KR102623776B1 - Electric brake system and Operating method of therof - Google Patents

Abstract

An electronic brake system is disclosed. The electronic brake system according to this embodiment includes a reservoir in which pressurized media is stored, an integrated master cylinder having a master chamber and a simulation chamber, a reservoir passage communicating the integrated master cylinder and the reservoir, and an electrical signal output in response to the displacement of the brake pedal. A hydraulic piston is operated to generate hydraulic pressure, and a first pressure chamber is provided on one side of the hydraulic piston movably accommodated inside the cylinder block and connected to one or more wheel cylinders, and a first pressure chamber is provided on the other side of the hydraulic piston and is connected to one or more wheel cylinders. A hydraulic pressure supply device including a second pressure chamber connected to a first hydraulic circuit that controls the hydraulic pressure delivered to two wheel cylinders and a second hydraulic circuit that controls the hydraulic pressure delivered to the other two wheel cylinders. It may be provided including an electronic control unit that controls the valves based on the control unit, hydraulic pressure information, and displacement information of the brake pedal.

Description

Electric brake system and operating method of therof}

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

Vehicles are essentially equipped with a brake system to perform braking, and various types of brake systems are being proposed to ensure the safety of drivers and passengers.

Conventional brake systems mainly use a method that supplies hydraulic pressure necessary for braking to wheel cylinders using a mechanically connected booster when the driver presses the brake pedal. However, as the market demand for implementing various braking functions in detailed response to the vehicle's operating environment increases, recently, when the driver presses the brake pedal, the driver's intention to brake is electronically transmitted through a pedal displacement sensor that detects the displacement of the brake pedal. Electronic brake systems and operating methods that include a hydraulic pressure supply device that receives signals and supplies hydraulic pressure necessary for braking to wheel cylinders are becoming widely available.

In this electronic brake system and operation method, in normal operating mode, the driver's brake pedal operation is generated and provided as an electrical signal, and based on this, the hydraulic pressure supply device is electrically operated and controlled to form the hydraulic pressure necessary for braking and pumped into the wheel cylinder. Deliver. In this way, these electronic brake systems and operating methods are electrically operated and controlled and can implement complex and diverse braking actions. However, if technical problems occur in electrical components, the hydraulic pressure required for braking is not stably formed. There is a risk that passenger safety may be threatened. Therefore, the electronic brake system and operation method enter an abnormal operation mode when one component fails or is in an uncontrollable state, and in this case, a mechanism is required in which the driver's brake pedal operation is directly linked to the wheel cylinder. In other words, in an abnormal operation mode of the electronic brake system and operation method, the hydraulic pressure necessary for braking must be immediately generated as the driver applies pressure to the brake pedal, and this must be directly transmitted to the wheel cylinder.

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

This embodiment aims to provide an electronic brake system and operating method that can reduce the number of parts and achieve miniaturization and weight reduction of the product by integrating the master cylinder and simulation device into one.

This embodiment seeks to provide an electronic braking system and operating method that can implement stable and effective braking even in various operating situations.

This embodiment seeks to provide an electronic brake system and operating method that can stably generate high-pressure braking pressure.

This embodiment seeks to provide an electronic brake system and operating method with improved performance and operational reliability.

This embodiment seeks to provide an electronic brake system and operating method that can improve product assembly and productivity while reducing product manufacturing costs.

According to one aspect of the present invention, a reservoir in which a pressurized medium is stored; A first simulation chamber and a second simulation chamber, a first master chamber and a second master chamber having a smaller diameter than the second simulation chamber, and the first simulation chamber is provided to be pressurized and can be displaced by a brake pedal. A first simulation piston provided to pressurize the second simulation chamber and the first master chamber and a second simulation piston provided to be capable of being displaced by displacement of the first simulation piston or hydraulic pressure of the first simulation chamber. A simulation piston, a master piston provided to pressurize the second master chamber and displaceable by displacement of the second simulation piston or hydraulic pressure of the first master chamber, the first simulation piston and the second An integrated master including an elastic member provided between simulation pistons, a first simulation passage connecting the first simulation chamber and the reservoir, and a first simulator valve provided in the first simulation passage to control the flow of pressurized medium. cylinder; a reservoir passage connecting the integrated master cylinder and the reservoir; The hydraulic piston is operated by an electrical signal output in response to the displacement of the brake pedal to generate hydraulic pressure, and a first pressure is provided on one side of the hydraulic piston movably accommodated inside the cylinder block 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 including a first hydraulic circuit that controls hydraulic pressure delivered to two wheel cylinders and a second hydraulic circuit that controls hydraulic pressure delivered to the other two wheel cylinders; and an electronic control unit that controls the valves based on hydraulic pressure information and displacement information of the brake pedal, wherein the hydraulic control unit includes a first hydraulic passage in communication with the first pressure chamber, the second pressure chamber, and A second hydraulic passage in communication, a third hydraulic passage where the first hydraulic passage and the second hydraulic passage join, and a fourth hydraulic passage branched from the third hydraulic passage and connected to the first hydraulic circuit, A fifth hydraulic passage branched from the third hydraulic passage and connected to the second hydraulic circuit, a sixth hydraulic passage in communication with the first hydraulic circuit, and a seventh hydraulic passage in communication with the second hydraulic circuit, An eighth hydraulic passage where the sixth hydraulic passage and the seventh hydraulic passage join, a ninth hydraulic passage branched from the eighth hydraulic passage and connected to the first pressure chamber, and a ninth hydraulic passage branched from the eighth hydraulic passage and connected to the first pressure chamber. It may be provided including a tenth hydraulic passage connected to the second pressure chamber.

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

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

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.

At least one first cut valve provided in the first backup passage to control the flow of pressurized medium; and at least one second cut valve provided in the second backup passage to control the flow of pressurized medium.

It further includes a dump control unit provided between the reservoir and the hydraulic pressure supply device to control the flow of pressurized medium, wherein the dump control unit includes a first dump flow path connecting the first pressure chamber and the reservoir, and the first dump A first dump check valve provided in the flow path to allow only the flow of pressurized medium from the reservoir to the first pressure chamber, and a first bypass flow path connected in parallel with the first dump check valve on the first dump flow path. and a first dump valve provided in the first bypass passage to control the two-way flow of the pressurized medium, a second dump passage connecting the second pressure chamber and the reservoir, and provided in the second dump passage. a second dump check valve that allows only the flow of pressurized medium from the reservoir to the second pressure chamber, a second bypass passage connected in parallel with the second dump check valve on the second dump passage, and 2 It may be provided including a second dump valve provided in the bypass flow path to control the two-way flow of the pressurized medium.

The first hydraulic circuit includes a first inlet valve and a second inlet valve that respectively control the flow of pressurized medium supplied to the first wheel cylinder and the second wheel cylinder, and the second hydraulic circuit includes a third wheel cylinder and It may be provided including a third inlet valve and a fourth inlet valve that respectively control the flow of pressurized medium supplied to the fourth wheel cylinder.

The reservoir flow path includes 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 path that communicates the reservoir and the second master chamber. It can be provided including 3 reservoir euros.

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

The integrated master cylinder may include a piston spring that elastically supports the master piston and a simulator spring that elastically supports the second simulation piston.

The first valve is provided as a check valve that allows only the flow of pressurized medium discharged from the first pressure chamber, and the second valve is provided as a check valve that allows only the flow of pressurized medium discharged from the second pressure chamber. The third valve is provided as a check valve that allows only the flow of pressurized medium from the third hydraulic passage to the first hydraulic circuit, and the fifth valve allows the flow of pressurized medium discharged from the first hydraulic circuit. The sixth valve is provided as a check valve that only allows the flow of pressurized medium discharged from the second hydraulic circuit, and the fourth valve, the seventh valve, and the eighth valve are provided as check valves that only allow the flow of pressurized medium discharged from the second hydraulic circuit. It can be provided with a solenoid valve that controls the two-way flow of pressurized medium.

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 It may be provided further including a generator provided for each.

The integrated master cylinder further includes a second simulation passage connecting the first simulation chamber and the second simulation chamber, and the second simulation passage includes a second simulator valve that controls the flow of the pressurized medium. You can.

In the normal operating mode, the first cut valve is closed to seal the first master chamber, the second cut valve is closed to seal the second master chamber, and the reservoir valve is closed to close the second simulator chamber. is sealed, and the first simulator valve is opened to communicate with the first simulation chamber and the reservoir, so that the first simulation piston compresses the elastic member by operation of the brake pedal, and the elastic restoring force of the elastic member This can be provided as a pedal feel to the driver.

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

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

The second braking mode closes the seventh valve and the second dump valve, and the hydraulic pressure formed in the second pressure chamber by the backward movement of the hydraulic piston after the first braking mode is connected to the second hydraulic oil passage and the second dump valve. It is provided to the first hydraulic circuit through the 3 hydraulic oil passage and the fourth hydraulic oil passage sequentially, and is provided to the second hydraulic circuit through the second hydraulic oil passage, the third hydraulic oil passage, and the fifth hydraulic oil passage sequentially. It can be.

The third braking mode opens the seventh valve and the eighth valve, closes the first dump valve and the second dump valve, and reduces the hydraulic pressure formed in the first pressure chamber by the advance of the hydraulic piston. A portion is provided to the first hydraulic circuit through the first hydraulic oil passage, the third hydraulic oil passage, and the fourth hydraulic oil passage sequentially, and the first hydraulic oil passage, the third hydraulic oil passage, and the fifth hydraulic oil passage are provided to the first hydraulic circuit. It is sequentially supplied to the second hydraulic circuit, and the remaining part of the hydraulic pressure formed in the first pressure chamber may be supplied to the second pressure chamber through the ninth hydraulic oil passage and the tenth hydraulic oil passage sequentially.

Releasing the first braking mode opens the seventh valve and the second dump valve, closes the eighth valve and the first dump valve, and causes negative pressure in the first pressure chamber due to the backward movement of the hydraulic piston. Forming, the pressurized medium provided in the first hydraulic circuit is recovered to the first pressure chamber through the sixth hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage sequentially, and is supplied to the second hydraulic circuit. The provided pressurized medium may be returned to the first pressure chamber through the seventh hydraulic oil passage, the eighth hydraulic oil passage, and the ninth hydraulic oil passage sequentially.

Releasing the second braking mode opens the eighth valve and the first dump valve, closes the seventh valve and the second dump valve, and causes negative pressure in the second pressure chamber due to the advancement of the hydraulic piston. Forming, the pressurized medium provided in the first hydraulic circuit is recovered to the second pressure chamber through the sixth hydraulic passage, the eighth hydraulic passage, and the tenth hydraulic passage sequentially, and is supplied to the second hydraulic circuit. The provided pressurized medium may be returned to the second pressure chamber through the seventh hydraulic oil passage, the eighth hydraulic oil passage, and the tenth hydraulic oil passage sequentially.

Releasing the third braking mode opens the seventh valve and the eighth valve, closes the first dump valve, and creates negative pressure in the first pressure chamber by the backward movement of the hydraulic piston. 1 The pressurized medium provided in the hydraulic circuit is returned to the first pressure chamber through the sixth hydraulic oil passage, the eighth hydraulic oil passage, and the ninth hydraulic oil passage sequentially, and the pressurized medium provided in the second hydraulic circuit is returned to the first pressure chamber. It is recovered to the first pressure chamber through the 7 hydraulic oil passage, the eighth hydraulic oil passage, and the ninth hydraulic oil passage sequentially, and at least a portion of the pressurized medium in the second pressure chamber is the tenth hydraulic oil passage and the ninth hydraulic oil. It may be supplied to the first pressure chamber through the furnace sequentially.

In an abnormal operation mode, the first cut valve is opened and the first simulator valve is closed so that the first simulation chamber and the first master chamber communicate with the first hydraulic circuit, and the second cut valve is opened. The second master chamber and the second hydraulic circuit are in communication, the reservoir valve is opened so that the second simulation chamber and the reservoir are in communication, and the pressurized medium in the first simulation chamber is supplied according to the pedal pressure of the brake pedal. It is provided to the first hydraulic circuit through a first backup passage, and the pressurized medium in the first master chamber is provided to the first hydraulic circuit through the auxiliary backup passage and the first backup passage sequentially, and the second The pressurized medium in the master chamber may be provided to the second hydraulic circuit through the second backup passage.

In the ABS dump mode, the first simulator valve is opened, and the hydraulic pressure of the first wheel cylinder and the second wheel cylinder is adjusted to the first backup passage and the first simulation by opening at least a portion of the first cut valve. It sequentially passes through the chamber and is discharged to the reservoir through the first simulation passage, and a portion of the hydraulic pressure of the third wheel cylinder and the fourth wheel cylinder flows into the second backup passage by opening at least a portion of the second cut valve. and may be sequentially discharged to the reservoir through the third reservoir passage through the second master chamber.

In the inspection mode to check for leaks in the integrated master cylinder, the second cut valve and the first simulator valve are closed, at least a part of the first cut valve is opened, and the hydraulic pressure supply device is operated to operate the hydraulic pressure. is provided to the first simulation chamber through the hydraulic control unit, the first cut valve, and the first backup passage, and a hydraulic pressure value of the pressurized medium expected to occur based on the displacement amount of the hydraulic piston, and the It can be tested by comparing the hydraulic pressure value of the pressurized medium actually provided to 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 due to the advancement of the hydraulic piston sequentially passes through the first hydraulic oil passage, the third hydraulic oil passage, and the fourth hydraulic oil passage to the first hydraulic oil pressure. It is provided as a circuit, and the supply of hydraulic pressure to the third and fourth wheel cylinders can be blocked by closing the fourth valve.

In the normal operating mode, the first cut valve is closed to seal the first master chamber, the second cut valve is closed to seal the second master chamber, and the reservoir valve and the second simulator valve are closed. The second simulator chamber is sealed, and the first simulator valve is opened to communicate the first simulation chamber and the reservoir, so that the first simulation piston compresses the elastic member by operation of the brake pedal, The elastic restoring force of the elastic member may be provided to the driver as a pedal feeling.

In an abnormal operation mode, the first cut valve is opened to communicate with the first simulation chamber and the first master chamber and the first hydraulic circuit, and the first simulator valve and the reservoir valve are closed and the second simulator The valve is opened to communicate with the second simulation chamber and the first simulation chamber, and the second cut valve is opened to communicate with the second master chamber and the second hydraulic circuit, and according to the pedal force of the brake pedal, the second cut valve is opened to communicate with the second simulation chamber. The pressurized medium in the first simulation chamber is provided to the first hydraulic circuit through the first backup passage, and the pressurized medium in the second simulation chamber is provided to the first simulation chamber and the first backup through the second simulation passage. The pressurized medium in the first master chamber is provided to the first hydraulic circuit through the auxiliary backup passage and the first backup passage sequentially, and the second master chamber is supplied to the first hydraulic circuit through the flow passage sequentially. The pressurized medium in the chamber may be provided to the second hydraulic circuit through the second backup passage.

In the inspection mode to check for leaks in the integrated master cylinder, the second cut valve, the first simulator valve, and the second simulator valve are closed, at least a portion of the first cut valve is opened, and the hydraulic pressure is supplied. The hydraulic pressure generated by operating the device is provided to the first simulation chamber through the hydraulic control unit, the first cut valve, and the first backup passage, and the pressurized medium is expected to be generated based on the displacement amount of the hydraulic piston. The hydraulic pressure value of can be compared with the hydraulic pressure value of the pressurized medium actually provided to the first simulation chamber or the first hydraulic circuit.

The electronic brake system and operating method according to this embodiment can reduce the number of parts and promote miniaturization and weight reduction of the product.

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

The electronic brake system and operating method according to this embodiment can stably generate high-pressure braking pressure.

The electronic brake system and operating method according to this embodiment can improve product performance and operational reliability.

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

The electronic brake system and operating method according to an embodiment of the present invention can improve product assembly and productivity and reduce product manufacturing costs.

1 is a hydraulic circuit diagram showing an electronic brake system according to a first embodiment of the present invention.
Figure 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 the first braking mode.
Figure 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 the second braking mode.
Figure 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 the third braking mode.
Figure 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 the third braking mode.
Figure 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 the second braking mode.
Figure 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 the first braking mode.
Figure 8 is a hydraulic circuit diagram showing a state (fallback mode) in which the electronic brake system according to the first embodiment of the present invention operates in an abnormal state.
Figure 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 the ABS dump mode.
Figure 10 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.
Figure 11 is a hydraulic circuit diagram showing an electronic brake system according to a second embodiment of the present invention.
Figure 12 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.
Figure 13 is a hydraulic circuit diagram showing an electronic brake system according to a third embodiment of the present invention.
Figure 14 is a hydraulic circuit diagram showing a state (fallback mode) in which the electronic brake system according to the third embodiment of the present invention operates when the system is abnormal.
Figure 15 is a hydraulic circuit diagram showing a state in which the electronic brake system according to the third embodiment of the present invention performs an inspection mode.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The following examples are presented to sufficiently convey the idea of the present invention to those skilled in the art. The present invention is not limited to the embodiments presented herein and may be embodied in other forms. In order to clarify the present invention, the drawings may omit illustrations of parts unrelated to the description and may slightly exaggerate the sizes of components to aid understanding.

Figure 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 reservoir 1100 in which pressurized medium is stored and a reaction force according to the pedal force of the brake pedal 10 to the driver, The driver's intention to brake is received as an electrical signal by an integrated master cylinder (1200) that pressurizes and discharges pressurized media such as brake oil stored inside, and a pedal displacement sensor (11) that detects the displacement of the brake pedal (10). A hydraulic pressure supply device 1300 that generates hydraulic pressure of the pressurized medium through mechanical operation, a hydraulic control unit 1400 that controls the hydraulic pressure provided from the hydraulic pressure supply device 1300, and the hydraulic pressure of the pressurized medium is transmitted to each wheel. It is provided between a hydraulic circuit (1510, 1520) having a wheel cylinder (20) that performs braking (RR, RL, FR, FL), a hydraulic pressure supply device (1300), and a reservoir (1100) to ensure the flow of pressurized medium. A dump control unit (1800) that controls, a backup passage (1610, 1620, 1630) that hydraulically connects the integrated master cylinder (1200) and the hydraulic circuit (1510, 1520), a reservoir (1100) and an integrated master cylinder (1200) ) and a reservoir passage 1700 that hydraulically connects the hydraulic pressure and pedal displacement information, and an electronic control unit (ECU, not shown) that controls the hydraulic pressure supply device 1300 and various valves.

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 pedal force to the brake pedal 10 for braking operation. This provides a stable pedal feel and is provided to pressurize and discharge the pressurized medium contained inside.

The integrated master cylinder 1200 can be divided into a pedal simulation unit that provides a pedal feel to the driver, and a master cylinder unit that delivers pressurized media to the second hydraulic circuit 1520, which will be described later. The integrated master cylinder 1200 is provided sequentially with a pedal simulation unit and a master cylinder unit from the brake pedal 10 side, and may be arranged coaxially within one cylinder block 1210.

Specifically, the integrated master cylinder 1200 includes a cylinder block 1210 forming a chamber on the inside, a first simulation chamber 1240a formed on the inlet side of the cylinder block 1210 to which the brake pedal 10 is connected, and , a first simulation piston 1240 provided in the first simulation chamber 1240a and connected to the brake pedal 10 to be displaced 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) provided in the second simulation chamber (1230a) or pressure received in the first simulation chamber (1240a) A second simulation piston 1230 is provided to be capable of displacement by the hydraulic pressure of the medium, and is formed on the cylinder block 1210 inside the second simulation chamber 1230a and has a smaller diameter than the second simulation chamber 1230a. A first master chamber (1220a) and a second master chamber (1220b) formed, and the displacement of the second simulation piston (1230) provided in the second master chamber (1220b) or the pressurized medium accommodated in the first master chamber (1220a) A master piston 1220 that is displaceable by hydraulic pressure, and an elastic member ( 1250), a simulator spring 1232 for elastically supporting the second simulation piston 1230, a piston spring 1222 for elastically supporting the master piston 1220, a first simulation chamber 1240a, and a reservoir 1100. It may include a first simulation flow path 1260 connecting the and a first simulator valve 1261 provided in the first 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 connected to the brake pedal ( 10) It can be formed sequentially from the side (right side in FIG. 1) to the inside (left side in FIG. 1).

The first simulation piston 1240 is provided in the first simulation chamber 1240a and can generate liquid pressure or negative pressure in the pressurized medium contained in the chamber as it moves forward and backward.

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

The master piston 1220 is provided in the second master chamber 1220b and can generate hydraulic pressure or negative pressure in the pressurized medium contained in the chamber as it moves forward and backward.

The first simulation chamber 1240a may be formed on the inlet side or the outermost side (right side in FIG. 1) of the cylinder block 1210, and a brake is applied to the first simulation chamber 1240a via the input rod 12. The first simulation piston connected to the pedal 10 may be accommodated to be capable of reciprocating movement.

Pressurized media may be introduced and discharged from the first simulation chamber 1240a through the first hydraulic port 1280a and the second hydraulic port 1280b. The first hydraulic port 1280a is connected to the first simulation flow path 1260, which will be described later, so that pressurized media can flow in and out of the first simulation chamber 1240a into the reservoir 1100, and the second hydraulic port 1280b is connected to the first backup passage 1610, which will be described later, and discharges the pressurized medium from the first simulation chamber 1240a to the first backup passage 1610, or conversely, from the first backup passage 1610 to the first simulation chamber 1240a. Pressurized medium may flow into the side.

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 pressurized medium between the first simulation chamber 1240a and the reservoir 1100, and is located in front of the auxiliary hydraulic port 1280h (Figure A sealing member 1290a, which will be described later (to the left based on 1), is provided to allow the supply of pressurized medium from the auxiliary reservoir passage 1740 to the first simulation chamber 1240a, but blocks the flow of pressurized medium in the opposite direction, and auxiliary A sealing member 1290b, which will be described later, is provided at the rear of the reservoir passage 1740 (on the right side with reference to FIG. 1) to prevent the pressurized medium from leaking from the first simulation chamber 1240a to the outside of the cylinder block 1210. there is.

The first simulation piston 1240 is provided and accommodated in the first simulation chamber 1240a, and presses the pressurized medium accommodated in the first simulation chamber 1240a by moving forward (leftward with respect to FIG. 1) to form hydraulic pressure. The elastic member 1250, which will be described later, can be pressed, and by moving backwards (to the right with respect to FIG. 1), negative pressure can be created inside the first simulation chamber 1240a or the elastic member 1250 can be returned to its original position and shape. You can do it.

The second simulation chamber 1230a may be formed inside the first simulation chamber 1240a (on the left side in FIG. 1) on the cylinder block 1210, and the second simulation chamber 1230a may include a second simulation piston ( 1230) can be accommodated for round-trip movement.

Pressurized media may be introduced and discharged from the second simulation chamber 1230a 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 contained in the second simulation chamber 1230a can be discharged toward the reservoir 1100, and conversely, the pressurized medium is discharged from the reservoir 1100. Media may flow in.

The second simulation piston 1230 is accommodated in the second simulation chamber 1230a, and moves forward to form a hydraulic pressure of the pressurized medium accommodated in the second simulation chamber 1230a, or moves backward to form a liquid pressure in the second simulation chamber 1230a. Negative pressure can be formed. 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, which will be described later. At least one sealing member ( 1290c) can be prepared.

A step portion may be formed to be stepped inward at the area where the second simulation chamber 1230a is formed on the cylinder block 1210, and may be formed to extend outward on the outer peripheral surface of the second simulation piston 1230 to be caught by the step portion. An expansion part may be provided. Specifically, the cylinder block 1210 is provided with a stepped portion that is stepped inwardly between the second simulation chamber 1230a and the first master chamber 1220a, and thus the first and second master chambers 1220a and 1220b. ) may be formed to have a smaller diameter than the first and second simulation chambers 1240a and 1230a. In addition, an extension part that is caught by the step is provided at the end of the second simulation piston 1230 on the side of the first simulation chamber 1240a, and at least one sealing member 1290c is provided in the expansion part to form the second simulation chamber 1230a. ) and the first simulation chamber 1240a, and at the same time, when the second simulation piston 1230 moves forward, the second simulation chamber 1230a can be pressed. The end of the second simulation piston 1230 on the side of the first master chamber 1220a seals the space between the second simulation chamber 1230a and the first master chamber 1220a by a sealing member 1290d to be described later, and at the same time, 2 When the simulation piston 1230 moves forward, the first master chamber 1220a may be pressed.

The first master chamber 1220a may be formed inside the second simulation chamber 1230a (on the left side in FIG. 1) on the cylinder block 1210, and the first master chamber 1220a may include a second simulation piston ( 1230) can be accommodated for round-trip movement.

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

The second simulation piston 1230 is accommodated in the first master chamber 1220a, and moves forward to form a hydraulic pressure of the pressurized medium contained in the first master chamber 1220a, or moves backward to form a hydraulic pressure in the first master chamber 1220a. Negative pressure can be formed.

Additionally, the second simulation piston 1230 may be provided with 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 to connect the first master chamber 1220a and the fourth hydraulic port 1280d when the second simulation piston 1230 is in the original position. is connected, and when the second simulation piston 1230 deviates from its original position, the cut-off hole 1231 and the fourth hydraulic port 1280d are misaligned, thereby causing the separation of the first master chamber 1220a and the second reservoir flow path 1720. Arrangements may be made 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. Accordingly, the second simulation piston 1230 connects the first master chamber 1220a and the reservoir 1100 in a normal operation mode, which will be described later, and the second simulation piston 1230 moves in an abnormal operation mode, so that the first The connection between the master chamber 1220a and the reservoir 1100 can be blocked.

The first master chamber 1220a may be formed inside the second simulation chamber 1230a (on the left side in FIG. 1) on the cylinder block 1210, and the first master chamber 1220a may include a second simulation piston ( 1230) can be accommodated for round-trip movement.

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

The master piston 1220 is provided and accommodated in the second master chamber 1220b, and moves forward to create hydraulic pressure of the pressurized medium accommodated in the second master chamber 1220b, or moves backward to create negative pressure in the second master chamber 1220b. can be formed.

Additionally, the master piston 1220 may be provided with a cut-off hole 1221 connecting the second master chamber 1220b and the sixth hydraulic port 1280f in 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 the original position, When the master piston 1220 deviates from its original position, the cut-off hole 1221 and the sixth hydraulic port 1280f are misaligned and are provided to block the connection between the second master chamber 1220b and the third reservoir passage 1730. You 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 a normal operation mode, which will be described later, and the master piston 1220 moves in an abnormal operation mode, so that the second master chamber 1220b The connection between and reservoir 1100 can be blocked.

Meanwhile, the integrated master cylinder 1200 according to the first embodiment of the present invention includes master chambers 1220a and 1220b and simulation chambers 1230a and 1240a, thereby ensuring safety in case of component failure. For example, the first simulation chamber 1220a and the first master chamber 1220a are connected to the right front wheel (FR), left front wheel (FL), and left rear wheel through the first backup passage 1610 and the auxiliary backup passage 1630, which will be described later. It is connected to any two wheel cylinders 20 of (RL) and the 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, which will be described later. It can be connected, and as a result, braking of the vehicle can be possible even if a problem such as a leak occurs in one chamber. A detailed description of this will be provided 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 feel of the brake pedal 10 to the driver through its elastic restoring force. The elastic member 1250 may be made of a material such as compressible and expandable rubber, and a displacement occurs in the first simulation piston 1240 by the operation of the brake pedal 10, but the second simulation piston 1230 is circular. When the position is maintained, the elastic member 1250 is compressed, and the driver can receive a stable and familiar pedal feeling due to the elastic restoring force of the compressed elastic member 1250. A detailed explanation of this will be provided later.

The rear surface (left side with respect to FIG. 1) of the first simulation piston 1240 facing the elastic member 1250 corresponds to the shape of the elastic member 1250 to ensure smooth compression and deformation of the elastic member 1250. A receiving groove that is recessed into the shape may be provided.

The simulator spring 1232 is provided to elastically support the second simulation piston 1230. The simulator spring 1232 can elastically support the second simulation piston 1230 by having one end supported by the master piston 1220 and the other end supported by the second simulation piston 1230. When the second simulation piston 1230 advances according to the braking operation and displacement occurs, the simulator spring 1232 is compressed, and when the braking is released, the simulator spring 1232 expands by elastic force and the second simulation piston ( 1230) can be returned to the original position.

The piston spring 1222 is provided to elastically support the master piston 1220. The piston spring 1222 can elastically support the master piston 1220 by having one end supported by the cylinder block and the other end supported by the master piston 1220. When the master piston 1220 moves forward according to the braking operation and displacement occurs, the piston spring 1222 is compressed. Then, when the braking is released, the piston spring 1222 expands by elastic force and the master piston 1220 returns to its original position. You can return to .

The first simulation flow path 1260 is provided to communicate with the first simulation chamber 1240a and the reservoir 1100, and the first simulation flow path 1260 includes a first simulator valve ( 1261) can be prepared. The first simulator valve 1261 may be a normally closed solenoid valve that is normally closed and opens when an electrical signal is received from the electronic control unit. The first 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, during normal operation, the driver operates the brake pedal 10 and simultaneously provides the first backup passage 1610 and the second backup passage 1620, which will be described later. The first cut valve 1611 and the second cut valve 1621 are closed, and the reservoir valve 1711 provided in the first reservoir passage 1710 is also closed. On the other hand, the first simulator valve 1261 provided in the first simulation passage 1260 is opened. As the operation of the brake pedal 10 progresses, 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 1611 is closed. The second master chamber 1220b is sealed by the closing operation of 1621, and the second simulation chamber 1230a is also sealed by the closing operation of the reservoir valve 1711, so that the pressurized pressure contained in the first simulation chamber 1240a As the hydraulic pressure of the medium is transmitted to the reservoir 1100 through the first simulation flow path 1260, the first simulation piston 1240 advances and displacement occurs. On the other hand, as the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b are sealed, the second simulation piston 1230 cannot be displaced, and accordingly, the first simulation piston (1220a) is sealed. The displacement of 1240 compresses the elastic member 1250, and the elastic restoring force caused by the compression of the elastic member 1250 can be provided to the driver as a pedal feeling. Afterwards, when the driver releases the pedal force of the brake pedal 10, the elastic member 1250 returns to its original shape and position by elastic restoring force, and the first simulation chamber 1240a is a reservoir through the first simulation flow path 1260. Pressurized medium may be supplied from 1100 or may be filled with pressurized medium supplied from the first hydraulic circuit 1510 through the first backup passage 1610, which will be described later.

In this way, since the interiors of the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b are always filled with pressurized medium, the master piston 1220 and the second simulation chamber are The friction of the piston 1230 is minimized, thereby improving the durability of the integrated master cylinder 1200 and preventing the inflow of foreign substances from the outside.

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

The reservoir 1100 can accommodate and store pressurized medium inside. The reservoir 1100 is connected to each component, such as the integrated master cylinder 1200, the hydraulic pressure supply device 1300, which will be described later, and the hydraulic circuits 1510 and 1520, which will be described later, and can supply or receive pressurized media. In the drawings, several reservoirs 1100 are shown with the same reference numerals. However, this is an example to aid understanding of the invention. The reservoir 1100 may be provided as a single part or as a plurality of separate, independent parts. You 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 passage 1730 connecting the second master chamber 1220b and the reservoir 1100.

A reservoir valve 1711, which is a two-way control valve that controls the flow of braking fluid delivered through the first reservoir passage 1710, may be provided in the first reservoir passage 1710. The reservoir valve 1711 may be provided as a normally open type solenoid valve that is normally open and operates to close the valve when it receives an electrical signal from the electronic control unit. 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 receive the driver's intention to brake as an electrical signal from the pedal displacement sensor 11 that detects the displacement of the brake pedal 10 and generate hydraulic pressure of the pressurized medium through mechanical operation.

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 movement of the motor into linear movement and transmits it to the hydraulic pressure provision unit. Poetry) may be included.

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

The pressure chambers 1330 and 1340 are a first pressure chamber 1330 located in front of the hydraulic piston 1320 (to the left of the hydraulic piston 1320 with respect to FIG. 1), and a rear of the hydraulic piston 1320 ( It may include a second pressure chamber 1340 located to the right of the hydraulic piston 1320 with respect to FIG. 1 . That is, the first pressure chamber 1330 is partitioned by the front surface of the cylinder block 1310 and the hydraulic piston 1320 and is provided so that its volume varies depending on the movement of the hydraulic piston 1320, and the second pressure chamber 1340 ) is provided as a partition by the rear surface of the cylinder block 1310 and the hydraulic piston 1320 so that the volume varies depending on the movement of the hydraulic piston 1320.

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

The sealing member includes a piston sealing member 1350a provided between the hydraulic piston 1320 and the cylinder block 1310 to seal between the first pressure chamber 1330 and the second pressure chamber 1340. The hydraulic pressure or negative pressure in 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, and the first pressure chamber 1340, described later, is sealed by the piston sealing member 1350a. It may be transmitted to the hydraulic passage 1401 and the second hydraulic passage 1402.

A motor (not shown) is provided to generate driving force for the hydraulic piston 1320 by an electrical signal output from an electronic control unit (ECU). The motor may include a stator and a rotor, and may provide power to generate displacement of the hydraulic piston 1320 by rotating in the forward or reverse direction. The rotational speed and rotation angle of the motor can be precisely controlled by the motor control sensor. Since the motor is already a widely known technology, 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 with a structure including a worm shaft (not shown), a worm wheel (not shown), and a drive shaft 1390.

The worm shaft may be formed integrally with the rotation axis of the motor, and a worm may be formed on the outer peripheral surface and engage with the worm wheel to rotate the worm wheel. The worm wheel is connected to engage with the drive shaft 1390 to move the drive shaft 1390 in a straight line, and the drive shaft 1390 is connected to the hydraulic piston 1320, through which the hydraulic piston 1320 moves the cylinder block 1310. It can be moved by sliding within it.

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

Conversely, when the pedal force 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 within the cylinder block 1310, thereby generating negative pressure in the first pressure chamber 1330.

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

Conversely, when the pedal force 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 within 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 when the motor is driven, and transmits the hydraulic pressure. It can be decided by controlling the valves whether to implement braking or release the braking using negative pressure. A detailed description of this will be provided later.

Meanwhile, 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 movement of the motor into the linear movement of the hydraulic piston 1320, and may be composed of devices with various structures and methods. It should be understood in 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 first dump passage 1810 that connects the first pressure chamber 1330 and the reservoir 1100, and a first bypass passage 1830 that diverges and rejoins the first dump passage 1810. ), a second dump passage 1820 connecting the second pressure chamber 1340 and the reservoir 1100, and a second bypass passage 1840 that diverges and rejoins the second dump passage 1820, It may include an auxiliary dump passage 1850 that auxiliarily connects the first pressure chamber 1330 and the reservoir 1100.

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

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

The auxiliary dump passage 1850 may assist communication between the first pressure chamber 1330 and the reservoir 1100 through the auxiliary hydraulic port 1850a. Specifically, the auxiliary hydraulic port 1850a is connected to the auxiliary dump flow path 1850, thereby assisting the flow of pressurized medium between the first pressure chamber 1330 and the reservoir 1100, and the auxiliary hydraulic port 1835a A sealing member 1350b is provided at the front (left side with respect to FIG. 1) to allow the supply of pressurized medium from the auxiliary dump passage 1850 to the first pressure chamber 1330, but blocks the flow of pressurized medium in the opposite direction, A sealing member 1350c is provided at the rear (right side in FIG. 1) of the auxiliary dump passage 1850 to prevent the pressurized medium from leaking 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 delivered to each wheel cylinder 20, and the electronic control unit (ECU) controls the hydraulic pressure supply device 1300 and various other devices based on hydraulic pressure information and pedal displacement information. It is provided to control the valves.

The hydraulic control unit 1400 includes a first hydraulic circuit 1510 that controls the flow of hydraulic pressure delivered to the first and second wheel cylinders 21 and 22 among the four wheel cylinders 20, and the third and third 4 A second hydraulic circuit 1520 may be provided to control the flow of hydraulic pressure transmitted to the wheel cylinders 23 and 24, and a plurality of hydraulic circuits may be provided to control the hydraulic pressure transmitted from the hydraulic pressure supply device 1300 to the wheel cylinder 20. Includes flow paths and valves.

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

The sixth hydraulic passage 1406 is provided to communicate with the first hydraulic circuit 1510, and the seventh hydraulic passage 1407 is provided to communicate with the second hydraulic circuit 1520. The sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 join the eighth hydraulic passage 1408, and then the ninth hydraulic passage 1409 communicating with the first pressure chamber 1330 and the second pressure passage It may be provided by branching back to the tenth hydraulic passage 1410 that communicates with the chamber 1340.

A first valve 1431 that controls the flow of pressurized medium may be provided in the first hydraulic passage 1401. The first valve 1431 may be provided as a check valve that allows the flow of pressurized medium discharged from the first pressure chamber 1330 but blocks the flow of pressurized medium in the opposite direction. Additionally, a second valve 1432 may be provided in the second hydraulic passage 1402 to control the flow of pressurized medium, and the second valve 1432 may be configured to control the flow of pressurized medium discharged from the second pressure chamber 1340. It can be provided with a check valve that allows but blocks the flow of pressurized medium in the opposite direction.

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

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

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

The ninth hydraulic passage 1409 is branched from the eighth hydraulic passage 1408, where the sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 join, and is connected to the first pressure chamber 1330. A seventh valve 1437 that controls the flow of pressurized medium may be provided in the ninth hydraulic passage 1409. The seventh valve 1437 may be provided as a two-way control valve that controls the flow of pressurized medium delivered along the ninth hydraulic passage 1409. The seventh valve 1437 may be a normally closed solenoid valve that is normally closed and opens when an electrical signal is received from the electronic control unit.

The tenth hydraulic passage 1410 is branched from the eighth hydraulic passage 1408, where the sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 join, and is connected to the second pressure chamber 1340. An eighth valve 1438 that controls the flow of pressurized medium may be provided in the tenth hydraulic oil passage 1410. The eighth valve 1438 may be provided as a two-way control valve that controls the flow of pressurized medium delivered along the tenth hydraulic passage 1410. The eighth valve 1438, like the seventh valve 1437, is provided as a normally closed solenoid valve that is normally closed and operates to open when it receives an electrical signal from the electronic control unit. It can be.

The hydraulic control unit 1400 is such that the hydraulic pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 advances due to the arrangement of the hydraulic oil path and the valve is divided into the first hydraulic oil path 1401 and the third hydraulic oil path ( 1403), can be sequentially transmitted to the first hydraulic circuit 1510 through the fourth hydraulic passage 1404, the first hydraulic passage 1401, the third hydraulic passage 1403, and the fifth hydraulic passage 1405. It may be sequentially transmitted to the second hydraulic circuit 1520. In addition, the hydraulic pressure formed in the second pressure chamber 1340 as the hydraulic piston 1320 moves backward sequentially passes through the second hydraulic passage 1402, the third hydraulic passage 1403, and the fourth hydraulic passage 1404. 1 It can be delivered to the hydraulic circuit 1510, and can be sequentially delivered to the second hydraulic circuit 1520 through the second hydraulic passage 1402, the third hydraulic passage 1403, and the fifth hydraulic passage 1405. there is.

On the contrary, the negative pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 moves backward causes the pressurized medium provided to the first hydraulic circuit 1510 to flow into the sixth hydraulic passage 1406, the eighth hydraulic passage 1408, The ninth hydraulic passage 1409 can be sequentially recovered to the first pressure chamber 1330, and the pressurized medium provided to the second hydraulic circuit 1520 is connected to the seventh hydraulic passage 1407 and the eighth hydraulic passage 1408. , It can be recovered to the first pressure chamber 1330 through the ninth hydraulic passage 1409 sequentially. In addition, the negative pressure formed in the second pressure chamber 1340 as the hydraulic piston 1320 advances causes the pressurized medium provided to the first hydraulic circuit 1510 to flow through the sixth hydraulic passage 1406, the eighth hydraulic passage 1408, and the sixth hydraulic passage 1408. 10 The hydraulic oil passage 1410 can be sequentially recovered to the first pressure chamber 1340, and the pressurized medium provided to the second hydraulic circuit 1520 is connected to the seventh hydraulic oil passage 1407, the eighth hydraulic oil passage 1408, It can be recovered to the second pressure chamber 1340 through the tenth hydraulic passage 1410 sequentially.

In addition, the negative pressure formed in the first pressure chamber 1330 as the hydraulic piston 1320 moves backward can receive pressurized media from the reservoir 1100 to the first pressure chamber 1330 through the first dump passage 1810. In addition, the negative pressure formed in the second pressure chamber 1340 as the hydraulic piston 1320 advances allows the pressurized medium to be supplied from the reservoir 1100 to the second pressure chamber 1340 through the second dump passage 1820. there is.

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

The first hydraulic circuit 1510 of the hydraulic control unit 1400 controls 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, FL). and the second hydraulic circuit 1520 can control the hydraulic pressure of the third and fourth wheel cylinders 23 and 24, which are the other two wheel cylinders 20.

The first hydraulic circuit 1510 may receive hydraulic pressure through the fourth hydraulic passage 1404 and discharge the hydraulic pressure through the sixth hydraulic passage 1406. For this purpose, as shown in FIG. 1, the fourth hydraulic passage 1404 and the sixth hydraulic passage 1406 are two passages that join and connect to the first wheel cylinder 21 and the second wheel cylinder 22. It can be prepared by branching. In addition, the second hydraulic circuit 1520 can receive hydraulic pressure through the fifth hydraulic passage 1405 and discharge the hydraulic pressure through the seventh hydraulic passage 1407, and accordingly, as shown in FIG. 1, the After the 5 hydraulic passage 1405 and the 7th hydraulic passage 1407 join, they may be branched into two passages connected to the third wheel cylinder 23 and the fourth wheel cylinder 24. However, the connection of the hydraulic oil path shown in FIG. 1 is an example to aid understanding of the present invention and is not limited to the structure, and the fourth hydraulic oil passage 1404 and the sixth hydraulic oil passage 1406 are each connected to the first hydraulic oil passage. It is connected to the circuit 1510 side and can be independently branched and connected to the first wheel cylinder 21 and the second wheel cylinder 22, and similarly, the fifth hydraulic passage 1405 and the seventh hydraulic passage 1407 It should be understood equally even when connected in various ways and structures, such as being connected to the second hydraulic circuit 1520 and independently branched and connected to the third wheel cylinder 23 and the fourth wheel cylinder 24. something to do.

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

The first and second hydraulic circuits (1510, 1520) are provided with first to fourth check valves (1513a, 1513b, 1523a) connected in parallel to the first to fourth inlet valves (1511a, 1511b, 1521a, 1521b). , 1523b) may be included. The check valves (1513a, 1513b, 1523a, 1523b) are 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, allowing only the flow of pressurized medium from each wheel cylinder 20 to the hydraulic pressure supply device 1300, and blocking the flow of pressurized medium from the hydraulic pressure supply device 1300 to the wheel cylinder 20. . The hydraulic pressure of the pressurized medium applied to each wheel cylinder 20 can be quickly released by the first to fourth check valves 1513a, 1513b, 1523a, and 1523b, and the first to fourth inlet valves 1511a, 1511b, Even when 1521a and 1521b) do not operate normally, the hydraulic pressure of the pressurized medium applied to the wheel cylinder 20 can be smoothly returned to the hydraulic pressure providing unit.

The first and second wheel cylinders 21 and 22 of the first hydraulic circuit 1510 may be branched and connected to a first backup passage 1610, which will be described later, and the first backup passage 1610 may have at least one first backup passage 1610. A cut valve 1611 is provided to control the flow of pressurized medium between the first and second wheel cylinders 21 and 22 and the integrated master cylinder 1200. In addition, the first cut valve 1611 selectively releases the hydraulic pressure of the pressurized medium applied to the first wheel cylinder 21 and the second wheel cylinder 22 when the vehicle is in ABS braking mode, thereby opening the first backup passage 1610. It can be delivered to the reservoir 1100 through the first simulation chamber 1240a and the simulation flow path 1260.

The third and fourth wheel cylinders 23 and 24 of the second hydraulic circuit 1520 may be branched and connected to a second backup passage 1620, which will be described later, and the second backup passage 1620 may have at least one second backup passage 1620. A cut valve 1621 is provided to control the flow of pressurized medium between the third and fourth wheel cylinders 23 and 24 and the integrated master cylinder 1200. In addition, the second cut valve 1621 selectively releases the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 when the vehicle is in ABS braking mode, thereby opening the second backup passage 1620. It can be delivered to the reservoir 1100 through the second master chamber 1220b.

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 device failure. It may include first and second backup channels and auxiliary backup channels 1610, 1620, and 1630 that can be implemented. The mode in which the hydraulic pressure of the integrated master cylinder 1200 is directly transmitted to the wheel cylinder 20 is called 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 provided to connect the 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 connected to the first master chamber 1220a and the first backup passage 1610 of the integrated master cylinder 1200. ) can be arranged to connect.

Specifically, the first backup passage 1610 has one end connected to the first simulation chamber 1240a, and the other end connected to the first inlet valve 1511a and the second inlet valve 1511b on the first hydraulic circuit 1510. It can be connected to the downstream side, and the second backup passage 1620 has one end connected to the second master chamber 1220b and the other end connected to the third inlet valve 1521a and the fourth inlet valve on the second hydraulic circuit 1520. It can be connected to the downstream side of (1521b). In addition, the auxiliary backup passage 1630 is connected to and joins the first backup passage 1610, but is not limited to this and is provided to connect the first simulation chamber 1240a and the first hydraulic circuit 1510 through a separate passage. You can.

The auxiliary backup passage 1630 may include an orifice 1631 that slows the flow rate of the pressurized medium passing through the auxiliary backup passage 1630. Accordingly, in the inspection mode to be described later, the pressurized medium delivered from the first hydraulic circuit 1510 to the integrated master cylinder 1200 may be filled with the first simulation chamber 1240a before the first master chamber 1220a, and thus More details will be provided later.

The first backup passage 1610 and the second backup passage 1620 include at least one first and second cut valve, respectively, to control the bidirectional flow and hydraulic pressure of the pressurized medium delivered to the first to fourth wheel cylinders 20. (1611, 1621) can be provided. Specifically, the first backup passage 1610 may be branched and connected to the first wheel cylinder 21 and the second wheel cylinder 22, and the first cut valve 1611 may be connected to the first wheel cylinder 21 and the second wheel cylinder 22. One pair may be provided in each of the two wheel cylinders 22. In addition, the second backup passage 1620 may be branched and connected to the third wheel cylinder 23 and the fourth wheel cylinder 24, and the second cut valve 1621 may be connected to the third wheel cylinder 23 and the fourth wheel cylinder 24. One pair may be provided on each wheel cylinder 24.

The first and second cut valves 1611 and 1621 are normally open and can be provided as solenoid valves of the normally open type that operate to close when an electrical signal is received from the electronic control unit. .

As a result, when the first and second cut valves 1611 and 1621 are closed in normal braking mode, the pressurized medium of the integrated master cylinder 1200 is prevented from being directly transmitted to the wheel cylinder 20, and the hydraulic pressure supply device Hydraulic pressure provided at 1300 may be supplied to the wheel cylinder 20 through the hydraulic control unit 1400 to perform braking. On the other hand, in abnormal braking mode, the first and second cut valves (1611, 1621) are opened to allow the pressurized medium pressurized in the integrated master cylinder (1200) to the wheel cylinder (20) through the backup passages (1610, 1620, 1630). It can be supplied directly to implement braking.

The electronic brake system 1000 according to the first embodiment of the present invention may include a pressure sensor (PS) that detects 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 as being provided on the first hydraulic circuit 1510, but it is not limited to the location and number. If it can detect the hydraulic pressure of the hydraulic circuit and the integrated master cylinder 1200, This includes cases where it is provided in various locations and in various numbers.

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 includes a normal operating mode in which various devices and valves operate normally without malfunctions or abnormalities, and a non-normal operation mode in which various devices and valves malfunction or malfunction. Normal operation mode (fallback mode), ABS dump mode that quickly and continuously reduces the hydraulic pressure of the wheel cylinder (20) for ABS operation, and whether the integrated master cylinder (1200) or the simulator valve (1261) leaks. It may include an inspection mode that inspects.

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

The normal operating mode of the electronic brake system 1000 according to the first embodiment of the present invention changes from the first to the third braking mode as the hydraulic pressure transmitted from the hydraulic pressure supply device 1300 to the wheel cylinder 20 increases. It can be operated separately. Specifically, the first braking mode primarily provides hydraulic pressure by the hydraulic pressure supply device 1300 to the wheel cylinder 20, and the second braking mode provides hydraulic pressure by the hydraulic pressure supply device 1300 to the wheel cylinder 20. It is possible to deliver a higher braking pressure than the first braking mode by providing it secondarily, and the third braking mode is a second braking mode by providing the hydraulic pressure by the hydraulic pressure supply device 1300 to the wheel cylinder 20 thirdly. It is possible to deliver higher braking pressure.

The first to third braking modes can be changed by varying the operations of the hydraulic pressure supply device 1300 and the hydraulic control unit 1400. By utilizing the first to third braking modes, the hydraulic pressure supply device 1300 can provide sufficiently high hydraulic pressure of the pressurized medium without a high-specification motor, and further prevent unnecessary load applied to the motor. As a result, stable braking force can be secured while reducing the cost and weight of the brake system, and durability and operational reliability of the device can be improved.

Figure 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 the first braking mode.

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

Specifically, the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fourth hydraulic passage 1404 to the first hydraulic circuit 1510. It is primarily transmitted to the first and second wheel cylinders 21 and 22 provided. At this time, the first valve 1431 allows only the flow of pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 flows from the third hydraulic passage 1403 to the first hydraulic circuit 1510. Since it is provided with a check valve that only allows the flow of the pressurized medium toward, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the first and second wheel cylinders 21 and 22. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in the open state, and the first cut valve 1611 is maintained in the closed state to maintain the hydraulic pressure of the pressurized medium. This prevents leakage into the reservoir 1100.

In addition, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fifth hydraulic passage 1405 to the second hydraulic circuit 1520. ) is primarily transmitted to the third and fourth wheel cylinders (23, 24) provided in the. As described above, the first valve 1431 allows only the flow of pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 connects the second hydraulic circuit ( 1520), the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth wheel cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in the open state, and the second cut valve 1621 is maintained in the closed state to maintain the hydraulic pressure of the pressurized medium. Leakage into the second backup passage 1620 can be prevented.

In the first braking mode, the eighth valve 1438 is controlled to be closed, thereby preventing the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 from leaking into the second pressure chamber 1340. Additionally, the first dump valve 1831 provided in the first bypass passage 1830 can be maintained in a closed state to prevent the hydraulic pressure formed in the first pressure chamber 1330 from leaking into the reservoir 1100.

Meanwhile, as the hydraulic piston 1320 advances, negative pressure is generated in the second pressure chamber 1340, and the second pressure chamber is discharged from the reservoir 1100 through the second dump passage 1820 and the second bypass passage 1840. The hydraulic pressure of the pressurized medium is transmitted to 1340 to prepare for the second braking mode described later. The second dump check valve 1821 provided in the second dump passage 1820 allows the flow of pressurized medium from the reservoir 1100 to the second pressure chamber 1340, and the pressurized medium flows into the second pressure chamber (1821). 1340), and the first dump valve 1841 provided in the second bypass passage 1840 is switched to the open state to supply pressurized medium from the reservoir 1100 to the first pressure chamber 1330. Can be supplied quickly.

In the first braking mode, which implements braking of the wheel cylinder 20 by the hydraulic pressure supply device 1300, the first cut valve 1611 provided in the first backup passage 1610 and the second backup passage 1620, respectively, and The second cut valve 1621 is switched closed, and the reservoir valve 1711 provided in the first reservoir passage 1710 is switched closed, so that the pressurized medium discharged from the integrated master cylinder 1200 is transferred to the wheel cylinder 20. Prevents transmission to the other side.

Specifically, when a pedal force is applied to the brake pedal 10, the first cut valve 1611 is closed to seal the first master chamber 1220a, and the second cut valve 1621 is closed to close the second master chamber 1220b. ) is sealed, and the reservoir valve 1711 is closed to seal the second simulation chamber (1230a). Therefore, as a pedal force is applied to the brake pedal 10, the first master chamber 1220a, the second master chamber 1220b, and the second simulation chamber 1230a are sealed, and the second simulation piston 1230 and the master piston 1220 are sealed. ) does not cause displacement. On the other hand, the simulator valve 1261 is open and the first simulation chamber 1240a and the reservoir 1100 are in communication, so the pressurized medium contained in the first simulation chamber 1240a flows to the reservoir 1100 through the simulation flow path 1260. is supplied, and the first simulation piston 1240 moves forward smoothly due to the pedal force of the brake pedal, thereby generating displacement. In this way, 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 force of the brake pedal is applied due to 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 can switch from the first braking mode to the second braking mode shown in FIG. 3 when a higher braking pressure than the first braking mode must be provided.

Figure 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 the second braking mode. Referring to Figure 3, the electronic control unit detects the pedal displacement sensor 11. If the displacement or operating speed of one brake pedal 10 is higher than the preset level, or the hydraulic pressure detected by the pressure sensor is higher than the preset level, it is determined that a higher braking pressure is required, and the first braking mode is performed. You can switch 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 providing unit by the power conversion unit, causing the hydraulic piston 1320 to move backwards to generate second pressure. Hydraulic pressure is generated in the chamber 1340. The hydraulic pressure discharged from the second pressure chamber 1340 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520 to generate braking force. .

Specifically, the hydraulic pressure formed in the second pressure chamber 1340 sequentially passes through the second hydraulic passage 1402, the third hydraulic passage 1403, and the fourth hydraulic passage 1404 to the first hydraulic circuit 1510. It is secondarily transmitted to the first and second wheel cylinders 21 and 22 provided. At this time, the second valve 1432 provided in the second hydraulic passage 1402 allows only the flow of pressurized medium discharged from the second pressure chamber 1340, and the third valve 1432 provided in the fourth hydraulic passage 1404 The valve 1433 is provided as a check valve that only allows the flow of pressurized medium from the third hydraulic passage 1403 to the first hydraulic circuit 1510, and the hydraulic pressure of the pressurized medium is applied to the first and second wheel cylinders 21 , 22) can be delivered smoothly. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in the open state, and the first cut valve 1611 is maintained in the closed state so that the hydraulic pressure of the pressurized medium is maintained. Prevents leakage into the reservoir 1100.

In addition, the hydraulic pressure formed in the second pressure chamber 1340 sequentially passes through the second hydraulic passage 1402, the third hydraulic passage 1403, and the fifth hydraulic passage 1405 to be provided in the second hydraulic circuit 1520. It is secondarily transmitted to the third and fourth wheel cylinders 23 and 24. As described above, the second valve 1432 provided in the second hydraulic passage 1403 allows only the flow of pressurized medium discharged from the second pressure chamber 1340, and the second valve 1432 provided in the fifth hydraulic passage 1405 The fourth valve 1434 is provided as a check valve that only allows the flow of pressurized medium from the third hydraulic passage 1403 to the second hydraulic circuit 1520, and the hydraulic pressure of the pressurized medium is applied to the third and fourth wheel cylinders. (23, 24) and can be transmitted smoothly. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in the open state, and the second cut valve 1621 is maintained in the closed state to maintain the hydraulic pressure of the pressurized medium. Leakage into the second backup passage 1620 can be prevented.

In the second braking mode, the seventh valve 1437 is controlled to be closed, thereby preventing the hydraulic pressure of the pressurized medium formed in the second pressure chamber 1340 from leaking into the first pressure chamber 1330. Additionally, the second dump valve 1841 is switched to a closed state, thereby preventing the hydraulic pressure of the pressurized medium formed in the second pressure chamber 1340 from leaking into the reservoir 1100.

Meanwhile, as the hydraulic piston 1320 moves backward, negative pressure is generated in the first pressure chamber 1330, and the first pressure chamber is discharged from the reservoir 1100 through the first dump passage 1810 and the first bypass passage 1830. The hydraulic pressure of the pressurized medium is transmitted to 1330 to prepare for the third braking mode described later. The first dump check valve 1811 provided in the first dump passage 1810 allows the flow of pressurized medium from the reservoir 1100 to the first pressure chamber 1330, and the pressurized medium flows into the first pressure chamber (1330). 1330), and the first dump valve 1831 provided in the first bypass passage 1830 is switched to the open state to supply pressurized medium from the reservoir 1100 to the first pressure chamber 1330. Can be supplied quickly.

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

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 higher braking pressure than the second braking mode must be provided.

Figure 4 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 the third braking mode.

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

When switching from the second braking mode to the third braking mode, the motor (not shown) operates to rotate in one direction, the rotational force of the motor is transmitted to the hydraulic pressure providing unit by the power conversion unit, and the hydraulic piston of the hydraulic pressure providing unit As 1320 moves forward again, 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, a portion of the hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fourth hydraulic passage 1404 to form the first hydraulic circuit 1510. ) is primarily transmitted to the first and second wheel cylinders 21 and 22 provided in the. At this time, the first valve 1431 allows only the flow of pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 flows from the third hydraulic passage 1403 to the first hydraulic circuit 1510. Since it is provided with a check valve that only allows the flow of the pressurized medium toward, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the first and second wheel cylinders 21 and 22. In addition, the first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in the open state, and the first cut valve 1611 is maintained in the closed state to maintain the hydraulic pressure of the pressurized medium. This prevents leakage into the reservoir 1100.

In addition, a portion of the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fifth hydraulic passage 1405 to the second hydraulic circuit. It is primarily transmitted to the third and fourth wheel cylinders 23 and 24 provided at 1520. As described above, the first valve 1431 allows only the flow of pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 connects the second hydraulic circuit ( 1520), the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth wheel cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in the open state, and the second cut valve 1621 is maintained in the closed state to maintain the hydraulic pressure of the pressurized medium. Leakage into the second backup passage 1620 can be prevented.

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

In the third braking mode, the first dump valve 1831 is switched to a closed state to prevent the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 from leaking into the reservoir 1100 along the first bypass passage 1830. This can be prevented, and the second dump valve 2841 is also controlled in a closed state, thereby rapidly forming negative pressure in the second pressure chamber 1340 due to the advance of the hydraulic piston 1320, thereby releasing the pressure from the first pressure chamber 1330. You can receive the provided pressurized media smoothly.

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

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

Figure 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 force applied to the brake pedal 10 is released, the motor generates rotational force in the other 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 released and negative pressure can be generated, and thus the pressurized medium in the wheel cylinder 20 can be delivered to the first pressure chamber 1330.

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

At the same time, to ensure rapid and smooth backward movement of the hydraulic piston 1320, the pressurized medium contained in the second pressure chamber 1340 sequentially passes through the 10th hydraulic passage 1410 and the 9th hydraulic passage 1409. 1 is transmitted to the pressure chamber 1330, and for this purpose, the eighth valve 1438 provided in the tenth hydraulic passage 1410 is also switched to the open state. At this time, the second dump valve 1841 may be closed to induce the pressurized medium in the second pressure chamber 1340 to be supplied to the first pressure chamber 1330. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in an open state, and the first cut valve 1611 is maintained in a closed state.

In addition, the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the first pressure chamber 1330 is the seventh hydraulic oil. It sequentially passes through the furnace 1407, the eighth hydraulic passage 1408, and the ninth hydraulic passage 1409 and is recovered into the first pressure chamber 1330. As described previously, the sixth valve 1436 provided in the seventh hydraulic passage 1407 is provided as a check valve that only allows the flow of pressurized medium discharged from the second hydraulic circuit 1520, so the pressurized medium can be recovered. And, the seventh valve 1437 is opened to allow the flow of pressurized medium through the ninth hydraulic passage 1409. Additionally, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1621 is maintained in a closed state.

After completing the release of the third braking mode, the operation can be switched to the release operation of the second braking mode shown in FIG. 6 in order to further lower the braking pressure of the wheel cylinder.

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

Referring to FIG. 6, when the pedal force applied to the brake pedal 10 is released, the motor generates rotational force in one direction and transmits it to the power conversion unit, and the power conversion unit moves the hydraulic piston 1320 forward. As a result, the hydraulic pressure in the second pressure chamber 1340 can be released and negative pressure can be generated, and thus the pressurized medium in the wheel cylinder 20 can be delivered to the second pressure chamber 1340.

Specifically, the hydraulic pressure of the pressurized medium applied to the first wheel cylinder 21 and the second wheel cylinder 22 provided in the first hydraulic circuit 1510 is the sixth hydraulic passage 1406 and the eighth hydraulic passage 1408. , sequentially passes through the tenth hydraulic passage 1410 and is recovered into the second pressure chamber 1340. At this time, the fifth valve 1435 provided in the sixth hydraulic oil passage 1406 allows only the flow of the pressurized medium discharged from the first hydraulic circuit 1510, so the pressurized medium can be recovered, and the pressurized medium can be recovered through the tenth hydraulic oil passage. The eighth valve 1438 provided at 1410 may be switched open to allow the flow of pressurized medium delivered along the tenth hydraulic passage 1410. In addition, the seventh valve 1437 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the first pressure chamber 1330 through the ninth hydraulic passage 1409. there is. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in an open state, and the first cut valve 1611 is maintained in a closed state.

In addition, the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the second pressure chamber 1340 is the seventh hydraulic oil. It sequentially passes through the furnace 1407, the 8th hydraulic passage 1408, and the 10th hydraulic passage 1410 and is recovered to the second pressure chamber 1340. As described previously, the sixth valve 1436 provided in the seventh hydraulic passage 1407 allows the flow of pressurized medium discharged from the second hydraulic circuit 1520, and the sixth valve 1436 provided in the tenth hydraulic passage 1410 The eighth valve 1438 is opened, so that the pressurized medium can be smoothly returned to the second pressure chamber 1340. Furthermore, the seventh valve 1437 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the first pressure chamber 1330 through the ninth hydraulic passage 1409. there is. The third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1621 is maintained in a closed state.

Meanwhile, when the second braking mode is released, the first dump valve 1831 is opened to facilitate smooth forward movement of the hydraulic piston 1320, and to quickly form negative pressure in the second pressure chamber 1340. 2 The dump valve (1841) can be switched to the closed state.

After completing the release of the second braking mode, the operation can be switched to the release operation of the first braking mode shown in FIG. 7 in order to completely release the braking pressure applied to the wheel cylinder 20.

Figure 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 again and releases the first braking mode.

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

Specifically, the hydraulic pressure of the first wheel cylinder 21 and the second wheel cylinder 22 provided in the first hydraulic circuit 1510 is the sixth hydraulic oil passage 1406, the eighth hydraulic oil passage 1408, and the ninth hydraulic oil. It sequentially passes through the furnace 1409 and is recovered into the first pressure chamber 1330. At this time, the fifth valve 1435 provided in the sixth hydraulic passage 1406 is provided as a check valve that only allows the flow of the pressurized medium discharged from the first hydraulic circuit 1510, so that the pressurized medium can be delivered, The seventh valve 1437 is opened to allow the flow of pressurized medium through the ninth hydraulic passage 1409. The first inlet valve 1511a and the second inlet valve 1511b provided in the first hydraulic circuit 1510 are maintained in an open state, and the first cut valve 1611 is maintained in a closed state. In addition, the eighth valve 1438 is controlled in a closed state to prevent the pressurized medium recovered from the first hydraulic circuit 1510 from leaking into the second pressure chamber 1340 through the tenth hydraulic passage 1410. , the first dump valve 1831 is closed and operated to effectively create negative pressure in the first pressure chamber 1330.

The hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 provided in the second hydraulic circuit 1520 by the negative pressure generated in the first pressure chamber 1330 is the seventh hydraulic oil path ( 1407), the eighth hydraulic passage 1408, and the ninth hydraulic passage 1409, and are returned to the first pressure chamber 1330. As previously described, the sixth valve 1436 provided in the seventh hydraulic passage 1407 is provided as a check valve that only allows the flow of pressurized medium discharged from the second hydraulic circuit 1520, so that the pressurized medium can be recovered. And, the seventh valve 1437 is opened to allow the flow of pressurized medium through the ninth hydraulic passage 1409. Additionally, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 remain open. Furthermore, the eighth valve 1438 is controlled in a closed state to prevent the pressurized medium recovered from the second hydraulic circuit 1520 from leaking into the second pressure chamber 1340 through the tenth hydraulic passage 1410. . The third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 are maintained in an open state, and the second cut valve 1621 is maintained in a closed state.

At the same time, the second dump valve 1841 is opened to promote rapid and smooth backward movement of the hydraulic piston 1320, so that the pressurized medium contained in the second pressure chamber 1340 flows through the second bypass flow path 1840. It may be discharged into the reservoir 1100.

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

Figure 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 cannot operate normally due to device failure.

Referring to FIG. 8, in the abnormal operation mode, each valve is controlled to the initial braking state, which is a non-operating state. At this time, when the driver applies pedal force to the brake pedal 10, the first simulation piston 1240 connected to the brake pedal 10 moves forward and displacement occurs. Since the first simulator valve 1261 is closed and the first cut valve 1611 remains open, the pressurized medium accommodated in the first simulation chamber 1240a by the advance of the first simulation piston 1240 is 1 It is transmitted to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510 along the 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 the elastic member 1250 is not compressed and the second simulation piston 1230 is not compressed. Moving forward causes displacement. At this time, since the reservoir valve 1711 is maintained in an open state, the pressurized medium accommodated in the second simulation chamber 1230a by the displacement of the second simulation piston 1230 flows into the reservoir 1100 through the first reservoir flow path 1710. ), and since the first cut valve 1611 is maintained in an open state, the pressurized medium contained in the first master chamber (1220a) is supplied with the first hydraulic pressure along the auxiliary backup passage 1630 and the first backup passage 1610. It can be transmitted to the first wheel cylinder 21 and the second wheel cylinder 22 of the circuit 1510 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 passage 1720 as the second simulation piston 1230 advances, thereby forming the first master chamber 1230. Prevents the pressurized medium contained in (1220a) from being delivered to the reservoir (1100).

In addition, when the second simulation piston 1230 advances, the pressurized medium in the first master chamber 1220a advances the master piston 1220 to generate displacement, and the second cut valve 1621 is opened. Since it is maintained, the pressurized medium contained in the second master chamber (1220b) is delivered to the third wheel cylinder (23) and fourth wheel cylinder (24) of the second hydraulic circuit (1520) along the second backup passage (1620) to perform braking. can be implemented. 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 passage 1730 as the master piston 1220 advances, so that the pressurized medium flows into the reservoir ( 1100).

In an abnormal operating mode, the first cut valve 1611, the second cut valve 1621, and the reservoir valve 1711 are in an open state, and the first simulator valve 1261 is in a closed state, so that the integrated master cylinder 1200 The hydraulic pressure transmitted from the first simulation chamber 1240a, the first master chamber 1220a, and the second master chamber 1220b can be directly transmitted to each wheel cylinder 20, thereby improving braking stability and promoting rapid braking. You can.

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

Figure 9 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 the ABS dump mode.

Referring to FIG. 9, when attempting to perform the ABS dump mode while the hydraulic pressure supply device 1300 is operating for braking the vehicle, the electronic control unit operates the first and second cut valves 1611 and 1621. It can be implemented through control.

Specifically, the hydraulic piston 1320 of the hydraulic pressure supply device 1300 advances and generates hydraulic pressure in the first pressure chamber 1330, and the hydraulic pressure in the first pressure chamber 1330 is generated by the hydraulic control unit 1400 and the first hydraulic pressure. It is transmitted to each wheel cylinder 20 through the circuit 1510 and the second hydraulic circuit 1520 to generate braking force. When the ABS dump mode is to be performed thereafter, the electronic control unit repeatedly opens and closes at least a portion of the first cut valve 1611, thereby controlling the first wheel cylinder 21 and the second wheel cylinder 22. A portion of the hydraulic pressure of the pressurized medium applied to the can be discharged to the reservoir 1100 through the first backup passage 1610, the first simulation chamber 1240a, and the first simulation passage 1260 sequentially. In addition, the electronic control unit repeatedly performs opening and closing operations of at least a portion of the second cut valve 1621, thereby releasing a portion of the hydraulic pressure of the pressurized medium applied to the third wheel cylinder 23 and the fourth wheel cylinder 24. It can be discharged to the reservoir 1100 through the second backup passage 1610, the second master chamber 1220b, and the third reservoir passage 1730 sequentially.

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

An inspection mode can be performed to inspect the integrated master cylinder 1200 of the electronic brake system 1000 according to the first embodiment of the present invention for leaks. Figure 10 is a hydraulic circuit diagram showing the inspection mode state of the electronic brake system 1000 according to the first embodiment of the present invention. Referring to Figure 10, when performing the inspection mode, the electronic control unit uses the hydraulic pressure generated from the hydraulic supply device 1300. The hydraulic pressure is controlled to be supplied to the first simulation chamber 1240a of the integrated master cylinder 1200.

Specifically, the electronic control unit operates to advance the hydraulic piston 1320 in a state where each valve is controlled to the initial braking state in which the valves are in a non-operated state, thereby generating hydraulic pressure in the first pressure chamber 1330 and simultaneously 2 The cut valve 1621 is controlled in a closed state. The hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fourth hydraulic passage 1404 and is transmitted to the first hydraulic circuit 1510, The pressurized medium delivered to the first hydraulic circuit 1510 opens at least a portion of the first cut valve 1611 and is delivered to the first simulation chamber 1240a through the first backup passage 1610.

At this time, an orifice 1631 is provided in the auxiliary backup passage 1630 to slow down 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 move forward. In addition, in order to prevent the second simulation piston 1230 from moving forward even if hydraulic pressure is preferentially applied to the first simulation chamber 1240a, the reservoir valve 1711 is briefly opened and then closed to create the second simulation chamber (1240a). The second simulation piston 1230 can be moved forward by partially relieving the hydraulic pressure in 1230a). As described above, when the second simulation piston 1230 advances, the cut-off hole 1231 crosses with the fourth hydraulic port 1280d and is blocked, thereby sealing the first master chamber 1220a.

Additionally, the first simulator valve 1261 remains closed and the first simulation chamber 1240a is maintained in a closed state.

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

In this state, the hydraulic pressure value of the pressurized medium expected to be generated due to the displacement of the hydraulic piston 1320 is compared with the hydraulic pressure value of the first simulation chamber (1240a) or the first hydraulic circuit (1510) measured by the pressure sensor (PS). By doing so, leaks in the integrated master cylinder 1200 or the simulator valve 1261 can be diagnosed. Specifically, the expected hydraulic pressure value calculated based on the displacement of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown), and the actual first simulation chamber 1240a measured by the pressure sensor (PS) or By comparing the hydraulic pressure values of the first hydraulic circuit 1510, if the two hydraulic values match, it can be determined that there is no leak in the integrated master cylinder 1200 or the first simulator valve 1261. In contrast, the actual first simulation chamber 1240a or 1 If the hydraulic pressure level of the hydraulic circuit 1510 is low, some of the hydraulic pressure of the pressurized medium applied to the first simulation chamber 1240a is lost, so it is assumed that a leak exists in the integrated master cylinder 1200 or the first simulator valve 1261. It can make a decision and inform the driver of this decision.

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

In addition, in the description of the electronic brake system 2000 according to the second embodiment of the present invention described below, except for cases where additional description is given using separate reference numerals, the electronic brake system according to the first embodiment of the present invention described above This is the same as the explanation for (1000), so the explanation is omitted to prevent duplication of content.

Recently, as market demand for eco-friendly vehicles increases, hybrid vehicles with improved fuel efficiency are gaining popularity. Hybrid vehicles recover kinetic energy as electrical energy while the vehicle is braking, store it in the battery, and then use the motor as an auxiliary driving source for the vehicle. Typically, hybrid vehicles use the vehicle's braking to increase energy recovery rate. During operation, energy is recovered by a generator (not shown), etc. This braking operation is called a regenerative braking mode, and the electronic brake system 2000 according to the second embodiment of the present invention uses the third wheel cylinder 23 and the fourth wheel cylinder 23 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 can be implemented through cooperative control of the generators of the third and fourth wheel cylinders 23 and 24 and the fourth valve 2434, and will be described later with reference to FIG. 11.

Figure 11 is a hydraulic circuit diagram showing an electronic brake system according to a second embodiment of the present invention. Referring to Figure 11, the flow of pressurized medium is controlled in the fifth hydraulic passage 1405 according to the second embodiment of the present invention. A fourth valve 2434 may be provided. The fourth valve 2434 may be provided as a two-way control valve that controls the flow of pressurized medium delivered along the fifth hydraulic passage 1405. The fourth valve 2434 may be a normally closed solenoid valve that is normally closed and opens when an electrical signal is received from the electronic control unit. The fifth valve 2415 is controlled to be open in the normal operating mode, but is closed when entering the regenerative braking mode by a generator (not shown) provided in the third wheel cylinder 23 and the fourth wheel cylinder 24. can be converted to

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

12 shows 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. 12, in the case of the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510, the braking force desired by the driver is only supplied by hydraulic pressure. While it is formed by the hydraulic pressure of the pressurized medium by the operation of the device 1300, the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 where an energy recovery device such as a generator is installed. In the case of , the sum of the total braking pressure including 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. must be the same as Therefore, when entering the regenerative braking mode, the braking pressure caused by the hydraulic pressure supply device 1300 applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 is removed or kept constant by closing the fourth valve 2434. By maintaining and at the same time increasing the regenerative braking pressure by the generator, the total braking force of the third and fourth wheel cylinders 23 and 24 can be made equal to the braking force of the first and second wheel cylinders 23 and 24.

Specifically, referring to FIG. 10, when the driver steps on 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. , the hydraulic piston 1320 of the hydraulic pressure supply device 1300 advances and generates hydraulic pressure in the first pressure chamber 1330. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 through the hydraulic control unit 2400, 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 supplied to the first hydraulic passage 1401, the third hydraulic passage 1403, and the third hydraulic passage 1403. 4 It is sequentially transmitted through the hydraulic oil path 1404 to implement braking of the first and second wheel cylinders 21 and 22.

On the other hand, in the case of the second hydraulic circuit 1520 where the generator is installed, the electronic control unit detects the vehicle's speed, deceleration, etc., and when it is determined that entry into the regenerative braking mode is possible, it closes the fourth valve 2434 to stop the vehicle. The hydraulic pressure of the pressurized medium is blocked from being transmitted to the third wheel cylinder 23 and the fourth wheel cylinder 24, and regenerative braking by the generator can be implemented. Afterwards, if the electronic control unit determines that the vehicle is in a state unsuitable for regenerative braking or that the braking pressure of the first hydraulic circuit 1510 and the braking pressure of the second hydraulic circuit 1520 are different, the fourth valve ( 2434) 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 controlled. You can synchronize. As a result, the braking pressure or braking force applied to the first to fourth wheel cylinders 21, 22, 23, and 24 is uniformly controlled to improve the braking stability of the vehicle and prevent oversteering or understeering. The driving stability of the vehicle can be improved.

Hereinafter, the electronic brake system 3000 according to the third embodiment of the present invention will be described.

In addition, in the description of the electronic brake system 3000 according to the third embodiment of the present invention described below, except for cases where additional description is given using separate reference numerals, the electronic brake system according to the first embodiment of the present invention described above This is the same as the explanation for (1000), so the explanation is omitted to prevent duplication of content.

Figure 13 is a hydraulic circuit diagram showing an electronic brake system 3000 according to a third embodiment of the present invention. Referring to Figure 13, the integrated master cylinder 3200 includes a first simulation chamber 1240a and a second simulation chamber ( It may further include a second simulation flow path 3270 connecting 1230a). However, the second simulation flow path 3270 is not limited to this and may be provided to connect the first simulation flow path 1260 and the first reservoir flow path 1720. Specifically, the second simulation flow path 3270 has one end 1 It is connected between the first simulator valve 1261 of the simulation flow path 1260 and the integrated master cylinder 3200, and the other end is between the reservoir valve 3711 of the first reservoir flow path 1260 and the integrated master cylinder 3200. can be connected

A second simulator valve 3271, which is a two-way control valve that controls the flow of braking fluid delivered through the second simulation passage 3270, may be provided in the second simulation passage 3270. The second simulator valve 3271 may be provided as a normally open type solenoid valve that is normally open and operates to close when receiving an electrical signal from the electronic control unit. Additionally, the second simulator valve 3271 may be closed in the normal operation mode and inspection mode of the electronic brake system 3000.

A reservoir valve 3711, which is a two-way control valve that controls the flow of braking fluid delivered through the first reservoir passage 1710, may be provided in the first reservoir passage 1710. The reservoir valve 3711 may be provided as a normally closed type solenoid valve that is normally closed and operates to open the valve when it receives an electrical signal from the electronic control unit. Accordingly, the reservoir valve 3711 may be closed in the normal operating mode, contrary to the reservoir valve 1711 of the electronic brake system 1000 according to the first embodiment of the present invention.

Therefore, in the electronic brake system 3000 according to the third embodiment of the present invention, when the second simulation piston 1230 advances when operating in an abnormal operation mode (fallback mode), the pressure contained in the second simulation chamber 1230a The medium is delivered to the first simulation chamber (1240a) through the second simulation flow path (3270), but since the reservoir valve (3711) is maintained in a closed state, the pressurized medium contained in the second simulation chamber (1230a) flows into the reservoir (1100). Block transmission. Accordingly, the pressurized medium contained in the second simulation chamber 1230a can also be provided to the first and second wheel cylinders 21 and 22 through the first backup passage 1610, improving braking stability and enabling rapid braking. It can be promoted. A detailed description of this will be provided later in FIG. 14.

As described above, the description of the same operation as the electronic brake system 1000 according to the first embodiment of the present invention is omitted to prevent duplication of content, and the electronic brake system 3000 according to the third embodiment of the present invention is omitted. ) will only describe the pedal simulation operation of the integrated master cylinder 1200 in the normal operating mode.

Describing the pedal simulation operation by the integrated master cylinder 1200, in the normal operating mode (braking and releasing brakes), the driver operates the brake pedal 10 and simultaneously operates the first cut valve 1611 and the second cut valve 1611. (1621), the reservoir valve 3711 and the second simulator valve 3271 are closed and the second simulation chamber (1230a), the first master chamber (1220a), and the second master chamber (1220b) are sealed, and the second simulation chamber (1230a) is closed. The piston 1230 cannot generate displacement. Accordingly, the displacement of the first simulation piston 1240 compresses the elastic member 1250, and the elastic restoring force due to compression of the elastic member 1250 is provided to the driver as a pedal feeling, and the first simulation chamber 1240a The pressurized medium contained in is delivered to the reservoir 1100 through the first simulation flow path 1260. Afterwards, when the driver releases the pedal force of the brake pedal 10, the elastic member 1250 returns to its original shape and position by elastic restoring force, and the first simulation chamber 1240a is a reservoir through the first simulation flow path 1260. Pressurized medium may be supplied from 1100 or may be filled with pressurized medium supplied from the first hydraulic circuit 1510 through the first backup passage 1610.

Hereinafter, the operating state in fall-back mode, that is, when the electronic brake system 3000 according to the third embodiment of the present invention does not operate normally, will be described.

Figure 14 is a hydraulic circuit diagram showing an operating state in an abnormal operation mode (fallback mode) when the electronic brake system 3000 according to the third embodiment of the present invention is unable to operate normally due to device failure.

Referring to FIG. 14, in the abnormal operation mode, each valve is controlled to the initial braking state, which is a non-operating state. At this time, when the driver applies pedal force to the brake pedal 10, the first simulation piston 1240 connected to the brake pedal 10 moves forward and displacement occurs. Since the first simulator valve 1261 is closed and the first cut valve 1611 remains open, the pressurized medium accommodated in the first simulation chamber 1240a by the advance of the first simulation piston 1240 is 1 It is transmitted to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510 along the 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 the elastic member 1250 is not compressed and the second simulation piston 1230 is not compressed. Moving forward causes displacement. At this time, the reservoir valve 3711 is maintained in a closed state and the second simulator valve 3271 is maintained in an open state, so that the The pressurized medium is delivered to the first simulation chamber (1240a) through the second simulation passage 3270, and as described above, the first and second wheels of the first hydraulic circuit 1510 along the first backup passage 1610. It can be transmitted to the cylinders 21 and 22 to implement braking.

At the same time, when displacement occurs by advancing the second simulation piston 1230, the first cut valve 1611 remains open, so the pressurized medium contained in the first master chamber 1220a flows through the auxiliary backup passage 1630. and sequentially through the first backup passage 1610 to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510, thereby implementing braking. On the other hand, 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 blocking the connection between the first master chamber 1220a and the second reservoir flow path 1720. Prevents the pressurized medium contained in the master chamber 1220a from being transferred to the reservoir 1100.

In addition, when the second simulation piston 1230 advances, the pressurized medium in the first master chamber 1220a advances the master piston 1220 to generate displacement, and the second cut valve 1621 is opened. Since it is maintained, the pressurized medium contained in the second master chamber (1220b) is delivered to the third wheel cylinder (23) and fourth wheel cylinder (24) of the second hydraulic circuit (1520) along the second backup passage (1620) to perform braking. can be implemented. 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 passage 1730 as the master piston 1220 advances, so that the pressurized medium flows into the reservoir ( 1100).

In an abnormal operating mode, the first cut valve 1611, the second cut valve 1621, and the second simulator valve 3271 are in an open state, and the reservoir valve 3711 and the first simulator valve 1261 are in a closed state. Therefore, the first simulation chamber 1240a and the second simulation chamber 1230a, the first master chamber 1220a, and the second master chamber 1220b of the integrated master cylinder 1200, that is, all chambers of the integrated master cylinder 1200 Since the hydraulic pressure transmitted from can be directly transmitted to each wheel cylinder 20, braking stability can be improved and more rapid braking can be achieved.

Hereinafter, the inspection mode of the electronic brake system 3000 according to the third embodiment of the present invention will be described.

An inspection mode can be performed to check whether the master cylinder 1200 integrated with the electronic brake system 3000 according to the third embodiment of the present invention is leaking. FIG. 15 is a hydraulic circuit diagram showing the inspection mode state of the electronic brake system 3000 according to the third embodiment of the present invention. Referring to FIG. 15, when performing the inspection mode, the electronic control unit uses the hydraulic pressure generated from the hydraulic supply device 1300. The hydraulic pressure is controlled to be supplied to the first simulation chamber 1240a of the integrated master cylinder 1200.

As described above, the description of the same operation as the electronic brake system 1000 according to the first embodiment of the present invention is omitted to prevent duplication of content, and the electronic brake system 3000 according to the third embodiment of the present invention is omitted. ), only the operation of the additional second simulation valve (3751) in the inspection mode is explained.

Specifically, the electronic control unit operates to advance the hydraulic piston 1320 in a state in which each valve is controlled to the initial braking state in which the valves are in a non-operated state, thereby generating hydraulic pressure in the first pressure chamber 1330 and simultaneously 2 Control the cut valve (1621) to the closed state. The hydraulic pressure formed in the first pressure chamber 1330 sequentially passes through the first hydraulic passage 1401, the third hydraulic passage 1403, and the fourth hydraulic passage 1404 and is transmitted to the first hydraulic circuit 1510, The pressurized medium delivered to the first hydraulic circuit 1510 opens at least a portion of the first cut valve 1611 and is delivered to the first simulation chamber 1240a through the first backup passage 1610.

At this time, the first simulator valve 1261 is maintained in a closed state, and the second simulator valve 3271 is additionally controlled to be closed so that the first simulation chamber 1240a and the second simulation chamber 1230a are in communication. prevents this and seals the first simulation chamber (1240a).

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

In this state, the hydraulic pressure value of the pressurized medium expected to be generated due to the displacement of the hydraulic piston 1320 is compared with the hydraulic pressure value of the first simulation chamber (1240a) or the first hydraulic circuit (1510) measured by the pressure sensor (PS). By doing so, leaks in the integrated master cylinder 1200 or the simulator valve 1261 can be diagnosed. Specifically, the expected hydraulic pressure value calculated based on the displacement of the hydraulic piston 1320 or the rotation angle measured by the motor control sensor (not shown), and the actual first simulation chamber 1240a measured by the pressure sensor (PS) or By comparing the hydraulic pressure values of the first hydraulic circuit 1510, if the two hydraulic values match, it can be determined that there is no leak in the integrated master cylinder 1200 or the first simulator valve 1261. In contrast, the actual first simulation chamber 1240a or 1 If the hydraulic pressure level of the hydraulic circuit 1510 is low, some of the hydraulic pressure of the pressurized medium applied to the first simulation chamber 1240a is lost, so it is assumed that a leak exists in the integrated master cylinder 1200 or the first simulator valve 1261. It can make a decision and inform the driver of this decision.

Above, the present invention has been described with reference to an embodiment shown in the attached drawings, but this is merely illustrative, and various modifications and other equivalent embodiments can be made by those skilled in the art. You will be able to understand. Therefore, the true scope of the present invention should be determined only by the appended claims.

1000, 2000, 3000: 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: first simulation flow path
1261: first simulator valve 1300: hydraulic pressure supply device
1320: Hydraulic piston 1330: First pressure chamber
1340: second pressure chamber 1400: hydraulic control unit
1401: first hydraulic oil passage 1402: second hydraulic oil passage
1403: Third hydraulic oil passage 1404: Fourth hydraulic oil passage
1405: Fifth hydraulic oil passage 1406: Sixth hydraulic oil passage
1407: 7th hydraulic oil path 1408: 8th hydraulic oil path
1409: 9th hydraulic oil passage 1410: 10th hydraulic oil passage
1431: first valve 1432: second valve
1433: third valve 1434: fourth valve
1435: 5th valve 1436: 6th valve
1437: 7th valve 1438: 8th valve
1510: 1st hydraulic circuit 1520: 2nd 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: 1st reservoir euro 1720: 2nd reservoir euro
1730: Third reservoir Euro 1800: Dump control unit
1810: 1st dump flow path 1811: 1st dump check valve
1820: 2nd dump flow path 1821: 2nd dump check valve
1830: 1st bypass flow path 1831: 1st dump valve
1840: 2nd bypass flow path 1841: 2nd dump valve
2434: fourth valve 3270: second simulation flow path
3271: Second simulator valve

Claims (28)

A reservoir in which the pressurized medium is stored;
A first simulation chamber and a second simulation chamber, a first master chamber and a second master chamber having a smaller diameter than the second simulation chamber, and the first simulation chamber is provided to be pressurized and can be displaced by a brake pedal. A first simulation piston provided to pressurize the second simulation chamber and the first master chamber and a second simulation piston provided to be capable of being displaced by displacement of the first simulation piston or hydraulic pressure of the first simulation chamber A simulation piston, a master piston provided to pressurize the second master chamber and displaceable by displacement of the second simulation piston or hydraulic pressure of the first master chamber, the first simulation piston and the second An integrated master including an elastic member provided between simulation pistons, a first simulation passage connecting the first simulation chamber and the reservoir, and a first simulator valve provided in the first simulation passage to control the flow of pressurized medium. cylinder;
a reservoir passage connecting the integrated master cylinder and the reservoir;
The hydraulic piston is operated by an electrical signal output in response to the displacement of the brake pedal to generate hydraulic pressure, and a first pressure is provided on one side of the hydraulic piston movably accommodated inside the cylinder block 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 including a first hydraulic circuit that controls hydraulic pressure delivered to two wheel cylinders and a second hydraulic circuit that controls hydraulic pressure delivered to the other two wheel cylinders; and
It includes an electronic control unit that controls the valves based on hydraulic pressure information and displacement information of the brake pedal,
The hydraulic control unit is
A first hydraulic passage in communication with the first pressure chamber, a second hydraulic passage in communication with the second pressure chamber, a third hydraulic passage in which the first hydraulic passage and the second hydraulic passage merge, and the first hydraulic passage in communication with the second pressure chamber. 3 A fourth hydraulic passage branched from the hydraulic passage and connected to the first hydraulic circuit, a fifth hydraulic passage branched from the third hydraulic passage and connected to the second hydraulic circuit, and a fifth hydraulic passage connected to the first hydraulic circuit. A sixth hydraulic passage, a seventh hydraulic passage in communication with the second hydraulic circuit, an eighth hydraulic passage where the sixth hydraulic passage and the seventh hydraulic passage join, and a branch from the eighth hydraulic passage to the seventh hydraulic passage. 1. An electronic brake system including a ninth hydraulic passage connected to the pressure chamber, and a tenth hydraulic passage branched from the eighth hydraulic passage and connected to the second pressure chamber. A reservoir in which the pressurized medium is stored;
An integrated master cylinder including a master chamber and a simulation chamber that provides reaction force to the driver according to the pedal pressure and simultaneously pressurizes and discharges the pressurized medium contained inside;
a reservoir passage connecting the integrated master cylinder and the reservoir;
The hydraulic piston is operated by an electrical signal output in response to the displacement of the brake pedal to generate hydraulic pressure, and a first pressure is provided on one side of the hydraulic piston movably accommodated inside the cylinder block 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 including a first hydraulic circuit that controls hydraulic pressure delivered to two wheel cylinders and a second hydraulic circuit that controls hydraulic pressure delivered to the other two wheel cylinders; and
It includes an electronic control unit that controls the valves based on hydraulic pressure information and displacement information of the brake pedal,
The hydraulic control unit is
A first hydraulic passage in communication with the first pressure chamber, a second hydraulic passage in communication with the second pressure chamber, a third hydraulic passage in which the first hydraulic passage and the second hydraulic passage merge, and the first hydraulic passage in communication with the second pressure chamber. 3 A fourth hydraulic passage branched from the hydraulic passage and connected to the first hydraulic circuit, a fifth hydraulic passage branched from the third hydraulic passage and connected to the second hydraulic circuit, and a fifth hydraulic passage connected to the first hydraulic circuit. A sixth hydraulic passage, a seventh hydraulic passage in communication with the second hydraulic circuit, an eighth hydraulic passage where the sixth hydraulic passage and the seventh hydraulic passage join, and a branch from the eighth hydraulic passage to the seventh hydraulic passage. 1. An electronic brake system including a ninth hydraulic passage connected to the pressure chamber and a tenth hydraulic passage branched from the eighth hydraulic passage and connected to the second pressure chamber. According to claim 1 or 2,
The hydraulic control unit is
A first valve provided in the first hydraulic passage to control the flow of the pressurized medium, a second valve provided in the second hydraulic passage to control the flow of the pressurized medium, and a second valve provided in the fourth hydraulic passage to control the flow of the pressurized medium. A third valve for controlling, a fourth valve provided in the fifth hydraulic passage to control the flow of pressurized medium, a fifth valve provided in the sixth hydraulic passage to control the flow of pressurized medium, and the seventh hydraulic passage A sixth valve provided in the 9th hydraulic passage to control the flow of the pressurized medium, a 7th valve provided in the 9th hydraulic passage to control the flow of the pressurized medium, and an 8th valve provided in the 10th hydraulic passage to control the flow of the pressurized medium Electronic braking system including. According to paragraph 3,
The first valve is provided as a check valve that allows only the flow of pressurized medium discharged from the first pressure chamber,
The second valve is provided as a check valve that only allows the flow of pressurized medium discharged from the second pressure chamber,
The third valve is provided as a check valve that only allows the flow of pressurized medium from the third hydraulic passage to the first hydraulic circuit,
The fourth valve is provided as a check valve that only allows the flow of pressurized medium from the third hydraulic passage to the second hydraulic circuit,
The fifth valve is provided as a check valve that allows only the flow of pressurized medium discharged from the first hydraulic circuit,
The sixth valve is provided as a check valve that allows only the flow of pressurized medium discharged from the second hydraulic circuit,
The seventh valve and the eighth valve are solenoid valves that control the two-way flow of pressurized medium. According to paragraph 4,
It further includes a dump control unit provided between the reservoir and the hydraulic pressure supply device to control the flow of pressurized medium,
The dump control unit
A first dump passage connecting the first pressure chamber and the reservoir, a first dump check valve provided in the first dump passage to allow only the flow of pressurized medium from the reservoir to the first pressure chamber, and the first dump check valve 1 A first bypass passage connected in parallel to the first dump check valve on the dump passage, a first dump valve provided in the first bypass passage to control the two-way flow of the pressurized medium, and the second pressure A second dump passage connecting the chamber and the reservoir, a second dump check valve provided in the second dump passage and allowing only the flow of pressurized medium from the reservoir to the second pressure chamber, and on the second dump passage An electronic brake system comprising a second bypass passage connected in parallel to the second dump check valve and a second dump valve provided in the second bypass passage to control bidirectional flow of pressurized medium. According to paragraph 2,
The simulation chamber is
Comprising a first simulation chamber and a second simulation chamber,
The master chamber is
It includes a first master chamber and a second master chamber having a smaller diameter than the second simulation chamber,
The integrated master cylinder is
A first simulation piston provided to pressurize the first simulation chamber and displaceable by a brake pedal, and a displacement of the first simulation piston provided to pressurize the second simulation chamber and the first master chamber. Or, a second simulation piston that is provided to be capable of being displaced by the hydraulic pressure of the first simulation chamber, and a second simulation piston that is provided to be capable of pressing the second master chamber and is displaced by the displacement of the second simulation piston or the hydraulic pressure of the first master chamber. A master piston that can be provided, an elastic member provided between the first simulation piston and the second simulation piston, a simulation passage connecting the first simulation chamber and the reservoir, and a pressure medium provided in the simulation passage. Electronic braking system with simulator valve to control flow. According to claim 1 or 6,
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;
an auxiliary backup passage connecting the first master chamber and the first backup passage;
At least one first cut valve provided in the first backup passage to control the flow of pressurized medium; and
The electronic brake system further includes at least one second cut valve provided in the second backup passage to control the flow of pressurized medium. In clause 7,
The reservoir euro is
A first reservoir flow path including a reservoir valve that communicates the reservoir and the second simulation chamber and controls the flow of pressurized medium, a second reservoir flow path that communicates the reservoir and the first master chamber, and the reservoir and the An electronic brake system including a third reservoir passage communicating with the second master chamber. According to clause 8,
The first hydraulic circuit is
It includes a first inlet valve and a second inlet valve that respectively control the flow of pressurized medium supplied to the first wheel cylinder and the second wheel cylinder,
The second hydraulic circuit is
An electronic brake system including a third inlet valve and a fourth inlet valve that respectively control the flow of pressurized medium supplied to the third wheel cylinder and the fourth wheel cylinder. According to paragraph 3,
The first valve is provided as a check valve that allows only the flow of pressurized medium discharged from the first pressure chamber,
The second valve is provided as a check valve that only allows the flow of pressurized medium discharged from the second pressure chamber,
The third valve is provided as a check valve that only allows the flow of pressurized medium from the third hydraulic passage to the first hydraulic circuit,
The fifth valve is provided as a check valve that allows only the flow of pressurized medium discharged from the first hydraulic circuit,
The sixth valve is provided as a check valve that allows only the flow of pressurized medium discharged from the second hydraulic circuit,
The fourth valve, the seventh valve, and the eighth valve are solenoid valves that control the two-way flow of pressurized medium. According to clause 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,
An electronic brake system further comprising a generator provided in each of the third wheel cylinder and the fourth wheel cylinder. In clause 7,
The integrated master cylinder is
Further comprising a second simulation flow path connecting the first simulation chamber and the second simulation chamber,
The second simulation flow path is
An electronic brake system including a second simulator valve that controls the flow of pressurized medium. In the method of operating the electronic brake system according to claim 5,
As the hydraulic pressure delivered from the hydraulic pressure supply device to the wheel cylinder gradually increases, a first braking mode that primarily provides hydraulic pressure and a second braking mode that secondarily provides hydraulic pressure by reversing the hydraulic piston. And, a method of operating an electronic brake system including a third braking mode that provides hydraulic pressure thirdly by advancing the hydraulic piston after the second braking mode. According to clause 13,
The first braking mode is
The eighth valve and the first dump valve are closed,
The hydraulic pressure formed in the first pressure chamber by the advancement of the hydraulic piston is provided to the first hydraulic circuit through the first hydraulic oil passage, the third hydraulic oil passage, and the fourth hydraulic oil passage sequentially, and the first hydraulic oil A method of operating an electronic brake system provided to the second hydraulic circuit through the furnace, the third hydraulic passage, and the fifth hydraulic passage sequentially. According to clause 14,
The second braking mode is
The seventh valve and the second dump valve are closed,
After the first braking mode, the hydraulic pressure formed in the second pressure chamber by the backward movement of the hydraulic piston is sequentially supplied to the first hydraulic circuit through the second hydraulic passage, the third hydraulic passage, and the fourth hydraulic passage. and is provided to the second hydraulic circuit through the second hydraulic passage, the third hydraulic passage, and the fifth hydraulic passage sequentially. According to clause 15,
The third braking mode is
The seventh valve and the eighth valve are opened, the first dump valve and the second dump valve are closed,
A portion of the hydraulic pressure formed in the first pressure chamber by the advancement of the hydraulic piston is provided to the first hydraulic circuit through the first hydraulic oil passage, the third hydraulic oil passage, and the fourth hydraulic oil passage sequentially, and the first hydraulic circuit is supplied to the first hydraulic circuit. It is provided to the second hydraulic circuit through the first hydraulic oil passage, the third hydraulic oil passage, and the fifth hydraulic oil passage sequentially,
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 ninth hydraulic passage and the tenth hydraulic passage sequentially. According to clause 14,
Release of the first braking mode is
The seventh valve and the second dump valve are opened, but the eighth valve and the first dump valve are closed,
Negative pressure is formed in the first pressure chamber by the backward movement of the hydraulic piston, so that the pressurized medium provided in the first hydraulic circuit sequentially passes through the sixth hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage. An electronic brake system in which the pressurized medium provided to the second hydraulic circuit is recovered to the first pressure chamber through the seventh hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage sequentially. How it works. According to clause 15,
Canceling the second braking mode is
The eighth valve and the first dump valve are opened, but the seventh valve and the second dump valve are closed,
Negative pressure is formed in the second pressure chamber by the advancement of the hydraulic piston, and the pressurized medium provided in the first hydraulic circuit sequentially passes through the sixth hydraulic passage, the eighth hydraulic passage, and the tenth hydraulic passage. An electronic brake system in which the pressurized medium provided to the second hydraulic circuit is recovered to the second pressure chamber through the seventh hydraulic passage, the eighth hydraulic passage, and the tenth hydraulic passage sequentially. How it works. According to clause 16,
Canceling the third braking mode is
The seventh valve and the eighth valve are opened, but the first dump valve is closed,
Negative pressure is formed in the first pressure chamber by the backward movement of the hydraulic piston, and the pressurized medium provided in the first hydraulic circuit sequentially passes through the sixth hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage. The pressurized medium provided to the second hydraulic circuit is recovered to the first pressure chamber and sequentially passes through the seventh hydraulic passage, the eighth hydraulic passage, and the ninth hydraulic passage and is recovered to the first pressure chamber,
A method of operating an electronic brake system in which at least a portion of the pressurized medium in the second pressure chamber is supplied to the first pressure chamber through the tenth hydraulic passage and the ninth hydraulic passage sequentially. In the method of operating the electronic brake system according to claim 11,
In regenerative braking mode by the generator,
The hydraulic pressure formed in the first pressure chamber by the advancement of the hydraulic piston is provided to the first hydraulic circuit through the first hydraulic passage, the third hydraulic passage, and the fourth hydraulic passage sequentially, and the fourth valve. A method of operating an electronic brake system that blocks provision of hydraulic pressure to the third wheel cylinder and the fourth wheel cylinder by closing the.

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