KR20200138576A - Electric brake system and Operating method of therof - Google Patents

Abstract

Disclosed is an electronic brake system. An electronic brake system according to an embodiment comprises: a reservoir in which a 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 hydraulic pressure supply device which generates hydraulic pressure by operating a hydraulic piston by an electrical signal which is output in response to the displacement of a brake pedal, and includes a first pressure chamber provided on one side of the hydraulic piston movably accommodated in a cylinder block and connected to one or more wheel cylinders, and a second pressure chamber provided on the other side of the hydraulic piston and connected to the one or more wheel cylinders; a hydraulic control unit having a first hydraulic circuit for controlling hydraulic pressure delivered to two wheel cylinders and a second hydraulic circuit for controlling hydraulic pressure delivered to two other wheel cylinders; and an electronic control unit which controls valves based on hydraulic pressure information and brake pedal displacement information. The present invention can reduce the number of parts by integrating the master cylinder and a simulation device into one.

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 supply device for supplying hydraulic pressure required for braking to a wheel cylinder by receiving a signal are widely spread.

Such an electronic brake system and operation method generates and provides the driver's brake pedal operation as an electrical signal in the normal operation mode, and based on this, the hydraulic pressure supply device 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, a reservoir in which a pressurized medium is stored; An integrated master cylinder including a master chamber and a simulation chamber for supplying a reaction force according to the pedal effort of the brake pedal to the driver and simultaneously pressurizing and discharging the pressurized medium accommodated therein; A reservoir flow path connecting the integrated master cylinder and the reservoir; A first pressure provided on one side of the hydraulic piston that is movably accommodated in the cylinder block by operating a hydraulic piston by an electrical signal output in response to the displacement of the brake pedal and connected to one or more wheel cylinders A hydraulic pressure supply device including a chamber and a second pressure chamber provided on the other side of the hydraulic piston and connected to one or more wheel cylinders; A hydraulic control unit having a first hydraulic circuit for controlling hydraulic pressure transmitted to two wheel cylinders and a second hydraulic circuit for controlling hydraulic pressure transmitted to two other wheel cylinders; And an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal, wherein the hydraulic control unit includes a first hydraulic flow path communicating with the first pressure chamber, and the second pressure chamber. A second hydraulic flow path in communication, a third hydraulic flow path connected to the first hydraulic flow path and the second hydraulic flow path, a fourth hydraulic flow path branching from the first hydraulic flow path, and branching from the second hydraulic flow path. A fifth hydraulic passage, a sixth hydraulic passage where the fourth hydraulic passage and the fifth hydraulic passage merge, a seventh hydraulic passage branched from the sixth hydraulic passage and connected to the first hydraulic circuit, and the fourth hydraulic passage 6 It may be provided including an eighth hydraulic flow path branched from the hydraulic flow path and connected to the second hydraulic circuit, and a ninth hydraulic flow path connected to the seventh hydraulic flow path and the eighth hydraulic flow path.

The hydraulic control unit includes a first valve provided in the fourth hydraulic passage to control the flow of the pressurized medium, a second valve provided in the fifth hydraulic passage to control the flow of the pressurized medium, and provided in the third hydraulic passage A third valve for controlling the flow of the pressurized medium, a fourth valve provided in the seventh hydraulic passage and controlling the flow of the pressurized medium, a fifth valve provided in the eighth hydraulic passage and controlling the flow of the pressurized medium, It may be provided including a sixth valve provided in the ninth 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 sixth hydraulic flow path, and the second valve is pressurized from the second pressure chamber to the sixth hydraulic flow path. It is provided as a check valve that allows only the flow of the medium, and the fourth valve is provided as a check valve that allows only the flow of the pressurized medium from the seventh hydraulic channel to the first hydraulic circuit, and the fifth valve is 8 It is provided as a check valve that allows only the flow of the pressurized medium from the hydraulic passage to the second hydraulic circuit, and the third valve and the sixth valve may be provided as solenoid valves that control the flow of the pressurized medium in both directions. .

The simulation chamber includes a first simulation chamber and a second simulation chamber, and the master chamber includes a first master chamber and a second master chamber having a diameter smaller than that of the second simulation chamber, and the integrated master The cylinder is provided so as to pressurize the first simulation chamber and to be displaceable by a brake pedal, and to pressurize the second simulation chamber and the first master chamber, and the first simulation piston The second simulation piston is provided to be displaceable by the displacement of the first simulation chamber or the hydraulic pressure of the first simulation chamber, and the second master chamber is provided to be pressurized, and the displacement of the second simulation piston or the hydraulic pressure of the first master chamber A master piston provided to be displaceable by a displacement, 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 pressurization provided in the simulation flow path A simulator valve that controls the flow of the medium, a piston spring elastically supporting the master piston, and a simulator spring elastically supporting the second simulation piston may be provided.

A first backup passage connecting the first simulation chamber and the first hydraulic circuit; A second backup passage connecting the second master chamber and the second hydraulic circuit; And an auxiliary backup passage connecting the first master chamber and the first backup passage.

The first hydraulic circuit includes a first inlet valve and a second inlet valve respectively controlling the flow of the pressurized medium supplied to the first wheel cylinder and the second wheel cylinder, and the first wheel cylinder and the second wheel cylinder. It includes a first cut valve and a second cut valve respectively controlling the flow of the pressurized medium discharged to the first backup passage, and the second hydraulic circuit is the flow of the pressurized medium supplied to the third wheel cylinder and the fourth wheel cylinder. A third inlet valve and a fourth inlet valve respectively controlling the flow of the pressurized medium discharged from the third wheel cylinder and the fourth wheel cylinder to the second backup passage; a third cut valve and a fourth It may be provided including a cut valve.

The reservoir flow path is a first reservoir flow path that communicates the reservoir and the second simulation chamber, a second reservoir flow path that communicates the reservoir and the first master chamber, and a second reservoir flow that communicates the reservoir and the second master chamber. It can be provided including 3 reservoir flow paths.

The first reservoir flow path may be provided including a reservoir valve that controls the flow of the pressurized medium.

A first dump passage connecting the first pressure chamber and the reservoir; A second dump passage connecting the second pressure chamber and the reservoir; A first dump check valve provided in the first dump flow path to allow only the flow of the pressurized medium from the first pressure chamber to the reservoir; A second dump check valve provided in the second dump passage and allowing only the flow of the pressurized medium from the second pressure chamber to the reservoir may be provided.

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

The first hydraulic circuit includes a first wheel cylinder and a second wheel cylinder, and the second hydraulic circuit includes a third wheel cylinder and a fourth wheel cylinder, and the third wheel cylinder and the fourth wheel cylinder Generators each provided; may be provided further including.

In the normal operation mode, the first cut valve and the second cut valve are closed to seal the first master chamber, and the third cut valve and the fourth cut valve are closed to seal the second master chamber. , By closing the reservoir valve to seal the second simulation chamber, and the simulator valve is opened to communicate the first simulation chamber and the reservoir, thereby causing the first simulation piston to become the elastic member And the elastic restoring force of the elastic member may be provided to the driver as a pedal feel.

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

In the first braking mode, the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston sequentially passes through the first hydraulic channel, the fourth hydraulic channel, and the sixth hydraulic channel, and the seventh hydraulic channel and the Branched to the eighth hydraulic flow path may be provided to the first hydraulic circuit and the second hydraulic circuit, respectively.

In the second braking mode, after the first braking mode, the hydraulic pressure formed in the second pressure chamber by the reversing of the hydraulic piston sequentially passes through the second hydraulic channel, the fifth hydraulic channel, and the sixth hydraulic channel, Branching into the seventh hydraulic flow path and the eighth hydraulic flow path may be provided to the first hydraulic circuit and the second hydraulic circuit, respectively.

In the third braking mode, the third valve is opened, and a part of the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston after the second braking mode is applied to the first hydraulic channel and the fourth hydraulic channel. The sixth hydraulic flow path is sequentially branched into the seventh hydraulic flow path and the eighth hydraulic flow path and provided to the first hydraulic circuit and the second hydraulic circuit, respectively, and the remainder of the hydraulic pressure formed in the first pressure chamber A portion may be supplied to the second pressure chamber through the first hydraulic flow path, the third hydraulic flow path, and the second hydraulic flow path sequentially.

The release of the first braking mode opens at least one of the first cut valve and the second cut valve, opens at least one of the third cut valve and the fourth cut valve, and opens the simulator valve. , The reservoir valve is closed, and the pressure medium of the second pressure chamber is sequentially passed through the second hydraulic channel, the fifth hydraulic channel, and the sixth hydraulic channel by reversing the hydraulic piston, and the seventh hydraulic oil Branching into the path and the eighth hydraulic flow path and sending them to the first hydraulic circuit and the second hydraulic circuit, and the pressure media of the first hydraulic circuit and the second hydraulic circuit are respectively the first backup flow path and the second backup flow path. It may be recovered to the reservoir through the first simulation chamber and the second master chamber through a flow path.

The release of the second braking mode opens at least one of the first cut valve and the second cut valve, opens at least one of the third cut valve and the fourth cut valve, and opens the simulator valve. , The reservoir valve is closed, and the pressurizing medium of the first pressure chamber is sequentially passed through the first hydraulic channel, the fourth hydraulic channel, and the sixth hydraulic channel by advancing the hydraulic piston, and the seventh hydraulic oil Branching into the path and the eighth hydraulic flow path and sending them to the first hydraulic circuit and the second hydraulic circuit, and the pressure media of the first hydraulic circuit and the second hydraulic circuit are respectively the first backup flow path and the second backup flow path. It may be recovered to the reservoir through the first simulation chamber and the second master chamber through a flow path.

The release of the third braking mode opens at least one of the first cut valve and the second cut valve, opens at least one of the third cut valve and the fourth cut valve, and opens the simulator valve. , The reservoir valve is closed, and the pressurizing medium of the first hydraulic circuit and the second hydraulic circuit passes through the first backup passage and the second backup passage, respectively, through the first reservoir chamber and the second master chamber. The first pressure is recovered to the reservoir, and at least a part of the pressurizing medium of the second pressure chamber is sequentially passed through the second hydraulic channel, the third hydraulic channel, and the first hydraulic channel by the reverse movement of the hydraulic piston. It can be supplied to the chamber.

In the abnormal operation mode, the first cut valve and the second cut valve are opened to communicate the first simulation chamber and the first hydraulic circuit, and the third cut valve and the fourth cut valve are opened to open the second cut valve. 2 The master chamber and the second hydraulic circuit are communicated, the simulator valve is closed to disconnect the first simulation chamber and the reservoir, and the reservoir valve is opened to communicate the second simulation chamber and the reservoir, and the According to the pedal effort of the brake pedal, the pressurizing medium of the first simulation chamber is provided to the first hydraulic circuit through the first backup passage, and the pressurizing medium of the first master chamber is the first hydraulic pressure through the auxiliary backup passage. It is provided as a circuit, and the pressurizing medium of the second master chamber may be provided to the second hydraulic circuit through the second backup passage.

In the diagnostic mode for checking whether the integrated master cylinder is leaking, the third cut valve, the fourth cut valve, and the simulator valve are closed, and at least one of the first cut valve and the second cut valve is opened. , Provides the hydraulic pressure generated by operating the hydraulic pressure supply device to the first simulation chamber through the hydraulic control unit, the first hydraulic circuit, and the first backup passage, and is generated based on the displacement amount of the hydraulic piston. It is possible to compare the expected hydraulic pressure value of the pressurized medium with the hydraulic pressure value of the pressurized medium actually provided in the first simulation chamber or the first hydraulic circuit.

In the regenerative braking mode by the generator, the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston is provided to the first hydraulic circuit sequentially through the first hydraulic channel and the fourth hydraulic channel, wherein the By closing the fifth valve, the supply of hydraulic pressure to the third wheel cylinder and the fourth wheel cylinder may be blocked.

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 of the present invention.
2 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention 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 of the present invention 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 of the present invention 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 of the present invention releases a third braking mode.
6 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention releases a second braking mode.
7 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention releases a first braking mode.
8 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention operates in an abnormal state (fallback mode).
9 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention performs an inspection mode.
10 is a hydraulic circuit diagram showing an electronic brake system according to a second embodiment of the present invention.
11 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the second embodiment of the present invention 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, and 1630 hydraulically connecting the integrated master cylinder 1200 and the hydraulic circuits 1510, 1520, the reservoir 1100 and the integrated master cylinder 1200 ), 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 master chambers 1220a and 1220b, and provides a reaction force to the driver when the driver applies a foot force to the brake pedal 10 for braking operation. Thus, while providing a stable pedal feel, it is provided to pressurize and discharge the pressurized medium accommodated therein.

The integrated master cylinder 1200 may be divided into a pedal simulation unit that provides a pedal feel to the driver and a master cylinder unit that delivers a pressurized medium to the second hydraulic circuit 1520 to be described later. The integrated master cylinder 1200 is sequentially provided with a pedal simulation unit and a master cylinder unit 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 therein, and a first simulation chamber 1240a formed on the inlet side of the cylinder block 1210 to which the brake pedal 10 is connected. , The first simulation piston 1240 provided in the first simulation chamber 1240a and connected to the brake pedal 10 so as to be displaceable by the operation of the brake pedal 10, and the first simulation piston 1240 on the cylinder block 1210 1 A second simulation chamber 1230a formed inside the simulation chamber 1240a, and a displacement of the first simulation piston 1240 or pressurization received in the first simulation chamber 1240a provided in the second simulation chamber 1230a The second simulation piston 1230 is provided to be displaceable by the fluid pressure of the medium, and the cylinder block 1210 is formed inside the second simulation chamber 1230a and has a diameter smaller than that of the second simulation chamber 1230a. The first master chamber 1220a and the second master chamber 1220b to be formed, and a pressure medium provided in the second master chamber 1220b and accommodated in the displacement of the second simulation piston 1230 or the first master chamber 1220a The master piston 1220 provided to be displaceable by the hydraulic pressure of and an elastic member that is disposed between the first simulation piston 1230 and the second simulation piston 1230 to provide a pedal feel through the elastic restoring force generated during compression ( 1250, a simulator spring 1270a elastically supporting the second simulation piston 1230, a piston spring 1270b elastically supporting the master piston 1220, a first simulation chamber 1240a and a reservoir 1100 It may include a simulation flow path 1260 connecting to and a simulator valve 1261 provided in the simulation flow path 1260 to control the flow of the pressurized medium.

The first simulation chamber 1240a, the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b are provided on the cylinder block 1210 of the integrated master cylinder 1200. 10) It may be formed sequentially from side (right side with reference to FIG. 1) to inner side (left side with reference to FIG. 1).

The first simulation piston 1240 may be provided in the first simulation chamber 1240a to generate hydraulic pressure or negative pressure in the pressurized medium accommodated in the chamber according to the forward and backward movement.

The second simulation piston 1230 may be provided across the second simulation chamber 1230a and the first master chamber 1220a to form hydraulic pressure or negative pressure in the pressurized medium accommodated in each chamber according to the forward and backward movement. Specifically, the second simulation piston 1230 has a diameter of one end (end on the side of the second simulation chamber 1230a) is larger than the diameter of the other end (end on the side of the first master chamber 1220a), 2 Each chamber may be partitioned by sealing the side of the simulation chamber 1230a and the other end of the first master chamber 1220a. Accordingly, as the second simulation piston 1230 moves forward and backward, a hydraulic pressure or negative pressure may be formed simultaneously in the pressurized medium accommodated in the second simulation chamber 1230a and the first master chamber 1220a.

The master piston 1220 may be provided in the second master chamber 1220b to form hydraulic pressure or negative pressure in the pressurized medium accommodated in the chamber according to the forward and backward movement.

The first simulation chamber 1240a may be formed on the inlet side or the outermost side (the right side based on FIG. 1) of the cylinder block 1210, and the first simulation chamber 1240a is provided with a brake via the input rod 12. A first simulation piston connected to the pedal 10 may be accommodated to be reciprocally moved.

In the first simulation chamber 1240a, the 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 the simulation flow path 1260 to be described later, so that the pressurized medium may flow in and out of the reservoir 1100 from the first simulation chamber 1240a, and the second hydraulic port 1280b will be described later. It is connected to the first backup flow path 1610 and discharges the pressurized medium from the first simulation chamber 1240a toward the first backup flow path 1610 or, conversely, pressurizes the pressure from the first backup flow path 1610 toward the first simulation chamber 1240a. Media may enter.

Meanwhile, the first simulation chamber 1240a may be assisted in communication with the reservoir 1100 through the auxiliary hydraulic port 1280h. By connecting the auxiliary reservoir flow path 1740 to the auxiliary hydraulic port 1280h, it is possible to assist the flow of the pressurized medium between the first simulation chamber 1240a and the reservoir 1100, and in front of the auxiliary hydraulic port 1280h (Fig. A sealing member (1290a), which will be described later, is provided on the left side based on 1), allowing supply of the pressurized medium from the auxiliary reservoir flow path 1740 to the first simulation chamber 1240a, but blocking the flow of the pressurized medium in the opposite direction, A sealing member 1290b, which will be described later, is provided at the rear of the reservoir flow path 1740 (on the right with reference to FIG. 1), so that the pressurized medium can be prevented from leaking out of the cylinder block 1210 from the first simulation chamber 1240a. have.

The first simulation piston 1240 is accommodated and provided in the first simulation chamber 1240a, but by moving forward (to the left based on FIG. 1), the pressurized medium accommodated in the first simulation chamber 1240a is pressed to form a hydraulic pressure, or It is possible to pressurize the elastic member 1250 to be described later, and form negative pressure inside the first simulation chamber 1240a or return the elastic member 1250 to its original position and shape by moving backward (to the right with reference to FIG. 1). I can make it.

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

In the second simulation chamber 1230a, a pressurized medium may be introduced and discharged through the third hydraulic port 1280c. The third hydraulic port 1280c is connected to the first reservoir flow path 1710, which will be described later, so that the pressurized medium accommodated in the second simulation chamber 1230a can be discharged to the reservoir 1100, and conversely, pressurized from the reservoir 1100. Media may enter.

The second simulation piston 1230 is accommodated and provided in the second simulation chamber 1230a, but by advancing to form the hydraulic pressure of the pressurized medium accommodated in the second simulation chamber 1230a, or by reversing the second simulation chamber 1230a. It can form negative pressure. At the same time, as the second simulation piston 1230 moves forward and backward, it may form hydraulic pressure or negative pressure in the first master chamber 1220a to be described later. Between the inner wall of the cylinder block 1210 and the outer circumferential surface of one end of the second simulation piston 1230 (the end of the first simulation chamber 1240a side), at least one sealing member ( 1290c) may be provided.

A step portion that is stepped inward may be provided at a portion where the second simulation chamber 1230a is formed on the cylinder block 1210, and a step portion formed to be stepped inward may be provided on the outer circumferential surface of the second simulation piston 1230 so that the step portion is formed to be extended to the outside. The provided extension may be provided. Specifically, the cylinder block 1210 is provided with a stepped portion formed to be stepped inward between the second simulation chamber 1230a and the first master chamber 1220a, and accordingly, the first and second master chambers 1220a and 1220b ) May have a diameter smaller than that of the first and second simulation chambers 1240a and 1230a. In addition, the second simulation piston 1230 is provided with an expansion portion provided to be caught in the step portion at the end of the first simulation chamber 1240a side, and at least one sealing member 1290c is provided in the expansion portion, and the second simulation chamber 1230a ) And the first simulation chamber 1240a may be sealed, and the second simulation chamber 1230a may be pressurized when the second simulation piston 1230 advances. The end of the second simulation piston 1230 on the side of the first master chamber 1220a is sealed between the second simulation chamber 1230a and the first master chamber 1220a by a sealing member 1290d to be described later. 2 When the simulation piston 1230 advances, the first master chamber 1220a may be pressurized.

The first master chamber 1220a may be formed inside the second simulation chamber 1230a on the cylinder block 1210 (left side based on FIG. 1), and the second simulation piston ( 1230) may be accommodated in a reciprocating manner.

In the first master chamber 1220a, a pressurized medium may be introduced and discharged through the fourth hydraulic port 1280d and the fifth hydraulic port 1280e. Specifically, the fourth hydraulic port 1280d may be connected to the second reservoir flow path 1720 to be described later to discharge the pressurized medium toward the reservoir 1100, or, conversely, the pressurized medium accommodated in the reservoir 1100 may be introduced. The fifth hydraulic port 1280e is connected to the auxiliary backup passage 1630 to be described later, and the pressurized medium is discharged from the first master chamber 1220a toward the auxiliary backup passage 1630 or, conversely, the first master from the auxiliary backup passage 1630. The pressurized medium may flow into the chamber 1220a. Meanwhile, a pair of sealing members 1290d are provided in front and rear of the fourth hydraulic port 1280d to prevent leakage of the pressurized medium.

The second simulation piston 1230 is accommodated and provided in the first master chamber 1220a, but by advancing to form the hydraulic pressure of the pressurized medium accommodated in the first master chamber 1220a, or by reversing the first master chamber 1220a. It can form negative pressure.

In addition, the second simulation piston 1230 may include a cut-off hole 1231 connecting the first master chamber 1220a and the fourth hydraulic port 1280d. Specifically, the cut-off hole 1231 is formed through the inside of the second simulation piston 1230 so that when the second simulation piston 1230 is in its original position, the first master chamber 1220a and the fourth hydraulic port 1280d When the second simulation piston 1230 is out of the original position, the cut-off hole 1231 and the fourth hydraulic port 1280d are shifted, so that the first master chamber 1220a and the second reservoir flow path 1720 are It can be arranged to block the connection. In other words, it may be provided to selectively connect the first master chamber 1220a and the second reservoir flow path 1720. Therefore, the second simulation piston 1230 connects the first master chamber 1220a and the reservoir 1100 in the normal operation mode, which will be described later, and the second simulation piston 1230 moves in the abnormal operation mode. The connection between the master chamber 1220a and the reservoir 1100 may be blocked.

The first master chamber 1220a may be formed inside the second simulation chamber 1230a on the cylinder block 1210 (left side based on FIG. 1), and the second simulation piston ( 1230) may be accommodated in a reciprocating manner.

In the second master chamber 1220b, the pressurized medium may be introduced and discharged through the sixth hydraulic port 1280f and the seventh hydraulic port 1280g. Specifically, the sixth hydraulic port 1280f may be connected to the third reservoir flow path 1730 to be described later to discharge the pressurized medium toward the reservoir 1100, or, conversely, the pressurized medium accommodated in the reservoir 1100 may be introduced. The seventh hydraulic port (1280g) is connected to the second backup passage (1620) to be described later, and the pressurized medium is discharged from the second master chamber (1220b) toward the second backup passage (1620) or, conversely, from the second backup passage (1620). The pressurized medium may be introduced into the second master chamber 1220b. Meanwhile, a pair of sealing members 1290e are provided in front and rear of the sixth hydraulic port 1280f to prevent leakage of the pressurized medium.

The master piston 1220 is accommodated and provided in the second master chamber 1220b, but by advancing to form a hydraulic pressure of the pressurized medium accommodated in the second master chamber 1220b, or by retreating, negative pressure is applied to the second master chamber 1220b. Can be formed.

In addition, the master piston 1220 may include a cut-off hole 1221 connecting the second master chamber 1220b and the sixth hydraulic port 1280f in the normal mode. Specifically, the cut-off hole 1221 is formed through the inside of the master piston 1220 to connect the second master chamber 1220b and the sixth hydraulic port 1280f when the master piston 1220 is in its original position, When the master piston 1220 is out of its original position, the cut-off hole 1221 and the sixth hydraulic port 1280f are displaced to block the connection between the second master chamber 1220b and the third reservoir flow path 1730. I can. In other words, it may be provided to selectively connect the second master chamber 1220b and the third reservoir flow path 1730. Therefore, the master piston 1220 connects the second master chamber 1220b and the reservoir 1100 in the normal operation mode to be described later, and in the abnormal operation mode, the master piston 1220 moves, so the second master chamber 1220b It is possible to block the connection between the and the reservoir 1100.

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

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

Corresponds to the shape of the elastic member 1250 to facilitate smooth compression and deformation of the elastic member 1250 on the rear surface of the first simulation piston 1240 facing the elastic member 1250 (the left surface based on FIG. 1). It may be provided with a receiving groove that is formed in a recessed shape.

The simulator spring 1270a is provided to elastically support the second simulation piston 1230. The simulator spring 1270a has one end supported by the master piston 1220 and the other end supported by the second simulation piston 1230, thereby elastically supporting the second simulation piston 1230. When the second simulation piston 1230 advances in accordance with the braking operation and displacement occurs, the simulator spring 1270a is compressed. After that, when the braking is released, the simulator spring 1270a expands by an elastic force and the second simulation piston ( 1230) can return to the original position.

The piston spring 1270b is provided to elastically support the master piston 1220. The piston spring 1270b has one end supported by the cylinder block and the other end supported by the master piston 1220, thereby elastically supporting the master piston 1220. When the master piston 1220 advances and displacement occurs according to the braking operation, the piston spring 1270b is compressed. After that, when the braking is released, the piston spring 1270b expands by the elastic force and the master piston 1220 is in its original position. You can return to

The simulation flow path 1260 is provided to communicate the first simulation chamber 1240a and the reservoir 1100 with each other, and a simulator valve 1261 that controls the flow of the pressurized medium in both directions may be provided in the simulation flow path 1260. have. The simulator valve 1261 may be provided as a normally closed type solenoid valve that operates to open the valve when it receives an electrical signal from the electronic control unit after being in a normally closed state. The simulator valve 1261 may be opened in the normal operating mode of the electronic brake system 1000.

When explaining the pedal simulation operation by the integrated master cylinder 1200, the driver operates the brake pedal 10 during normal operation and is provided in the first backup passage 1610 and the second backup passage 1620 to be described later. The first cut valve 1611, the second cut valve 1612, the third cut valve 1621, and the fourth cut valve 1622 are closed, and the reservoir valve 1711 of the first reservoir flow path 1710 is also Closed. On the other hand, the simulator valve 1261 provided in the simulation flow path 1260 is opened. As the operation of the brake pedal 10 proceeds, the first simulation piston 1240 moves forward, but the first master chamber 1220a is closed by the closing operation of the first cut valve 1611 and the second cut valve 1612. Is sealed, the second master chamber 1220b is sealed by the closing operation of the third cut valve 1613 and the fourth cut valve 1614, and the second simulation chamber ( 1230a) is also sealed, so that the hydraulic pressure of the pressurized medium accommodated in the first simulation chamber 1240a is transmitted to the reservoir 1100 through the simulation flow path 1260, and the first simulation piston 1240 advances to generate displacement. On the other hand, as the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b are closed, the second simulation piston 1230 cannot be displaced. Accordingly, the first simulation piston ( The displacement of the 1240 compresses the elastic member 1250, and an elastic restoring force due to compression of the elastic member 1250 may be provided to the driver as a pedal feel. Thereafter, when the driver releases the pedal effort of the brake pedal 10, the elastic member 1250 returns to its original shape and position by the elastic restoring force, and the first simulation chamber 1240a is transferred to the reservoir 1100 through the simulation flow path 1260. ), or the pressurized medium may be supplied and filled from the first hydraulic circuit 1510 through a first backup passage 1610 to be described later.

As described above, since the inside of the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b is always filled with a pressurized medium, the master piston 1220 and the second simulation during pedal simulation operation As friction of the piston 1230 is minimized, durability of the integrated master cylinder 1200 may be improved, as well as 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 state will be described later with reference to FIG. 8.

The reservoir 1100 may accommodate and store a pressurized medium therein. The reservoir 1100 may be connected to respective component elements such as an integrated master cylinder 1200, a hydraulic pressure supply device 1300 to be described later, and hydraulic circuits 1510 and 1520 to be described later to supply or receive a pressurized medium. In the drawings, several reservoirs 1100 are shown with the same reference numerals, but this is an example for helping understanding of the invention, and the reservoir 1100 is provided as a single component or a plurality of separate and independent components. I can.

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

The reservoir flow path 1700 includes a first reservoir flow path 1710 connecting the second simulation chamber 1230a and the reservoir 1100, and a second reservoir flow path connecting the first master chamber 1220a and the reservoir 1100. 1720 and a third reservoir flow path 1730 connecting the second master chamber 1220b and the reservoir 1100 may be included.

The first reservoir flow path 1710 may be provided with a reservoir valve 1711 provided as a two-way control valve that controls the flow of the braking fluid transmitted through the first reservoir flow path 1710. The reservoir valve 1711 may be provided as a normal open type solenoid valve that operates to close the valve when it receives an electrical signal from the electronic control unit after being in an open state normally. The reservoir valve 1711 may be closed in the normal operating mode of the electronic brake system 1000.

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

The hydraulic pressure supply device 1300 includes a motor (not shown) that generates rotational force by an electrical signal from the pedal displacement sensor 11, and a power conversion unit (not shown) that converts the rotational motion of the motor into linear motion and transmits it to the hydraulic pressure providing unit. Poem).

The hydraulic pressure supply device 1300 is provided between the cylinder block 1310 to accommodate the pressurized medium, the hydraulic piston 1320 accommodated in the cylinder block 1310, and the hydraulic piston 1320 and the cylinder block 1310. A sealing member 1350a provided to seal the pressure chambers 1330 and 1340, and a drive shaft 1390 for transmitting power output from the power conversion unit to the hydraulic piston 1320.

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

The first pressure chamber 1330 is connected to a first hydraulic flow path 1401 to be described later through a first communication hole 1360a formed in the cylinder block 1310, and the second pressure chamber 1340 is a cylinder block 1310. ) Is connected to a second hydraulic flow path 1402 to be described later through a second communication hole 1360b formed in ).

The sealing member includes a piston sealing member 1350a provided between the hydraulic piston 1320 and the cylinder block 1310 and sealing between the first pressure chamber 1330 and the second pressure chamber 1340. The hydraulic or negative pressure of the first pressure chamber 1330 and the second pressure chamber 1340 generated by the forward or backward movement of the hydraulic piston 1320 is sealed by the piston sealing member 1350a and does not leak. It may be delivered to the hydraulic flow path 1401 and the second hydraulic flow path 1402.

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

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

The worm shaft may be integrally formed with the rotational shaft of the motor, and a worm may be formed on an outer circumferential surface to be coupled to mesh with the worm wheel to rotate the worm wheel. The worm wheel is connected to be engaged with the drive shaft 1390 to linearly move the drive shaft 1390, and the drive shaft 1390 is connected to the hydraulic piston 1320, through which the hydraulic piston 1320 is connected to the cylinder block 1310. It can be moved sliding within.

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

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

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

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

In this way, the hydraulic pressure supply device 1300 may generate hydraulic pressure or negative pressure in the first pressure chamber 1330 and the second pressure chamber 1340, respectively, depending on the rotation direction of the worm shaft by driving the motor. It can be determined by controlling the valves whether to implement braking by doing so or to release braking using negative pressure. A detailed description of this will be described later.

On the other hand, the power conversion unit according to the first embodiment of the present invention is not limited to any one structure as long as it can convert the rotational motion of the motor into the linear motion of the hydraulic piston 1320, and is made of a device of various structures and methods. It should be understood the same way.

The hydraulic pressure supply device 1300 may be hydraulically connected to the reservoir 1100 by the dump control unit 1800. The dump control unit 1800 includes a second dump passage 1820 connecting the second pressure chamber 1340 and the reservoir 1100, and a first dump passage connecting the first pressure chamber 1330 and the reservoir 1100 ( 1810) and an auxiliary dump passage 1830 auxiliaryly connecting the first pressure chamber 1330 and the reservoir 1100 to each other.

A second dump check valve 1821 and a first dump check valve 1811 for controlling the flow of the pressurized medium may be provided in the second dump passage 1820 and the first dump passage 1810, respectively. The second dump check valve 1821 may be provided to allow only the flow of the pressurized medium from the reservoir 1100 to the second pressure chamber 1340 and block the flow of the pressurized medium in the opposite direction, and the first dump check valve 1811 may be provided to allow only the flow of the pressurized medium from the reservoir 1100 to the first pressure chamber 1330 and block the flow of the pressurized medium in the opposite direction.

The auxiliary dump passage 1830 may assist in communication between the first pressure chamber 1330 and the reservoir 1100 through the auxiliary hydraulic port 1830a. Specifically, the auxiliary hydraulic port 1830a is connected to the auxiliary dump passage 1830, thereby assisting the flow of the pressurized medium between the first pressure chamber 1330 and the reservoir 1100, and the auxiliary hydraulic port 1830a A sealing member 1350b is provided on the front side (on the left side of Fig. 1), allowing the supply of the pressurized medium from the auxiliary dump passage 1830 to the first pressure chamber 1330, but blocking the flow of the pressurized medium in the opposite direction, A sealing member 1350c is provided at the rear (right side of FIG. 1) of the auxiliary dump passage 1830 to prevent leakage of the pressure medium from the first pressure chamber 1330 to the outside of the cylinder block 1310. .

The hydraulic control unit 1400 may be provided to control the hydraulic pressure transmitted to each wheel cylinder 20, and the electronic control unit (ECU) is based on the hydraulic pressure information and the pedal displacement information. It is provided to control the valves.

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

The first hydraulic flow path 1401 is provided to communicate with the first pressure chamber 1330, and may be provided by branching into the third hydraulic flow path 1403 and the fourth hydraulic flow path 1404. In addition, the second hydraulic flow path 1402 is provided to communicate with the second pressure chamber 1340, and may be provided to branch into the third hydraulic flow path 1403 and the fifth hydraulic flow path 1405. That is, the third hydraulic flow path 1403 has one end connected to the first hydraulic flow path 1401 and the other end connected to the second hydraulic flow path 1402, so that the first hydraulic flow path 1401 and the second hydraulic flow path 1402 Connect

A first valve 1411 for controlling the flow of the pressurized medium may be provided in the fourth hydraulic flow path 1404. The first valve 1411 may be provided as a check valve that allows only the flow of the pressurized medium in a direction discharged from the first pressure chamber 1330 toward the sixth hydraulic flow path 1406 and blocks the flow of the pressurized medium in the opposite direction. . That is, the first valve 1411 allows the hydraulic pressure of the pressurized medium generated in the first pressure chamber 1330 to be transferred to the first hydraulic circuit 1510 or the second hydraulic circuit 1520, while allowing the pressure medium in the opposite direction. It is possible to prevent the flow from leaking into the first pressure chamber 1330 through the fourth hydraulic flow path 1404.

A second valve 1412 for controlling the flow of the pressurized medium may be provided in the fifth hydraulic flow path 1405. The second valve 1412 may be provided as a check valve that allows only the flow of the pressurized medium in a direction discharged from the second pressure chamber 1340 toward the sixth hydraulic flow path 1406 and blocks the flow of the pressurized medium in the opposite direction. . That is, the second valve 1412 allows the hydraulic pressure of the pressurized medium generated in the second pressure chamber 1340 to be transferred to the first hydraulic circuit 1510 or the second hydraulic circuit 1520, while allowing the pressure medium in the opposite direction. It is possible to prevent the flow from leaking into the second pressure chamber 1340 through the fifth hydraulic flow path 1405.

A third valve 1413 for controlling the flow of the pressurized medium may be provided in the third hydraulic flow path 1403. The third valve 1413 may be provided as a two-way control valve that controls the flow of the pressurized medium delivered along the third hydraulic flow path 1403. The third valve 1413 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 sixth hydraulic passage 1406 may be provided by joining the fourth hydraulic passage 1404 and the fifth hydraulic passage 1405, and the seventh hydraulic passage 1407 and the eighth hydraulic passage 1408 are sixth hydraulic oil. From the furnace 1406 to the first hydraulic circuit 1510 and the second hydraulic circuit 1520, each branch may be provided. In addition, the ninth hydraulic flow path 1409 may be branched from the seventh hydraulic flow path 1407 and connected to the eighth hydraulic flow path 1408.

A fourth valve 1414 and a fifth valve 1415 for controlling the flow of the pressurized medium may be provided in the seventh hydraulic passage 1407 and the eighth hydraulic passage 1408, respectively. The fourth valve 1414 may be provided as a check valve that allows only the flow of the pressurized medium from the sixth hydraulic flow path 1406 to the first hydraulic circuit 201 and blocks the flow of the pressurized medium in the opposite direction. That is, the fourth valve 1414 allows hydraulic pressure to be transmitted from the sixth hydraulic flow path 1406 to the first hydraulic circuit 201, while the hydraulic pressure from the first hydraulic circuit 201 to the sixth hydraulic flow path 1406 This leakage can be prevented. Likewise, the fifth valve 1415 may be provided as a check valve that allows only the flow of the pressurized medium from the sixth hydraulic flow passage 1406 to the second hydraulic circuit 1520 and blocks the flow of the pressurized medium in the opposite direction. . As a result, the fifth valve 1415 allows hydraulic pressure to be transferred from the sixth hydraulic flow path 1406 to the second hydraulic circuit 1520, while the hydraulic pressure decreases from the second hydraulic circuit 1520 to the sixth hydraulic flow path 1406. It can prevent leakage.

The ninth hydraulic passage 1409 has one end connected to the seventh hydraulic passage 1407 and the other end connected to the eighth hydraulic passage 1408 to connect the seventh hydraulic passage 1407 and the 8th hydraulic passage 1408 Can be arranged to do. Specifically, the ninth hydraulic flow path 1409 has one end connected to the rear of the fourth valve 1414 of the seventh hydraulic flow path 1407, and the other end of the fifth valve 1415 of the eighth hydraulic flow path 1408 Can be connected to the rear of the.

In addition, a sixth valve 1416 for controlling the flow of the pressurized medium may be provided in the ninth hydraulic flow path 1409. The sixth valve 1416 may be provided as a two-way control valve that controls the flow of the pressurized medium delivered along the ninth hydraulic flow path 1409. The sixth valve 1416 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. Therefore, during normal operation, the pressurized medium can flow to the ninth hydraulic flow path 1409 by opening the sixth valve 1416 by receiving an electrical signal from the electronic control unit, and the first hydraulic circuit 1510 and the second hydraulic circuit 1520 ) Of the pressurized medium can be transmitted to each other, and accordingly, it can be adjusted to be equally pressed to the first hydraulic circuit 1510 and the second hydraulic circuit 1520. Further, when a leak occurs in any of the first hydraulic circuit 1510 and the second hydraulic circuit 1520, the sixth valve 1416 may be closed to block the hydraulic circuit where the leak occurs.

In the hydraulic control unit 1400, the hydraulic pressure formed in the first pressure chamber 1330 according to the advance of the hydraulic piston 1320 by the arrangement of the hydraulic flow paths and valves is the first hydraulic flow path 1401, the fourth hydraulic flow path ( 1404), the sixth hydraulic flow passage 1406, the seventh hydraulic flow passage 1407 can be sequentially transmitted to the first hydraulic circuit 1510, the first hydraulic passage 1401, the fourth hydraulic passage 1404 , It may be transferred to the second hydraulic circuit 1520 through the sixth hydraulic flow path 1406 and the eighth hydraulic flow path 1408 in sequence. In addition, the hydraulic pressure formed in the second pressure chamber 1340 according to the retraction of the hydraulic piston 1320 is the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the 7th hydraulic flow path. It can be transferred to the first hydraulic circuit 1510 sequentially through (1407), and the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408 ) May be transferred to the second hydraulic circuit 1520 through sequentially.

Conversely, the negative pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 moves backward may recover the pressurized medium of the reservoir 1100 communicated with the first pressure chamber 1330. Specifically, the first pressure chamber 1330 may receive a pressurized medium through the first dump passage 1810 communicating the first pressure chamber 1330 and the reservoir 1100, and the first dump passage 1810 The first dump check valve 1811 provided in the reservoir 1100 allows the pressurized medium to flow from the reservoir 1100 to the first pressure chamber 1330, so that the pressurized medium of the reservoir 1100 can be recovered. In addition, the negative pressure formed in the second pressure chamber 1340 as the hydraulic piston 1320 advances may recover the pressurized medium of the reservoir 1100 communicated with the second pressure chamber 1340. Specifically, the second pressure chamber 1340 may receive the pressurized medium through the second dump passage 1820 communicating the second pressure chamber 1340 and the reservoir 1100, and the second dump passage 1820 The second dump check valve 1821 provided in the reservoir 1100 allows the pressurized medium to flow from the reservoir 1100 to the second pressure chamber 1340, thereby recovering the pressurized medium of the reservoir 1100. A detailed description of the delivery and supply of hydraulic pressure by the arrangement of these hydraulic flow paths and valves will be described later with reference to FIGS. 2 to 8.

The first hydraulic circuit 1510 of the hydraulic control unit 1400 is the hydraulic pressure of the first and second wheel cylinders 21 and 22, which are two wheel cylinders 20 among the four wheels RR, RL, FR, and FL. And the second hydraulic circuit 1520 may control the hydraulic pressure of the third and fourth wheel cylinders 23 and 24, which are two other wheel cylinders 20.

The first hydraulic circuit 1510 receives hydraulic pressure through the seventh hydraulic flow path 1407, and the seventh hydraulic flow path 1407 is two flow paths connected to the first wheel cylinder 21 and the second wheel cylinder 22. Can be provided by branching into. In addition, the second hydraulic circuit 1520 receives hydraulic pressure from the hydraulic pressure supply device 1300 through the eighth hydraulic flow path 1408, and the eighth hydraulic flow path 1408 includes a third wheel cylinder 23 and a fourth wheel cylinder. It may be provided by branching into two flow paths connected to (24).

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

The first and second hydraulic circuits 1510 and 1520 are first to fourth check valves 1513a, 1513b, 1523a, and 1523b connected in parallel to the first to fourth inlet valves 1511a, 1511b, 1521a, and 1521b. ) Can be included. Check valves (1513a, 1513b, 1523a, 1523b) are a bypass connecting the front and rear of the first to fourth inlet valves (1511a, 1511b, 1521a, 1521b) on the first and second hydraulic circuits (1510, 1520) It may be provided in the flow path, and allows only the flow of the pressurized medium from each wheel cylinder 20 to the hydraulic pressure supply device 1300, and the flow of the pressurized medium from the hydraulic pressure supply device 1300 to the wheel cylinder 20 can be blocked. . The first to fourth check valves 1513a, 1513b, 1523a, 1523b can quickly remove the hydraulic pressure of the pressurized medium applied to each wheel cylinder 20, and the first to fourth inlet valves 1511a, 1511b, Even when 1521a and 1521b do not operate normally, the hydraulic pressure of the pressurized medium applied to the wheel cylinder 20 can be smoothly returned to the hydraulic pressure supply device 1300.

The first backup passage 1610 and the second backup passage 1620 are first to fourth cut valves 1611 and 1612 to control the bidirectional flow and hydraulic pressure of the pressurized medium delivered to the first to fourth wheel cylinders 24. , 1621, 1622) may be provided. Specifically, the first backup passage 1610 is branched and connected in parallel with the first wheel cylinder 21 and the second wheel cylinder 22 to provide a first cut valve 1611 and a second cut valve 1612, respectively. And, the second backup passage 1620 is branched and connected in parallel with the third wheel cylinder 23 and the fourth wheel cylinder 24 to provide a third cut valve 1621 and a fourth cut valve 1622, respectively. I can.

The first to fourth cut valves 1611, 1612, 1621, 1622 are normally open type solenoid valves that operate to close when an electrical signal is received from the electronic control unit. Can be provided.

Accordingly, when the first to fourth cut valves 1611, 1612, 1621, 1622 are closed in the normal braking mode, the pressurized medium of the integrated master cylinder 1200 is prevented from being directly transferred to the wheel cylinder 20 and at the same time , The hydraulic pressure provided from the hydraulic pressure supply device 1300 may be supplied to the wheel cylinder 20 through the hydraulic control unit 1400 to brake. On the other hand, when the normal braking mode is released, at least a part of the first to fourth cut valves 1611, 1612, 1621, 1622 is opened to pass through the first backup passage 1610 and the second backup passage 1620, and an integrated master cylinder ( A pressurized medium may be delivered to the reservoir 1100 through 1200 to release the brake. In addition, in the abnormal braking mode, the first to fourth cut valves 1611, 1612, 1621, 1622 are opened so that the pressurized medium pressurized in the integrated master cylinder 1200 is transferred to the wheel cylinder through the backup channels 1610, 1620, 1630. It can be supplied directly to (40) to implement braking.

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

The first backup passage 1610 is provided to connect the first simulation chamber 1240a of the integrated master cylinder 1200 and the first hydraulic circuit 1510, and the second backup passage 1620 is an integrated master cylinder 1200 It is provided to connect the second master chamber 1220b and the second hydraulic circuit 1520, and the auxiliary backup passage 1630 is the first master chamber 1220a and the first hydraulic circuit 1510 of the integrated master cylinder 1200. ) Can be provided to connect.

Specifically, the first backup passage 1610 has one end connected to the first simulation chamber 1240a, and the other end of the first inlet valve 1511a and the second inlet valve 1511b on the first hydraulic circuit 1510. It may be connected to the downstream side, and the second backup passage 1620 has one end connected to the second master chamber 1220b, the other end on the second hydraulic circuit 1520, the third inlet valve 1521a and the fourth inlet valve It can be connected to the downstream side of (1521b). In addition, the auxiliary backup passage 1630 may connect the first simulation chamber 1240a and the first hydraulic circuit 1510, but may be connected to and joined to the first backup passage 1610.

The auxiliary backup passage 1630 may include an orifice 1631 for slowing the flow velocity of the pressurized medium passing through the auxiliary backup passage 1630. Accordingly, in the diagnostic mode to be described later, the pressurized medium transferred from the first hydraulic circuit 1510 to the integrated master cylinder 1200 may be filled with the first simulation chamber 1240a earlier than the first master chamber 1220a. The contents will be described later.

Accordingly, in the abnormal operation mode, the first to fourth cut valves 1611, 1612, 1621, 1622 are opened so that the pressurized medium pressurized by the integrated master cylinder 1200 is transferred to the first and second backup passages and the auxiliary backup passage 1610, Braking may be implemented by being directly supplied to the wheel cylinder 20 through 1620 and 1630.

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

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

The operation of the electronic brake system 1000 according to the first 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. It may include a normal operating mode (fallback mode).

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

In the normal operation mode of the electronic brake system 1000 according to the first embodiment of the present invention, as the hydraulic pressure transmitted from the hydraulic pressure supply device 1300 to the wheel cylinder 20 increases, the first braking mode and the second braking mode And a third braking mode. Specifically, in the first braking mode, hydraulic pressure by the hydraulic pressure supply device 1300 is primarily provided to the wheel cylinder, and in the second braking mode, hydraulic pressure by the hydraulic pressure supply device 1300 is secondarily provided to the wheel cylinder. A higher braking pressure than the first braking mode is transmitted, and in the third braking mode, the hydraulic pressure by the hydraulic pressure supply device 1300 is thirdly provided to the wheel cylinder to deliver the highest braking pressure.

The first to third braking modes can be changed by varying the operation of the hydraulic pressure supply device 1300 and the hydraulic control unit 1200. The hydraulic pressure supply device 1300 can provide a sufficiently high hydraulic pressure without a high-spec motor (not shown) by utilizing the first to third braking modes, and further, it is possible to prevent unnecessary loads applied to the motor. Accordingly, while reducing the cost and weight of the brake system, a stable braking force can be secured, and durability and operational reliability of the device can be improved.

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

Referring to FIG. 2, when the driver presses the brake pedal 10 at the initial braking, the motor (not shown) operates to rotate in one direction, and the rotational force of the motor is transmitted to the hydraulic pressure supply device 1300 by the power conversion unit. , As the hydraulic piston 1320 of the hydraulic pressure supply device 1300 advances, a hydraulic pressure is generated in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is primarily transmitted to the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510. In this case, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be kept open.

In addition, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially flows through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. It passes through and is primarily transmitted to the wheel cylinder 20 provided in the second hydraulic circuit 1520. In this case, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 may be kept open.

In addition, the third valve 1413 provided in the third hydraulic passage 1403 is maintained in a closed state to block the flow of the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 toward the second pressure chamber 1340 Thus, all of the hydraulic pressure of the pressurized medium passing through the first hydraulic flow path 1401 may be transmitted to the first hydraulic circuit 1510 and the second hydraulic circuit 1520.

In the first braking mode, the first dump check valve 1811 provided in the first dump passage 1810 connected to the first pressure chamber 1330 is pressurized from the reservoir 1100 to the first pressure chamber 1330 While allowing the flow of the medium, it blocks the flow of the pressurized medium from the first pressure chamber 1330 to the reservoir 1100. The pressure formed in the first pressure chamber 1330 by the advance of the hydraulic piston 1320 The fluid pressure of the medium is all delivered to the first hydraulic flow path 1401, so that quick braking can be implemented.

In the first braking mode implementing the braking of the wheel cylinder 20 by the hydraulic pressure supply device 1300, the first cut valve 1611 and the second cut valve 1612 provided in the first backup passage 1610, The third cut valve 1621 and the fourth cut valve 1622 provided in the second backup passage 1620 are closed and switched, and the pressurized medium discharged from the integrated master cylinder 1200 is transferred to the wheel cylinder 20 Is prevented. In addition, the simulator valve 1261 provided in the simulation flow path 1260 is opened so that the first simulation chamber 1240a and the reservoir 1100 may communicate with each other.

Specifically, when a pedal effort is applied to the brake pedal 10, the first cut valve 1611, the second cut valve 1612, the third cut valve 1621, the fourth cut valve 1622, and the reservoir valve 1711 Is closed, so that the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b are closed. Therefore, even if a pedal effort is applied to the brake pedal 10, the second simulation piston 1230 and the master piston 1220 do not displace. On the other hand, since the simulator valve 1261 is open and the first simulation chamber 1240a and the reservoir 1100 communicate with each other, the pressurized medium accommodated in the first simulation chamber 1240a is transferred to the reservoir 1100 through the simulation flow path 1260. It is supplied, and the first simulation piston 1240 smoothly advances by the pedal effort of the brake pedal to generate displacement. As the first simulation piston 1240 advances while the second simulation piston 1230 is fixed, the elastic member 1250 disposed between the first simulation piston 1240 and the second simulation piston 1230 is compressed. In addition, a reaction force corresponding to the pedal effort of the brake pedal is applied by the elastic restoring force of the compressed elastic member 1250, thereby providing a stable and appropriate pedal feel to the driver.

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 when a braking pressure higher than the first braking mode is to be provided.

3 is a hydraulic circuit diagram showing a state in which the electronic brake system 1000 according to the first embodiment of the present invention performs a second braking mode. Referring to FIG. 4, the electronic control unit is sensed by the pedal displacement sensor 11 When the displacement or operating speed of one brake pedal 10 is higher than the preset first displacement level, or the hydraulic pressure sensed by the flow path pressure sensor is higher than the preset first pressure level, a higher braking pressure is required. It is determined that the first braking mode can be switched to the second braking mode.

When switching from the first braking mode to the second braking mode, the motor operates to rotate in the other direction, and the rotational force of the motor is transmitted to the hydraulic pressure supply device 1300 by the power conversion unit, and the hydraulic piston 1320 moves backward. Hydraulic pressure is generated in the second pressure chamber 1340. The hydraulic pressure discharged from the second pressure chamber 1340 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the second pressure chamber 1340 sequentially passes through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is transmitted secondarily to the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510. In this case, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be kept open.

In addition, the hydraulic pressure formed in the second pressure chamber 1340 is sequentially passed through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. 2 Secondly transmitted to the third and fourth wheel cylinders 23 and 24 provided in the hydraulic circuit 1520. In this case, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 may be kept open.

In addition, the third valve 1413 provided in the third hydraulic flow path 1403 is maintained in a closed state to block the flow of the hydraulic pressure of the pressurized medium formed in the second pressure chamber 1340 toward the first pressure chamber 1330 As such, all of the hydraulic pressure of the pressurized medium passing through the second hydraulic flow path 1402 may be transmitted to the first hydraulic circuit 1510 and the second hydraulic circuit 1520.

In the second braking mode, the second dump check valve 1821 provided in the second dump passage 1820 connected to the second pressure chamber 1340 is pressurized from the reservoir 1100 to the second pressure chamber 1340. While allowing the flow of the medium, it blocks the flow of the pressurized medium from the second pressure chamber 1340 to the reservoir 1100, and the pressure formed in the second pressure chamber 1340 by the backward movement of the hydraulic piston 1320 The fluid pressure of the medium is all delivered to the second hydraulic flow path 1402, so that quick braking can be implemented.

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

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

4 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the first embodiment of the present invention performs a third braking mode. Referring to FIG. 4, the electronic control unit is a brake pedal sensed by the pedal displacement sensor 11 If the displacement of (10) is higher than the preset second displacement level or the hydraulic pressure detected by the flow path pressure sensor is higher than the preset second pressure level, it is determined that a higher braking pressure is required and the second braking mode You can switch to the third braking mode at.

When switching from the second braking mode to the third braking mode, the motor (not shown) operates to rotate in one direction again, and the rotational force of the motor is transmitted to the hydraulic pressure supply device 1300 by the power conversion unit, and the hydraulic piston ( As the 1320 advances, hydraulic pressure is generated in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is thirdly transmitted to the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510. In this case, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be kept open.

In addition, the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. 2 It is thirdly transmitted to the third and fourth wheel cylinders 23 and 24 provided in the hydraulic circuit 202. In this case, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 may be kept open.

On the other hand, since high-pressure hydraulic pressure is provided, as the hydraulic piston 1320 advances, the hydraulic pressure in the first pressure chamber 1330 also increases the force to move the hydraulic piston 1320 backward, and the load applied to the motor (not shown). Will increase rapidly. Accordingly, in the third braking mode, the third valve 1413 is opened to allow the flow of the pressurized medium through the third hydraulic flow path 1403. In other words, a part of the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the second hydraulic flow path 1402, and the second pressure chamber 1340 ), through which the first pressure chamber 1330 and the second pressure chamber 1340 communicate with each other to synchronize the hydraulic pressure, thereby reducing the load applied to the motor and improving the durability and reliability of the device. . At this time, the second dump check valve 1821 blocks the flow of the pressurized medium from the second pressure chamber 1340 to the reservoir, so that negative pressure is generated in the second pressure chamber 1340 by the advance of the hydraulic piston 114. It can be formed stably, and a part of the hydraulic pressure formed in the first pressure chamber 1330 flows into the second pressure chamber 1340 quickly and smoothly.

Since the operation of the integrated master cylinder 1200 in the third braking mode is the same as the operation of the integrated master cylinder 1200 in the first braking mode described above, a description will be omitted to prevent duplication of contents.

Hereinafter, a method of releasing braking 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 hydraulic piston 1320 of the electronic brake system 1000 according to the first embodiment of the present invention moves backward and releases the third braking mode.

Referring to FIG. 5, when the pedal effort applied to the brake pedal 10 is released, a motor (not shown) generates a rotational force in another direction and transmits it to the power conversion unit, and the power conversion unit moves the hydraulic piston 1320 backward. As a result, the hydraulic pressure in the first pressure chamber 1330 can be relieved and hydraulic pressure can be generated in the second pressure chamber 1340, and the pressure medium discharged from the second pressure chamber 1340 is the hydraulic control unit 1400. It may be transmitted to the first and second hydraulic circuits 1510 and 1520 through. At the same time, the first cut valve 1611 or the second cut valve 1612 operates to open, and the third cut valve 1613 or the fourth cut valve 1614 operates to open, and the first and second hydraulic circuits The pressure medium of (1510, 1520) and the pressure medium of the first to fourth wheel cylinders (21, 22, 23, 24) are integrated through the first and second backup passages and auxiliary backup passages (1610, 1620, 1630). It may be delivered to the reservoir 1100 through the master cylinder 1200.

Specifically, the hydraulic pressure generated in the first pressure chamber 1330 by the third braking mode is resolved as the hydraulic piston moves backward, and the hydraulic pressure is generated in the second pressure chamber 1340. The pressurized medium discharged from the second pressure chamber 1340 is sequentially passed through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is transmitted to the hydraulic circuit 1510. The hydraulic pressure transmitted from the second pressure chamber 1340 to the first hydraulic circuit 1510 and the hydraulic pressures of the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510 are the first cut valves. As at least one of the 1611 and the second cut valve 1612 is opened, the first backup passage 1610 and the auxiliary backup passage 1630, the first simulation chamber 1240a and the first master chamber 1220a It is recovered to the reservoir 1100 through the simulation flow path 1260 and the second reservoir flow path 1720 connected to each chamber through sequentially passing through. At this time, the simulator valve 1261 is opened to allow the flow of the pressurized medium on the simulation flow path 1260, and the reservoir valve 1711 is closed to block the flow of the pressurized medium on the first reservoir flow path 1710. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 201 may maintain an open state.

In addition, the pressure medium discharged from the second pressure chamber 1340 sequentially passes through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. It is transmitted to the second hydraulic circuit 1520. The hydraulic pressure transferred from the second pressure chamber 1340 to the second hydraulic circuit 1520 and the hydraulic pressure of the third and fourth wheel cylinders 23 and 24 provided in the second hydraulic circuit 1520 are the third cut valve As at least one of the 1613 and the fourth cut valve 1614 is opened, it sequentially passes through the second backup passage 1620 and the second master chamber 1220b to be connected to the second master chamber 1220b. It is recovered to the reservoir 1100 through the third reservoir flow path 1730. In addition, the third inlet valve 291a and the fourth inlet valve 291b provided in the second hydraulic circuit 201 may maintain an open state.

As described above, the sixth valve 1416 allows the flow of the pressurized medium between the first hydraulic circuit 201 and the second hydraulic circuit, and a failure of the cut valve causes the first backup passage 1610 and the second backup passage. Even if the hydraulic pressure in any one of (1620) cannot be relieved, the hydraulic pressure is relieved through the backup flow path of the hydraulic circuit on the other side to enable braking release. In addition, the third valve 1413 is closed so that the pressurized medium of the first pressure chamber 1330 is prevented from being transferred to the second pressure chamber 1340 so that the hydraulic piston 1320 can be moved back quickly and smoothly. .

When the third braking mode is released, the first dump check valve 1821 blocks the movement of the pressurized medium of the second pressure chamber 1340 toward the reservoir 1100, and the pressurized medium in the second pressure chamber 1340 is It can be discharged only through the second hydraulic flow path 1402.

After completing the releasing of the third braking mode, the releasing operation of the second braking mode shown in FIG. 6 may be switched to lower the braking pressure of the wheel cylinder 20.

6 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 releases the second braking mode.

Referring to FIG. 6, when the pedal effort applied to the brake pedal 10 is released, a motor (not shown) generates a rotational force in one direction and transmits it to the power conversion unit, and the power conversion unit advances the hydraulic piston 1320. As a result, the hydraulic pressure in the second pressure chamber 1340 can be relieved, and a hydraulic pressure can be generated in the first pressure chamber 1330, and the pressure medium discharged from the first pressure chamber 1330 is the hydraulic control unit 1400. It may be transmitted to the first and second hydraulic circuits 21 and 22 through. At the same time, the first cut valve 1611 or the second cut valve 1612 operates to open, and the third cut valve 1613 or the fourth cut valve 1614 operates to open, and thus the first and second hydraulic circuits The pressure medium of (1510, 1520) and the pressure medium of the first to fourth wheel cylinders (21, 22, 23, 24) are integrated through the first and second backup passages and auxiliary backup passages (1610, 1620, 1630). It may be delivered to the reservoir 1100 through the master cylinder 1200.

Specifically, the hydraulic pressure generated in the second pressure chamber 1340 by the second braking mode is resolved as the hydraulic piston advances, and the hydraulic pressure is generated in the first pressure chamber 1330. The pressurized medium discharged from the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is transmitted to the hydraulic circuit 1510. The hydraulic pressure transmitted from the first pressure chamber 1330 to the first hydraulic circuit 1510 and the hydraulic pressures of the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510 are the first cut valves. As at least one of the 1611 and the second cut valve 1612 is opened, the first backup passage 1610 and the auxiliary backup passage 1630, the first simulation chamber 1240a, and the first master chamber 1220a are opened. It is recovered to the reservoir 1100 through the simulation flow path 1260 and the second reservoir flow path 1720 connected to each chamber through sequential passage. At this time, the simulator valve 1261 is opened to allow the flow of the pressurized medium on the simulation flow path 1260, and the reservoir valve 1711 is closed to block the flow of the pressurized medium on the first reservoir flow path 1710. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be kept open.

In addition, the pressurized medium discharged from the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. It is transmitted to the second hydraulic circuit 1520. The hydraulic pressure transferred from the first pressure chamber 1330 to the second hydraulic circuit 1520 and the hydraulic pressure of the third and fourth wheel cylinders 23 and 24 provided in the second hydraulic circuit 1520 are the third cut valve As at least one of the 1613 and the fourth cut valve 1614 is opened, it sequentially passes through the second backup passage 1620 and the second master chamber 1220b to be connected to the second master chamber 1220b. It is recovered to the reservoir 1100 through the third reservoir flow path 1730. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 may maintain an open state.

As described above, the sixth valve 1416 allows the flow of the pressurized medium between the first hydraulic circuit 1510 and the second hydraulic circuit 1520, and the first hydraulic circuit 1510 and the second hydraulic circuit 1520 ), even if any one of the hydraulic pressures cannot be relieved, the hydraulic pressure is relieved through the backup flow path of the hydraulic circuit on the other side to enable braking release. In addition, the third valve 1413 is closed so that the pressurized medium of the first pressure chamber 1330 is prevented from being transferred to the second pressure chamber 1340 so that the hydraulic piston 1320 can be moved back quickly and smoothly. .

When the second braking mode is released, the first dump check valve 1811 blocks the movement of the pressurized medium of the first pressure chamber 1330 toward the reservoir 1100, and the pressurized medium in the first pressure chamber 1330 is It may be discharged only through the first hydraulic flow path 1401.

After releasing of the second braking mode is completed, the releasing operation of the first braking mode shown in FIG. 7 may be switched to lower the braking pressure of the wheel cylinder 20.

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

Referring to FIG. 7, when the pedal effort applied to the brake pedal 10 is released, the motor generates rotational force in another direction and transmits it to the power conversion unit, and the power conversion unit moves the hydraulic piston backward. As a result, the hydraulic pressure in the first pressure chamber 1330 can be relieved and hydraulic pressure can be generated in the second pressure chamber 1340, and the pressure medium discharged from the second pressure chamber 1340 is the hydraulic control unit 1400. It may be transmitted to the first and second hydraulic circuits 1510 and 1520 through. At the same time, the first cut valve 1611 or the second cut valve 1612 operates to open, and the third cut valve 1613 or the fourth cut valve 1614 operates to open, and thus the first and second hydraulic circuits The pressure medium of (1510, 1520) and the pressure medium of the first to fourth wheel cylinders (21, 22, 23, 24) are integrated through the first and second backup passages and auxiliary backup passages (1610, 1620, 1630). It may be delivered to the reservoir 1100 through the master cylinder 1200.

Specifically, the hydraulic pressure generated in the first pressure chamber 1330 by the first braking mode is resolved as the hydraulic piston moves backward, and the hydraulic pressure is generated in the second pressure chamber 1340. The pressurized medium discharged from the second pressure chamber 1340 is sequentially passed through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. It is transmitted to the hydraulic circuit 1510. The hydraulic pressure transmitted from the second pressure chamber 1340 to the first hydraulic circuit 1510 and the hydraulic pressures of the first and second wheel cylinders 21 and 22 provided in the first hydraulic circuit 1510 are the first cut valves. As at least one of the 1611 and the second cut valve 1612 is opened, the first backup passage 1610 and the auxiliary backup passage 1630, the first simulation chamber 1240a, and the first master chamber 1220a are opened. It is recovered to the reservoir 1100 through the simulation flow path 1260 and the second reservoir flow path 1720 connected to each chamber through sequential passage. At this time, the simulator valve 1261 is opened to allow the flow of the pressurized medium on the simulation flow path 1260, and the reservoir valve 1711 is closed to block the flow of the pressurized medium on the first reservoir flow path 1710. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 may be kept open.

In addition, the pressure medium discharged from the second pressure chamber 1340 sequentially passes through the second hydraulic flow path 1402, the fifth hydraulic flow path 1405, the sixth hydraulic flow path 1406, and the eighth hydraulic flow path 1408. It is transmitted to the second hydraulic circuit 1520. The hydraulic pressure transferred from the second pressure chamber 1340 to the second hydraulic circuit 1520 and the hydraulic pressure of the third and fourth wheel cylinders 23 and 24 provided in the second hydraulic circuit 1520 are the third cut valve As at least one of the 1613 and the fourth cut valve 1614 is opened, the second backup passage 1620 and the second master chamber 1220b are sequentially passed, thereby connecting the second master chamber 1220b. 3 It is recovered to the reservoir 1100 through the reservoir flow path 1730. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 may maintain an open state.

As described above, the sixth valve 1416 allows the flow of the pressurized medium between the first hydraulic circuit 1510 and the second hydraulic circuit 1520, and a failure of the cut valve causes the first backup passage 1610 and the 2 Even if the hydraulic pressure in any one of the backup flow paths 1620 cannot be relieved, the hydraulic pressure is relieved through the backup flow path of the hydraulic circuit on the opposite side, so that the brake can be released. In addition, the third valve 1413 is closed so that the pressurized medium of the first pressure chamber 1330 is prevented from being transferred to the second pressure chamber 1340 so that the hydraulic piston 1320 can be moved back quickly and smoothly. .

When the first braking mode is released, the second dump check valve 1821 blocks the movement of the pressurized medium of the second pressure chamber 1340 toward the reservoir 1100, and the pressurized medium in the second pressure chamber 1340 is It can be discharged only through the second hydraulic flow path 1402.

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, the operation state of the fall-back mode will be described.

8 is a hydraulic circuit diagram showing an operating state in an abnormal operation mode (fallback mode) when the electronic brake system 1000 according to the first embodiment of the present invention is unable to operate normally due to a device failure or the like.

Referring to FIG. 8, in the abnormal operation mode, each of the valves is controlled to an initial braking state, which is a non-operation state. At this time, when the driver applies a pedal effort to the brake pedal 10, the first simulation piston 1240 connected to the brake pedal 10 advances and displacement occurs. Since the simulator valve 1261 is closed and the first cut valve 1611 and the second cut valve 1612 are kept open, the first simulation chamber 1240a by the advance of the first simulation piston 1240 The pressurized medium accommodated therein may be transferred to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510 along the first backup passage 1610 to implement braking.

In addition, when the first simulation piston 1240 advances, the second simulation chamber 1230a and the first master chamber 1220a are not sealed, so that the elastic member 1250 is not compressed and the second simulation piston 1230 is By moving forward, displacement occurs. At this time, since the reservoir valve 1711, the first cut valve 1611, and the second cut valve 1612 are kept open, the second simulation chamber 1230a by the displacement of the second simulation piston 1230 The pressurized medium of is delivered to the reservoir 1100 through the first reservoir flow path 1710, and the pressurizing medium of the first master chamber 1220a is the first of the first hydraulic circuit 1510 along the auxiliary backup flow path 1630. It is transmitted to the wheel cylinder 21 and the second wheel cylinder 22 to implement braking. The cut-off hole 1231 provided in the second simulation piston 1230 blocks the connection between the first master chamber 1220a and the second reservoir flow path 1720 as the second simulation piston 1230 advances, thereby forming a first master chamber. The pressurized medium accommodated in 1220a is prevented from being transferred to the reservoir 1100.

In addition, when the second simulation piston 1230 advances, the pressurized medium of the first master chamber 1220a advances the master piston 1220 to generate displacement, and the pressurized medium accommodated in the second master chamber 1220b is Braking may be implemented by being transmitted to the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 along the second backup passage 1620. At this time, the cut-off hole 1221 provided in the master piston 1220 blocks the connection between the second master chamber 1220b and the third reservoir flow path 1730 as the master piston 1220 advances, so that the pressurized medium becomes a reservoir ( 1100).

In the abnormal operation mode, the first to fourth cut valves 1611, 1612, 1621, 1622 and the reservoir valve 1711 are in an open state, and the simulator valve 1261 is in a closed state. 1 Since the hydraulic pressure delivered from the simulation chamber 1240a, the first master chamber 1220a, and the second master chamber 1220b can be directly transferred to each wheel cylinder 20, it is possible to improve braking stability and promote rapid braking. have.

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

A diagnostic mode for checking whether the master cylinder 1200 integrated in the electronic brake system 1000 according to the first embodiment of the present invention is leaked may be performed. 9 is a hydraulic circuit diagram showing the state of the diagnosis mode of the electronic brake system 1000 according to the first embodiment of the present invention. Referring to FIG. 9, when performing the diagnosis mode, the electronic control unit is generated from the hydraulic pressure supply device 1300. It controls to supply hydraulic pressure to the first simulation chamber 1240a of the integrated master cylinder 1200.

Specifically, the electronic control unit generates hydraulic pressure in the first pressure chamber 1330 by operating to advance the hydraulic piston 1320 while each valve is controlled to an initial braking state in a non-operating state. The three cut valve 1621 and the fourth cut valve 1622 are controlled in a closed state. The hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the fourth hydraulic flow path 1404, the sixth hydraulic flow path 1406, and the seventh hydraulic flow path 1407. The pressurized medium delivered to the circuit 1510 side, by opening at least one of the first cut valve 1611 and the second cut valve 1612, is transferred to the first hydraulic circuit 1510 side, and the first backup passage 1610 And it is transferred to the first simulation chamber 1240a and the first master chamber 1220a through the auxiliary backup passage 1630.

At this time, an orifice 1631 is provided in the auxiliary backup passage 1630 to slow the delivery of the pressurized medium, so that hydraulic pressure is preferentially applied to the first simulation chamber 1240a, and accordingly, the second simulation piston 1230 is slightly You can go ahead. In addition, in order to prevent the case where the second simulation piston 1230 does not advance even if the hydraulic pressure is preferentially applied to the first simulation chamber 1240a, the reservoir valve 1711 is briefly opened and then closed, and the second simulation chamber ( The second simulation piston 1230 may be advanced by relieving the hydraulic pressure of 1230a).

When the second simulation piston 1230 advances, the cut-off hole 1231 crosses the fourth hydraulic port 1280d and is blocked, so that the first master chamber 1220a may be closed.

The simulator valve 1261 is maintained in a closed state so that the first simulation chamber 1240a is provided in a closed state.

In this state, by comparing the hydraulic pressure value of the pressurized medium expected to be generated by the displacement of the hydraulic piston 1320 and the internal pressure of the integrated master cylinder 1200 or the first hydraulic circuit 1510 measured by the pressure sensor PS Leak in the integrated master cylinder 1200 can be diagnosed. Specifically, the hydraulic pressure value of the first pressure chamber 1330 calculated and predicted based on the displacement amount of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown), measured by the pressure sensor PS. In contrast to the actual hydraulic pressure values of the integrated master cylinder 1200 or the first hydraulic circuit 1510, when the two hydraulic pressure values match, it may be determined that there is no leakage in the integrated master cylinder 1200. On the contrary, the actual measured pressure sensor (PS) than the hydraulic pressure value of the first pressure chamber 1330 calculated and expected based on the displacement amount of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown). When the hydraulic pressure value of the integrated master cylinder 1200 or the first hydraulic circuit 1510 is low, a part of the hydraulic pressure applied to the first simulation chamber 1240a is lost, so that a leak exists in the integrated master cylinder 1200. It can judge and inform the driver.

Hereinafter, an electronic brake system 2000 according to a second embodiment of the present invention will be described.

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

In recent years, as the market demand for eco-friendly vehicles increases, hybrid vehicles with improved fuel efficiency 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. Such a braking operation is referred to as a regenerative braking mode, and the electronic brake system 2000 according to the second embodiment of the present invention includes the third wheel cylinder 23 and the fourth of the second hydraulic circuit 1520 to implement the regenerative braking mode. A generator (not shown) may be provided in the wheel cylinder 24. The regenerative braking mode may be implemented through cooperative control between the generators of the third and fourth wheel cylinders 23 and 24 and the fifth valve 2415, which will be described later with reference to FIG. 9.

FIG. 10 is a hydraulic circuit diagram showing an electronic brake system according to a second embodiment of the present invention. Referring to FIG. 10, the flow of the pressurized medium is controlled in the eighth hydraulic flow path 1408 according to the second embodiment of the present invention. A fifth valve 2415 may be provided. The fifth valve 2415 may be provided as a two-way control valve that controls the flow of the pressurized medium delivered along the eighth hydraulic flow path 1408. 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. The fifth valve 2415 is controlled to be opened in the normal operation mode, but is closed when entering the regenerative braking mode by generators (not shown) provided in the third wheel cylinder 23 and the fourth wheel cylinder 24 Can be converted to

In addition, the sixth valve 1416 provided in the ninth hydraulic flow path 1409 is provided as a two-way control valve (normally closed type) as in the first embodiment of the present invention, but is closed when entering the regenerative braking mode. It is converted into a state to block the flow of the pressurized medium between the first hydraulic circuit 1510 and the second hydraulic circuit 1520.

Hereinafter, a regenerative braking mode of the electronic brake system 1000 according to a second embodiment of the present invention will be described.

11 is a regeneration of the electronic brake system 2000 according to the second embodiment of the present invention As a hydraulic circuit diagram showing the braking mode, referring to FIG. 11, in the case of the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510, only the braking force that the driver wants to implement is supplied with hydraulic pressure. 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, while formed by the hydraulic pressure of the pressurized medium by the operation of the device 1300 In the case of, the sum of the total braking pressure obtained by adding the braking pressure of the pressurized medium by the hydraulic pressure supply device 1300 and the regenerative braking pressure by the generator is the total braking force of the first wheel cylinder 21 and the second wheel cylinder 22 Should be the same as Therefore, when entering the regenerative braking mode, the fifth valve 1415 and the sixth valve 1416 are closed by the hydraulic pressure supply device 1300 applied to the third wheel cylinder 23 and the fourth wheel cylinder 24. The braking pressure is removed or kept constant, and at the same time, by increasing the regenerative braking pressure by the generator, the total braking force of the third and fourth wheel cylinders 23 and 24 is reduced to that of the first and second wheel cylinders 23 and 24. It can be equal to the braking force.

Specifically, referring to FIG. 11, when the driver presses the brake pedal 10 in the first braking mode, the motor operates to rotate in one direction, and the rotational force of the motor is transmitted to the hydraulic pressure supply device 1300 by the power transmission unit. , As the hydraulic piston 1320 of the hydraulic pressure supply device 1300 advances, a hydraulic pressure is generated in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, 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 reduced to the first hydraulic flow path 1401 The first and second wheel cylinders 21 and 22 are braked by sequentially passing through the 6 hydraulic flow path 1406 and the seventh hydraulic flow path 1407.

On the other hand, in the case of the second hydraulic circuit 1520 in which the generator is installed, the electronic control unit senses the speed and deceleration of the vehicle, and if it is determined that it is possible to enter the regenerative braking mode, the fifth valve 1415 and the sixth valve By closing the 1516, it is possible to block the transfer of the hydraulic pressure of the pressurized medium to the third 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 fifth valve ( 1415) is switched to the open state to control the hydraulic pressure of the pressurized medium to be transmitted 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.

In the above, the present invention has been described with reference to an embodiment shown in the accompanying drawings, but this is only illustrative, and a person of ordinary skill in the art can make various modifications and other equivalent embodiments therefrom. You will be able to understand. Therefore, the true scope of the present invention should be determined only by the appended claims.

1000, 2000: electronic brake system
1100: reservoir 1200: integrated master cylinder
1220: master piston 1220a: first master chamber
1220b: second master chamber
1230: first simulation piston 1230a: first simulation chamber
1240: second simulation piston 1240a: second simulation chamber
1250: elastic member 1260: simulation flow path
1261: simulator valve 1300: hydraulic supply
1320: hydraulic piston 1330: first pressure chamber
1340: second pressure chamber 1400: hydraulic control unit
1401: first hydraulic flow path 1402: second hydraulic flow path
1403: third hydraulic flow path 1404: fourth hydraulic flow path
1405: 5th hydraulic flow 1406: 6th hydraulic flow
1407: 7th hydraulic flow 1408: 8th hydraulic flow
1409: 9th hydraulic flow path
1411: first valve 1412: second valve
1413: third valve 1414: fourth valve
1415: fifth valve 1416: sixth valve
1510: first hydraulic circuit 1520: second hydraulic circuit
1610: first backup flow path 1611: first cut valve
1620: second backup flow path 1621: second cut valve
1630: auxiliary backup flow path 1631: inspection valve
1710: first reservoir euro 1720: second reservoir euro
1730: 3rd reservoir euro 1800: dump control unit
1810: first dump passage 1811: first dump check valve
1820: second dump passage 1821: second dump check valve
2415: fifth valve

Claims (22)

A reservoir in which the pressurized medium is stored;
An integrated master cylinder including a master chamber and a simulation chamber for supplying a reaction force according to the pedal effort of the brake pedal to the driver and simultaneously pressurizing and discharging the pressurized medium accommodated therein;
A reservoir flow path connecting the integrated master cylinder and the reservoir;
A first pressure provided on one side of the hydraulic piston that is movably accommodated in the cylinder block by operating a hydraulic piston by an electrical signal output in response to the displacement of the brake pedal and connected to one or more wheel cylinders A hydraulic pressure supply device including a chamber and a second pressure chamber provided on the other side of the hydraulic piston and connected to one or more wheel cylinders;
A hydraulic control unit having a first hydraulic circuit for controlling hydraulic pressure transmitted to two wheel cylinders and a second hydraulic circuit for controlling hydraulic pressure transmitted to two other 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 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 connected to the first hydraulic flow path and the second hydraulic flow path, and the second hydraulic flow path. 1 A fourth hydraulic flow path branching from the hydraulic path, a fifth hydraulic path branching from the second hydraulic path, a sixth hydraulic path where the fourth hydraulic path and the fifth hydraulic path merge, and the sixth hydraulic oil A seventh hydraulic passage branched from the furnace and connected to the first hydraulic circuit, an eighth hydraulic passage branched from the sixth hydraulic passage and connected to the second hydraulic circuit, the seventh hydraulic passage and the eighth hydraulic oil Electronic brake system comprising a ninth hydraulic flow path connected to the furnace. The method of claim 1,
The hydraulic control unit
A first valve provided in the fourth hydraulic passage to control the flow of the pressurized medium, a second valve provided in the fifth hydraulic passage to control the flow of the pressurized medium, and a flow of the pressurized medium provided in the third hydraulic passage A third valve to control, a fourth valve provided in the seventh hydraulic passage to control the flow of the pressurized medium, a fifth valve provided in the eighth hydraulic passage to control the flow of the pressurized medium, and the ninth hydraulic passage An electronic brake system including a sixth valve provided in the pressurized medium to control the flow of the pressurized medium. The method of claim 2,
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 sixth hydraulic flow path,
The second valve is provided as a check valve that allows only the flow of the pressurized medium from the second pressure chamber to the sixth hydraulic flow path,
The fourth valve is provided as a check valve that allows only the flow of the pressurized medium from the seventh hydraulic flow path to the first hydraulic circuit,
The fifth valve is provided as a check valve that allows only the flow of the pressurized medium from the eighth hydraulic flow path to the second hydraulic circuit,
The third valve and the sixth valve are provided with solenoid valves that control the flow of the pressurized medium in both directions. The method of claim 3,
The simulation chamber is
A first simulation chamber and a second simulation chamber,
The master chamber is
And a first master chamber and a second master chamber having a diameter smaller than that of the second simulation chamber,
The integrated master cylinder
The first simulation piston is provided to be pressurized and displaceable by a brake pedal, and the second simulation chamber and the first master chamber are provided to be pressurized, and displacement of the first simulation piston Or a second simulation piston provided to be displaceable by the hydraulic pressure in the first simulation chamber, and a second simulation piston provided to be pressurized and displaced by the displacement of the second simulation piston or the hydraulic pressure in the first master chamber. A master piston that is possible, 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 pressure medium provided in the simulation flow path. An electronic brake system comprising a simulator valve for controlling flow, a piston spring elastically supporting the master piston, and a simulator spring elastically supporting the second simulation piston. The method of claim 4,
A first backup passage connecting the first simulation chamber and the first hydraulic circuit;
A second backup passage connecting the second master chamber and the second hydraulic circuit; And
Electronic brake system further comprising a; auxiliary backup passage connecting the first master chamber and the first backup passage. The method of claim 5,
The first hydraulic circuit is
A first inlet valve and a second inlet valve respectively controlling the flow of the pressurized medium supplied to the first wheel cylinder and the second wheel cylinder, and discharge from the first wheel cylinder and the second wheel cylinder into the first backup passage It includes a first cut valve and a second cut valve each controlling the flow of the pressurized medium,
The second hydraulic circuit is
A third inlet valve and a fourth inlet valve respectively controlling the flow of the pressurized medium supplied to the third wheel cylinder and the fourth wheel cylinder, and discharge from the third wheel cylinder and the fourth wheel cylinder to the second backup passage Electronic brake system comprising a third cut valve and a fourth cut valve respectively controlling the flow of the pressurized medium. The method of claim 6,
The reservoir flow path is
A first reservoir flow path for communicating the reservoir and the second simulation chamber, a second reservoir flow path for communicating the reservoir and the first master chamber, and a third reservoir flow path for communicating the reservoir and the second master chamber. Electronic brake system including. The method of claim 7,
The first reservoir flow path is
Electronic brake system including a reservoir valve that controls the flow of the pressurized medium. The method of claim 8,
A first dump passage connecting the first pressure chamber and the reservoir;
A second dump passage connecting the second pressure chamber and the reservoir;
A first dump check valve provided in the first dump passage and allowing only the flow of the pressurized medium from the first pressure chamber to the reservoir;
The electronic brake system further comprises a second dump check valve provided in the second dump passage and allowing only the flow of the pressurized medium from the second pressure chamber to the reservoir. 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 sixth hydraulic flow path,
The second valve is provided as a check valve that allows only the flow of the pressurized medium from the second pressure chamber to the sixth hydraulic flow path,
The fourth valve is provided as a check valve that allows only the flow of the pressurized medium from the seventh hydraulic flow path to the first hydraulic circuit,
The third valve, the fifth valve, and the sixth valve are provided as solenoid valves that control the flow of the pressurized medium in both directions. The method of claim 10,
The first hydraulic circuit includes a first wheel cylinder and a second wheel cylinder, and the second hydraulic circuit includes a third wheel cylinder and a fourth wheel cylinder,
The electronic brake system further comprising a generator provided in each of the third wheel cylinder and the fourth wheel cylinder. In the method of operating the electronic brake system according to claim 8,
In normal operation mode,
The first cut valve and the second cut valve are closed to seal the first master chamber, the third cut valve and the fourth cut valve are closed to seal the second master chamber, and the reservoir valve is closed. The second simulation chamber is closed by closing, and the simulator valve is opened to communicate the first simulation chamber and the reservoir, so that the first simulation piston compresses the elastic member by the operation of the brake pedal, and the A method of operating an electronic brake system in which the elastic restoring force of the elastic member is provided to the driver as a pedal feel. The method of claim 12,
The normal operation mode is
As the hydraulic pressure transmitted from the hydraulic pressure supply device to the wheel cylinder gradually increases, a first braking mode primarily provides hydraulic pressure, a second braking mode secondarily provides hydraulic pressure, and a third hydraulic pressure. A method of operating an electronic brake system including a third braking mode provided. The method of claim 13,
The first braking mode is
The hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston sequentially passes through the first hydraulic channel, the fourth hydraulic channel, and the sixth hydraulic channel, to the seventh hydraulic channel and the eighth hydraulic channel. The method of operating an electronic brake system branched and provided to the first hydraulic circuit and the second hydraulic circuit, respectively. The method of claim 14,
The second braking mode is
After the first braking mode, the hydraulic pressure formed in the second pressure chamber by the reversing of the hydraulic piston sequentially passes through the second hydraulic channel, the fifth hydraulic channel, and the sixth hydraulic channel, and the seventh hydraulic channel and the A method of operating an electronic brake system branched into the eighth hydraulic flow path and provided to the first hydraulic circuit and the second hydraulic circuit, respectively. The method of claim 15,
The third braking mode is
Open the third valve,
After the second braking mode, a part of the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston sequentially passes through the first hydraulic channel, the fourth hydraulic channel, and the sixth hydraulic channel, and the seventh hydraulic oil Branched into the furnace and the eighth hydraulic flow passage and provided to the first hydraulic circuit and the second hydraulic circuit, respectively,
A method of operating an electronic brake system in which the remaining part of the hydraulic pressure formed in the first pressure chamber is supplied to the second pressure chamber through the first hydraulic channel, the third hydraulic channel, and the second hydraulic channel in sequence. The method of claim 14,
Release of the first braking mode
At least one of the first cut valve and the second cut valve is opened, at least one of the third cut valve and the fourth cut valve is opened, the simulator valve is opened, and the reservoir valve is closed,
By reversing the hydraulic piston, the pressure medium of the second pressure chamber is sequentially passed through the second hydraulic channel, the fifth hydraulic channel, and the sixth hydraulic channel, to the seventh hydraulic channel and the eighth hydraulic channel. Branched and sent to the first hydraulic circuit and the second hydraulic circuit, the pressure medium of the first hydraulic circuit and the second hydraulic circuit passes through the first and second backup channels, respectively, and the first simulation chamber And a method of operating an electronic brake system that is recovered to the reservoir through the second master chamber. The method of claim 15,
Release of the second braking mode
At least one of the first cut valve and the second cut valve is opened, at least one of the third cut valve and the fourth cut valve is opened, the simulator valve is opened, and the reservoir valve is closed,
By advancing the hydraulic piston, the pressurizing medium of the first pressure chamber is sequentially passed through the first hydraulic channel, the fourth hydraulic channel, and the sixth hydraulic channel, and into the seventh hydraulic channel and the eighth hydraulic channel. Branched and sent to the first hydraulic circuit and the second hydraulic circuit, the pressure medium of the first hydraulic circuit and the second hydraulic circuit passes through the first and second backup channels, respectively, and the first simulation chamber And a method of operating an electronic brake system that is recovered to the reservoir through the second master chamber. The method of claim 16,
Release of the third braking mode
At least one of the first cut valve and the second cut valve is opened, at least one of the third cut valve and the fourth cut valve is opened, the simulator valve is opened, and the reservoir valve is closed,
The pressurizing medium of the first hydraulic circuit and the second hydraulic circuit is recovered to the reservoir through the first and second master chambers through the first and second backup passages, respectively,
At least a part of the pressurizing medium of the second pressure chamber is supplied to the first pressure chamber through the second hydraulic flow path, the third hydraulic flow path, and the first hydraulic flow path sequentially by the reverse of the hydraulic piston How the system works. The method of claim 12,
In abnormal operation mode,
The first cut valve and the second cut valve are opened to communicate the first simulation chamber and the first hydraulic circuit, and the third cut valve and the fourth cut valve are opened to open the second master chamber and the first hydraulic circuit. A second hydraulic circuit is communicated, the simulator valve is closed to disconnect the first simulation chamber and the reservoir, and the reservoir valve is opened to communicate the second simulation chamber and the reservoir,
According to the pedal effort of the brake pedal, the pressurizing medium of the first simulation chamber is provided to the first hydraulic circuit through the first backup passage, and the pressurizing medium of the first master chamber is supplied to the first hydraulic circuit through the auxiliary backup passage. A method of operating an electronic brake system provided as a hydraulic circuit, wherein the pressurizing medium of the second master chamber is provided to the second hydraulic circuit through the second backup passage. In the method of operating the electronic brake system according to claim 8,
In the diagnostic mode to check whether the integrated master cylinder is leaking,
Closing the third cut valve, the fourth cut valve, and the simulator valve, and opening at least one of the first cut valve and the second cut valve,
Provides the hydraulic pressure generated by operating the hydraulic pressure supply device to the first simulation chamber through the hydraulic control unit, the first hydraulic circuit, and the first backup passage,
A method of operating an electronic brake system that compares the hydraulic pressure value of the pressurized medium expected to occur based on the displacement amount of the hydraulic piston and the hydraulic pressure value of the pressurized medium actually provided to the first simulation chamber or the first hydraulic circuit. In the method of operating the electronic brake system according to claim 11,
In the regenerative braking mode by the generator,
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 flow path and the fourth hydraulic flow path sequentially, and the third valve is closed by closing the fifth valve. A method of operating an electronic brake system that blocks the supply of hydraulic pressure to the wheel cylinder and the fourth wheel cylinder.

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