KR20200138585A - Electric brake system and Operating method of therof - Google Patents

Abstract

Disclosed are an electronic brake system and an operating method thereof. According to an embodiment of the present invention, the electronic brake system includes: a reservoir storing a pressing medium; an integrated master cylinder including a master chamber and a simulation chamber; a reservoir flow path making the integrated master cylinder and the reservoir communicate with each other; a fluid pressure supply apparatus generating fluid pressure by actuating a hydraulic piston by an electric signal output in response to the displacement of the brake pedal, and including a first pressure chamber provided on one side of the hydraulic piston stored to be movable in a cylinder block to be connected with at least one wheel cylinder, and a second pressure chamber provided on the other side of the hydraulic piston to be connected with at least one wheel cylinder; a hydraulic control unit including a first hydraulic circuit controlling fluid pressure delivered to two wheel cylinders and a second hydraulic circuit controlling fluid pressure delivered to two other wheel cylinders; and an electronic control unit controlling valves based on displacement information of the brake pedal and fluid pressure information. The hydraulic control unit includes: a first hydraulic flow path communicating with the first pressure chamber; a second hydraulic flow path communicating with the second pressure chamber; a third hydraulic flow path where the first and second hydraulic flow paths join; a fourth hydraulic flow path branched from the third hydraulic flow path to be connected with the first hydraulic circuit; and a fifth hydraulic flow path branched from the third hydraulic flow path to be connected with the second hydraulic circuit.

Description

Electric brake system and operating method of therof

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

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 has been 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. Electronic brake systems and operating methods including a hydraulic pressure providing unit that receives a signal and supplies hydraulic pressure required for braking to a wheel cylinder are widely spread.

In such an electronic brake system and operation method, 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 unit is electrically operated and controlled to generate the hydraulic pressure required for braking to the wheel cylinder. Deliver. 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 and operation method enters an abnormal operation mode when one component element fails or falls into an uncontrollable state, and in this case, a mechanism in which the driver's brake pedal operation is directly linked to the wheel cylinder is required. That is, in the abnormal operation mode of the electronic brake system and the operation method, 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 is to provide an electronic brake system and operation method capable of reducing the number of parts and miniaturization and weight reduction of products by integrating a master cylinder and a simulation device into one.

The present embodiment is to provide an electronic brake system and operation method capable of implementing stable and effective braking even in various operating situations.

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

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

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

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 unit including a second pressure chamber connected to one or more wheel cylinders, a first hydraulic circuit controlling hydraulic pressure transmitted to two wheel cylinders, and a second hydraulic pressure controlling hydraulic pressure transmitted to the other two wheel cylinders A hydraulic control unit having a circuit 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 path in communication with the first pressure chamber, 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 branched from the third hydraulic flow path and connected to the first hydraulic circuit. A fourth hydraulic flow path and a fifth hydraulic flow path branching from the third hydraulic flow path and connected to the second hydraulic circuit may be provided.

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 pressure discharged from the first wheel cylinder and the second wheel cylinder. A first outlet valve and a second outlet valve respectively controlling the flow of the medium, and a discharge valve for controlling the flow of the pressurized medium supplied to the reservoir through the first outlet valve and the second outlet valve, respectively, , The discharge valve may be provided as a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium.

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 It may be provided, including a third valve for controlling the flow of the pressurized medium, and a fourth valve provided in the fifth hydraulic flow path for controlling the flow of the pressurized medium.

The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is provided as a solenoid valve that controls the flow of the pressurized medium in both directions. , 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 directed from the third hydraulic flow path to the second hydraulic circuit. It may be provided with a check valve that allows only the flow of the pressurized medium.

The simulation chamber includes a first simulation chamber and a second simulation chamber, and the integrated master cylinder includes a master chamber, a master piston provided in the master chamber and displaceable by a brake pedal, and a first simulation chamber. And, a first simulation piston provided in the first simulation chamber and displaceable by a displacement of the master piston or a hydraulic pressure of a pressurized medium accommodated in the master chamber, a second simulation chamber, and the second simulation chamber. A second simulation piston provided to be displaced by displacement of the first simulation piston or by hydraulic pressure in the first simulation chamber, an elastic member provided between the first simulation piston and the second simulation piston, and the 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 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 The auxiliary backup passage may further include a first cut valve provided in the first backup passage to control the flow of the pressurized medium, and a second cut valve provided in the second backup passage to control the flow of the pressurized medium.

The second cut valve or the simulator valve may be provided as a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium discharged from the third and fourth wheel cylinders to the reservoir.

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 second hydraulic circuit includes third and fourth inlet valves respectively controlling the flow of the pressurized medium supplied to the third and fourth wheel cylinders, and the second backup flow channel is a downstream side of the fourth inlet valve and It may be provided to connect the first simulation chamber.

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 includes a first dump passage connecting the first pressure chamber and the reservoir, and the second pressure chamber And a second dump passage connecting the reservoir and a first dump check valve provided in the first dump passage and allowing only the flow of the pressurized medium from the reservoir to the first pressure chamber, and provided in the second dump passage It may be provided including a second dump check valve allowing only the flow of the pressurized medium from the reservoir to the second pressure chamber.

The integrated master cylinder may be provided including a first simulator spring elastically supporting the second simulation piston.

The integrated master cylinder may further include a second simulator spring interposed between the first simulation piston and the second simulation piston.

The hydraulic control unit may include a sixth hydraulic flow path provided to connect the first and second hydraulic flow paths, and may further include a fifth valve provided in the sixth hydraulic flow path to control the flow of the pressurized medium. .

The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is pressurized from the second pressure chamber to the third hydraulic flow path. It is provided as a check valve that allows only the flow of the medium, and the third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic channel to the first hydraulic circuit, and the fourth valve is 3 It is provided as a check valve that allows only the flow of the pressurized medium from the hydraulic flow path to the second hydraulic circuit, and the fifth valve may be provided as a solenoid valve that controls the flow of the pressurized medium in both directions.

The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is pressurized from the second pressure chamber to the third hydraulic flow path. It is provided as a check valve that allows only the flow of the medium, and the third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic channel to the first hydraulic circuit, and the fourth and fifth valves May be provided as a solenoid valve that controls the flow of the pressurized medium in both directions.

It may further include a generator provided in each of the third wheel cylinder and the fourth wheel cylinder of the second hydraulic circuit.

In the method of operating an electronic brake system, in a normal operation mode, the first cut valve is closed to seal the master chamber, the second cut valve is closed, but the simulator valve is opened to open the first simulation chamber and the 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 can be provided to the driver as a pedal feel.

In the normal operation mode, as the hydraulic pressure transferred from the hydraulic pressure providing unit 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 to operate sequentially in a third braking mode that provides a third hydraulic pressure.

The release of the first to third braking modes controls the degree of opening of the discharge valve, so that the pressurized medium provided to the first hydraulic circuit is recovered to the reservoir through the discharge valve, and the second cut valve and the simulator valve And the pressurizing medium provided in the second hydraulic circuit may be provided to be recovered to the reservoir through the second backup passage, the first simulation chamber, and the simulation passage in sequence.

In the 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 to the first and second simulation chambers and the The second hydraulic circuit is communicated, and the pressurizing medium of the master chamber is provided to the first hydraulic circuit through the first backup passage according to the pedal effort of the brake pedal, and the pressurizing medium of the first simulation chamber is the second It is provided to the second hydraulic circuit through a backup channel, and the pressurizing medium of the second simulation chamber may be provided to the second hydraulic circuit through the auxiliary jack-up channel and the second backup channel in sequence.

In the method of operating the electronic brake system, in the inspection mode in which the integrated master cylinder or the simulator valve is leaked, the first cut valve and the simulator valve are closed, and the hydraulic pressure generated by operating the hydraulic pressure supply device is controlled. The hydraulic control unit, the third inlet valve, the fourth inlet valve, and the second backup passage are sequentially passed to the first simulation chamber, and the pressure is expected to occur based on the displacement amount of the hydraulic piston. It may be provided to compare the hydraulic pressure value of the medium with the hydraulic pressure value of the pressurized medium measured by the pressure sensor in the first simulation chamber or the second hydraulic circuit.

In the method of operating an electronic brake system, in the regenerative braking mode by the generator, the fourth valve is closed, and the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston is applied to the first hydraulic flow path and the first pressure. It is provided to the first hydraulic circuit through the 3 hydraulic flow path and the fourth hydraulic flow path in sequence, and the supply of hydraulic pressure to the third and fourth wheel cylinders may be blocked and provided.

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

The electronic brake system and operation method according to the present embodiment can implement stable and effective braking in various operating situations of a vehicle.

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

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

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

The electronic brake system and operation method according to the exemplary embodiment of the present invention 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 a first embodiment.
2 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment performs a first braking mode.
3 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment performs a second braking mode.
4 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment performs a third braking mode.
5 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment releases a braking mode.
6 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment operates in an abnormal state (fallback mode).
7 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment performs an inspection mode.
8 is a hydraulic circuit diagram showing an electronic brake system according to a second embodiment.
9 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the second embodiment performs a first braking mode.
10 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the second embodiment performs a second braking mode.
11 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the second embodiment performs a third braking mode.
12 is a hydraulic circuit diagram showing an electronic brake system according to a third embodiment.
13 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the third embodiment performs a regenerative braking 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 a first embodiment of the present invention.

Referring to FIG. 1, the electronic brake system 1000 according to the first embodiment of the present invention provides a reaction force according to the foot of the brake pedal 10 and a reservoir 1100 in which a pressurized medium is stored, and at the same time, An integrated master cylinder 1200 that pressurizes and discharges a pressurized medium such as brake oil contained inside, 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. The hydraulic pressure supply device 1300 for generating hydraulic pressure of the pressurized medium through mechanical operation, 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 are transmitted to each wheel It is provided between hydraulic circuits 1510 and 1520 having wheel cylinders 20 for braking (RR, RL, FR, FL), and between the hydraulic pressure supply device 1300 and the reservoir 1100 to prevent the flow of the pressurized medium. A control dump control unit 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 It includes a reservoir flow path 1700 that is hydraulically connected, and an electronic control unit (ECU, not shown) that controls the hydraulic pressure supply device 1300 and various valves based on hydraulic pressure information and 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 to be displaceable by the operation of the brake pedal 10, a piston spring elastically supporting the master piston 1220, and a cylinder A first simulation chamber 1230a formed inside the master chamber 1220a on the block 1210, and provided in the first simulation chamber 1230a, the displacement of the master piston 1220 or accommodated in the master chamber 1220a. A first simulation piston 1230 provided to be displaceable by the hydraulic pressure of the pressurized medium, a second simulation chamber 1240a formed inside the first simulation chamber 1230a on the cylinder block 1210, and a second A second simulation piston 1240 provided in the simulation chamber 1240a and capable of being displaced by the displacement of the first simulation piston 1230 or the hydraulic pressure of the pressurized medium accommodated in the first simulation chamber 1230a, and a first simulation An elastic member 1250 disposed between the piston 1230 and the second simulation piston 1240 to provide a pedal feel through an elastic restoring force generated during compression, and a first simulator spring elastically supporting the second simulation piston 1240 1272, a second simulator spring 1271 interposed between the first simulation piston 1230 and the second simulation piston 1240 to elastically support the first simulation piston 1230, and the master chamber 1220a A first reservoir flow path 1710 connecting the reservoir 1100, a second reservoir flow path 1720 connecting the first simulation chamber 1230a and the reservoir 1100, and a second simulation chamber 1240a and a reservoir ( The third reservoir flow path 1730 connecting the 1100 and the first simulator A simulation flow path 1260 connecting the ration chamber 1230a and the reservoir 1100 and a simulator valve 1261 provided in the simulation flow path 1260 to control the flow of the pressurized medium may be included.

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.

The master chamber 1220a is connected to the reservoir 1100 through the first reservoir flow path 1710, and the first simulation chamber 1230a is the reservoir 1100 through the second reservoir flow path 1720 and the simulation flow path 1260. And the second simulation chamber 1240a may be connected to the reservoir 1100 through the third reservoir flow path 1730.

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.

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 simulation flow path 1260 is connected in parallel with the second reservoir flow path 1720, and a simulator valve 1261 provided as a two-way valve that controls the flow of the pressurized medium transmitted through the simulation flow path 1260 is installed. In addition, 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 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 able to reciprocate.

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 and the fourth hydraulic port 1280d are connected to the second reservoir passage 1720 and the second backup passage 1620 so that the pressurized medium accommodated in the first simulation chamber 1230a is stored in the reservoir 1100. And the second backup passage 1620 may be discharged, and on the contrary, the pressurized medium may be introduced from the reservoir 1100 and the second backup passage 1620.

Meanwhile, in the drawing, several reservoirs 1100 are shown, and each of the reservoirs 1100 is denoted by the same reference numeral. These reservoirs 1100 may be provided with the same parts or different parts.

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.

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 and the sixth hydraulic port 1280f are connected to the third reservoir flow path 1730 and the auxiliary backup flow path 1630 so that the pressurized medium is discharged toward the second simulation chamber 1240a, or vice versa. The pressurized medium accommodated in the second simulation chamber 1240a may be introduced.

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.

When the pedal simulation operation by the integrated master cylinder 1200 is described in more detail, the first cut provided in the first backup passage 1610 to be described later when the driver applies the pedal effort by operating the brake pedal 10 during normal operation. The valve 1611 is closed, and the simulator valve 1261 of the simulation flow path 1260 is opened. The master piston 1220 moves according to the displacement of the brake pedal to pressurize the pressurized medium in the master chamber 1220a, and the hydraulic pressure is the front surface of the first simulation piston 1230 (the right side of the first simulation piston based on the drawing). ), a displacement occurs in the first simulation piston 1230. Since the second simulation chamber 1240a is sealed and the second simulation piston 1240 does not displace, the displacement of the first simulation piston 1230 compresses the elastic member 1250, and the elastic member 1250 The pedal feel can be provided to the driver by the elastic restoring force by compression. 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 restoration spring (not shown) and the elastic member 1250 expand by the elastic force so that the first simulation piston 1230 and the master piston 1220 return to their original positions. Then, the first simulation chamber 1230a may be filled by supplying a pressurized medium through the second reservoir flow path 1720.

In this way, since the inside of the first simulation chamber 1230a is always filled with the pressurized medium, friction between the first simulation piston 1230 and the second simulation piston and the elastic members 1240 and 1250 is minimized during the pedal simulation operation. In addition to improving the durability of the master cylinder 1200, the inflow of foreign substances from the outside may 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 method will be described later with reference to FIG. 6.

The hydraulic pressure providing unit 1300 is provided to generate the 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 providing unit 1300 provides a pressurized medium pressure transmitted to the wheel cylinders 21, 22, 23, 24, but a motor (not shown) that generates rotational force by an electrical signal from the pedal displacement sensor 11, It may include a power conversion unit (not shown) for converting and transmitting the rotational motion of the motor (not shown) into linear motion. The hydraulic pressure providing unit 1300 may be operated not by a driving force supplied from a motor (not shown) but by a pressure supplied from a high pressure accumulator. The hydraulic pressure providing unit 1300 includes a cylinder block 1310 having a pressure chamber that receives and stores a pressurized medium, a hydraulic piston 1320 accommodated in the cylinder block 1310, a hydraulic piston 1320, and a cylinder block. It includes a sealing member (1350, 1350b) provided between 1310 and sealing the pressure chamber, and a drive shaft (1390) for transmitting the power output from the power conversion unit (not shown) to the hydraulic piston 1320.

The pressure chamber is a first pressure chamber 1330 located in front of the hydraulic piston 1320 (in the forward direction, in the left direction of the hydraulic piston based on the drawing), and the rear of the hydraulic piston 1320 (reverse direction, based on the drawing). It may include a second pressure chamber 1340 located in the right direction of the hydraulic piston). 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 (not shown) formed in the cylinder block 1310, and the second pressure chamber 1340 is a cylinder block. It is connected to a second hydraulic flow path 1402 to be described later through a second communication hole (not shown) formed in 1310.

The sealing member is provided between the hydraulic piston 1320 and the cylinder block 1310 and seals between the first pressure chamber 1330 and the second pressure chamber 1340, a piston sealing member 1350, and a drive shaft 1390. It includes a drive shaft sealing member (1350b) provided between the cylinder block (1310) to seal 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 1350 and the drive shaft sealing member 1350b. It can be delivered to the first hydraulic flow path 1401 and the second hydraulic flow path 1402 described later without leakage.

The dump control unit 1800 includes a first dump check valve 1811 and a second dump check provided on the first dump passage 1810, the second dump passage 1820, and the first and second dump passages 1820, respectively. Equipped with a valve 1821. The first and second pressure chambers 1330 and 113 are connected to the reservoir 1100 by first and second dump passages 1810 and 1820, respectively, and are connected to the reservoir 1100 by first and second dump passages 1810 and 1820, respectively. It is possible to receive and receive the pressurized medium from the reservoir 1100. To this end, the first dump passage 1810 may be provided in communication with the first pressure chamber 1330 by a third communication hole (not shown) formed in the cylinder block 1310 and connected to the reservoir 1100, The second dump passage 1820 may be provided in communication with the second pressure chamber 1340 by a fourth communication hole (not shown) formed in the cylinder block 1310 to be connected to the reservoir 1100. First and second dump check valves 1811 and 1821 for controlling the flow of the pressurized medium may be provided in the first and second dump passages 1810 and 1820, respectively. Referring again to FIG. 1, the first dump check valve 1811 is 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 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 1340 and block the flow of the pressurized medium in the opposite direction.

The motor (not shown) is provided to generate a driving force by an electrical signal output from the electronic control unit (ECU). The motor (not shown) may be provided including the stator 121 and the rotor 122, and may provide power for generating 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 (not shown) can be precisely controlled by a motor control sensor (not shown). Since the motor (not shown) is a well-known technology, detailed description will be omitted.

The power conversion unit (not shown) is provided to convert the rotational force of the motor (not shown) into linear motion. The power conversion unit (not shown) may be provided in a structure including, for example, a worm shaft (not shown), a worm wheel (not shown), and a drive shaft 1390.

The worm shaft (not shown) may be integrally formed with a rotational shaft of a motor (not shown), and a worm is formed on an outer circumferential surface to engage with the worm wheel (not shown) to rotate the worm wheel (not shown). The worm wheel (not shown) is connected to mesh with the drive shaft 1390 to move the drive shaft 1390 linearly, and the drive shaft 1390 is connected to the hydraulic piston 1320, through which the hydraulic piston 1320 is a cylinder. It may be slidably moved within the block 1310.

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 a motor (not shown) to cause a worm. The shaft (not shown) is rotated in one direction. The rotational force of the worm shaft (not shown) is transmitted to the drive shaft 1390 via a worm wheel (not shown), and the hydraulic piston 1320 connected to the drive shaft 1390 advances within the cylinder block 1310, while the first pressure chamber ( 1330) can generate hydraulic pressure.

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 a motor (not shown) to drive a worm shaft (not shown). Rotate in the opposite direction. The rotational force of the worm shaft (not shown) is transmitted to the drive shaft 1390 via a worm wheel (not shown), and the hydraulic piston 1320 connected to the drive shaft 1390 moves backward in the cylinder block 1310 while the second pressure chamber ( 1340) can generate hydraulic pressure.

Meanwhile, although not shown in the drawings, the power conversion unit (not shown) may be configured as a ball screw nut assembly. For example, a screw formed integrally with the rotation shaft of a motor (not shown) or connected to rotate with the rotation shaft of a motor (not shown), and a ball nut that is screwed with the screw in a state where rotation is restricted to move linearly according to the rotation of the screw The structure of such a ball screw nut assembly is a well-known technique, so a detailed description thereof will be omitted. In addition, the power conversion unit (not shown) according to the first embodiment of the present invention is not limited to any one structure as long as it can convert a rotational motion into a linear motion, and it is also understood in the case of a device of various structures and methods. Should be.

The hydraulic control unit 1400 may be provided to control the hydraulic pressure transmitted to the wheel cylinders 21, 22, 23, 24, and the electronic control unit (ECU) is based on the hydraulic pressure information and the pedal displacement information. 1300) and various valves are provided to control.

The hydraulic control unit 1400 is a first hydraulic circuit 1510 that controls the flow of hydraulic pressure delivered to the first and second wheel cylinders 21 and 22 among the four wheel cylinders 21, 22, 23, and 24. And, it may be provided with a second hydraulic circuit (1520) for controlling the flow of hydraulic pressure delivered to the third and fourth wheel cylinders (23, 24), from the integrated master cylinder 1200 and the hydraulic pressure providing unit (1300). It includes a plurality of flow paths and valves to control the hydraulic pressure delivered to the wheel cylinder.

Hereinafter, the hydraulic control unit 1400 will be described with reference to FIG. 1 again.

Referring to FIG. 1, a first hydraulic flow path 1401, a third hydraulic flow path 1403, and a fourth hydraulic flow path 1404 are provided to connect the first pressure chamber 1330 and the first hydraulic circuit 1510. , The first hydraulic passage 1401, the third hydraulic passage 1403, and the fifth hydraulic passage 1405 may be provided to connect the first pressure chamber 1330 and the second hydraulic circuit 1520. Accordingly, the hydraulic pressure generated in the first pressure chamber 1330 due to the advance of the hydraulic piston 1320 is transferred to the first hydraulic circuit 1510 and the second hydraulic circuit through the fourth hydraulic flow path 1404 and the fifth hydraulic flow path 1405. Can be passed to (1520).

A first valve 1411 and a second valve 1412 for controlling the flow of the pressurized medium may be provided in the first hydraulic passage 1401 and the second hydraulic passage 1402, and the first valve 1411 1 Allows only the flow of the pressurized medium from the pressure chamber 1330 to the first and second hydraulic circuits 1510 and 1520, and the second valve 1412 is a second hydraulic oil in communication with the second pressure chamber 1340. It may be provided as a two-way valve that controls the flow of the pressurized medium delivered along the furnace 1402. The second valve 2412 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 third valve 1413 and a fourth valve 1414 for controlling the flow of the pressurized medium may be provided in the fourth hydraulic flow path 1404 and the fifth hydraulic flow path 1405. The third valve 1413 allows only the flow of the pressurized medium in the direction from the first and second pressure chambers 1330 and 113 toward the first hydraulic circuit 1510, and the fourth valve 1414 is the first and second A check valve may be provided that allows only the flow of the pressurized medium in a direction from the pressure chambers 1330 and 1340 toward the second hydraulic circuit 1520 and blocks the flow of the pressurized medium in the opposite direction. The third hydraulic flow path 1403 may be provided to connect the first hydraulic flow path 1401 and the second hydraulic flow path 1402, the fourth hydraulic flow path 1404 and the fifth hydraulic flow path 1405.

Hereinafter, the first hydraulic circuit 1510 and the second hydraulic circuit 1520 of the hydraulic control unit 1400 will be described.

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

The first hydraulic circuit 1510 receives hydraulic pressure from the hydraulic pressure providing unit 1300 through the fourth hydraulic flow path 1404, and the fourth hydraulic flow path 1404 includes the first wheel cylinder 21 and the second wheel cylinder. It can be provided by branching into two flow paths connected to 22). Likewise, the second hydraulic circuit 1520 receives hydraulic pressure from the hydraulic pressure providing unit 1300 through the fifth hydraulic flow path 1405, and the fifth hydraulic flow path 1405 includes a third wheel cylinder 23 and a fourth wheel. It may be provided by branching into two flow paths connected to the cylinder 24.

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

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 may be provided to allow only the flow of the pressurized medium from each wheel cylinder to the hydraulic pressure providing unit 1300 and to block the flow of the pressurized medium from the hydraulic pressure providing unit 1300 to the wheel cylinder. . The first to fourth check valves 1513a, 1513b, 1523a, and 1523b can quickly remove the hydraulic pressure of the pressurized medium applied to the first to fourth wheel cylinders 21, 22, 23, and 24. 4 Even when the inlet valves 1511a, 1511b, 1521a, and 1521b do not operate normally, the hydraulic pressure of the pressurized medium applied to the wheel cylinder is allowed to flow into the hydraulic pressure providing unit 1300.

The first hydraulic circuit 1510 is connected to the first and second wheel cylinders 21 and 22, respectively, and is selectively opened when braking is released, thereby discharging the pressurized medium from the first and second wheel cylinders. Outlet valves 1512a and 1512b are provided. In addition, the first hydraulic circuit 1510 includes a discharge valve 1550 for controlling the flow of the pressurized medium supplied to the reservoir 1100 by passing through the first and second outlet valves 1512a and 1512b, respectively. The discharge valve 1550 may be provided as a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium.

When the braking of the first and second wheel cylinders 21 and 22 is released, the first and second outlet valves 1512a and 1512b detect the braking pressure of the first and second wheel cylinders 21 and 22, and the reduced pressure braking is performed. It is selectively opened if necessary, and the discharge valve 1550 may control the flow rate of the pressurized medium discharged from the outlet valves 1512a and 1512b. At this time, since the discharge valve 1550 is linearly controlled, it is possible to integrally control the pressure reduction of the first and second wheel cylinders 21 and 22. The first and second outlet valves 1512a and 1512b and the discharge valve 1550 are normally closed, but a normally closed type solenoid valve that operates to open the valve upon receiving an electrical signal from the electronic control unit. Can be provided with.

Meanwhile, a second backup flow path 1620 to be described later is connected to the rear end or the downstream side of the third and fourth inlet valves 1521a and 1521b on the side of the third and fourth wheel cylinders 23 and 24, respectively, and a second backup At least one second cut valve 1621 for controlling the flow of the pressurized medium may be provided in the flow path 1620. In addition, an auxiliary backup passage 1630 may be provided that is branched from the second backup passage 1620 and assists in communication between the second simulation chamber 1240a and the second hydraulic circuit 1520.

When the braking of the third and fourth wheel cylinders 23 and 24 is released, the second cut valve 1621 senses the braking pressure of the third and fourth wheel cylinders 23 and 24, and optionally The pressurized medium is opened to reach the simulation flow path 1260 through the second backup flow path 1620, and the simulator valve 1261 provided in the simulation flow path 1260 controls the flow of the pressurized medium, thereby controlling the flow of the pressurized medium. The decompression of (23, 24) can be adjusted. In this case, the second cut valve 1621 or the simulator valve 1261 may be provided as a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium.

The hydraulic pressure providing unit 1300 of the electronic brake system 1000 according to the exemplary embodiment of the present invention may operate in a double-acting manner.

Specifically, as the hydraulic piston 1320 advances, the hydraulic pressure generated in the first pressure chamber 1330 is applied to the first hydraulic channel 1401, the third hydraulic channel 1403, and the fourth hydraulic channel 1404. It is transmitted to the hydraulic circuit 1510 to implement braking of the first and second wheel cylinders 21 and 22, and the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405 Through this, it is transmitted to the second hydraulic circuit 1520 to implement the braking of the third and fourth wheel cylinders 23 and 24.

Similarly, the hydraulic pressure generated in the second pressure chamber 1340 while the hydraulic piston 1320 moves backward is applied to the first hydraulic pressure through the second hydraulic channel 1402, the third hydraulic channel 1403, and the fourth hydraulic channel 1404. It is transmitted to the circuit 1510 to implement braking of the first and second wheel cylinders 21 and 22, and in the same manner, the second hydraulic flow path 1402, the third hydraulic flow path 1403 and the fifth hydraulic flow path 1405 ) Is transmitted to the second hydraulic circuit 1520 to implement braking of the third and fourth wheel cylinders 23 and 24.

In addition, the electronic brake system 1000 according to the first embodiment of the present invention can implement braking by directly supplying the pressurized medium discharged from the integrated master cylinder 1200 to the wheel cylinder when normal operation is impossible due to a device failure. First and second backup channels 1610 and 1620 may be included. The mode in which the hydraulic pressure of the integrated master cylinder 1200 is directly transmitted to the wheel cylinder is referred to as 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 from the second backup passage 1620 and the second backup passage 1620 An auxiliary backup passage 1630 may be provided in which one end communicates with the second simulation chamber 1240a by branching and the other end joins the second backup passage 1620. The second backup passage 1620 and the auxiliary backup passage 1630 may be provided to connect the first and second simulation chambers 1230a and 1240a of the integrated master cylinder 1200 and the second hydraulic circuit 1520. Specifically, the first backup passage 1610 may be connected to join at least one of the rear ends of the first inlet valve 1511a and the second inlet valve 1511b on the first hydraulic circuit 1510, and the second backup The flow path 1620 may be connected to at least one of the rear end of the third inlet valve 1521a and the rear end of the fourth inlet valve 1521b on the second hydraulic circuit 1520. In the drawing, it is shown that the second backup passage 1620 is branched and connected to the rear end of the third inlet valve 1521a and the rear end of the fourth inlet valve 1521b on the second hydraulic circuit 1520, respectively. It is not limited, and if it joins at least one of the rear end of the third inlet valve 1521a and the rear end of the fourth inlet valve 1521b, it should be understood the same.

A first cut valve 1611 for controlling the flow of the pressurized medium is provided in the first backup passage 1610, and a second cut valve 1621 for controlling the flow of the pressurized medium is provided in the second backup passage 1620 at least. One can be prepared. When the second cut valve 1621 is connected to the rear end of the third inlet valve 1521a and the rear end of the fourth inlet valve 1521b by branching the second backup passage 1620, as shown in the figure, the branched A plurality of points may be provided between the points and the joined points. The first and second cut valves 1611 and 1621 may be provided as solenoid valves of a normal open type that operate to close when a closing signal is received from the electronic control unit after being opened normally. .

Accordingly, when the first and second cut valves 1611 and 1621 are closed, the hydraulic pressure provided from the hydraulic pressure providing unit 1300 is transferred to the wheel cylinders 21 and 22 through the first and second hydraulic circuits 1510 and 1520. , 23, 24), and when opening the first and second cut valves 1611 and 1621, the hydraulic pressure provided from the integrated master cylinder 1200 is applied to the first and second backup passages 1610 and 1620. ) May be supplied to the wheel cylinders 21, 22, 23, 24.

The electronic brake system 1000 according to the first embodiment of the present invention may include a flow path pressure sensor PS1 that senses the hydraulic pressure of at least one of the first hydraulic circuit 1510 and the second hydraulic circuit 1520. have. The flow path pressure sensor PS1 is provided at a front end of at least one of the inlet valves 1511a, 1511b, 1521a, and 1521b among the first hydraulic circuit 1510 and the second hydraulic circuit 1520. 2 It is possible to detect the hydraulic pressure of the pressurized medium applied to the hydraulic circuit 1520. In the drawing, although it is shown that the flow path pressure sensor PS1 is provided in the second hydraulic circuit 1520, it is not limited to the structure, and if it can sense the hydraulic pressure applied to the hydraulic circuits 1510 and 1520, one Or, it includes cases provided in various numbers.

Hereinafter, a method of operating the electronic brake system 1000 according to the first embodiment of the present invention to provide braking pressure in a normal operation mode will be described.

The electronic brake system 1000 according to the first embodiment of the present invention may use the hydraulic pressure providing unit 1300 by dividing into a first braking mode, a second braking mode, and a third braking mode. In the first braking mode, hydraulic pressure by the hydraulic pressure providing unit 1300 is primarily provided to the wheel cylinders 21, 22, 23, 24, and the second braking mode is the hydraulic pressure by the hydraulic pressure providing unit 1300 in the wheel cylinder. (21, 22, 23, 24) is secondarily provided to deliver a higher braking pressure than the first braking mode, and in the third braking mode, hydraulic pressure by the hydraulic pressure providing unit 1300 is supplied to the wheel cylinders 21, 22, 23, 24) can be provided to deliver a higher braking pressure than the second braking mode. The first to third braking modes can be changed by different operations of the hydraulic pressure providing unit 1300 and the hydraulic control unit 1400. The hydraulic pressure providing unit 1300 can provide high hydraulic pressure without increasing the output of the motor (not shown) by utilizing the first to third braking modes, and further prevent unnecessary loads applied to the motor (not shown). can do. 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.

When the hydraulic piston 1320 advances by driving a motor (not shown), hydraulic pressure is generated in the first pressure chamber 1330. As the hydraulic piston 1320 advances from the initial position, that is, as the operating stroke of the hydraulic piston 1320 increases, the amount of supply of the pressurized medium transmitted from the first pressure chamber 1330 to the wheel cylinder increases, and the braking pressure increases. However, since the hydraulic piston 1320 has an effective stroke, there is a maximum pressure due to the advance of the hydraulic piston 1320. On the other hand, when the hydraulic piston 1320 moves backward by driving of a motor (not shown), hydraulic pressure is generated in the second pressure chamber 1340. In this case, since the drive shaft 1390 is present in the second pressure chamber 1340, the stroke The sugar pressure increase rate is lower than that of the first pressure chamber 1330.

Therefore, the hydraulic piston 1320 is operated to move forward so that the pressure increase rate per stroke is large in the initial braking period, where the braking response is important, but in the late braking where the maximum braking force is important, the hydraulic piston 1320 is moved backward and forward again to increase the maximum pressure. Can work to do.

2 is a hydraulic circuit diagram showing a state in which the hydraulic piston 1320 of the electronic brake system 1000 according to the first embodiment of the present invention moves forward and 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 (not shown) is provided with hydraulic pressure by the power transmission unit 1330 It is transmitted to the unit 1300, and the hydraulic piston 1320 of the hydraulic pressure providing unit 1300 advances to generate hydraulic pressure in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is the first to fourth wheel cylinders 21, 22, 23, respectively provided on the four wheels through the first hydraulic circuit 1510 and the second hydraulic circuit 1520. 24) to generate braking force.

Specifically, the hydraulic pressure provided from 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 It is primarily transmitted to the wheel cylinders 21 and 22 provided in the. At this time, the first and second inlet valves 1511a and 1511b respectively installed in the two flow paths branching from the first hydraulic circuit 1510 are provided in an open state, and the first and second inlet valves of the first hydraulic circuit 1510 2 The outlet valves 1512a and 1512b are maintained in a closed state to prevent hydraulic pressure from leaking to the reservoir 1100.

In addition, the hydraulic pressure provided from 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 to the second hydraulic circuit 1520. It is primarily transmitted to the provided wheel cylinders 23 and 24. At this time, the third and fourth inlet valves 1521a and 1521b respectively installed in the two flow paths branching from the second hydraulic circuit 1520 are provided in an open state. In addition, as described later, since the second cut valve 1621 of the second backup passage 1610 is also provided to be closed during normal operation, the hydraulic pressure transmitted through the third and fourth inlet valves 1521a and 1521b is It is possible to prevent leakage toward the backup passage 1620.

In the first braking mode, the second valve 2412 may block the second hydraulic flow path 1402 by maintaining the closed state. This prevents the hydraulic pressure generated in the first pressure chamber 1330 from being transmitted to the second pressure chamber 1340 through the second hydraulic flow path 1402, thereby improving the pressure increase rate per stroke of the hydraulic piston 1320. . Therefore, it is possible to achieve a quick braking response at the beginning of braking.

When the hydraulic pressure of the pressurized medium is generated by the hydraulic pressure providing unit 1300, the first and second cut valves 1611 and 1621 provided in the first and second backup passages 1610 and 1620 are closed, and the integrated master cylinder 1200 It is possible to prevent the hydraulic pressure discharged from being transmitted to the wheel cylinders 21, 22, 23, 24. The hydraulic pressure generated in the master chamber 1220a according to the pedal effort of the brake pedal 10 is transmitted to the first simulation piston 1230. At this time, the third reservoir flow path 1730 and the second cut valve 1621 are closed, so that the second simulation chamber 1240a is closed, and the simulator valve 1261 provided in the simulation flow path 1260 is opened. The simulation chamber 1230a and the reservoir 1100 are in communication. As the pressurized medium pressurized in the master chamber 1220a by the master piston 1220 is transferred to the first simulation piston 1230, the elastic member 1250 of the first simulation piston 1230 is compressed, and the first simulation chamber ( The pressurized medium accommodated in 1230a) is transmitted to the reservoir 1100 through the first reservoir flow path 1710, and a reaction force corresponding to the foot force of the brake pedal 10 acts by the elastic restoring force of the compressed elastic member 1250. It can provide the driver with an appropriate pedal feel.

The electronic brake system 1000 according to the first embodiment of the present invention may switch from the first braking mode to the second braking mode shown in FIG. 3 to generate a braking pressure higher than the first braking mode.

3 is a hydraulic circuit diagram showing a state in which the hydraulic piston 1320 of the electronic brake system 1000 according to the first embodiment of the present invention performs a second braking mode while reversing.

3, in the electronic control unit, the displacement of the brake pedal 10 detected by the pedal displacement sensor 11 is higher than a preset first displacement level, or the hydraulic pressure detected by the flow path pressure sensor PS1 is If it is higher than the set first pressure level, it is determined that a higher braking pressure is required, and the first braking mode can be switched to the second braking mode.

When switching to the second braking mode, the motor (not shown) operates to rotate in the other direction, and the rotational force of the motor (not shown) is transmitted to the hydraulic pressure providing unit 1300 by the power transmission unit 1330, and the hydraulic pressure providing unit As the hydraulic piston 1320 of 1300 moves backward, it generates hydraulic pressure in the second pressure chamber 1340. The hydraulic pressure discharged from the second pressure chamber 1340 is first to fourth wheel cylinders 21, 22, 23, respectively provided on the four wheels through the first hydraulic circuit 1510 and the second hydraulic circuit 1520. 24) to generate braking force.

In the second braking mode, the second valve 2412 may be converted to an open state, so that the second hydraulic flow path 1402 may be opened. Specifically, the hydraulic pressure provided from the second pressure chamber 1340 sequentially passes through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404 to the first hydraulic circuit 1510. It is transmitted secondary to the wheel cylinders 21 and 22 provided in the. At this time, the first and second inlet valves 1511a and 1511b are maintained in an open state, and the first and second outlet valves 1512a and 1512b of the first hydraulic circuit 1510 are maintained in a closed state to reduce hydraulic pressure. It prevents leakage into the reservoir 1100. In addition, the hydraulic pressure provided from the second pressure chamber 1340 is sequentially passed through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405 to the second hydraulic circuit 1520. It is transmitted secondary to the provided wheel cylinders (23, 24). At this time, the third and fourth inlet valves 1521a and 1521b are maintained in an open state, and the second cut valve 1621 of the second backup passage 1610 is maintained in a closed state so that the hydraulic pressure is reduced to the second backup passage ( 1620) side leakage can be prevented.

The electronic brake system 2000 may switch from the second braking mode to the third braking mode shown in FIG. 4 to generate a braking pressure higher than the second braking mode.

The electronic brake system 1000 according to the first embodiment of the present invention may switch from the second braking mode to the third braking mode shown in FIG. 6 to generate a braking pressure higher than the second braking mode.

4 is a hydraulic circuit diagram showing a state in which the hydraulic piston 1320 of the electronic brake system 1000 according to the first embodiment of the present invention moves forward again and performs a third braking mode.

4, in the electronic control unit, the displacement of the brake pedal 10 detected by the pedal displacement sensor 11 is higher than a preset second displacement level, or the hydraulic pressure detected by the flow path pressure sensor PS1 is If it is higher than the set second pressure level, it is determined that a higher braking pressure is required, and the second braking mode may be switched to the third braking mode.

When switching to the third braking mode, the motor (not shown) operates to rotate in one direction again, and the rotational force of the motor (not shown) is transmitted to the hydraulic pressure supply unit 1300 by the power transmission unit 1330, and provides hydraulic pressure. As the hydraulic piston 1320 of the unit 1300 advances, hydraulic pressure is again generated in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is the first to fourth wheel cylinders 21, 22, 23, respectively provided on the four wheels through the first hydraulic circuit 1510 and the second hydraulic circuit 1520. 24) to generate braking force.

Specifically, the hydraulic pressure provided from 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 It is thirdly transmitted to the wheel cylinders 21 and 22 provided in the. At this time, the first and second inlet valves 1511a and 1511b are maintained in an open state, and the first and second outlet valves 1512a and 1512b of the first hydraulic circuit 1510 are maintained in a closed state to reduce hydraulic pressure. It prevents leakage into the reservoir 1100. In addition, the hydraulic pressure provided from 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 to the second hydraulic circuit 1520. It is thirdly transmitted to the provided wheel cylinders 23 and 24. At this time, the third and fourth inlet valves 1521a and 1521b are maintained in an open state, and the second cut valve 1621 of the second backup passage 1610 is also maintained in a closed state so that the hydraulic pressure is reduced to the second backup passage ( 1620) side leakage can be prevented.

In the third braking mode, the second valve 2412 remains open. The hydraulic pressure provided from the first pressure chamber 1330 may be transmitted to the second pressure chamber 1340 by sequentially passing through the first hydraulic flow path 1401 and the fourth hydraulic flow path 1404. That is, the first pressure chamber 1330 and the second pressure chamber 1340 are in communication with each other so that the braking pressures are synchronized to coincide with each other, and through this, the load applied to the motor (not shown) may be reduced. In the third braking mode, as in the first and second braking modes, the first and second cut valves 1611 and 1621 are closed, but the simulator valve 1261 is controlled in an open state.

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

5 is a hydraulic circuit diagram showing a state in which the braking mode of the electronic brake system 1000 according to the first embodiment of the present invention is released.

5, when the pedal effort applied to the brake pedal 10 is released, the motor generates a rotational force in any one direction to return to its original position and transmits it to the power conversion unit, and the power conversion unit generates a hydraulic piston 1320. Return to the position. As the hydraulic piston 1320 moves forward or backward to return to its original position, the hydraulic pressure formed in the first pressure chamber 1330 or the second pressure chamber 1340 passes through the hydraulic control unit 1400 to the first hydraulic circuit ( 1510) or the second hydraulic circuit 1520, and discharged to the reservoir 1100 together with the hydraulic pressure of the pressurized medium applied to the wheel cylinder 20.

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 first outlet valve 1512a and the second outlet valve 1512b. , It may be discharged to the reservoir 1100 through the discharge valve 1550 in sequence. To this end, the first and second outlet valves 1512a and 1512b may be switched to an open state, and the discharge valve 1550 is discharged to the reservoir 1100 by adjusting the opening amount according to the displacement amount of the brake pedal 10. It is possible to adjust the flow rate of the pressurized medium, thereby implementing reduced pressure braking or braking release. At this time, as described above, the hydraulic pressure formed in the first pressure chamber 1330 or the second pressure chamber 1340 by the return of the hydraulic piston 1320 to the original position is also the first outlet valve 1512a and the second outlet. The first inlet valve 1511a and the second inlet valve 1511b may maintain an open state so that they can be discharged to the reservoir 1100 through the valve 1512b and the discharge valve 1550 in sequence.

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 is the second backup passage 1620, the first simulation chamber 1230a, It may be discharged to the reservoir 1100 through the simulation flow path 1260 sequentially. To this end, the second cut valve 1621 and the simulator valve 1261 may be switched to an open state, and in response to the hydraulic pressure applied to the first hydraulic circuit 1510 adjusting the degree of decompression by the discharge valve 1550, At least one of the second cut valve 1621 and the simulator valve 1261 may be provided as a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium passing through, like the discharge valve 1550. At this time, as described above, the hydraulic pressure formed in the first pressure chamber 1330 or the second pressure chamber 1340 by the return of the hydraulic piston 1320 to the original position is also the second backup passage 1620, the first simulation The third inlet valve 1521a and the fourth inlet valve 1521b may maintain an open state so that they can be discharged to the reservoir 1100 through the chamber 1230a and the simulation flow path 1260 in sequence.

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

6 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment operates in an abnormal state (fallback mode).

Referring to FIG. 6, when the electronic brake system 1000 does not operate normally, each valve is controlled to a non-operational braking initial state. Thereafter, when the driver presses the brake pedal 10, the master piston 1220 connected to the brake pedal 10 advances, and the pressurizing medium contained in the master chamber 1220a is pressurized by the movement of the master piston 1220. . The pressurized medium pressurized in the master chamber 1220a is transferred to the first and second wheel cylinders 21 and 22 through the first backup passage 1610 to implement braking.

In addition, the pressurized medium pressurized in the master chamber 1220a moves the first simulation piston 1230 forward, and the second simulation piston and the elastic members 1240 and 1250 are also moved forward by the first simulation piston 1230. Moving forward, the pressurized medium accommodated in the first simulation chamber 1230a and the pressurized medium accommodated in the second simulation chamber 1240a pass through the second backup passage 1620 and the auxiliary backup passage 1630 through the third and fourth wheel cylinders ( 23, 24) to implement braking.

When not in operation, in other words, first and second cut valves 1611 and 1621 respectively provided in the first and second backup passages 1610 and 1620, which do not receive an electrical signal from the electronic control unit, and the first and The first to fourth inlet valves 1511a, 1511b, 1521a, 1521b provided in the second hydraulic circuits 1510 and 1520 are in an open state, and the simulator valve 1261 of the simulation flow path 1260 is in a closed state, Since the hydraulic pressure generated in the master chamber 1220a and the first and second simulation chambers 1230a and 1240a of the integrated master cylinder 1200 can be directly transferred to the four wheel cylinders 21, 22, 23, 24, In addition to improving braking stability, rapid braking can be achieved.

Hereinafter, a test mode of the electronic brake system 1000 according to the first embodiment of the present invention will be described.

7 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment performs an inspection mode.

Referring to FIG. 7, it is possible to perform an inspection mode in which the electronic brake system 1000 according to an embodiment of the present invention has a leak in the integrated master cylinder 1200. When performing the inspection mode, the electronic control unit controls to supply the hydraulic pressure generated from the hydraulic pressure providing unit 1300 to the first simulation chamber 1230a.

Specifically, the electronic control unit generates hydraulic pressure in the first pressure chamber 1330 by operating the hydraulic piston 1320 to advance while the valves are controlled to the initial braking state, which is a non-operation method, One cut valve 1611 is controlled in a closed state. In addition, the simulator valve 1261 is controlled in a closed state, and the first and second simulation chambers 1230a and 1240a are provided in a closed state. 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 channel 1401, the third hydraulic channel 1403, and the fifth hydraulic channel 1405. In addition, the second cut valve 1621 maintains an open state in a normal state, and the pressurized medium delivered to the second hydraulic circuit 1520 passes through the second backup passage 1620 to the first simulation chamber 1230a. Delivered.

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, the hydraulic pressure value of the pressurized medium expected to be generated by the displacement of the hydraulic piston 1320 and the first simulation chamber 1230a measured by the pressure sensor PS1 or the second hydraulic circuit measured by the pressure sensor PS2 By comparing the hydraulic pressure value of 1520, it is possible to diagnose a leak in the integrated master cylinder 1200 or the simulator valve 1261. Specifically, by comparing 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 sensors (PS1, PS2), two If the hydraulic pressure values match, 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 sensors (PS1, PS2) 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). 1 Since part of the hydraulic pressure of the pressurized medium applied to the simulation chamber 1230a is lost, it is determined that a leak exists in the integrated master cylinder 1200 or the simulator valve 1261, and this can be notified to the driver.

Hereinafter, an electronic brake system 2000 according to a second embodiment of the present invention will be described. The operation of the electronic brake system 2000 according to the second embodiment of the present invention is a normal operation mode in which various devices and valves operate normally without failure or abnormality, and a non-normal operation due to failure or abnormality in various devices and valves. A normal operation mode (fallback mode) and an inspection mode for determining whether a leak exists in the integrated master cylinder 2200 may be included.

In the description of the electronic brake system 2000 according to the second embodiment of the present invention described below, the electronic brake system 1000 according to the first embodiment of the present invention described above is described above except for the case where a separate reference numeral is used for additional description. ), and the description is omitted to prevent duplication of content.

8 is a hydraulic circuit diagram showing an electronic brake system 2000 according to a second embodiment of the present invention.

Referring to FIG. 8, a first valve 1411 and a second valve 2412 for controlling the flow of the pressurized medium may be provided in the first hydraulic flow path 1401 and the second hydraulic flow path 1402, and the present invention In the second embodiment of, the second valve 2412 allows only the pressurized medium flow in the direction from the second pressure chamber 1340 to the first and second hydraulic circuits 1510 and 1520, and pressurization in the opposite direction. The medium flow may be provided with a check valve that blocks.

In the second embodiment of the present invention, a sixth hydraulic flow path 1406 connecting the first hydraulic flow path 1401 and the second hydraulic flow path 1402 is provided. That is, the sixth hydraulic flow path 1406 may be provided to connect the front end of the first valve 1411 and the front end of the second valve 2414 on the second hydraulic flow path 1402 from the first hydraulic flow path 1401. A third valve 1413 for controlling the flow of the pressurized medium may be provided in the fourth hydraulic passage 1404. A fifth valve 2415 for controlling the flow of the pressurized medium may be provided in the sixth hydraulic flow path 1406.

The fifth valve 2415 may be provided as a two-way valve that controls the flow of the pressurized medium delivered along the sixth hydraulic flow path 1406 communicated with the first and second pressure chambers 1330 and 113. The fifth valve 2415 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.

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

Referring to FIG. 9, in the first braking mode, the fifth valve 1413 is maintained in a closed state to block the sixth hydraulic flow path 1406. Through this, it is possible to improve the pressure increase rate per stroke of the hydraulic piston 1320 by preventing the hydraulic pressure generated in the first pressure chamber 1330 from being transmitted to the second pressure chamber 1340 through the sixth hydraulic flow path 1406. . Therefore, it is possible to achieve a quick braking response at the beginning of braking.

10 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the second embodiment performs a second braking mode.

Referring to FIG. 10, in the second braking mode, the fifth valve 1405 is still maintained in a closed state to block the sixth hydraulic flow path 1406, and the hydraulic pressure generated in the second pressure chamber 1340 is It can be prevented from being transmitted to the first pressure chamber 1330 through the hydraulic flow path 1406. In the second braking mode, as in the first braking mode, the first and second cut valves 1611 and 1621 are closed, but the simulator valve 1261 is controlled in an open state.

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

Referring to FIG. 11, in the third braking mode, the fifth valve 2415 is switched to an open state to open the sixth hydraulic flow path 1406. Accordingly, the first pressure chamber 1330 and the second pressure chamber 1340 are communicated with each other to synchronize the braking pressures to match each other, thereby reducing the load applied to the motor (not shown). This is because the third braking mode is a state in which high-pressure braking pressure is provided, and as the hydraulic piston 1320 advances, the hydraulic pressure of the first pressure chamber 1330 increases the force to move the hydraulic piston 1320 backward. The load applied to the motor (not shown) also increases. However, by opening the sixth hydraulic flow path 1406 through the control of the fifth valve 2415, the second pressure chamber 1340 is synchronized by synchronizing the braking pressures of the first pressure chamber 1330 and the second pressure chamber 1340. Also, the hydraulic pressure is formed, so that the load applied to the motor (not shown) can be reduced. In the third braking mode, as in the first and second braking modes, the first and second cut valves 1611 and 1621 are closed, but the simulator valve 1261 is controlled in an open state.

Among the operating methods of the electronic brake system 2000 according to the second embodiment of the present invention, the release of the braking mode, the abnormal operation mode, and the inspection mode are the operating method of the electronic brake system 1000 according to the first embodiment described above. The explanation is omitted because they are the same.

Hereinafter, an electronic brake system 3000 according to a third embodiment of the present invention will be described. The operation of the electronic brake system 3000 according to the third embodiment of the present invention includes a normal operation mode in which various devices and valves operate normally without failure or abnormality, and a generator provided in the third and fourth wheel cylinders 23 and 24 It is determined whether a regenerative braking mode using (not shown), an abnormal operation mode (fallback mode) that operates abnormally due to failure or abnormality in various devices and valves, and whether a leak exists in the integrated master cylinder 2200 It may include a test mode to perform.

In the description of the electronic brake system 3000 according to the third embodiment of the present invention described below, the electronic brake system 2000 according to the second embodiment of the present invention described above is described above, except for the case where a separate reference numeral is used for additional description. ), and the description is omitted to prevent duplication of content.

12 is a hydraulic circuit diagram showing an electronic brake system according to a third embodiment. Referring to FIG. 13, the fourth valve 3414 of the electronic brake system 3000 according to the third embodiment of the present invention is provided to perform cooperative control for the regenerative braking mode.

Meanwhile, in recent years, as the market demand for eco-friendly vehicles increases, hybrid vehicles with improved fuel economy are gaining popularity. Hybrid vehicles take a method of recovering kinetic energy as electric energy while the vehicle is braking, storing it in a battery, and then using a motor as an auxiliary drive source for the vehicle. During operation, energy is recovered by a generator (not shown) or the like. This braking operation is referred to as a regenerative braking mode, and in the electronic brake system 3000 according to the third embodiment of the present invention, the fourth valve 3414 is controlled to be opened in the normal operation mode, and the third and fourth wheels When entering the regenerative braking mode by a generator (not shown) provided in the cylinders 23 and 24, it may be converted into a closed state. A detailed description of this will be described later with reference to FIG. 13.

13 is a hydraulic circuit diagram showing a state in which the electronic brake system 3000 according to the third embodiment of the present invention performs a regenerative braking mode including a regenerative braking mode.

In the case of the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510, the braking force that the driver wants to implement is formed by the hydraulic pressure of the pressurized medium by the operation of the hydraulic pressure supply device 1300 On the other hand, in the case of the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 in which an energy recovery device such as a generator is installed, the pressurized medium by the hydraulic pressure supply device 1300 is The sum of the total braking pressure obtained by adding the braking pressure and the regenerative braking pressure by the generator should be equal to the total braking force of the first wheel cylinder 21 and the second wheel cylinder 22.

Therefore, when entering the regenerative braking mode, the braking pressure by the hydraulic pressure supply device 1300 applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 by closing the fourth valve 3414 is removed or The total braking force of the third and fourth wheel cylinders 23 and 24 may be equal to the braking force of the first and second wheel cylinders 21 and 22 by maintaining and increasing the regenerative braking pressure by the generator at the same time.

Specifically, referring to FIG. 13, when the driver presses the brake pedal 10, the motor (not shown) operates to rotate in one direction, and the rotational force of the motor (not shown) is provided by the power transmission unit 1330 It is transmitted to the unit 1300 and the hydraulic piston 1320 of the hydraulic pressure providing unit 1300 advances to generate hydraulic pressure in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each of the wheel cylinders 20 through the first hydraulic circuit 1510 and the second hydraulic circuit 1520 to generate braking force.

In the case of the first hydraulic circuit 1510 in which an energy recovery device such as a generator is not installed, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 is the first hydraulic channel 1401, the third hydraulic channel 1403, and 4 The first and second wheel cylinders 21 and 22 are braked by passing through the hydraulic flow passage 1404 in sequence. As described above, the first valve 1411 and the third valve 1413 allow the flow of the pressurized medium from the first pressure chamber 1330 to the first hydraulic circuit 1510. The hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 may be transmitted to the first hydraulic circuit 1510.

On the other hand, in the case of the second hydraulic circuit 1520 in which the generator is installed, the electronic control unit detects the speed and deceleration of the vehicle and closes the fourth valve 3414 when it is determined that it is possible to enter the regenerative braking mode. It is possible to block the transfer of the hydraulic pressure of the pressurized medium to the 3 wheel cylinder 23 and the fourth wheel cylinder 24 and implement regenerative braking by the generator. Thereafter, the electronic control unit determines that the vehicle is in an unsuitable state for regenerative braking, or when it is determined that the braking pressure of the first hydraulic circuit 1510 and the braking pressure of the second hydraulic circuit 1520 are different, the fourth valve ( 3414) is switched to the open state to control the hydraulic pressure of the pressurized medium to be transferred to the second hydraulic circuit 1520, and at the same time, the braking pressure of the first hydraulic circuit 1510 and the braking pressure of the second hydraulic circuit 1520 are reduced. Can be synchronized. Accordingly, the braking pressure or braking force applied to the first to fourth wheel cylinders 21, 22, 23, 24 is uniformly controlled to prevent oversteering or understeering in addition to the braking stability of the vehicle. Thus, driving stability of the vehicle can be improved.

Among the operating methods of the electronic brake system 2000 according to the third embodiment of the present invention, the release of the braking mode, the abnormal operation mode, and the inspection mode are of the electronic brake system 1000 according to the first and second embodiments described above. The description is omitted because it is the same as the operation method.

1000, 2000, 3000: 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 1300: hydraulic pressure supply device
1320: hydraulic piston 1330: first pressure chamber
1340: second pressure chamber 1400, 2400: 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
1411: first valve
1412, 2412: second valve 1413: third valve
1414, 3414: fourth valve 2415: fifth 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
1710: first reservoir euro 1260: second reservoir euro
1261: simulator valve 1730: third reservoir flow path
1800: dump control unit 1810: first dump flow
1811: first dump check valve 1820: second dump passage
1821: second dump check valve

Claims (23)

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 providing unit 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 An electronic brake system comprising a fourth hydraulic channel branched from the hydraulic channel and connected to the first hydraulic circuit, and a fifth hydraulic channel branched from the third hydraulic channel and connected to the second hydraulic circuit. The method of claim 1,
The first hydraulic circuit is
Controls the flow of the pressurized medium discharged from the first and second inlet valves and the first and second wheel cylinders, respectively, to control the flow of the pressurized medium supplied to the first and second wheel cylinders A first outlet valve and a second outlet valve, and a discharge valve for controlling the flow of the pressurized medium supplied to the reservoir through the first outlet valve and the second outlet valve, respectively,
The discharge valve is
Electronic brake system provided with a linearly controlled solenoid valve to control the flow rate of the pressurized medium. The method of claim 2,
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 An electronic brake system including a third valve to control and a fourth valve provided in the fifth hydraulic flow path to control the flow of the pressurized medium. The method of claim 3,
The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is provided as a solenoid valve that controls the flow of the pressurized medium in both directions. , 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 directed from the third hydraulic flow path to the second hydraulic circuit. An electronic brake system provided with a check valve that allows only the flow of pressurized media. The method of claim 4,
The simulation chamber is
A first simulation chamber and a second simulation chamber,
The integrated master cylinder
A master chamber, a master piston provided in the master chamber and displaceable by a brake pedal, a first simulation chamber, and a displacement of the master piston or a pressurized medium accommodated in the master chamber provided in the first simulation chamber The first simulation piston provided to be displaceable by the hydraulic pressure of, the second simulation chamber, and the second simulation chamber, provided to be displaceable by the displacement of the first simulation piston or the hydraulic pressure of the first simulation chamber A second simulation piston to be formed, 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 a flow of a pressurized medium provided in the simulation flow path Electronic brake system having a simulator valve to control the. The method of claim 5,
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;
A first cut valve provided in the first backup passage to control the flow of the pressurized medium; And
The electronic brake system further comprising a; second cut valve provided in the second backup passage to control the flow of the pressurized medium. The method of claim 6,
The second cut valve or the simulator valve
Electronic brake system provided with a solenoid valve that is linearly controlled to adjust the flow rate of the pressurized medium discharged from the third and fourth wheel cylinders to the reservoir. The method of claim 7,
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 8,
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 9,
The second hydraulic circuit is
It includes third and fourth inlet valves respectively controlling the flow of the pressurized medium supplied to the third and fourth wheel cylinders,
The second backup flow path
An electronic brake system provided to connect the downstream side of the fourth inlet valve and the first simulation chamber. The method of claim 10,
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 second dump passage connecting the second pressure chamber and the reservoir, and provided in the first dump passage from the reservoir to the first pressure chamber An electronic brake system including a first dump check valve that allows only the flow of the pressurized medium to be directed, and a second dump check valve provided in the second dump flow path to allow only the flow of the pressurized medium from the reservoir to the second pressure chamber . The method of claim 11,
The integrated master cylinder
Electronic brake system comprising a first simulator spring elastically supporting the second simulation piston. The method of claim 12,
The integrated master cylinder
Electronic brake system further comprising a second simulator spring interposed between the first simulation piston and the second simulation piston. The method of claim 3,
The hydraulic control unit
An electronic brake system comprising a sixth hydraulic flow passage provided to connect the first and second hydraulic flow passages, and a fifth valve provided in the sixth hydraulic flow passage to control the flow of the pressurized medium. The method of claim 14,
The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is pressurized from the second pressure chamber to the third hydraulic flow path. It is provided as a check valve that allows only the flow of the medium, and the third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic channel to the first hydraulic circuit, and the fourth valve is 3 An electronic brake system provided with a check valve that allows only the flow of the pressurized medium from the hydraulic passage to the second hydraulic circuit, and the fifth valve is provided with a solenoid valve that controls the flow of the pressurized medium in both directions. The method of claim 14,
The first valve is provided as a check valve that allows only the flow of the pressurized medium from the first pressure chamber to the third hydraulic flow path, and the second valve is pressurized from the second pressure chamber to the third hydraulic flow path. It is provided as a check valve that allows only the flow of the medium, and the third valve is provided as a check valve that allows only the flow of the pressurized medium from the third hydraulic channel to the first hydraulic circuit, and the fourth and fifth valves Is an electronic brake system provided with a solenoid valve that controls the flow of the pressurized medium in both directions. The method of claim 16,
The electronic brake system further comprising a generator provided in each of the third wheel cylinder and the fourth wheel cylinder of the second hydraulic circuit. In the method of operating the electronic brake system according to claim 10,
In normal operation mode,
The first cut valve is closed to seal the master chamber, and the second cut valve is closed, but the simulator valve is opened to communicate the first simulation chamber and the reservoir, thereby causing the first cut valve to operate. 1 A method of operating an electronic brake system in which a simulation piston compresses the elastic member and the elastic restoring force of the elastic member is provided to the driver as a pedal feel. The method of claim 18,
The normal operation mode is
As the hydraulic pressure transferred from the hydraulic pressure providing unit to the wheel cylinder gradually increases, a first braking mode for providing hydraulic pressure primarily, a second braking mode for providing hydraulic pressure secondly, and a third braking mode for providing hydraulic pressure. A method of operating an electronic brake system sequentially operated in a provided third braking mode. The method of claim 19,
Release of the first to third braking modes
By controlling the degree of opening of the discharge valve, the pressurized medium provided in the first hydraulic circuit is recovered to the reservoir through the discharge valve,
An electronic brake system in which the second cut valve and the simulator valve are opened, and the pressurizing medium provided in the second hydraulic circuit is sequentially returned to the reservoir through the second backup passage, the first simulation chamber, and the simulation passage. How it works. The method of claim 19,
In 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 so that the first and second simulation chambers and the second hydraulic circuit are Communicate,
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 through the auxiliary jack-up passage and the second backup passage in sequence. In the method of operating the electronic brake system according to claim 10,
In the inspection mode to check whether the integrated master cylinder or the simulator valve is leaking,
Closing the first cut valve and the simulator 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 first simulation chamber or the second hydraulic circuit. How it works. In the method of operating the electronic brake system according to claim 17,
In the regenerative braking mode by the generator,
Closing the fourth valve,
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, A method of operating an electronic brake system that blocks the supply of hydraulic pressure to the third and fourth wheel cylinders.

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