dump valve
An electronic brake system provided with a normally closed type solenoid valve that is normally closed and opens when an electric signal is received from the electronic control unit. 6. The method of claim 5,
The diameter or cross-sectional area of the orifice provided in the dump valve is
An electromagnetic brake system provided to be larger than a diameter or a cross-sectional area of the flow passage orifice.

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