KR20200127501A - Electric brake system and Operating method of thereof - Google Patents

Abstract

Disclosed is an electronic brake system capable of reducing the number of applied parts and achieving miniaturization and weight reduction of products. According to an embodiment of the present invention, the electronic brake system comprises: a reservoir in which a pressurizing medium is stored; an integrated master cylinder having a master chamber and a simulation chamber; a reservoir flow path for allowing the integrated master cylinder to communicate with the reservoir; a hydraulic pressure supply device that generates hydraulic pressure by operating a hydraulic piston by an electrical signal output in response to displacement of a brake pedal, and includes a first pressure chamber provided on one side of the hydraulic piston movably accommodated in a cylinder block and connected to one or more wheel cylinders, and a second pressure chamber provided on the other side of the hydraulic piston and connected to one or more wheel cylinders; a hydraulic pressure control part having a first hydraulic circuit for controlling hydraulic pressure transmitted to the two wheel cylinders and a second hydraulic circuit for controlling hydraulic pressure transmitted to the other two wheel cylinders; and an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal.

Description

TECHNICAL FIELD [0001] Electric brake system and operating method of thereof

The present invention relates to an electronic brake system and a method of operating the same, and more particularly, to an electronic brake system for generating a braking force using an electric signal corresponding to a displacement of a brake pedal, and a method of operating the same.

Vehicles are essentially equipped with a brake system for performing braking, and various types of brake systems have been proposed for the safety of drivers and passengers.

In the conventional brake system, when the driver presses the brake pedal, a method of supplying hydraulic pressure required for braking to a wheel cylinder using a mechanically connected booster is mainly used. However, as the demand of the market to implement various braking functions in detail in response to the operating environment of the vehicle is increasing, recently, when the driver presses the brake pedal, the driver's braking will is electrically controlled from a pedal displacement sensor that senses the displacement of the brake pedal. An electronic brake system that receives a signal and operates a hydraulic pressure supply device based on this to supply hydraulic pressure required for braking to a wheel cylinder has been widely spread.

In such an electronic brake system, the driver's brake pedal operation is generated and provided as an electrical signal in the normal operation mode, and based on this, the hydraulic pressure supply device is electrically operated and controlled to form the hydraulic pressure required for braking and transmit it to the wheel cylinder. As described above, since these electronic brake systems and operating methods are electrically operated and controlled, they can implement complex and various braking actions, but when a technical problem occurs in an electrical component element, the hydraulic pressure required for braking is not stably formed. There is a risk of threatening the safety of passengers.

Therefore, the electronic brake system enters an abnormal operation mode when a component element fails or is in a state of inability to control. In this case, a mechanism in which the driver's brake pedal operation is directly linked to the wheel cylinder is required. In other words, in the abnormal operation mode of the electronic brake system, the hydraulic pressure required for braking is immediately formed as the driver applies a pedal effort to the brake pedal, and it must be transmitted directly to the wheel cylinder.

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

The present embodiment aims to provide an electronic brake system capable of reducing the number of applied parts and achieving miniaturization and weight reduction of products.

The present embodiment is to provide an electronic brake system capable of effectively implementing braking even in various operating situations.

The present embodiment is to provide an electronic brake system capable of stably generating a high-pressure braking pressure.

The present embodiment is to provide an electronic brake system with improved performance and operational reliability.

The present embodiment is to provide an electronic brake system with improved durability of a product by reducing a load applied to a component element.

The present embodiment is to provide an electronic brake system capable of improving product assembly and productivity while reducing manufacturing cost of products.

According to an aspect of the present invention, an integrated master cylinder having a reservoir storing a pressurized medium, a master chamber, and a simulation chamber, a reservoir flow path communicating the integrated master cylinder and the reservoir, and output corresponding to the displacement of the brake pedal The hydraulic piston is operated by an electrical signal to generate hydraulic pressure, but is provided on one side of the hydraulic piston that is movably accommodated in the cylinder block and is provided on the first pressure chamber connected to one or more wheel cylinders and the other side of the hydraulic piston. A hydraulic pressure supply device including a second pressure chamber connected to one or more wheel cylinders, a first hydraulic circuit controlling hydraulic pressure delivered to two wheel cylinders, and a second hydraulic circuit controlling hydraulic pressure delivered to two other wheel cylinders And an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal, wherein the hydraulic control unit includes a first hydraulic flow passage in communication with the first pressure chamber, and the A second hydraulic flow path in communication with the second pressure chamber, a third hydraulic flow path where the first hydraulic flow path and the second hydraulic flow path merge, and a third hydraulic flow path branched from the third hydraulic flow path and connected to the first hydraulic circuit. 4 a hydraulic flow path, a fifth hydraulic flow path branched from the third hydraulic flow path and connected to the second hydraulic circuit, a sixth hydraulic flow path in communication with the first hydraulic circuit, and a first hydraulic flow path in communication with the second hydraulic circuit. A 7 hydraulic flow path, an eighth hydraulic flow path where the sixth hydraulic flow path and the seventh hydraulic flow path merge, a ninth hydraulic flow path branched from the eighth hydraulic flow path and connected to the first pressure chamber, and the eighth It may be provided including a tenth hydraulic flow path branched from the hydraulic flow path and connected to the second pressure chamber.

The hydraulic control unit includes a first valve provided in the first hydraulic passage to control the flow of the pressurized medium, a second valve provided in the second hydraulic passage to control the flow of the pressurized medium, and provided in the fourth hydraulic passage A third valve for controlling the flow of the pressurized medium, a fourth valve provided in the fifth hydraulic passage to control the flow of the pressurized medium, a fifth valve provided in the sixth hydraulic passage to control the flow of the pressurized medium, A sixth valve provided in the seventh hydraulic passage to control the flow of the pressurized medium, a seventh valve provided in the ninth hydraulic passage to control the flow of the pressurized medium, and a flow of the pressurized medium provided in the tenth hydraulic passage It may be provided including an eighth valve to control.

The first valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the first pressure chamber, and the second valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the second pressure chamber The third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic flow path to the first hydraulic circuit, and the fourth valve is from the third hydraulic flow path to the second hydraulic circuit. It is provided as a check valve that allows only the flow of the pressurized medium toward, the fifth valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the first hydraulic circuit, and the sixth valve is the second hydraulic circuit It is provided as a check valve that allows only the flow of the pressurized medium discharged from, and the seventh valve and the eighth valve may be provided as solenoid valves that control the flow of the pressurized medium in both directions.

The simulation chamber includes a first simulation chamber and a second simulation chamber, and the integrated master cylinder is provided in the master chamber, a master piston disposed to be displaceable by a brake pedal, and a master piston provided in the first simulation chamber, The first simulation piston provided to be displaceable by the displacement of the master piston or the hydraulic pressure of the pressurized medium accommodated in the master chamber, and the displacement of the first simulation piston provided in the second simulation chamber or of the first simulation chamber. A second simulation piston provided to be displaceable by hydraulic pressure, an elastic member provided between the first simulation piston and the second simulation piston, a simulation flow path connecting the first simulation chamber and the reservoir, and the simulation A simulator valve provided in the flow path to control the flow of the pressurized medium may be provided.

A first backup passage connecting the master chamber and the first hydraulic circuit, a second backup passage connecting the first simulation chamber and the second hydraulic circuit, and connecting the second simulation chamber and the second backup passage It may be provided further comprising an auxiliary backup passage and an inspection valve provided in the auxiliary backup passage to control the flow of the pressurized medium.

A first cut valve provided in the first backup passage to control the flow of the pressurized medium, and at least one second cut valve provided in the second backup passage to control the flow of the pressurized medium may be provided.

Further comprising a dump control unit provided between the reservoir and the hydraulic pressure supply device to control the flow of the pressurized medium, wherein the dump control unit comprises a first dump passage connecting the first pressure chamber and the reservoir, and the first dump passage A first dump check valve that is provided in and allows only the flow of the pressurized medium from the reservoir to the first pressure chamber, and a first bypass flow path connected in parallel to the first dump check valve on the first dump flow path , A first dump valve provided in the first bypass flow path to control the flow of the pressurized medium in both directions, a second dump flow path connecting the second pressure chamber and the reservoir, and the reservoir provided in the second dump flow path A second dump check valve allowing only the flow of the pressurized medium from the second pressure chamber to the second pressure chamber, a second bypass flow path connected in parallel to the second dump check valve on the second dump flow path, and the second It may be provided including a second dump valve provided in the bypass flow path to control the flow of the pressurized medium in both directions.

The first hydraulic circuit includes a first inlet valve and a second inlet valve respectively controlling the flow of the pressurized medium supplied to the first wheel cylinder and the second wheel cylinder, and the first wheel cylinder and the second wheel cylinder. It includes a first outlet valve and a second outlet valve respectively controlling the flow of the pressurized medium discharged to the reservoir, and the second hydraulic circuit controls the flow of the pressurized medium supplied to the third wheel cylinder and the fourth wheel cylinder, respectively. And a third inlet valve and a fourth inlet valve, and the second backup passage may be provided to connect at least one of downstream sides of the third and fourth inlet valves to the first simulation chamber.

The reservoir flow path includes a first reservoir flow path connecting the reservoir and the master chamber, a second reservoir flow path connecting the reservoir and the first simulation chamber, and a third reservoir connecting the reservoir and the second simulation chamber. It may be provided including a flow path.

It is provided in the second reservoir flow path, the reservoir valve may be provided to allow only the flow of the pressurized medium from the reservoir to the first simulation chamber.

The integrated master cylinder may include a piston spring elastically supporting the master piston, a first simulator spring elastically supporting the first simulation piston, and a second simulator spring elastically supporting a second simulation piston. .

In the normal operation mode, the first cut valve is closed to seal the master chamber, the inspection valve is closed to seal the second simulation chamber, and the second cut valve is closed but the simulator valve is opened to By communicating the first simulation chamber and the reservoir, the first simulation piston compresses the elastic member by the operation of the brake pedal, and the elastic restoring force of the elastic member can be provided to the driver as a pedal feel.

In the normal operation mode, as the hydraulic pressure of the pressurized medium transferred from the hydraulic pressure supply device to the wheel cylinder gradually increases, a first braking mode primarily provides hydraulic pressure, and a second braking mode secondarily provides hydraulic pressure. It may be provided including a mode, and a third braking mode that thirdly provides hydraulic pressure.

In the first braking mode, the eighth valve and the first dump valve are closed, and the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston is applied to the first hydraulic channel, the third hydraulic channel, and the third hydraulic channel. It may be provided to the first hydraulic circuit sequentially through 4 hydraulic channels, and may be provided to the second hydraulic circuit sequentially through the first hydraulic channel, the third hydraulic channel, and the fifth hydraulic channel.

In the second braking mode, the seventh valve and the second dump valve are closed, and after the first braking mode, the hydraulic pressure formed in the second pressure chamber by the backward movement of the hydraulic piston is applied to the second hydraulic flow path and the second dump valve. Provided to the first hydraulic circuit through the 3 hydraulic flow path and the fourth hydraulic flow path sequentially, and provided to the second hydraulic circuit through the second hydraulic flow path, the third hydraulic flow path, and the fifth hydraulic flow path sequentially Can be.

In the third braking mode, the seventh valve and the seventh valve are opened, the first dump valve and the second dump valve are closed, and the hydraulic pressure formed in the first pressure chamber is applied by advancing the hydraulic piston. Some are provided to the first hydraulic circuit sequentially through the first hydraulic channel, the third hydraulic channel, and the fourth hydraulic channel, and the first hydraulic channel, the third hydraulic channel, and the fifth hydraulic channel are connected to each other. It is provided to the second hydraulic circuit sequentially, and the remaining part of the hydraulic pressure formed in the first pressure chamber may be supplied to the second pressure chamber sequentially through the ninth hydraulic flow path and the tenth hydraulic flow path.

When the first braking mode is released, the seventh valve and the second dump valve are opened, the eighth valve and the first dump valve are closed, and a negative pressure is applied to the first pressure chamber by reversing the hydraulic piston. Formed, the pressurizing medium provided in the first hydraulic circuit is recovered to the first pressure chamber through the sixth hydraulic flow path, the eighth hydraulic flow path, and the ninth hydraulic flow path sequentially, and the second hydraulic circuit The provided pressurized medium may be recovered to the first pressure chamber through the seventh hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage sequentially.

When the second braking mode is released, the eighth valve and the first dump valve are opened, the seventh valve and the second dump valve are closed, and negative pressure in the second pressure chamber by the advance of the hydraulic piston. And the pressurizing medium provided in the first hydraulic circuit is recovered to the second pressure chamber through the sixth hydraulic flow path, the eighth hydraulic flow path, and the tenth hydraulic flow path sequentially, and the second hydraulic circuit The provided pressurized medium may be recovered to the second pressure chamber through the seventh hydraulic passage, the eighth hydraulic passage, and the tenth hydraulic passage sequentially.

When the third braking mode is released, the seventh valve and the eighth valve are opened, the first dump valve is closed, and a negative pressure is formed in the first pressure chamber by reversing the hydraulic piston. 1 The pressurizing medium provided in the hydraulic circuit is recovered to the first pressure chamber through the sixth hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage sequentially, and the pressurized medium provided in the second hydraulic circuit is It is recovered to the first pressure chamber through the 7 hydraulic flow path, the eighth hydraulic flow path, and the ninth hydraulic flow path sequentially, and at least a part of the pressurizing medium of the second pressure chamber is the tenth hydraulic flow path and the ninth hydraulic oil. It may be supplied to the first pressure chamber through the furnace sequentially.

In the abnormal operation mode, the first cut valve is opened to communicate with the master chamber and the first hydraulic circuit, and the simulator valve is closed, but the second cut valve is opened to open the first simulation chamber and the second hydraulic circuit. The circuit is communicated, the inspection valve is opened, the second simulation chamber and the second hydraulic circuit are communicated, and the pressurizing medium of the master chamber is transmitted through the first backup channel according to the pressure of the brake pedal. 1 is provided as a hydraulic circuit, the pressurization medium of the first simulation chamber is provided to the second hydraulic circuit through the second backup passage, and the pressurization medium of the second simulation chamber includes the auxiliary backup passage and the second backup passage. It may be provided to the second hydraulic circuit sequentially through a flow path.

In the inspection mode for checking whether the integrated master cylinder or simulator valve is leaking, the first cut valve, the simulator valve and the inspection valve are closed, and the hydraulic pressure generated by operating the hydraulic pressure supply device is controlled by the hydraulic control unit, A hydraulic pressure value of the pressurized medium that is provided to the first simulation chamber sequentially through the third inlet valve, the fourth inlet valve, and the second backup passage, and is expected to occur based on the displacement amount of the hydraulic piston, It may be determined by comparing the hydraulic pressure value of the pressurized medium measured by the pressure sensor in the second hydraulic circuit or the first simulation chamber.

The electronic brake system according to the present embodiment can reduce the number of parts and achieve miniaturization and weight reduction of products.

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

The electronic brake system according to the present embodiment can stably generate a high-pressure braking pressure.

The electronic brake system according to the present embodiment may improve product performance and operational reliability.

The electronic brake system according to the present embodiment can stably provide a braking pressure even when a component element fails or a pressurized medium leaks.

The electronic brake system according to the present embodiment has an effect of improving durability of a product by reducing a load applied to a component element.

The electronic brake system according to the present embodiment can improve product assembly and productivity, and at the same time reduce the manufacturing cost of the product.

1 is a hydraulic circuit diagram showing an electronic brake system according to the present embodiment.
2 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment performs a first braking mode.
3 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment performs a second braking mode.
4 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment performs a third braking mode.
5 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment releases a third braking mode.
6 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment releases a second braking mode.
7 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment releases the first braking mode.
8 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment performs an abnormal operation mode (fallback mode).
9 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the present embodiment performs an inspection mode.

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 exemplary embodiments presented here, but may be embodied in other forms. In the drawings, in order to clarify the present invention, portions not related to the description may be omitted, and sizes of components may be slightly exaggerated to aid 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 the present embodiment provides a reaction force according to the foot force of the reservoir 1100 and the brake pedal 10 in which the pressurized medium is stored, and at the same time, the brake accommodated in the inside. An integrated master cylinder 1200 that pressurizes and discharges a pressurized medium such as oil, and a pedal displacement sensor 11 that senses the displacement of the brake pedal 10 receives the driver's braking intention as an electrical signal to perform mechanical operation. Through the hydraulic pressure supply device 1300 for generating the hydraulic pressure of the pressurized medium, the hydraulic control unit 1400 for controlling the hydraulic pressure provided from the hydraulic pressure supply device 1300, and the hydraulic pressure of the pressurized medium is transmitted to each wheel (RR, RL). , FR, FL) hydraulic circuits (1510, 1520) having a wheel cylinder (20) to perform braking, and a dump control unit provided between the hydraulic pressure supply device (1300) and the reservoir (1100) to control the flow of the pressurized medium (1800), backup flow paths (1610, 1620) hydraulically connecting the integrated master cylinder 1200 and the hydraulic circuits (1510, 1520), and the reservoir (1100) and the integrated master cylinder (1200) hydraulically connected And an electronic control unit (ECU, not shown) that controls the hydraulic pressure supply device 1300 and various valves based on the reservoir flow path 1700 and the pedal displacement information.

The integrated master cylinder 1200 includes simulation chambers 1230a and 1240a and a master chamber 1220a, and when the driver applies a foot force to the brake pedal 10 for braking operation, a reaction force is provided to the driver to provide a stable It is provided to pressurize and discharge the pressurized medium accommodated in the inside while providing a pedal feel.

The integrated master cylinder 1200 may be divided into a pedal simulation unit that provides a pedal feeling to the driver and a master cylinder unit that delivers a pressurized medium to the first hydraulic circuit 1510 to be described later. The integrated master cylinder 1200 is sequentially provided with a master cylinder part and a pedal simulation part from the brake pedal 10 side, and may be disposed coaxially within one cylinder block 1210.

Specifically, the integrated master cylinder 1200 includes a cylinder block 1210 forming a chamber inside, a master chamber 1220a formed at the inlet side of the cylinder block 1210 to which the brake pedal 10 is connected, and the master A master piston 1220 provided in the chamber 1220a and connected to the brake pedal 10 so as to be displaceable by the operation of the brake pedal 10, and a piston spring 1220b elastically supporting the master piston 1220 And, the first simulation chamber 1230a formed inside the master chamber 1220a on the cylinder block 1210, and the displacement of the master piston 1220 or the master chamber 1220a provided in the first simulation chamber 1230a A first simulation piston 1230 provided to be displaceable by the hydraulic pressure of the pressurized medium accommodated in ), and a second simulation chamber 1240a formed inside the first simulation chamber 1230a on the cylinder block 1210, and , A second simulation piston 1240 provided in the second simulation chamber 1240a and provided to be displaceable by the displacement of the first simulation piston 1230 or the hydraulic pressure of the pressurized medium accommodated in the first simulation chamber 1230a, An elastic member 1250 disposed between the first simulation piston 1230 and the second simulation piston 1240 to provide a pedal feel through elastic restoring force generated during compression, and an elastic member for elastically supporting the first simulation piston 1230. 1 simulator spring 1271, a second simulator spring 1272 for elastically supporting the second simulation piston 1240, a simulation flow path 1260 connecting the first simulation chamber 1230a and the reservoir 1100, It may include a simulator valve 1261 provided in the simulation flow path 1260 to control the flow of the pressurized medium.

The master chamber 1220a, the first simulation chamber 1230a, and the second simulation chamber 1240a are on the cylinder block 1210 of the integrated master cylinder 1200 from the brake pedal 10 side (right side based on FIG. 1). It may be formed sequentially inward (left with reference to FIG. 1). In addition, the master piston 1220, the first simulation piston 1230, and the second simulation piston 1240 are provided in the master chamber 1220a, the first simulation chamber 1230a, and the second simulation chamber 1240a, respectively, and advance and According to the backward movement, a hydraulic pressure or negative pressure may be formed in the pressurized medium accommodated in each chamber.

The master chamber 1220a may be formed on the inlet side or the outermost side (right side based on FIG. 1) of the cylinder block 1210, and the master chamber 1220a includes the brake pedal 10 via the input rod 12. The master piston 1220 connected to the reciprocating motion may be accommodated.

In the master chamber 1220a, a pressurized medium may be introduced and discharged through the first hydraulic port 1280a and the second hydraulic port 1280b. The first hydraulic port 1280a is connected to a first reservoir flow path 1710, which will be described later, so that a pressurized medium can flow into the master chamber 1220a from the reservoir 1100, and the second hydraulic port 1280b is 1 The pressurized medium may be connected to the backup passage 1610 to be discharged from the master chamber 1220a toward the first backup passage 1610 or, conversely, the pressurized medium may be introduced from the first backup passage 1610 toward the master chamber 1220a. . Meanwhile, a pair of sealing members 1290a are provided at the front and rear of the first hydraulic port 1280a to prevent leakage of the pressurized medium. The pair of sealing members 1290a allow the flow of the pressurized medium from the reservoir 1100 to the first master chamber 1220a through the first reservoir flow path 1710, but the first from the first master chamber 1220a. The flow of the pressurized medium toward the reservoir flow path 1710 may be blocked.

The master piston 1220 is accommodated and provided in the master chamber 1220a, but by moving forward (to the left based on FIG. 1), the pressurized medium accommodated in the master chamber 1220a is pressurized to form a hydraulic pressure, or backward (see FIG. 1 ). It is possible to form a negative pressure in the interior of the master chamber 1220a by performing a right direction as a reference). The master piston 1220 may be elastically supported by a piston spring 1220b, and the piston spring 1220b has one end supported by the cylinder block 1210, and the other end extended outwardly to the end of the master piston 1220. It may be provided supported by the flange portion.

The first simulation chamber 1230a may be formed inside the master chamber 1220a on the cylinder block 1210 (left side based on FIG. 1), and the first simulation piston 1230 in the first simulation chamber 1230a It can be accommodated so as to be reciprocated.

In the first simulation chamber 1230a, a pressurized medium may be introduced and discharged through the third hydraulic port 1280c and the fourth hydraulic port 1280d. The third hydraulic port 1280c is connected to the second reservoir flow path 1720 and the simulation flow path 1260 to be described later, so that the pressurized medium accommodated in the first simulation chamber 1230a may be discharged to the reservoir 1100. The pressurized medium may be introduced from the reservoir 1100. In addition, the fourth hydraulic port 1280d is connected to the second backup passage 1620 to be described later, so that the pressurized medium accommodated in the first simulation chamber 1230a may be discharged to the second hydraulic circuit 1520, and conversely, the second backup passage 1520 The pressurized medium may be introduced from the flow path 1620 to the first simulation chamber 1230a.

The first simulation piston 1230 is accommodated and provided in the first simulation chamber 1230a, but by moving forward, it can form a hydraulic pressure of the pressurized medium accommodated in the first simulation chamber 1230a or pressurize the elastic member 1250 to be described later. Further, by moving backward, negative pressure may be formed in the first simulation chamber 1230a or the elastic member 1250 may be returned to its original position and shape. At least one sealing member 1290b may be provided between the inner wall of the cylinder block 1210 and the outer circumferential surface of the first simulation piston 1230 to prevent leakage of the pressurized medium between adjacent chambers.

A step portion formed to be stepped may be provided at a portion where the first simulation chamber 1230a is formed on the cylinder block 1210, and a step portion formed to be stepped may be provided on the outer circumferential surface of the first simulation piston 1230 to be extended to the outside to be caught in the step portion. An extension may be provided. As the extended portion of the first simulation piston 1230 is provided to be caught on the step of the cylinder block 1210, the first simulation piston 1230 is moved forward and then reversed to return to the original position by the operation of the brake pedal 10. 1 The degree of the reverse stroke of the simulation piston 1230 can be limited.

The second simulation chamber 1240a may be formed inside the first simulation chamber 1230a on the cylinder block 1210 (left side based on FIG. 1 ), and the second simulation chamber 1240a includes a second simulation piston ( 1240) may be accommodated to be reciprocating.

In the second simulation chamber 1240a, the pressurized medium may be introduced and discharged through the fifth hydraulic port 1280e and the sixth hydraulic port 1280f. Specifically, the fifth hydraulic port 1280e may be connected to a third reservoir flow path 1730 to be described later, and a pressurized medium may be introduced or discharged from the reservoir 1100 toward the second simulation chamber 1240a. In addition, the sixth hydraulic port (1280f) is connected to the auxiliary backup passage (1630) to be described later, the pressurized medium accommodated in the second simulation chamber (1240a) can be discharged to the side of the second backup passage (1620). The pressurized medium may be introduced from the flow path 1620 to the second simulation chamber 1240a.

The second simulation piston 1240 is accommodated and provided in the second simulation chamber 1240a, but by advancing, it forms a hydraulic pressure of the pressurized medium accommodated in the second simulation chamber 1240a, or by reversing the second simulation chamber 1240a. It can form negative pressure. At least one sealing member 1290c may be provided between the inner wall of the cylinder block 1210 and the outer circumferential surface of the second simulation piston 1240 to prevent leakage of the pressurized medium between adjacent chambers. The sealing member 1290c allows the flow of the pressurized medium from the reservoir 1100 to the second simulation chamber 1240a through the third reservoir flow path 1730, but the third reservoir flow path from the second simulation chamber 1240a ( The flow of the pressurized medium toward 1730 can be blocked.

On the other hand, the integrated master cylinder 1200 according to the present exemplary embodiment includes a master chamber 1220a and simulation chambers 1230a and 1240a, thereby ensuring safety in the event of a component element failure. For example, the master chamber 1220a includes any two wheel cylinders 20 of the right front wheel FR, the left front wheel FL, the left rear wheel RL, and the right rear wheel RR through a first backup passage 1610 to be described later. ), and the simulation chambers 1230a and 1240a may be connected to the other two wheel cylinders 20 through a second backup passage 1620 and an auxiliary backup passage 1630 to be described later, and accordingly, any one chamber Even when a problem such as a leak occurs, braking of the vehicle may be possible. A detailed description of this will be described later with reference to FIG. 8.

The elastic member 1250 is interposed between the first simulation piston 1230 and the second simulation piston 1240, and is provided to provide a pedal feel of the brake pedal 10 to the driver by its own elastic restoring force. The elastic member 1250 may be made of a material such as compressible and expandable rubber, and displacement occurs in the first simulation piston 1230 by the operation of the brake pedal 10, but the second simulation piston 1240 is circular. When the position is maintained, the elastic member 1250 is compressed, and the driver can receive a stable and familiar pedal feeling by the elastic restoring force of the compressed elastic member 1250. A detailed description of this will be described later.

The rear surface of the first simulation piston 1230 facing the elastic member 1250 (the left side based on Fig. 1) and the front side of the second simulation piston 1240 (the right side based on Fig. 1) have an elastic member ( In order to facilitate smooth compression and deformation of the 1250, a receiving groove recessed in a shape corresponding to the shape of the elastic member 1250 may be provided, respectively.

The first simulator spring 1271 is provided to elastically support the first simulation piston 1230. To this end, the first simulation spring 1271 has one end supported on the rear surface of the first simulation piston 1230 (the left surface based on FIG. 1), and the other end is the front surface of the second simulation piston 1240 (FIG. 1). Can be supported on the right side). When the first simulation piston 1230 advances according to the braking operation and displacement occurs, the first simulator spring 1271 is compressed, and at this time, the elastic member 1250 together with the elastic member 1250 can provide a pedal feel to the driver by the elastic restoring force. have. Thereafter, when the braking is released, the first simulator spring 1271 expands by an elastic force, and the first simulation piston 1230 may return to its original position.

The second simulator spring 1272 is provided to elastically support the second simulation piston 1240. The second simulator spring 1272 has one end supported by the cylinder block 1210 and the other end supported by the second simulation piston 1240, thereby elastically supporting the second simulation piston 1240. When the second simulation piston 1240 advances according to the braking operation and displacement occurs, the second simulator spring 1272 is compressed. After that, when the braking is released, the second simulator spring 1272 expands by an elastic force and is controlled. 2 Simulation piston 1240 can return to its original position.

The simulation flow path 1260 is provided to communicate the first simulation chamber 1230a and the reservoir 1100 with each other, and the simulation flow path 1260 may be provided with a simulator valve 1261 for controlling the flow of the pressurized medium in both directions. have. The simulator valve 1261 may be provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state. The simulator valve 1261 may be opened in the normal operating mode of the electronic brake system 1000.

When explaining the pedal simulation operation by the integrated master cylinder 1200, the driver operates the brake pedal 10 during normal operation, and at the same time, the first backup passage 1610 and the second backup passage 1620 described later are respectively The provided first cut valve 1611 and the second cut valve 1621 are closed, while the simulator valve 1261 of the simulation flow path 1260 is opened. As the operation of the brake pedal 10 proceeds, the master piston 1220 advances, but the master chamber 1220a is closed by the closing operation of the first cut valve 1611, thereby holding the pressurized medium contained in the master chamber 1220a. As the hydraulic pressure of is transmitted to the first simulation piston 1230, the first simulation piston 1230 advances and displacement occurs. On the other hand, as the second cut valve 1621 is closed, the second simulation chamber 1240a is closed and the second simulation piston 1240 cannot be displaced. Accordingly, the displacement of the first simulation piston 1230 is an elastic member. The 1250 and the first simulator spring 1271 are compressed, and an elastic restoring force due to compression of the elastic member 1250 and the first simulator spring 1271 may be provided to the driver as a pedal feel. At this time, the pressurized medium accommodated in the first simulation chamber 1230a is transferred to the reservoir 1100 through the simulation flow path 1260. Thereafter, when the driver releases the pedal effort of the brake pedal 10, the piston spring 1220b, the elastic member 1250, and the first simulator spring 1271 return to their original shape and position by the elastic restoring force, and the first simulation chamber The pressure medium 1230a may be supplied and filled from the reservoir 1100 through the simulation flow path 1260.

As described above, since the inside of the first simulation chamber 1230a and the second simulation chamber 1240a is always filled with the pressurized medium, friction between the first simulation piston 1230 and the second simulation piston 1240 during pedal simulation operation This minimizes the durability of the integrated master cylinder 1200, as well as the inflow of foreign substances from the outside can be blocked.

Meanwhile, when the electronic brake system 1000 operates abnormally, that is, the operation of the integrated master cylinder 1200 in the fallback mode operation state will be described later with reference to FIG. 8.

The reservoir 1100 may accommodate and store a pressurized medium therein. The reservoir 1100 may be connected to respective component elements such as an integrated 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. In the drawings, several reservoirs 1100 are shown with the same reference numerals, but this is an example for helping understanding of the invention, and the reservoir 1100 is provided as a single component or a plurality of separate and independent components. I can.

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

The reservoir flow path 1700 is a first reservoir flow path 1710 that connects the master chamber 1220a and the reservoir 1100, and a second reservoir flow path 1720 that connects the first simulation chamber 1230a and the reservoir 1100. And, a third reservoir flow path 1730 connecting the second simulation chamber 1240a and the reservoir 1100 may be included. To this end, one end of the first reservoir flow path 1710 is in communication with the master chamber 1220a of the integrated master cylinder 1200, the other end may be in communication with the reservoir 1100, and one end of the second reservoir flow path 1720 is The first simulation chamber 1230a of the integrated master cylinder 1200 is in communication, the other end is in communication with the reservoir 1100, and one end of the third reservoir flow path 1730 is the second simulation chamber of the integrated master cylinder 1200 ( 1240a) and the other end may be in communication with the reservoir 1100. Meanwhile, the second reservoir flow path 1720 may be connected to the reservoir 1100 by joining after the simulation flow path 1260 is branched, as shown in the figure, but is not limited to the structure and is independently a separate flow path. It can also be connected.

A reservoir valve 1721 may be provided in the second reservoir flow path 1720 to control the flow of the braking fluid transmitted through the second reservoir flow path 1720. The reservoir valve 1721 is a check that allows the flow of the pressurized medium from the reservoir 1100 to the first simulation chamber 1230a, but blocks the flow of the pressurized medium from the first simulation chamber 1230a to the reservoir 1100. It can be provided with a valve.

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 senses the displacement of the brake pedal 10.

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

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

The pressure chambers 1330 and 1340 include a first pressure chamber 1330 positioned in front of the hydraulic piston 1320 (to the left of the hydraulic piston 1320 based on FIG. 1), and the rear of the hydraulic piston 1320 ( Referring to FIG. 1, a second pressure chamber 1340 positioned on the right side of the hydraulic piston 1320 may be included. That is, the first pressure chamber 1330 is partitioned by the cylinder block 1310 and the front surface of the hydraulic piston 1320 so that the volume is changed according to the movement of the hydraulic piston 1320, and the second pressure chamber 1340 ) Is partitioned by the cylinder block 1310 and the rear surface of the hydraulic piston 1320 so that the volume varies according to the movement of the hydraulic piston 1320.

The first pressure chamber 1330 is connected to a first hydraulic flow path 1401 to be described later through a first communication hole 1360a formed in the cylinder block 1310, and the second pressure chamber 1340 is a cylinder block 1310. ) Is connected to a fourth hydraulic flow path 1404 to be described later through a second communication hole 1360b formed in ).

The sealing member is provided between the hydraulic piston 1320 and the cylinder block 1310 to seal between the first pressure chamber 1330 and the second pressure chamber 1340, a piston sealing member 1350a, a drive shaft 1390 and a cylinder. It includes a drive shaft sealing member 1350b provided between the blocks 1310 and sealing the opening of the second pressure chamber 1340 and the cylinder block 1310. Hydraulic or negative pressure of the first pressure chamber 1330 and the second pressure chamber 1340 generated by the forward or backward movement of the hydraulic piston 1320 is sealed by the piston sealing member 1350a and the drive shaft sealing member 1350b. It may not leak and may be delivered to the first hydraulic flow path 1401 and the fourth hydraulic flow path 1404 to be described later.

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

The power conversion unit (not shown) is provided to convert the rotational force of the motor into linear motion. As an example, the power conversion unit may be provided in a structure including 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 an outer circumferential surface to be coupled to mesh with the worm wheel to rotate the worm wheel. The worm wheel is connected to be engaged with the drive shaft 1390 to linearly move the drive shaft 1390, and the drive shaft 1390 is connected to the hydraulic piston 1320, through which the hydraulic piston 1320 is connected to the cylinder block 1310. It can be moved sliding within.

To explain the above operations again, when displacement is detected in the brake pedal 10 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 with 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 within 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 also rotates in the opposite direction, and the hydraulic piston 1320 connected to the drive shaft 1390 moves backward in the cylinder block 1310 to generate negative pressure in the first pressure chamber 1330.

The generation of hydraulic pressure and negative pressure in the second pressure chamber 1340 may be implemented by operating in the opposite direction to the above. That is, when displacement is detected by the brake pedal 10 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 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 moves forward in the cylinder block 1310, thereby generating negative pressure in the second pressure chamber 1340.

In this way, 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 braking by doing so or to release braking using negative pressure. A detailed description of this will be described later.

On the other hand, the power conversion unit according to the present embodiment 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 is understood even when it is made of various structures and devices Should be.

The hydraulic pressure supply device 1300 may be hydraulically connected to the reservoir 1100 by the dump control unit 1800. The dump control unit 1800 includes a first dump passage 1810 connecting the first pressure chamber 1330 and the reservoir 1100, and a first bypass passage 1830 branched and rejoined on the first dump passage 1810. ), and a second dump passage 1820 connecting the second pressure chamber 1340 and the reservoir 1100, and a second bypass passage 1840 branched and rejoined on the second dump passage 1820 can do.

A first dump check valve 1811 and a first dump valve 1831 for controlling the flow of the pressurized medium may be provided in the first dump passage 1810 and the first bypass passage 1830, respectively. The first dump check valve 1811 may be provided to allow only the flow of the pressurized medium from the reservoir 1100 to the first pressure chamber 1330 and to block the flow of the pressurized medium in the opposite direction. ), the first bypass flow path 1830 is connected in parallel with the first dump check valve 1811, and the first bypass flow path 1830 is pressed between the first pressure chamber 1330 and the reservoir 1100. A first dump valve 1831 for controlling the flow of the medium may be provided. In other words, the first bypass flow path 1830 may be connected by bypassing the front end and the rear end of the first dump check valve 1811 on the first dump flow path 1810, and the first dump valve 1831 has a first pressure. It may be provided as a two-way solenoid valve that controls the flow of the pressurized medium between the chamber 1330 and the reservoir 1100. The first dump valve 1831 may be provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state.

A second dump check valve 1821 and a second dump valve 1841 for controlling the flow of the pressurized medium may be provided in the second dump passage 1820 and the second bypass passage 1840, respectively. The second dump check valve 1821 may be provided to allow only the flow of the pressurized medium from the reservoir 1100 to the second pressure chamber 1330 and to block the flow of the pressurized medium in the opposite direction. ), a second bypass flow path 1840 is connected in parallel to the second dump check valve 1821, and the second bypass flow path 1840 is pressed between the second pressure chamber 1330 and the reservoir 1100. A second dump valve 1841 for controlling the flow of the medium may be provided. In other words, the second bypass flow path 1840 may be connected to the second dump flow path 1820 by bypassing the front and rear ends of the second dump check valve 1821, and the second dump valve 1841 has a second pressure. It may be provided as a two-way solenoid valve that controls the flow of the pressurized medium between the chamber 1330 and the reservoir 1100. The second dump valve 1841 may be provided as a normal open type solenoid valve that is open normally and operates to close the valve upon receiving an electrical signal from the electronic control unit.

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 based on the hydraulic pressure information and the pedal displacement information. It is provided to control the valves.

The hydraulic control unit 1400 includes a first hydraulic circuit 1510 for controlling the flow of hydraulic pressure delivered to the first and second wheel cylinders 21 and 22 among the four wheel cylinders 20, and the third and third wheel cylinders. 4 It may be provided with a second hydraulic circuit (1520) for controlling the flow of hydraulic pressure delivered to the wheel cylinders (23, 24), and to control the hydraulic pressure transferred from the hydraulic pressure supply device (1300) to the wheel cylinder (20). Includes flow path and valve.

The first hydraulic flow path 1401 may be provided to communicate with the first pressure chamber 1330, and the second hydraulic flow path 1402 may be provided in communication with the second pressure chamber 1340. After the first hydraulic flow path 1401 and the second hydraulic flow path 1402 are joined to the third hydraulic flow path 1403, the fourth hydraulic flow path 1404 connected to the first hydraulic circuit 1510 and the second hydraulic flow path 1402 It may be provided by branching back to the fifth hydraulic flow path 1405 connected to the circuit 1520.

The sixth hydraulic flow path 1406 is provided to communicate with the first hydraulic circuit 1510, and the seventh hydraulic flow path 1407 is provided to communicate with the second hydraulic circuit 1520. After the sixth hydraulic flow path 1406 and the seventh hydraulic flow path 1407 join the 8th hydraulic flow path 1408, the ninth hydraulic flow path 1409 communicating with the first pressure chamber 1409 and the second pressure It may be provided to branch back to the tenth hydraulic flow path 1410 communicating with the chamber 1410.

A first valve 1431 for controlling the flow of the pressurized medium may be provided in the first hydraulic flow path 1401. The first valve 1431 may be provided as a check valve that allows the flow of the pressurized medium discharged from the first pressure chamber 1330 but blocks the flow of the pressurized medium in the opposite direction. In addition, a second valve 1432 for controlling the flow of the pressurized medium may be provided in the second hydraulic flow path 1402, and the second valve 1432 is the flow of the pressurized medium discharged from the second pressure chamber 1340. Allowed, but may be provided with a check valve that blocks the flow of the pressurized medium in the opposite direction.

The fourth hydraulic flow path 1404 is provided by branching again from the third hydraulic flow path 1403 where the first hydraulic flow path 1401 and the second hydraulic flow path 1402 join, and connected to the first hydraulic circuit 1510. A third valve 1433 for controlling the flow of the pressurized medium may be provided in the fourth hydraulic flow path 1404. The third valve 1433 may be provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic flow path 1403 to the first hydraulic circuit 1510 and blocks the flow of the pressurized medium in the opposite direction.

The fifth hydraulic flow path 1405 is provided by branching again from the third hydraulic flow path 1403 where the first hydraulic flow path 1401 and the second hydraulic flow path 1402 join, and connected to the second hydraulic circuit 1520. A fourth valve 1434 for controlling the flow of the pressurized medium may be provided in the fifth hydraulic flow path 1405. The fourth valve 1434 may be provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520 and blocks the flow of the pressurized medium in the opposite direction.

The sixth hydraulic flow path 1406 communicates with the first hydraulic circuit 1510, and the seventh hydraulic flow path 1407 communicates with the second hydraulic circuit 1520, and is provided to merge into the eighth hydraulic flow path 1408. . A fifth valve 1435 for controlling the flow of the pressurized medium may be provided in the sixth hydraulic flow path 1406. The fifth valve 1435 may be provided as a check valve that allows only the flow of the pressurized medium discharged from the first hydraulic circuit 1510 and blocks the flow of the pressurized medium in the opposite direction. In addition, a sixth valve 1436 for controlling the flow of the pressurized medium may be provided in the seventh hydraulic passage 1407. The sixth valve 1436 may be provided as a check valve that allows only the flow of the pressurized medium discharged from the second hydraulic circuit 1520 and blocks the flow of the pressurized medium in the opposite direction.

The ninth hydraulic flow path 1409 is provided by branching from the eighth hydraulic flow path 1408 where the sixth hydraulic flow path 1406 and the seventh hydraulic flow path 1407 join, and connected to the first pressure chamber 1330. A seventh valve 1437 for controlling the flow of the pressurized medium may be provided in the ninth hydraulic flow path 1409. The seventh valve 1437 may be provided as a two-way control valve that controls the flow of the pressurized medium delivered along the ninth hydraulic flow path 1409. The seventh valve 1437 may be provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state.

The tenth hydraulic passage 1410 is provided by branching from the eighth hydraulic passage 1408 where the sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 join, and connected to the second pressure chamber 1340. An eighth valve 1438 for controlling the flow of the pressurized medium may be provided in the tenth hydraulic flow path 1410. The eighth valve 1438 may be provided as a two-way control valve that controls the flow of the pressurized medium delivered along the tenth hydraulic flow path 1410. Like the seventh valve 1437, the eighth valve 1438 is provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state. Can be.

In the hydraulic control unit 1400, the hydraulic pressure formed in the first pressure chamber 1330 according to the advance of the hydraulic piston 1320 by the arrangement of the hydraulic flow path and the valve is the first hydraulic flow path 1401 and the third hydraulic flow path ( 1403), can be transferred to the first hydraulic circuit 1510 sequentially through the fourth hydraulic flow path 1404, the first hydraulic flow path 1401, the third hydraulic flow path 1403, the fifth hydraulic flow path 1405 It may be transferred to the second hydraulic circuit 1520 through sequentially. In addition, the hydraulic pressure formed in the second pressure chamber 1340 as the hydraulic piston 1320 moves backward is sequentially passed through the second hydraulic channel 1402, the third hydraulic channel 1403, and the fourth hydraulic channel 1404. 1 may be transferred to the hydraulic circuit 1510, and may be transferred to the second hydraulic circuit 1520 through sequentially through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405. have.

On the contrary, the negative pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 moves backwards converts the pressurizing medium provided to the first hydraulic circuit 1510 into the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and The ninth hydraulic flow path 1409 can be sequentially recovered to the first pressure chamber 1330, and the pressurized medium provided through the second hydraulic circuit 1520 is transferred to the 7th hydraulic flow path 1407 and the 8th hydraulic flow path 1408. , It may be recovered to the first pressure chamber 1330 sequentially through the ninth hydraulic flow path 1409. In addition, the negative pressure formed in the second pressure chamber 1340 according to the advance of the hydraulic piston 1320 is applied to the pressurizing medium provided to the first hydraulic circuit 1510 by the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and 10 The hydraulic flow path 1410 can be sequentially recovered to the first pressure chamber 1340, and the pressurized medium provided through the second hydraulic circuit 1520 is transferred to the 7th hydraulic flow path 1407, the 8th hydraulic flow path 1408, and It may be recovered to the second pressure chamber 1340 sequentially through the tenth hydraulic flow path 1410.

In addition, the negative pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 moves backward can be supplied with a pressurizing medium from the reservoir 1100 to the first pressure chamber 1330 through the first dump passage 1810. In addition, the negative pressure formed in the second pressure chamber 1340 according to the advance of the hydraulic piston 1320 can be supplied with the pressurizing medium from the reservoir 1100 to the second pressure chamber 1340 through the second dump passage 1820. have.

A detailed description of the delivery of hydraulic pressure and negative pressure by the arrangement of these hydraulic flow paths and valves will be described later with reference to FIGS. 2 to 7.

The first hydraulic circuit 1510 of the hydraulic control unit 1400 is the hydraulic pressure of 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 the hydraulic pressure of the third and fourth wheel cylinders 23 and 24, which are two other wheel cylinders 20.

The first hydraulic circuit 1510 may receive hydraulic pressure through the fourth hydraulic flow path 1404 and discharge the hydraulic pressure through the sixth hydraulic flow path 1406. To this end, as shown in FIG. 1, after the fourth hydraulic flow path 1404 and the sixth hydraulic flow path 1406 join, two flow paths connected to the first wheel cylinder 21 and the second wheel cylinder 22 It can be branched and provided. In addition, the second hydraulic circuit 1520 can receive hydraulic pressure through the fifth hydraulic flow path 1405 and discharge the hydraulic pressure through the seventh hydraulic flow path 1407. Accordingly, as shown in FIG. After the 5 hydraulic flow passage 1405 and the seventh hydraulic flow passage 1407 join, the third wheel cylinder 23 and the fourth wheel cylinder 24 may be branched into two flow passages. However, the connection of the hydraulic flow path shown in FIG. 1 is an example for aiding understanding of the present invention, and is not limited to the structure, and the fourth hydraulic flow path 1404 and the sixth hydraulic flow path 1406 It is connected to the circuit 1510 side, can be independently branched and connected to the first wheel cylinder 21 and the second wheel cylinder 22, similarly, the fifth hydraulic flow passage 1405 and the seventh hydraulic flow passage 1407 Is connected to the second hydraulic circuit (1520) side, and is independently branched and connected to the third wheel cylinder 23 and the fourth wheel cylinder 24. something to do.

The first and second hydraulic circuits 1510 and 1520 are first to fourth inlet valves 1511a, 1511b, 1521a, and 1521b to control the flow and hydraulic pressure of the pressurized medium delivered to the first to fourth wheel cylinders 24. ) Can be provided. The first to fourth inlet valves 1511a, 1511b, 1521a, and 1521b are respectively disposed on the upstream side of the first to fourth wheel cylinders 20 and are open normally, but when an electric signal is received from the electronic control unit, the valve It may be provided with a normal open type solenoid valve that operates to close.

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, and 1521b. , 1523b). Check valves (1513a, 1513b, 1523a, 1523b) are a bypass connecting the front and rear of the first to fourth inlet valves (1511a, 1511b, 1521a, 1521b) on the first and second hydraulic circuits (1510, 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, and the flow of the pressurized medium from the hydraulic pressure supply device 1300 to the wheel cylinder 20 can be blocked. . The first to fourth check valves 1513a, 1513b, 1523a, 1523b can quickly remove 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 can be smoothly returned to the hydraulic pressure providing unit.

The first hydraulic circuit 1510 controls the flow of the pressurized medium discharged from the first and second wheel cylinders 21 and 22 in order to improve performance when the first and second wheel cylinders 21 and 22 are brake released. First and second outlet valves 1512a and 1512b may be provided. The first and second outlet valves 1512a and 1512b are provided on the discharge side of the first and second wheel cylinders 21 and 22, respectively, and transferred from the first and second wheel cylinders 21 and 22 to the reservoir 1100 Controls the flow of the pressurized medium. The first and second outlet valves 1512a and 1512b may be provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state. . In the ABS braking mode of the vehicle, the first and second outlet valves 1512a and 1512b selectively release the hydraulic pressure of the pressurized medium applied to the first wheel cylinder 21 and the second wheel cylinder 22, and the reservoir 1100 Can be delivered to the side.

The third and fourth wheel cylinders 23 and 24 of the second hydraulic circuit 1520 may be connected by branching a second backup passage 1620 to be described later, and the second backup passage 1620 may have at least one second A cut valve 1621 may be provided to control the flow of the pressurized medium between the third and fourth wheel cylinders 23 and 24 and the integrated master cylinder 1200.

The electronic brake system 1000 according to the present embodiment is designed to implement braking by directly supplying the pressurized medium discharged from the integrated master cylinder 1200 to the wheel cylinder 20 when normal operation is impossible due to a device failure. It may include first and second backup passages 1610 and 1620 and auxiliary backup passages 1630. The mode in which the hydraulic pressure of the integrated master cylinder 1200 is directly transmitted to the wheel cylinder 20 is referred to as an abnormal operation mode, that is, a fallback mode.

The first backup passage 1610 is provided to connect the master chamber 1220a of the integrated master cylinder 1200 and the first hydraulic circuit 1510, and the second backup passage 1620 is the first of the integrated master cylinder 1200. It may be provided to connect the 1 simulation chamber 1230a and the second hydraulic circuit 1520. In addition, the auxiliary backup passage 1630 is provided to connect the second simulation chamber 1240a of the integrated master cylinder 1200 and the second backup passage 1620.

Specifically, the first backup passage 1610 has one end connected to the master chamber 1220a, and the other end connected between the first inlet valve 1511a and the first outlet valve 1512a on the first hydraulic circuit 1510. The second backup passage 1620 has one end connected to the first simulation chamber 1230a, and the other end on the second hydraulic circuit 1520 on the downstream side of the third and fourth inlet valves 1521a and 1521b. Can be branched and connected. In FIG. 1, the first backup passage 1610 is shown to be connected between the first inlet valve 1511a and the first outlet valve 1512a, but the first backup passage 1610 diverges and the first outlet valve ( 1512a) and the second outlet valve 1512b, if connected to at least one of the upstream side will be understood to be the same. In addition, the auxiliary backup passage 1630 is provided so that one end is connected to the second simulation chamber 1240a and the other end joins the second backup passage 1620, so that the pressurized medium accommodated in the second simulation chamber 1240a is a second backup. It may be delivered to the flow path 1620.

A first cut valve 1611 for controlling the flow of the pressurized medium in both directions is provided in the first backup passage 1610, and at least one second cut-off valve 1611 for controlling the flow of the pressurized medium in both directions is provided in the second backup passage 1620. A cut valve 1621 may be provided. The first cut valve 1611 and the second cut valve 1621 are provided as normal open type solenoid valves that operate to close when a closing signal is received from the electronic control unit after being opened normally. Can be.

As shown in FIG. 1, a pair of the second cut valve 1621 may be provided on the side of the third and fourth wheel cylinders 23 and 24, respectively, and the third wheel cylinder 23 in the ABS braking mode of the vehicle ) And the hydraulic pressure of the pressurized medium applied to the fourth wheel cylinder 24 is selectively released to the reservoir 1100 through the second backup passage 1620, the first simulation chamber 1230a, and the simulation passage 1260 in sequence. Can be discharged.

The auxiliary backup flow path 1630 is provided with an inspection valve 1631 for controlling the flow of the pressurized medium in both directions, and the inspection valve 1631 is open normally and closes when a closing signal is received from the electronic control unit. It may be provided with a normal open type solenoid valve that operates. The inspection valve 1631 may be closed during normal operation of the electronic brake system 1000 to seal the second simulation chamber 1240a, and determine whether the integrated master cylinder 1200 or the simulator valve 1261 leaks. It can be closed during the inspection mode to be tested. A detailed description of this will be described later.

Accordingly, when the first and second cut valves 1621 are closed, the pressurized medium of the integrated master cylinder 1200 is prevented from being directly transferred to the wheel cylinder 20, and at the same time, provided from the hydraulic pressure supply device 1300. When hydraulic pressure can be supplied to the first and second hydraulic circuits 1510 and 1520 via the hydraulic control unit 1400, and the first and second cut valves 1611 and 1621 and the inspection valve 1631 are opened The pressurized medium pressurized by the integrated master cylinder 1200 is directly supplied to the first and second hydraulic circuits 1510 and 1520 through the first and second backup passages 1620 and the auxiliary backup passage 1630 to prevent braking. Can be implemented.

The electronic brake system 1000 according to the present embodiment may include a pressure sensor PS that senses the hydraulic pressure of at least one of the first hydraulic circuit 1510 and the second hydraulic circuit 1520. In the drawing, the pressure sensor (PS) is shown to be provided on the side of the second hydraulic circuit 1520, but is not limited to the location and number, if it can detect the hydraulic pressure of the hydraulic circuit and the integrated master cylinder 1200 This includes cases where various numbers are provided in various locations.

Hereinafter, a method of operating the electronic brake system 1000 according to the present embodiment will be described.

The operation of the electronic brake system 1000 according to the present embodiment is a normal operation mode in which various devices and valves operate normally without failure or abnormality, and an abnormal operation mode in which malfunctions or abnormalities occur in various devices and valves. Fallback mode), and an inspection mode for checking whether the integrated master cylinder 1200 or the simulator valve 1261 is leaked.

First, a normal operation mode of the operation method of the electronic brake system 1000 according to the present embodiment will be described.

In the normal operation mode of the electronic brake system 1000 according to the present embodiment, as the hydraulic pressure transmitted from the hydraulic pressure supply device 1300 to the wheel cylinder 20 increases, the first braking mode to the third braking mode are classified and operated. can do. Specifically, the first braking mode primarily provides hydraulic pressure by the hydraulic pressure supply device 1300 to the wheel cylinder 20, and the second braking mode is the hydraulic pressure by the hydraulic pressure supply device 1300 to the wheel cylinder 20 It is possible to deliver a higher braking pressure than the first braking mode by providing a second braking mode, and the third braking mode is a second braking mode by thirdly providing hydraulic pressure from the hydraulic pressure supply device 1300 to the wheel cylinder 20. Higher braking pressure can be delivered.

The first to third braking modes can be changed by changing the operation of the hydraulic pressure supply device 1300 and the hydraulic control unit 1400. The hydraulic pressure supply device 1300 may provide a sufficiently high hydraulic pressure of the pressurized medium without a high-spec motor by utilizing the first to third braking modes, and further, it is possible to prevent unnecessary loads applied to the motor. Accordingly, while reducing the cost and weight of the brake system, a stable braking force can be secured, and durability and operational reliability of the device can be improved.

2 is a hydraulic circuit diagram showing a state in which the electronic brake system 1000 according to the present embodiment performs a first braking mode.

Referring to FIG. 2, when the driver presses the brake pedal 10 at the beginning of braking, the motor (not shown) operates to rotate in one direction, and the rotational force of the motor is transmitted to the hydraulic pressure providing unit by the power converter, providing hydraulic pressure As the hydraulic piston 1320 of the unit advances, it generates hydraulic pressure in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the first pressure chamber 1330 is sequentially passed through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404 to the first hydraulic circuit 1510. It is primarily transmitted to the provided first and second wheel cylinders 21 and 22. At this time, the first valve 1431 allows only the flow of the pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 is the first hydraulic circuit 1510 from the third hydraulic flow path 1403. It is provided with a check valve that allows only the flow of the pressurized medium toward the bar, so that the hydraulic pressure of the pressurized medium can be smoothly transferred to the first and second wheel cylinders 21 and 22. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are kept open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. By maintaining the state, the hydraulic pressure of the pressurized medium is prevented from leaking to the reservoir 1100.

In addition, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405, and the second hydraulic circuit 1520 ) Is primarily transmitted to the third and fourth wheel cylinders 23 and 24 provided in). As described above, the first valve 1431 allows only the flow of the pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 is from the third hydraulic flow path 1403 to the second hydraulic circuit ( It is provided with a check valve that allows only the flow of the pressurized medium toward 1520, and the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth wheel cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1622 is maintained in a closed state to prevent hydraulic pressure of the pressurized medium. It is possible to prevent leakage toward the second backup passage 1620.

In the first braking mode, the eighth valve 1438 is controlled in a closed state, so that the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 can be prevented from leaking into the second pressure chamber 1340. In addition, the first dump valve 1831 provided in the first bypass flow path 1830 may be kept in a closed state to prevent the hydraulic pressure formed in the first pressure chamber 1330 from leaking into the reservoir 1100.

On the other hand, as the hydraulic piston 1320 advances, negative pressure is generated in the second pressure chamber 1340, so that the hydraulic pressure of the pressurized medium is reduced from the reservoir 1100 to the second pressure chamber 1340 through the second dump passage 1820. It can be transferred to prepare a second braking mode to be described later. The second dump check valve 1821 provided in the second dump passage 1820 allows the flow of the pressurized medium from the reservoir 1100 to the second pressure chamber 1340, and the pressurized medium is the second pressure chamber ( 1340 can be stably supplied, and the first dump valve 1841 provided in the second bypass flow path 1840 is converted to an open state to transfer the pressurized medium from the reservoir 1100 to the first pressure chamber 1330 Can supply quickly.

In the first braking mode that implements the braking of the wheel cylinder 20 by the hydraulic pressure supply device 1300, the first cut valve 1611 and the first cut valve 1611 provided in the first backup passage 1610 and the second backup passage 1620, respectively, The second cut valve 1621 is closed and switched to prevent the pressurized medium discharged from the integrated master cylinder 1200 from being transferred to the wheel cylinder 20.

Specifically, when a pedal effort is applied to the brake pedal 10, the first cut valve 1611 is closed, and thus the master chamber 1220a is closed. Therefore, as the pedal effort is applied to the brake pedal 10, the pressurized medium accommodated in the master chamber 1220a is pressurized to form a hydraulic pressure, and the hydraulic pressure of the pressurized medium formed in the master chamber 1220a is the electric pressure of the first simulation piston 1230. It is transmitted to the direction (right side based on FIG. 2), and the simulator valve 1261 is opened in the normal operation mode, so that displacement occurs in the first simulation piston 1230. Meanwhile, in the normal operation mode of the electronic brake system 1000, since the inspection valve 1631 is closed, the second simulation chamber 1240a is closed, so that no displacement occurs in the second simulation piston 1240, and accordingly, the first simulation The displacement of the piston 1230 compresses the elastic member 1250, and an elastic restoring force by compression of the elastic member 1250 is provided to the driver as a pedal feel. At this time, the pressurized medium accommodated in the first simulation chamber 1230a is discharged to the reservoir 1100 through the simulation flow path 1260.

The electronic brake system 1000 according to the present embodiment may switch from the first braking mode to the second braking mode shown in FIG. 3 when a higher braking pressure than the first braking mode is to be provided.

3 is a hydraulic circuit diagram showing a state in which the electronic brake system 1000 according to the present embodiment performs a second braking mode. Referring to FIG. 3, the electronic control unit is a brake pedal sensed by the pedal displacement sensor 11 ( If the displacement or operating speed of 10) is higher than the preset level or the hydraulic pressure detected by the pressure sensor is higher than the preset level, it is determined that a higher braking pressure is required and the first braking mode is the second braking mode. Can be switched to.

When switching from the first braking mode to the second braking mode, the motor operates to rotate in the other direction, and the rotational force of the motor is transmitted to the hydraulic pressure supply unit by the power conversion unit, and the hydraulic piston 1320 moves backward, thereby causing the second pressure. A hydraulic pressure is generated in the chamber 1340. The hydraulic pressure discharged from the second pressure chamber 1340 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the second pressure chamber 1340 is sequentially passed through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404 to reach the first hydraulic circuit 1510. It is transmitted secondarily to the provided first and second wheel cylinders 21 and 22. At this time, the second valve 1432 provided in the second hydraulic flow path 1402 allows only the flow of the pressurized medium discharged from the second pressure chamber 1340, and a third valve provided in the fourth hydraulic flow path 1404 The valve 1433 is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic passage 1403 to the first hydraulic circuit 1510, and the hydraulic pressure of the pressurized medium is applied to the first and second wheel cylinders 21 , 22) can be transferred smoothly. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 remain open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. To prevent leakage of the hydraulic pressure of the pressurized medium to the reservoir 1100.

In addition, the hydraulic pressure formed in the second pressure chamber 1340 is provided in the second hydraulic circuit 1520 by sequentially passing through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405. It is transmitted secondary to the third and fourth wheel cylinders (23, 24). As described above, the second valve 1432 provided in the second hydraulic passage 1403 allows only the flow of the pressurized medium discharged from the second pressure chamber 1340, and is provided in the fifth hydraulic passage 1405. The fourth valve 1434 is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520, and the hydraulic pressure of the pressurized medium is the third and fourth wheel cylinders. It can be transferred smoothly to (23, 24). In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1622 is maintained in a closed state to prevent hydraulic pressure of the pressurized medium. It is possible to prevent leakage toward the second backup passage 1620.

In the second braking mode, the seventh valve 1437 is controlled in a closed state, so that the hydraulic pressure of the pressurized medium formed in the second pressure chamber 1340 can be prevented from leaking to the first pressure chamber 1330. In addition, The dump valve 1841 is converted to a closed state, so that the hydraulic pressure of the pressurized medium formed in the second pressure chamber 1340 may be prevented from leaking to the reservoir 1100.

On the other hand, as the hydraulic piston 1320 moves backward, negative pressure is generated in the first pressure chamber 1330, so that the hydraulic pressure of the pressurized medium from the reservoir 1100 to the first pressure chamber 1330 through the first dump passage 1810 is reduced. It is transferred to prepare a third braking mode to be described later. The first dump check valve 1811 provided in the first dump passage 1810 allows the flow of the pressurized medium from the reservoir 1100 to the first pressure chamber 1330, and the pressurized medium is the first pressure chamber ( 1330 can be stably supplied, and the first dump valve 1831 provided in the first bypass flow path 1830 is switched to an open state to transfer the pressurized medium from the reservoir 1100 to the first pressure chamber 1330 Can supply quickly.

The operation of the integrated master cylinder 1200 in the second braking mode is the same as the operation of the integrated master cylinder 1200 in the first braking mode of the electronic brake system described above, and a description thereof will be omitted to prevent duplication of contents.

The electronic brake system 1000 according to the present embodiment may switch from the second braking mode to the third braking mode shown in FIG. 4 when a higher braking pressure than the second braking mode is to be provided.

4 is a hydraulic circuit diagram showing a state in which the electronic brake system 1000 according to the present embodiment performs a third braking mode.

Referring to FIG. 4, the electronic control unit is configured such that the displacement or operating speed of the brake pedal 10 detected by the pedal displacement sensor 11 is higher than a preset level, or the hydraulic pressure detected by the pressure sensor is higher than a preset level. In this case, it is determined that a higher braking pressure is required and the second braking mode can be switched to the third braking mode.

When switching from the second braking mode to the third braking mode, the motor (not shown) operates to rotate in one direction, and the rotational force of the motor is transmitted to the hydraulic pressure supply unit by the power conversion unit, and the hydraulic piston of the hydraulic pressure supply unit As the 1320 advances again, a hydraulic pressure is generated in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 3400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, a part of the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404, and the first hydraulic circuit 1510 ) Is primarily transmitted to the first and second wheel cylinders 21 and 22 provided in the. At this time, the first valve 1431 allows only the flow of the pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 is the first hydraulic circuit 1510 from the third hydraulic flow path 1403. It is provided with a check valve that allows only the flow of the pressurized medium toward the bar, so that the hydraulic pressure of the pressurized medium can be smoothly transferred to the first and second wheel cylinders 21 and 22. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are kept open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. By maintaining the state, the hydraulic pressure of the pressurized medium is prevented from leaking to the reservoir 1100.

In addition, part of the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405, and the second hydraulic circuit It is primarily transmitted to the third and fourth wheel cylinders 23 and 24 provided in 1520. As described above, the first valve 1431 allows only the flow of the pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 is from the third hydraulic flow path 1403 to the second hydraulic circuit ( It is provided with a check valve that allows only the flow of the pressurized medium toward 1520, and the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth wheel cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1622 is maintained in a closed state to prevent hydraulic pressure of the pressurized medium. It is possible to prevent leakage toward the second backup passage 1620.

On the other hand, in the third braking mode, since high pressure hydraulic pressure is provided, as the hydraulic piston 1320 advances, the hydraulic pressure in the first pressure chamber 1330 also increases the force to move the hydraulic piston 1320 backward. The load will increase rapidly. Accordingly, in the third braking mode, the seventh valve 1437 and the eighth valve 1438 are opened to allow the flow of the pressurized medium through the ninth hydraulic flow path 1409 and the tenth hydraulic flow path 1410. In other words, a part of the hydraulic pressure formed in the first pressure chamber 1330 may be supplied to the second pressure chamber 1340 by passing through the ninth hydraulic passage 1409 and the tenth hydraulic passage 1410 in sequence. Through this, the first pressure chamber 1330 and the second pressure chamber 1340 communicate with each other to synchronize hydraulic pressure, thereby reducing a load applied to the motor and improving durability and reliability of the device.

In the third braking mode, the first dump valve 1831 is switched to a closed state so that the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 leaks into the reservoir 1100 along the first bypass flow path 1830. It can be prevented, and the second dump valve 2841 is also controlled in a closed state, thereby rapidly forming negative pressure in the second pressure chamber 1340 by the advance of the hydraulic piston 1320 from the first pressure chamber 1330 The provided pressurized medium can be smoothly supplied.

The operation of the integrated master cylinder 1200 in the third braking mode is the same as the operation of the integrated master cylinder 1200 in the first and second braking modes of the electronic brake system described above, and the description has been omitted to prevent duplication of the contents. do.

Hereinafter, a method of releasing braking in the normal operation mode of the electronic brake system 1000 according to the present embodiment will be described.

5 is a hydraulic circuit diagram showing a state in which a third braking mode is released while the hydraulic piston 1320 of the electronic brake system 1000 according to the present embodiment moves backward.

Referring to FIG. 5, when the pedal effort applied to the brake pedal 10 is released, the motor generates rotational force in another direction and transmits it to the power conversion unit, and the power conversion unit moves the hydraulic piston 1320 backward. Accordingly, while releasing the hydraulic pressure in the first pressure chamber 1330, negative pressure may be generated, and thus the pressurizing medium of the wheel cylinder 20 may be transmitted to the first pressure chamber 1330.

Specifically, the hydraulic pressure of the first wheel cylinder 21 and the second wheel cylinder 22 provided in the first hydraulic circuit 1510 is the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and the ninth hydraulic oil. It is recovered to the first pressure chamber 1330 by passing through the furnace 1409 in sequence. At this time, since the fifth valve 1435 provided in the sixth hydraulic flow path 1406 is provided as a check valve that allows only the flow of the pressurized medium discharged from the first hydraulic circuit 1510, the pressurized medium can be recovered, The seventh valve 1437 is opened to allow the flow of the pressurized medium through the ninth hydraulic flow path 1409. In addition, the first dump valve 1831 is closed so as to effectively form negative pressure in the first pressure chamber 1330.

At the same time, the pressurizing medium accommodated in the second pressure chamber 1340 is sequentially passed through the tenth hydraulic passage 1410 and the ninth hydraulic passage 1409 so that the hydraulic piston 1320 can be moved back quickly and smoothly. 1 It is transmitted to the pressure chamber 1330, and for this purpose, the eighth valve 1438 provided in the tenth hydraulic flow path 1410 is also converted to an open state. At this time, the second dump valve 1841 may be operated to be closed to induce the pressurized medium of the second pressure chamber 1340 to be supplied to the first pressure chamber 1330. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 remain open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. Keep it.

In addition, the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the first pressure chamber 1330 is the seventh hydraulic oil. The furnace 1407, the eighth hydraulic flow passage 1408, and the ninth hydraulic flow passage 1409 are sequentially passed through and are recovered to the first pressure chamber 1330. As described above, the sixth valve 1436 provided in the seventh hydraulic flow path 1407 is provided as a check valve that allows only the flow of the pressurized medium discharged from the second hydraulic circuit 1520 so that the pressurized medium can be recovered. In addition, the seventh valve 1437 is opened to allow the flow of the pressurized medium through the ninth hydraulic flow path 1409. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are kept open.

After completing the release of the third braking mode, it is possible to switch to the release operation of the second braking mode shown in FIG. 6 in order to further lower the braking pressure of the wheel cylinder.

6 is a hydraulic circuit diagram showing a state in which the hydraulic piston 1320 of the electronic brake system 1000 according to the present embodiment moves forward and releases the second braking mode.

Referring to FIG. 6, when the pedal effort applied to the brake pedal 10 is released, the motor generates rotational force in one direction and transmits it to the power conversion unit, and the power conversion unit advances the hydraulic piston 1320. Accordingly, while releasing the hydraulic pressure in the second pressure chamber 1340, negative pressure may be generated, and thus the pressurizing medium of the wheel cylinder 20 may be transmitted to the second pressure chamber 1340.

Specifically, the hydraulic pressure of the pressurized medium applied to the first wheel cylinder 21 and the second wheel cylinder 22 provided in the first hydraulic circuit 1510 is the sixth hydraulic passage 1406 and the eighth hydraulic passage 1408 , Passing through the tenth hydraulic flow path 1410 sequentially, it is recovered to the second pressure chamber 1340. At this time, the fifth valve 1435 provided in the sixth hydraulic passage 1406 allows only the flow of the pressurized medium discharged from the first hydraulic circuit 1510, so that the pressurized medium can be recovered, and the tenth hydraulic passage The eighth valve 1438 provided in the 1410 may be switched open to allow the flow of the pressurized medium delivered along the tenth hydraulic flow path 1410. In addition, the seventh valve 1437 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the first pressure chamber 1330 through the ninth hydraulic flow path 1409. have. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 remain open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. Keep it.

In addition, the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the second pressure chamber 1340 is the seventh hydraulic oil. The furnace 1407, the eighth hydraulic flow passage 1408, and the tenth hydraulic flow passage 1410 are sequentially passed through and are recovered to the second pressure chamber 1340. As described above, the sixth valve 1436 provided in the seventh hydraulic passage 1407 allows the flow of the pressurized medium discharged from the second hydraulic circuit 1520, and is provided in the tenth hydraulic passage 1410. Since the eighth valve 1438 is opened, the pressurized medium can be smoothly recovered to the second pressure chamber 1340. Furthermore, the seventh valve 1437 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the first pressure chamber 1330 through the ninth hydraulic flow path 1409. have. The third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the third outlet valve 1522a is maintained in a closed state.

On the other hand, when the second braking mode is released, the first dump valve 1831 is opened to facilitate smooth forward movement of the hydraulic piston 1320, and the second pressure chamber 1340 is controlled to rapidly form negative pressure. 2 The dump valve 1841 can be switched to a closed state.

After completing the release of the second braking mode, it is possible to switch to the release operation of the first braking mode shown in FIG. 7 in order to completely release the braking pressure applied to the wheel cylinder 20.

7 is a hydraulic circuit diagram showing a state in which the hydraulic piston 1320 of the electronic brake system 1000 according to the present exemplary embodiment moves backward and releases the first braking mode.

Referring to FIG. 7, when the pedal effort applied to the brake pedal 10 is released, the motor generates rotational force in another direction and transmits it to the power conversion unit, and the power conversion unit moves the hydraulic piston 1320 backward. As a result, negative pressure may be generated in the first pressure chamber 1330, whereby the pressure medium of the wheel cylinder 20 may be transmitted to the first pressure chamber 1330.

Specifically, the hydraulic pressure of the first wheel cylinder 21 and the second wheel cylinder 22 provided in the first hydraulic circuit 1510 is the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and the ninth hydraulic oil. It is recovered to the first pressure chamber 1330 by passing through the furnace 1409 in sequence. At this time, since the fifth valve 1435 provided in the sixth hydraulic flow path 1406 is provided as a check valve that allows only the flow of the pressurized medium discharged from the first hydraulic circuit 1510, the pressurized medium can be transmitted, The seventh valve 1437 is opened to allow the flow of the pressurized medium through the ninth hydraulic flow path 1409. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 remain open, and the first outlet valve 1512a and the second outlet valve 1512b are closed. Keep it. In addition, the eighth valve 1438 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the second pressure chamber 1340 through the tenth hydraulic flow path 1410. , The first dump valve 1831 is closed to effectively form a negative pressure in the first pressure chamber 1330.

The hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the first pressure chamber 1330 is the seventh hydraulic flow path ( 1407), the eighth hydraulic flow passage 1408, and the ninth hydraulic flow passage 1409 are sequentially passed, and are recovered to the first pressure chamber 1330. As described above, the sixth valve 1436 provided in the seventh hydraulic flow path 1407 is provided as a check valve that allows only the flow of the pressurized medium discharged from the second hydraulic circuit 1520 so that the pressurized medium can be recovered. In addition, the seventh valve 1437 is opened to allow the flow of the pressurized medium through the ninth hydraulic flow path 1409. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are kept open. Furthermore, the eighth valve 1438 is controlled in a closed state to prevent leakage of the pressurized medium recovered from the second hydraulic circuit 1520 to the second pressure chamber 1340 through the tenth hydraulic passage 1410. . The third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are kept open.

At the same time, the second dump valve 1841 is opened so that the hydraulic piston 1320 can be moved back quickly and smoothly, so that the pressurized medium accommodated in the second pressure chamber 1340 passes through the second bypass flow path 1840. It may be discharged to the reservoir 1100.

Hereinafter, a case in which the electronic brake system 1000 according to the present embodiment does not operate normally, that is, an operating state of a fall-back mode will be described.

8 is a hydraulic circuit diagram showing an operation state in an abnormal operation mode (fallback mode) when the electronic brake system 1000 according to the present embodiment cannot be operated normally due to a device failure or the like.

Referring to FIG. 8, in the abnormal operation mode, each of the valves is controlled to an initial braking state, which is a non-operation state. At this time, when the driver applies a pedal effort to the brake pedal 10, the master piston 1220 connected to the brake pedal 10 advances and displacement occurs. In the non-operating state, since the first cut valve 1611 is provided in an open state, the pressurized medium accommodated in the master chamber 1220a by the advance of the master piston 1220 is subjected to the first hydraulic pressure along the first backup passage 1610. Braking may be implemented by being transmitted to the first wheel cylinder 21 and the second wheel cylinder 22 of the circuit 1510.

In addition, the pressurized medium accommodated in the master chamber 1220a advances the first simulation piston 1230 to generate displacement, whereby the pressurized medium accommodated in the first simulation chamber 1230a flows along the second backup passage 1620 It is transmitted to the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 to implement braking. At the same time, by the displacement of the first simulation piston 1230, the second simulation piston 1240 also advances to generate a displacement, so that the pressurized medium accommodated in the second simulation chamber 1240a is transferred along the auxiliary backup passage 1630 It may be provided to the second hydraulic circuit 1520 by joining the backup passage 1620. At this time, since the simulator valve 1261 is provided in a closed state in a non-operating state, the pressurized medium accommodated in the first simulation chamber 1230a is not discharged to the reservoir 1100 but is transferred to the second backup passage 1620 At the same time, it is possible to form a hydraulic pressure that advances the second simulation piston 1240, and since the inspection valve 1631 and the second cut valve 1621 are provided in an open state, the first simulation chamber 1230a and the second simulation The pressurized medium accommodated in the chamber 1240a may be delivered to the second backup passage 1620.

Hereinafter, an inspection mode of the electronic brake system 1000 according to the present embodiment will be described.

9 is a hydraulic circuit diagram showing the state of the inspection mode of the electronic brake system 1000 according to the present embodiment. Referring to FIG. 9, the electronic brake system 1000 according to the present embodiment is an integrated master cylinder 1200 or a simulator valve. It is possible to perform a test mode for checking whether the 1261 is leaked. When performing the inspection mode, the electronic control unit controls to supply the hydraulic pressure generated from the hydraulic pressure supply device 1300 to the first simulation chamber 1230a of the integrated master cylinder 1200.

Specifically, the electronic control unit operates to advance the hydraulic piston 1320 in a state in which each valve is controlled to an initial braking state in a non-operation state, thereby generating hydraulic pressure in the first pressure chamber 1330 and inspecting The valve 1631 and the first cut valve 1611 are switched to a closed state, and the second cut valve 1621 is maintained in an open state. Accordingly, the hydraulic pressure formed in the first pressure chamber 1330 is transmitted to the second hydraulic circuit 1520 through sequentially passing through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405. , The third inlet valve 1521a and the fourth inlet valve 1521b are kept open at normal times, and the pressurized medium delivered to the second hydraulic circuit 1520 is removed through the second backup passage 1620. 1 It flows into the simulation chamber 1230a. At this time, the simulator valve 1261 maintains a closed state to induce the first simulation chamber 1230a to be closed.

Meanwhile, for a quick inspection mode, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be switched to a closed state.

In this state, by comparing the hydraulic pressure value of the pressurized medium expected to be generated by the displacement of the hydraulic piston 1320 and the hydraulic pressure value of the second hydraulic circuit 1520 or the first simulation chamber 1230a measured by the pressure sensor PS , It is possible to diagnose the leak of the integrated master cylinder 1200 or the simulator valve 1261. Specifically, two hydraulic pressure values are compared with the expected hydraulic pressure value calculated based on the displacement amount of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown) and the actual hydraulic pressure value measured by the pressure sensor PS. If is matched, it may be determined that there is no leak in the integrated master cylinder 1200 or the simulator valve 1261. On the contrary, if the actual hydraulic pressure value measured by the pressure sensor PS is lower than the expected hydraulic pressure value calculated based on the displacement amount of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown), the first simulation Since a part of the hydraulic pressure of the pressurized medium applied to the chamber 1230a is lost, it is determined that a leak exists in the integrated master cylinder 1200 or the simulator valve 1261, and this may be notified to the driver.

1000: electronic brake system
1100: reservoir 1200: integrated master cylinder
1220: master piston 1220a: master chamber
1230: first simulation piston 1230a: first simulation chamber
1240: second simulation piston 1240a: second simulation chamber
1250: elastic member 1260: simulation flow path
1261: simulator valve 1300: hydraulic supply
1320: hydraulic piston 1330: first pressure chamber
1340: second pressure chamber 1400: hydraulic control unit
1401: first hydraulic flow path 1402: second hydraulic flow path
1403: third hydraulic flow path 1404: fourth hydraulic flow path
1405: 5th hydraulic flow 1406: 6th hydraulic flow
1407: 7th hydraulic flow 1408: 8th hydraulic flow
1409: 9th hydraulic flow 1410: 10th hydraulic flow
1431: first valve 1432: second valve
1433: third valve 1434: fourth valve
1435: fifth valve 1436: sixth valve
1437: seventh valve 1438: eighth valve
1510: first hydraulic circuit 1520: second hydraulic circuit
1610: first backup flow path 1611: first cut valve
1620: second backup flow path 1621: second cut valve
1630: auxiliary backup flow path 1631: inspection valve
1710: first reservoir euro 1720: second reservoir euro
1730: 3rd reservoir Euro 1800: dump control unit
1810: first dump passage 1811: first dump check valve
1820: second dump passage 1821: second dump check valve
1830: first bypass flow path 1831: first dump valve
1840: second bypass flow path 1841: second dump valve

Claims (21)

A reservoir in which the pressurized medium is stored;
An integrated master cylinder having a master chamber and a simulation chamber;
A reservoir flow path for communicating the integrated master cylinder and the reservoir;
A first pressure provided on one side of the hydraulic piston that is movably accommodated in the cylinder block by operating a hydraulic piston by an electrical signal output in response to the displacement of the brake pedal and connected to one or more wheel cylinders A hydraulic pressure supply device including a chamber and a second pressure chamber provided on the other side of the hydraulic piston and connected to one or more wheel cylinders;
A hydraulic control unit having a first hydraulic circuit for controlling hydraulic pressure transmitted to the two wheel cylinders and a second hydraulic circuit for controlling hydraulic pressure transmitted to the other two wheel cylinders; And
Including; an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal,
The hydraulic control unit
A first hydraulic flow passage in communication with the first pressure chamber, a second hydraulic flow passage in communication with the second pressure chamber, a third hydraulic flow passage in which the first hydraulic flow passage and the second hydraulic flow passage merge, and the second hydraulic flow passage 3 A fourth hydraulic channel branched from the hydraulic channel and connected to the first hydraulic circuit, a fifth hydraulic channel branched from the third hydraulic channel and connected to the second hydraulic circuit, and the first hydraulic circuit A sixth hydraulic passage, a seventh hydraulic passage communicating with the second hydraulic circuit, an eighth hydraulic passage where the sixth hydraulic passage and the seventh hydraulic passage merge, and the eighth hydraulic passage branched from the An electronic brake system comprising: a ninth hydraulic passage connected to the first pressure chamber, and a tenth hydraulic passage branched from the eighth hydraulic passage and connected to the second pressure chamber. The method of claim 1,
The hydraulic control unit
A first valve provided in the first hydraulic passage to control the flow of the pressurized medium, a second valve provided in the second hydraulic passage to control the flow of the pressurized medium, and a flow of the pressurized medium provided in the fourth hydraulic passage A third valve to control, a fourth valve provided in the fifth hydraulic passage to control the flow of the pressurized medium, a fifth valve provided in the sixth hydraulic passage to control the flow of the pressurized medium, and the seventh hydraulic passage A sixth valve provided in the pressurized medium to control the flow of the pressurized medium, a seventh valve provided in the ninth hydraulic passage to control the flow of the pressurized medium, and an eighth valve provided in the tenth hydraulic passage to control the flow of the pressurized medium Electronic brake system comprising a. The method of claim 2,
The first valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the first pressure chamber,
The second valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the second pressure chamber,
The third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic flow path to the first hydraulic circuit,
The fourth valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic passage to the second hydraulic circuit,
The fifth valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the first hydraulic circuit,
The sixth valve is provided as a check valve that allows only the flow of the pressurized medium discharged from the second hydraulic circuit,
The seventh valve and the eighth valve are provided with solenoid valves that control the flow of the pressurized medium in both directions. The method of claim 3,
The simulation chamber is
A first simulation chamber and a second simulation chamber,
The integrated master cylinder
A master piston provided in the master chamber and provided to be displaceable by a brake pedal, and a master piston provided in the first simulation chamber and provided to be displaceable by the displacement of the master piston or the hydraulic pressure of the pressurized medium accommodated in the master chamber. 1 simulation piston, a second simulation piston provided in the second simulation chamber and capable of being displaced by the displacement of the first simulation piston or the hydraulic pressure of the first simulation chamber, the first simulation piston and the second An electronic brake system comprising an elastic member provided between the simulation pistons, a simulation flow path connecting the first simulation chamber and the reservoir, and a simulator valve provided in the simulation flow path to control the flow of a pressurized medium. The method of claim 4,
A first backup passage connecting the master chamber and the first hydraulic circuit;
A second backup passage connecting the first simulation chamber and the second hydraulic circuit;
An auxiliary backup passage connecting the second simulation chamber and the second backup passage; And
An electronic brake system further comprising a; inspection valve provided in the auxiliary backup passage to control the flow of the pressurized medium. The method of claim 5,
A first cut valve provided in the first backup passage to control the flow of the pressurized medium; And
An electronic brake system further comprising at least one second cut valve provided in the second backup passage and controlling the flow of the pressurized medium. The method of claim 6,
A dump control unit provided between the reservoir and the hydraulic pressure supply device to control the flow of the pressurized medium; further comprising,
The dump control unit
A first dump passage connecting the first pressure chamber and the reservoir; a first dump check valve provided in the first dump passage and allowing only a flow of a pressurized medium from the reservoir to the first pressure chamber; and 1 A first bypass flow path connected in parallel with the first dump check valve on the dump flow path, a first dump valve provided in the first bypass flow path to control flow in both directions of the pressurized medium, and the second pressure A second dump passage connecting the chamber and the reservoir; a second dump check valve provided in the second dump passage and allowing only the flow of a pressurized medium from the reservoir to the second pressure chamber; and on the second dump passage An electronic brake system including a second bypass flow path connected in parallel with the second dump check valve, and a second dump valve provided in the second bypass flow path to control flow of the pressurized medium in both directions. The method of claim 7,
The first hydraulic circuit is
A first inlet valve and a second inlet valve respectively controlling the flow of the pressurized medium supplied to the first wheel cylinder and the second wheel cylinder, and a pressurizing medium discharged from the first wheel cylinder and the second wheel cylinder to the reservoir Including a first outlet valve and a second outlet valve respectively controlling the flow of,
The second hydraulic circuit is
A third inlet valve and a fourth inlet valve respectively controlling the flow of the pressurized medium supplied to the third wheel cylinder and the fourth wheel cylinder,
The second backup flow path
An electronic brake system provided to connect at least one of the downstream side of the third and fourth inlet valves to the first simulation chamber. The method of claim 8,
The reservoir flow path is
A first reservoir flow path connecting the reservoir and the master chamber, a second reservoir flow path connecting the reservoir and the first simulation chamber, and a third reservoir flow path connecting the reservoir and the second simulation chamber. Electronic brake system. The method of claim 9,
The electronic brake system further comprises a reservoir valve provided in the second reservoir flow path and allowing only the flow of the pressurized medium from the reservoir to the first simulation chamber. The method of claim 4,
The integrated master cylinder
An electronic brake system comprising a piston spring elastically supporting the master piston, a first simulator spring elastically supporting the first simulation piston, and a second simulator spring elastically supporting a second simulation piston. In the method of operating the electronic brake system according to claim 7,
In normal operation mode,
The first cut valve is closed to seal the master chamber, the inspection valve is closed to seal the second simulation chamber, and the second cut valve is closed, but the simulator valve is opened and the first simulation chamber and By communicating the reservoir, the first simulation piston compresses the elastic member by the operation of the brake pedal, and the elastic restoring force of the elastic member is provided to the driver as a pedal feel. In the method of operating the electronic brake system according to claim 12,
The normal operation mode is
As the hydraulic pressure of the pressurized medium transferred from the hydraulic pressure supply device to the wheel cylinder gradually increases, a first braking mode providing hydraulic pressure primarily, a second braking mode providing hydraulic pressure secondary, and a third A method of operating an electronic brake system including a third braking mode providing hydraulic pressure. The method of claim 13,
The first braking mode is
The eighth valve and the first dump valve are closed,
The hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston is provided to the first hydraulic circuit through the first hydraulic channel, the third hydraulic channel, and the fourth hydraulic channel in sequence, and the first hydraulic oil A method of operating an electronic brake system provided to the second hydraulic circuit through a furnace, the third hydraulic flow path, and the fifth hydraulic flow path sequentially. The method of claim 14,
The second braking mode is
The seventh valve and the second dump valve are closed,
After the first braking mode, the hydraulic pressure formed in the second pressure chamber by the reversing of the hydraulic piston is provided to the first hydraulic circuit through the second hydraulic channel, the third hydraulic channel, and the fourth hydraulic channel in sequence. And the second hydraulic flow path, the third hydraulic flow path, and the fifth hydraulic flow path sequentially to be provided to the second hydraulic circuit. The method of claim 15,
The third braking mode is
The seventh valve and the seventh valve are opened, the first dump valve and the second dump valve are closed,
Part of the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston is provided to the first hydraulic circuit sequentially through the first hydraulic channel, the third hydraulic channel, and the fourth hydraulic channel. It is provided to the second hydraulic circuit sequentially through 1 hydraulic flow path, the third hydraulic flow path and the fifth hydraulic flow path,
A method of operating an electronic brake system in which the remaining part of the hydraulic pressure formed in the first pressure chamber is sequentially supplied to the second pressure chamber through the ninth hydraulic flow path and the tenth hydraulic flow path. The method of claim 14,
Release of the first braking mode
The seventh valve and the second dump valve are opened, the eighth valve and the first dump valve are closed,
By reversing the hydraulic piston, negative pressure is generated in the first pressure chamber, and the pressurizing medium provided to the first hydraulic circuit sequentially passes through the sixth hydraulic flow path, the eighth hydraulic flow path, and the ninth hydraulic flow path. An electronic brake system that is recovered to the first pressure chamber, and the pressurized medium provided to the second hydraulic circuit is recovered to the first pressure chamber through the seventh hydraulic flow path, the eighth hydraulic flow path, and the ninth hydraulic flow path sequentially How it works. The method of claim 15,
Release of the second braking mode
The eighth valve and the first dump valve are opened, the seventh valve and the second dump valve are closed,
By advancing the hydraulic piston, negative pressure is generated in the second pressure chamber, so that the pressurizing medium provided to the first hydraulic circuit sequentially passes through the sixth hydraulic flow path, the eighth hydraulic flow path, and the tenth hydraulic flow path. An electronic brake system that is recovered to the second pressure chamber, and the pressurized medium provided to the second hydraulic circuit is recovered to the second pressure chamber through the seventh hydraulic passage, the eighth hydraulic passage, and the tenth hydraulic passage sequentially How it works. The method of claim 16,
Release of the third braking mode
The seventh valve and the eighth valve are opened, the first dump valve is closed,
By reversing the hydraulic piston, negative pressure is generated in the first pressure chamber, and the pressurizing medium provided to the first hydraulic circuit sequentially passes through the sixth hydraulic flow path, the eighth hydraulic flow path, and the ninth hydraulic flow path. The pressurized medium is recovered to the first pressure chamber and provided to the second hydraulic circuit is recovered to the first pressure chamber through the seventh hydraulic channel, the eighth hydraulic channel, and the ninth hydraulic channel sequentially,
At least a portion of the pressurizing medium of the second pressure chamber is supplied to the first pressure chamber sequentially through the tenth hydraulic flow path and the ninth hydraulic flow path. The method of claim 12,
In abnormal operation mode,
The first cut valve is opened so that the master chamber and the first hydraulic circuit are communicated, the simulator valve is closed, but the second cut valve is opened so that the first simulation chamber and the second hydraulic circuit are communicated, The inspection valve is opened to communicate the second simulation chamber and the second hydraulic circuit,
According to the pedal effort of the brake pedal, the pressurizing medium of the master chamber is provided to the first hydraulic circuit through the first backup passage, and the pressurizing medium of the first simulation chamber is the second hydraulic pressure through the second backup passage. A method of operating an electronic brake system provided as a circuit, wherein the pressurizing medium of the second simulation chamber is provided to the second hydraulic circuit sequentially through the auxiliary backup passage and the second backup passage. In the method of operating the electronic brake system according to claim 8,
In the inspection mode to check whether the integrated master cylinder or simulator valve is leaking,
Closing the first cut valve, the simulator valve, and the inspection valve,
The hydraulic pressure generated by operating the hydraulic pressure supply device is provided to the first simulation chamber through the hydraulic control unit, the third inlet valve, the fourth inlet valve, and the second backup passage in sequence,
An electronic brake system that compares the hydraulic pressure value of the pressurized medium that is expected to occur based on the displacement amount of the hydraulic piston and the hydraulic pressure value of the pressurized medium measured by a pressure sensor in the second hydraulic circuit or the first simulation chamber. How it works.

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