Electronic brake system

Abstract

This invention discloses an electronic braking system. The electronic braking system according to this embodiment may include: a reservoir storing a pressurized medium; an integrated master cylinder having a master piston connected to the brake pedal, a main chamber whose volume changes according to the displacement of the master piston, and a sealing component sealing the main chamber; a hydraulic supply device that operates a hydraulic piston to generate hydraulic pressure according to an electrical signal output corresponding to the displacement of the brake pedal; a hydraulic control unit disposed between the hydraulic supply device and a plurality of wheel cylinders, and controlling the flow of the pressurized medium supplied to the plurality of wheel cylinders; a loop pressure sensor that senses the hydraulic pressure supplied through the hydraulic supply device; a cylinder pressure sensor that senses the hydraulic pressure in the main chamber; a check flow path connecting the main chamber and the hydraulic supply device; and a check valve disposed in the check flow path to control the flow of the pressurized medium.

Description

Technical Field

[0001] The present invention relates to an electronic braking system, and more specifically, to an electronic braking system that generates braking force using an electrical signal corresponding to the displacement of the brake pedal. Background Technology

[0002] Vehicles must be equipped with braking systems to perform braking, and various types of braking systems have been proposed for the safety of drivers and passengers.

[0003] Traditional braking systems primarily use a mechanically connected booster to supply the hydraulic pressure required for braking to the wheel cylinders when the driver depresses the brake pedal. However, with the increasing market demand for various braking functions to precisely respond to different vehicle operating environments, electronic braking systems are becoming increasingly popular. These systems receive electrical signals from a pedal displacement sensor that senses the driver's braking intention when the brake pedal is depressed, and then operate a hydraulic supply device based on these signals to supply the necessary hydraulic pressure to the wheel cylinders.

[0004] As described above, the electronic braking system generates and provides electrical signals for the driver's brake pedal operation in normal operating mode or for braking judgment during autonomous driving, thereby electrically operating and controlling the hydraulic supply device to generate the hydraulic pressure required for braking and transmit it to the wheel cylinders. As mentioned above, this electronic braking system and operating method can be electrically operated and controlled, and can achieve a variety of complex braking actions. However, when technical problems occur in the electrical components, the hydraulic pressure required for braking cannot be stably generated, which may pose a risk to passenger safety.

[0005] Therefore, in an electronic braking system, when a component malfunctions or becomes uncontrollable, it enters an abnormal operating mode. In this mode, the driver's brake pedal operation needs to be directly linked to the wheel cylinder mechanism. That is, in the abnormal operating mode of the electronic braking system, as the driver applies force to the brake pedal, the hydraulic pressure required for braking should be immediately generated and directly transmitted to the wheel cylinders. Furthermore, a solution is needed to accurately and quickly check for malfunctions in the electronic braking system, enabling rapid entry into the abnormal operating mode in emergencies to ensure passenger safety. Summary of the Invention

[0006] (a) Technical problems to be solved

[0007] This embodiment aims to provide an electronic braking system that can effectively achieve braking in various application situations.

[0008] This embodiment aims to provide an electronic braking system that can quickly determine whether a malfunction is present through a simple structure and operation.

[0009] This embodiment aims to provide an electronic braking system that improves braking performance and operational reliability.

[0010] This embodiment aims to provide an electronic braking system that reduces the load applied to components to improve product durability.

[0011] (II) Technical Solution

[0012] According to one aspect of the present invention, an electronic braking system may be provided, comprising: a reservoir storing a pressurized medium; an integrated master cylinder having a master piston connected to a brake pedal, a main chamber whose volume changes according to the displacement of the master piston, and a sealing member sealing the main chamber; a hydraulic supply device that operates a hydraulic piston to generate hydraulic pressure according to an electrical signal output corresponding to the displacement of the brake pedal; a hydraulic control unit disposed between the hydraulic supply device and a plurality of wheel cylinders, and controlling the flow of the pressurized medium supplied to the plurality of wheel cylinders; a loop pressure sensor that senses the hydraulic pressure supplied through the hydraulic supply device; a cylinder pressure sensor that senses the hydraulic pressure in the main chamber; a check flow path connecting the main chamber and the hydraulic supply device; and a check valve disposed in the check flow path to control the flow of the pressurized medium.

[0013] The integrated master cylinder may include: a first master piston connected to the brake pedal; and a first main chamber whose volume changes according to the displacement of the first master piston. One end of the inspection flow path may be connected to the hydraulic supply device side, and the other end may branch into a first branch flow path and a second branch flow path, which are respectively connected to the first main chamber. The inspection valve may be provided in the first branch flow path, and the second branch flow path may be provided with an inspection check valve that only allows the flow of pressurized medium from the first main chamber to the hydraulic supply device.

[0014] The hydraulic supply device may include a first pressure chamber located in front of the hydraulic piston and a second pressure chamber located behind the hydraulic piston, and one end of the inspection flow path may be connected to the second pressure chamber.

[0015] The electronic braking system may further include: a discharge control unit disposed between the reservoir and the hydraulic supply device to control the flow of the pressurized medium. The discharge control unit may include a first discharge control unit that controls the flow of the pressurized medium between the first pressure chamber and the reservoir, and a second discharge control unit that controls the flow of the pressurized medium between the second pressure chamber and the reservoir.

[0016] The integrated master cylinder may further include: a second master piston configured to be displaced according to the displacement of the first master piston; and a second master chamber whose volume changes according to the displacement of the second master piston, wherein the cylinder pressure sensor can sense the hydraulic pressure of the second master chamber.

[0017] The integrated master cylinder may further include: a first sealing component that seals the first main chamber relative to the outside; a second sealing component that seals the first main chamber relative to the second main chamber; and a third sealing component that blocks the flow of pressurized medium from the first branch flow path into the first main chamber.

[0018] The first sealing component may be disposed on the rear side of the third sealing component, and the second branch flow path may be connected between the first sealing component and the third sealing component of the integrated master cylinder.

[0019] The first main piston may include: a first shut-off orifice, which connects the first main chamber and the second branch flow path in the non-operating state.

[0020] The electronic braking system may further include: a first reservoir flow path connecting the reservoir and the first main chamber; and a simulator valve disposed in the first reservoir flow path to control the flow of the pressurized medium between the reservoir and the first main chamber.

[0021] The hydraulic control unit may include: a first hydraulic circuit for controlling the flow of pressurized medium supplied to the first and second wheel cylinders; and a second hydraulic circuit for controlling the flow of pressurized medium supplied to the third and fourth wheel cylinders. The electronic braking system may further include: a first backup flow path connecting the first main chamber and the first hydraulic circuit; and a second backup flow path connecting the second main chamber and the second hydraulic circuit.

[0022] The electronic braking system may further include: a first shut-off valve disposed in the first backup flow path to control the flow of the pressurized medium; and a second shut-off valve disposed in the second backup flow path to control the flow of the pressurized medium.

[0023] The integrated master cylinder may further include: a pedal simulator disposed between the first master piston and the second master piston to provide pedal feel through the elastic restoring force generated during compression.

[0024] The electronic braking system may further include: a second reservoir flow path connecting the reservoir and the second main chamber; the integrated master cylinder may further include: a fourth sealing component blocking the flow of pressurized medium discharged from the second main chamber to the second reservoir flow path.

[0025] The second main piston may include a second shut-off orifice, which connects the second main chamber and the flow path of the second reservoir in the non-operating state.

[0026] The hydraulic control unit may include: a first hydraulic circuit for controlling the flow of pressurized medium supplied to the first and second wheel cylinders; and a second hydraulic circuit for controlling the flow of pressurized medium supplied to the third and fourth wheel cylinders, wherein the third and fourth wheel cylinders may each be equipped with a generator. The hydraulic control unit may further include: a solenoid valve for blocking the transmission of hydraulic pressure of the pressurized medium to the third and fourth wheel cylinders in regenerative braking mode.

[0027] (III) Beneficial Effects

[0028] The electronic braking system according to this embodiment can achieve stable and effective braking in various application conditions of the vehicle.

[0029] The electronic braking system according to this embodiment can quickly and accurately determine whether the device is malfunctioning through a simple structure and operation, thereby ensuring passenger safety.

[0030] The electronic braking system according to this embodiment can improve braking performance and operational reliability.

[0031] The electronic braking system according to this embodiment can stably provide braking pressure even when components fail or the pressurized medium leaks.

[0032] The electronic braking system according to this embodiment has the effect of reducing the load applied to the components to improve the durability of the product. Attached Figure Description

[0033] Figure 1 This is a hydraulic circuit diagram illustrating an electronic braking system according to a first embodiment of the present invention.

[0034] Figure 2 This is a hydraulic circuit diagram showing the state of the electronic braking system performing a first check mode according to a first embodiment of the present invention.

[0035] Figure 3 This is a hydraulic circuit diagram showing the state of the electronic braking system performing the second inspection mode according to a first embodiment of the present invention.

[0036] Figure 4 This is a hydraulic circuit diagram showing the state of the electronic braking system according to a first embodiment of the present invention executing a first braking mode.

[0037] Figure 5 This is a hydraulic circuit diagram showing the state of the electronic braking system executing the second braking mode according to a first embodiment of the present invention.

[0038] Figure 6 This is a hydraulic circuit diagram showing the state of the electronic braking system executing the third braking mode according to the first embodiment of the present invention.

[0039] Figure 7 This is a hydraulic circuit diagram showing the state of the electronic braking system according to the first embodiment of the present invention performing an abnormal operation mode (standby mode).

[0040] Figure 8 This is a hydraulic circuit diagram illustrating an electronic braking system according to a second embodiment of the present invention.

[0041] Figure 9 This is a hydraulic circuit diagram illustrating an electronic braking system according to a third embodiment of the present invention. Detailed Implementation

[0042] Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. These embodiments are provided to fully convey the spirit of the invention to those skilled in the art. The invention is not limited to the embodiments described below and can be embodied in other forms. In the drawings, for clarity of illustration, parts unrelated to the description may be omitted, and for aid of understanding, the dimensions of components may be enlarged.

[0043] Figure 1 This is a hydraulic circuit diagram showing an electronic braking system 1000 according to a first embodiment of the present invention.

[0044] Reference Figure 1The electronic braking system 1000 according to a first embodiment of the present invention includes: a reservoir 1100 storing a pressurized medium; an integrated master cylinder 1200 providing the driver with a reaction force based on the pedal force of the brake pedal 10, while simultaneously pressurizing and discharging the pressurized medium, such as brake fluid, contained within it; a hydraulic supply device 1300 receiving an electrical signal representing the driver's braking intention via a pedal displacement sensor that senses the displacement of the brake pedal 10, and generating hydraulic pressure for the pressurized medium through mechanical operation; a hydraulic control unit 1400 controlling the hydraulic pressure supplied from the hydraulic supply device 1300; and hydraulic circuits 1510 and 1520, each equipped with a wheel cylinder 20, through which the hydraulic pressure of the pressurized medium is transmitted to... The wheel cylinders, which perform braking for each wheel (RR, RL, FR, FL); a dump control unit 1800, located between the hydraulic supply unit 1300 and the reservoir 1100, controls the flow of the pressurized medium; backup flow paths 1610 and 1620, hydraulically connected to the integrated master cylinder 1200 and hydraulic circuits 1510 and 1520; a reservoir flow path 1700, hydraulically connected to the reservoir 1100 and the integrated master cylinder 1200; a check flow path 1900, connected to the main chamber of the integrated master cylinder 1200; and an electronic control unit (ECU, not shown) that controls the hydraulic supply unit 1300 and various valves based on hydraulic information and pedal displacement information.

[0045] The integrated master cylinder 1200 is configured to provide a reaction force to the driver when the driver applies pedal force to the brake pedal 10 for braking operation, thereby providing a stable pedal feel, while pressurizing and discharging the pressurized medium contained inside according to the operation of the brake pedal 10.

[0046] In the integrated master cylinder 1200, the analog part that provides pedal feel to the driver and the master cylinder part that pressurizes and discharges the pressurized medium contained inside according to the pedal force of the brake pedal can be arranged coaxially in a cylinder body 1210.

[0047] Specifically, the integrated master cylinder 1200 may include: a cylinder body 1210, with a chamber formed on its inner side; a first main chamber 1220a, formed on the inlet side of the cylinder body 1210 connected to the brake pedal 10; a first master piston 1220, disposed in the first main chamber 1220a and configured to be connected to the brake pedal 10 for displacement according to the operation of the brake pedal 10; and a second main chamber 1230a, formed on the inner or front side of the first main chamber 1220a in the cylinder body 1210 (to...). Figure 1(Left side as reference); second main piston 1230, disposed in second main chamber 1230a and configured to be hydraulically displaceable according to the displacement of first main piston 1220 or the pressurized medium contained in first main chamber 1220a; and pedal simulator 1240, disposed between first main piston 1220 and second main piston 1230, and providing pedal feel by means of elastic restoring force generated during compression.

[0048] The first main chamber 1220a and the second main chamber 1230a can be located in the cylinder body 1210 of the integrated master cylinder 1200 from the brake pedal 10 side (towards). Figure 1 (based on the right side) towards the inside (with) Figure 1 (Based on the left side) are formed sequentially. In addition, the first main piston 1220 and the second main piston 1230 are respectively disposed in the first main chamber 1220a and the second main chamber 1230a, so that hydraulic or negative pressure can be formed on the pressurized medium contained in each chamber according to the forward and backward movement.

[0049] The cylinder block 1210 may include: a large-diameter portion 1211, in which a first main chamber 1220a is formed on its inner side, and the inner diameter is formed to be relatively large; and a small-diameter portion 1212, in which a second main chamber 1230a is formed on its inner side, and the inner diameter is formed to be relatively smaller than the inner diameter of the large-diameter portion 1211. The large-diameter portion 1211 and the small-diameter portion 1212 of the cylinder block 1210 may be integrally formed.

[0050] The first main chamber 1220a can be formed on the inlet side or rear side of the cylinder body 1210 (to...). Figure 1 Inside the large-diameter portion 1211 (with the right side as reference), the first master piston 1220 is reciprocally movably housed in the first main chamber 1220a, and the first master piston 1220 is connected to the brake pedal 10 via the input rod 12.

[0051] The first main chamber 1220a can be supplied with and discharged pressurized medium through the first hydraulic port 1280a, the second hydraulic port 1280b, the third hydraulic port 1280c, and the fourth hydraulic port 1280d. The first hydraulic port 1280a can be connected to the first reservoir flow path 1710 described below, so that pressurized medium flows from the reservoir 1100 into the first main chamber 1220a, or discharges pressurized medium contained in the first main chamber 1220a into the reservoir 1100. The second hydraulic port 1280b can be connected to the first backup flow path 1610 described below, so that pressurized medium is discharged from the first main chamber 1220a to the first backup flow path 1610 side, or conversely, so that pressurized medium flows from the first backup flow path 1610 into the first main chamber 1220a side.

[0052] Additionally, the first main chamber 1220a can be connected to the first branch flow path 1910 and the second branch flow path 1920 of the inspection flow path 1900 described below via the third hydraulic port 1280c and the fourth hydraulic port 1280d, respectively, so that the pressurized medium contained in the first main chamber 1220a can be discharged to the inspection flow path 1900 side, or the pressurized medium can flow from the inspection flow path 1900 into the first main chamber 1220a. This will be described in detail below.

[0053] The first main piston 1220 is housed and disposed in the first main chamber 1220a, and can be moved forward (to... Figure 1 (Based on the left-hand direction) pressurize the pressurized medium contained in the first main chamber 1220a to form hydraulic pressure, or it can be achieved by moving backward (towards) Figure 1 (Based on the right-hand direction) a negative pressure is formed inside the first main chamber 1220a. The first main piston 1220 may include: a first body 1221, formed in a cylindrical shape to fit tightly against the inner circumferential surface of the first main chamber 1220a; and a first flange 1222, at the rear end of the first body 1221 (towards the right-hand direction) to form a negative pressure. Figure 1 The first master piston 1220 is formed radially extending from the right end of the first flange 1222 and connected to the input rod 12. The first master piston 1220 can be elastically supported by a first piston spring 1220b, which can be configured such that one end of the first piston spring 1220b is supported by the front surface of the first flange 1222 (with the first piston spring 1220b being the first piston spring 1220b). Figure 1 The left side of the cylinder is supported by the reference surface, and the other end is supported by the outer surface of the cylinder block 1210.

[0054] The first main piston 1220 is provided with a first cut-off hole 1220d. This first cut-off hole connects to the first main chamber 1220a and, in a non-operating state (i.e., a preparatory state before displacement), connects to the fourth hydraulic port 1280d and the second branch flow path 1920. Additionally, a first sealing member 1290a can be provided between the outer peripheral surface of the first main piston 1220 and the cylinder body 1210 to seal the first main chamber 1220a from the outside. The first sealing member 1290a can be configured to be disposed in a receiving groove recessed into the inner peripheral surface of the cylinder body 1210, so as to contact the outer peripheral surface of the first main piston 1220. Through the first sealing member 1290a, the pressurized medium contained in the first main chamber 1220a is prevented from leaking to the outside, while external impurities are prevented from flowing into the first main chamber 1220a. The first sealing component 1290a can be disposed on the outermost side of the inner circumferential surface of the cylinder body 1210, that is, on the rear side of the fourth hydraulic port 1280d connected to the second branch flow path 1920 described below (to... Figure 1 (Based on the right side).

[0055] A third sealing member 1290c may be provided between the outer peripheral surface of the first main piston 1220 and the cylinder body 1210. The third sealing member 1290c blocks the flow of pressurized medium from the first branch flow path 1910 connected to the third hydraulic port 1280c into the first main chamber 1220a. The third sealing member 1290c may be respectively disposed on the inner peripheral surface of the cylinder body 1210 in a pair of receiving grooves respectively recessed in front of and behind the third hydraulic port 1280c, so as to contact the outer peripheral surface of the first main piston 1220. A pair of third sealing members 1290c may be disposed in front of the first sealing member 1290a (towards...). Figure 1 (Based on the left side), it can allow the pressurized medium contained in the first main chamber 1220a to flow through the third hydraulic port 1280c to the first branch flow path 1910, and can block the flow of pressurized medium flowing from the first branch flow path 1910 into the first main chamber 1220a.

[0056] The second main chamber 1230a may be formed on the inner or front side of the cylinder body 1210 (i.e., ...). Figure 1 Inside the small-diameter portion 1212 (with the left side as the reference), the second main piston 1230 is reciprocally accommodated in the second main chamber 1230a.

[0057] The second main chamber 1230a can be supplied with and discharged pressurized medium via the fifth hydraulic port 1280e and the sixth hydraulic port 1280f. The fifth hydraulic port 1280e can be connected to the second reservoir flow path 1720 described below, so that the pressurized medium contained in the reservoir 1100 flows into the second main chamber 1230a. In addition, the sixth hydraulic port 1280d can be connected to the second backup flow path 1620 described below, so that the pressurized medium contained in the second main chamber 1230a is discharged to the second backup flow path 1620 side, and conversely, the pressurized medium can flow from the second backup flow path 1620 to the second main chamber 1230a side.

[0058] The second main piston 1230 is housed and disposed within the second main chamber 1230a, and can generate hydraulic pressure by moving forward to form a pressurized medium contained in the second main chamber 1230a, and can generate negative pressure by moving backward in the second main chamber 1230a. The second main piston 1230 may include: a second body 1231, formed in a cylindrical shape to fit tightly against the inner circumferential surface of the second main chamber 1230a; and a second flange 1232 at the rear end of the second body 1231 (towards...). Figure 1The second flange 1232 is formed radially extending from the right end of the second main chamber 1230a and is disposed inside the first main chamber 1220a. The diameter of the second flange 1232 can be formed to be larger than the diameter of the inner circumferential surface of the second main chamber 1230a. The second main piston 1230 can be elastically supported by a second piston spring 1230b, which can be configured such that one end of the second piston spring 1230b is supported by the front surface of the second body 1231 (with the right end of the second main chamber 1230a as a reference). Figure 1 The left side surface of the cylinder 1210 is used as a reference for support, while the other end is supported by the inner surface of the cylinder 1210.

[0059] A second sealing member 1290b may be provided between the outer peripheral surface of the second main piston 1230 and the cylinder 1210. The second sealing member 1290b seals the first main chamber 1220a relative to the second main chamber 1230a. The second sealing member 1290b may be configured to be disposed in a receiving groove recessed in the inner peripheral surface of the cylinder 1210 to contact the outer peripheral surface of the second main piston 1230, and the second sealing member 1290b may prevent the pressurized medium contained in the first main chamber 1220a from leaking into the second main chamber 1230a.

[0060] The second main piston 1230 is provided with a second shut-off hole 1230d. This second shut-off hole 1230d connects to the second main chamber 1230a, and in a non-operating state (i.e., a preparatory state before displacement), connects to the fifth hydraulic port 1280e and the second reservoir flow path 1720. Additionally, a fourth sealing member 1290d can be provided between the outer peripheral surface of the second main piston 1230 and the cylinder body 1210. This fourth sealing member 1290d blocks the flow of pressurized medium discharged from the second main chamber 1230a to the second reservoir flow path 1720 connected to the fifth hydraulic port 1280e. The fourth sealing member 1290d can be positioned on the inner peripheral surface of the cylinder body 1210, recessed in front of the fifth hydraulic port 1280e (towards...). Figure 1 The fourth sealing member 1290d can be disposed in the receiving groove (on the left side of the reference) to contact the outer peripheral surface of the second main piston 1230. Figure 1 (Based on the left side), and can block the flow of pressurized medium from the second main chamber 1230a to the fifth hydraulic port 1280e and the second reservoir flow path 1720 while allowing the flow of pressurized medium from the second reservoir flow path 1720 connected to the fifth hydraulic port 1280e to the second main chamber 1230a.

[0061] The integrated master cylinder 1200 can be independently equipped with a first main chamber 1220a and a second main chamber 1230a, thereby ensuring safety in the event of component failure. For example, the first main chamber 1220a can be connected to any two wheel cylinders 21 and 22 via the first backup flow path 1610 described below, and the second main chamber 1230a can be connected to the other two wheel cylinders 23 and 24 via the second backup flow path 1620 described below. Therefore, even if a leak occurs in any of the chambers, vehicle braking can still be achieved.

[0062] The pedal simulator 1240 is disposed between the first master piston 1220 and the second master piston 1230, and can provide the driver with the pedal feel of the brake pedal 10 through its own elastic restoring force. Specifically, the pedal simulator 1240 can be sandwiched between the front surface of the first master piston 1220 and the rear surface of the second master piston 1230, and can be formed of an elastic material such as compressible and expandable rubber. The pedal simulator 1240 may include: a cylindrical main body portion, at least a portion of which is inserted into and supported by the front surface of the first master piston 1220; and a conical portion, at least a portion of which is inserted into and supported by the rear surface of the second master piston 1230, with its diameter facing forward (towards...). Figure 1 (Based on the left side) gradually decreases. At least a portion of each end of the pedal simulator 1240 is inserted into the first master piston 1220, thereby being stably supported. Furthermore, the elastic restoring force can be varied according to the magnitude of the pedal force of the brake pedal 10 via the cone, thereby providing the driver with a stable and familiar pedal feel.

[0063] A simulator valve 1711 is provided on the first reservoir flow path 1710 described below, thereby controlling the flow of the pressurized medium between the reservoir 1100 and the first main chamber 1220a. The simulator valve 1711 can be configured as a normally closed solenoid valve that is normally closed and operates to open when receiving an electrical signal from the electronic control unit, and can be opened in the normal operating mode of the electronic braking system 1000.

[0064] The pedal simulation operation based on the integrated master cylinder 1200 is described below. In normal operating mode, when the driver operates the brake pedal 10, the first shut-off valve 1611 and the second shut-off valve 1621, respectively located in the first backup flow path 1610 and the second backup flow path 1620, are closed. Conversely, the simulator valve 1711 of the first reservoir flow path 1710 is open. As the brake pedal 10 is operated, the first master piston 1220 moves forward, but because the second shut-off valve 1621 is closed, the second main chamber 1230a is sealed, and therefore the second master piston 1230 cannot move. At this time, according to the closing operation of the first shut-off valve 1611 and the opening operation of the simulator valve 1711, the pressurized medium contained in the first main chamber 1220a flows in along the first reservoir flow path 1710. The second master piston 1230 cannot move forward; however, because the first master piston 1220 continues to move forward, it compresses the pedal simulator 1240, and the elastic restoring force of the pedal simulator 1240 can be provided to the driver as pedal feel. Subsequently, when the driver releases the pedal force of the brake pedal 10, the first master piston 1220, the second master piston 1230, and the pedal simulator 1240 can return to their original shape and position according to the elastic restoring force of the first piston spring 1220b, the second piston spring 1230b, and the pedal simulator 1240, and the first main chamber 1220a can receive and be filled with pressurized medium from the reservoir 1100 through the first reservoir flow path 1710.

[0065] As described above, since the interiors of the first main chamber 1220a and the second main chamber 1230a are always filled with pressurized medium, the friction between the first main piston 1220 and the second main piston 1230 is minimized during pedal simulation operation. This not only improves the durability of the integrated master cylinder 1200, but also prevents impurities from flowing in from the outside.

[0066] The reservoir 1100 can internally contain and store pressurized medium. The reservoir 1100 can be connected to each component, such as the integrated master cylinder 1200, the hydraulic supply device 1300 described below, and the hydraulic circuit described below, to provide or receive pressurized medium. Although multiple reservoirs 1100 are shown with the same reference numerals in the drawings, this is merely one example to aid in understanding the invention; the reservoir 1100 can be configured as a single component or as multiple independent components.

[0067] The reservoir flow path 1700 is configured to connect the integrated master cylinder 1200 and the reservoir 1100.

[0068] The reservoir flow path 1700 may include: a first reservoir flow path 1710, connecting the first main chamber 1220a and the reservoir 1100; and a second reservoir flow path 1720, connecting the second main chamber 1230a and the reservoir 1100. For this purpose, one end of the first reservoir flow path 1710 can be connected to the first main chamber 1220a via the first hydraulic port 1280a of the integrated master cylinder 1200, and the other end can be connected to the reservoir 1100. Similarly, one end of the second reservoir flow path 1720 can be connected to the second main chamber 1230a via the fifth hydraulic port 1280e of the integrated master cylinder 1200, and the other end can be connected to the reservoir 1100. In addition, as described above, the first reservoir flow path 1710 is provided with a simulator valve 1711 that is open in the normal operating mode, so the flow of the pressurized medium between the reservoir 1100 and the first main chamber 1220a through the first reservoir flow path 1710 can be controlled.

[0069] The hydraulic supply device 1300 is configured to receive an electrical signal as the driver’s braking intention from a pedal displacement sensor that senses the displacement of the brake pedal 10, and to generate hydraulic pressure of the pressurized medium through mechanical operation.

[0070] The hydraulic supply device 1300 may include: a hydraulic supply unit that provides pressure of the pressurized medium to the wheel cylinder 20; a motor (not shown) that generates rotational force based on the electrical signal from the pedal displacement sensor; and a power conversion unit (not shown) that converts the rotational motion of the motor into linear motion and transmits it to the hydraulic supply unit.

[0071] The hydraulic supply unit includes: a cylinder block 1310 configured to contain a pressurized medium; a hydraulic piston 1320 housed in the cylinder block 1310; a sealing member 1350 disposed between the hydraulic piston 1320 and the cylinder block 1310 to seal pressure chambers 1330 and 1340; and a drive shaft 1390 that transmits power from the power conversion unit to the hydraulic piston 1320.

[0072] Pressure chambers 1330 and 1340 may include those located in front of the hydraulic piston 1320 (to... Figure 1 The first pressure chamber 1330 (located to the left of the hydraulic piston 1320 as a reference) and the rear of the hydraulic piston 1320 (within the left direction) Figure 1 The second pressure chamber 1340 is located to the right of the reference hydraulic piston 1320. That is, the first pressure chamber 1330 is separated by the cylinder body 1310 and the front surface of the hydraulic piston 1320, and is configured to change its volume according to the movement of the hydraulic piston 1320, and the second pressure chamber 1340 is separated by the cylinder body 1310 and the rear surface of the hydraulic piston 1320, and is configured to change its volume according to the movement of the hydraulic piston 1320.

[0073] The first pressure chamber 1330 is connected to the first hydraulic flow path 1401 via a first connecting hole 1360a formed in the cylinder body 1310, and the second pressure chamber 1340 is connected to the second hydraulic flow path 1402 via a second connecting hole 1360b formed in the cylinder body 1310.

[0074] The sealing components include: a piston sealing component 1350a, disposed between the hydraulic piston 1320 and the cylinder 1310 to seal the space between the first pressure chamber 1330 and the second pressure chamber 1340; and a drive shaft sealing component 1350b, disposed between the drive shaft 1390 and the cylinder 1310 to seal the openings of the second pressure chamber 1340 and the cylinder 1310. The hydraulic 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 component 1350a and the drive shaft sealing component 1350b, thereby allowing leakage to the first hydraulic flow path 1401 and the second hydraulic flow path 1402 described below. Additionally, a chamber sealing component 1350c may be provided between the second pressure chamber 1340 and the drive shaft sealing component 1350b. The chamber sealing component 1350c can block the flow of pressurized medium leaking from the second pressure chamber 1340 to the auxiliary inflow path 1850 while allowing the flow of pressurized medium into the second pressure chamber 1340 through the auxiliary inflow path 1850 described below.

[0075] A motor (not shown) is configured to generate driving force for the hydraulic piston 1320 based on electrical signals output from an electronic control unit (ECU). The motor may be configured to include a stator and a rotor, and may thereby rotate forward or backward to provide the power to displace the hydraulic piston 1320. The angular velocity and angle of rotation of the motor can be precisely controlled by a motor control sensor. Since motors are well-known and widely known technology, a detailed description will be omitted.

[0076] The power conversion unit (not shown) is configured to convert the rotational force of the motor into linear motion. As an example, the power conversion unit may be configured to include a worm shaft (not shown), a worm wheel (not shown), and a drive shaft 1390.

[0077] The worm shaft can be integrally formed with the rotating shaft of the motor, and a worm can be formed on the outer circumferential surface and mesh with a worm wheel to make the worm wheel rotate. The worm wheel can mesh with the drive shaft 1390 to make the drive shaft 1390 move linearly, and the drive shaft 1390 is connected to the hydraulic piston 1320 and operates integrally, thereby allowing the hydraulic piston 1320 to slide within the cylinder 1310.

[0078] To reiterate the above operation, when the displacement of the brake pedal 10 is sensed by the pedal displacement sensor, the sensed signal is transmitted to the electronic control unit. The electronic control unit drives the motor to rotate the worm shaft in one direction. The rotational force of the worm shaft is transmitted to the drive shaft 1390 through the worm wheel. The hydraulic piston 1320 connected to the drive shaft 1390 can generate hydraulic pressure in the first pressure chamber 1330 while moving forward in the cylinder 1310.

[0079] Conversely, when the pedal force of the brake pedal 10 is released, the electronic control unit drives the motor to rotate the worm gear axis in the opposite direction. Therefore, the worm wheel also rotates in the opposite direction, and the hydraulic piston 1320 connected to the drive shaft 1390 can move backward in the cylinder 1310 while generating negative pressure in the first pressure chamber 1330.

[0080] The generation of hydraulic and negative pressure in the second pressure chamber 1340 can be achieved by operating in the opposite direction to the aforementioned directions. That is, when the displacement of the brake pedal 10 is sensed by the pedal displacement sensor, the sensed signal is transmitted to the electronic control unit, which 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 can generate hydraulic pressure in the second pressure chamber 1340 while moving backward in the cylinder 1310.

[0081] 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 gear axis in that direction. Therefore, the worm wheel also rotates in the opposite direction, and the hydraulic piston 1320 connected to the drive shaft 1390 can generate negative pressure in the second pressure chamber 1340 while moving forward in the cylinder 1310.

[0082] As described above, the hydraulic supply device 1300 can 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 driven by the motor. Furthermore, a control valve can determine whether braking is achieved by transmitting hydraulic pressure or by using negative pressure to release the brake. This will be described in detail below.

[0083] On the other hand, as long as the rotational motion of the motor can be converted into the linear motion of the hydraulic piston 1320, the power conversion unit according to this embodiment is not limited to any particular structure, and should be understood in the case of implementation by devices of various structures and methods.

[0084] The hydraulic supply device 1300 can be hydraulically connected to the reservoir 1100 via the discharge control unit 1800. The discharge control unit 1800 may include: a first discharge control unit for controlling the flow of pressurized medium between the first pressure chamber 1330 and the reservoir 1100; and a second discharge control unit for controlling the flow of pressurized medium between the second pressure chamber 1340 and the reservoir 1100. The first discharge control unit may include: a first discharge path 1810 connecting the first pressure chamber 1330 and the reservoir 1100; and a first bypass path 1830 that branches off from the first discharge path 1810 and then rejoins. The second discharge control unit may include: a second discharge path 1820 connecting the second pressure chamber 1340 and the reservoir 1100; and a second bypass path 1840 that branches off from the second discharge path 1820 and then rejoins.

[0085] The first discharge path 1810 and the first bypass path 1830 may be respectively equipped with a first discharge check valve 1811 and a first discharge valve 1831 to control the flow of the pressurized medium. The first discharge check valve 1811 may be configured to allow only the flow of the pressurized medium from the reservoir 1100 to the first pressure chamber 1330, and to block the flow of the pressurized medium in the opposite direction. In the first discharge path 1810, the first bypass path 1830 is connected in parallel with the first discharge check valve 1811, and the first bypass path 1831 may be provided to control the flow of the pressurized medium between the first pressure chamber 1330 and the reservoir 1100. In other words, the first bypass flow path 1830 can bypass and connect the front and rear ends of the first discharge check valve 1811 on the first discharge flow path 1810, and the first discharge valve 1831 can be configured as a bidirectional solenoid valve controlling the flow of the pressurized medium between the first pressure chamber 1330 and the reservoir 1100. The first discharge valve 1831 can be configured as a normally closed solenoid valve that is normally closed and operates to open when receiving an electrical signal from the electronic control unit.

[0086] The second discharge path 1820 and the second bypass path 1840 may be respectively equipped with a second discharge check valve 1821 and a second discharge valve 1841 to control the flow of the pressurized medium. The second discharge check valve 1821 may be configured to allow only the flow of the pressurized medium from the reservoir 1100 to the second pressure chamber 1340, and to block the flow of the pressurized medium in the opposite direction. In the second discharge path 1820, the second bypass path 1840 is connected in parallel with the second discharge check valve 1821, and the second bypass path 1840 may be equipped with a second discharge valve 1841 to control the flow of the pressurized medium between the second pressure chamber 1340 and the reservoir 1100. In other words, the second bypass flow path 1840 can bypass and connect the front and rear ends of the second discharge check valve 1821 on the second discharge flow path 1820, and the second discharge valve 1841 can be configured as a bidirectional solenoid valve controlling the flow of the pressurized medium between the second pressure chamber 1340 and the reservoir 1100. The second discharge valve 1841 can be configured 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.

[0087] Additionally, the discharge control unit 1800 may include an auxiliary inflow path 1850 connecting the reservoir 1100 and the second pressure chamber 1340, so that the pressurized medium can fill the second pressure chamber 1340. The auxiliary inflow path 1850 may be connected to the rear of the chamber sealing component 1350c of the cylinder body 1310 (towards...). Figure 1 (Right side as reference). Thus, the pressurized medium can flow from the reservoir 1100 into the second pressure chamber 1340 through the auxiliary inflow path 1850, and the flow of pressurized medium leaking from the second pressure chamber 1340 into the auxiliary inflow path 1850 can be blocked by the chamber sealing component 1350c.

[0088] The hydraulic control unit 1400 can be configured to control the hydraulic pressure transmitted to each wheel cylinder 20, and the electronic control unit (ECU) is configured to control the hydraulic supply device 1300 and various valves based on hydraulic information and pedal displacement information.

[0089] The hydraulic control unit 1400 may be provided with a first hydraulic circuit 1510 for controlling the hydraulic flow transmitted to the first wheel cylinder 21 and the second wheel cylinder 22 of the four wheel cylinders 20, and a second hydraulic circuit 1520 for controlling the hydraulic flow transmitted to the third wheel cylinder 23 and the fourth wheel cylinder 24. The hydraulic control unit 1400 includes multiple flow paths and valves to control the hydraulic pressure transmitted from the hydraulic supply device 1300 to the wheel cylinders 20.

[0090] The first hydraulic flow path 1401 can be configured to connect to the first pressure chamber 1330, and the second hydraulic flow path 1402 can be configured to connect to the second pressure chamber 1340. The first hydraulic flow path 1401 and the second hydraulic flow path 1402 can be configured to, after merging into the third hydraulic flow path 1403, branch again into a fourth hydraulic flow path 1404 connected to the first hydraulic circuit 1510 and a fifth hydraulic flow path 1405 connected to the second hydraulic circuit 1520.

[0091] The sixth hydraulic flow path 1406 is configured to connect to the first hydraulic circuit 1510, and the seventh hydraulic flow path 1407 is configured to connect to the second hydraulic circuit 1520. The sixth hydraulic flow path 1406 and the seventh hydraulic flow path 1407 can be configured to, after merging into the eighth hydraulic flow path 1408, branch again into the ninth hydraulic flow path 1409, which connects to the first pressure chamber 1330, and the tenth hydraulic flow path 1410, which connects to the second pressure chamber 1340.

[0092] The first hydraulic flow path 1401 may be provided with a first valve 1431 for controlling the flow of pressurized medium. The first valve 1431 may be configured as a check valve that allows the flow of pressurized medium discharged from the first pressure chamber 1330 and blocks the flow of pressurized medium in the opposite direction. Additionally, the second hydraulic flow path 1402 may be provided with a second valve 1432 for controlling the flow of pressurized medium. The second valve 1432 may be configured as a check valve that allows the flow of pressurized medium discharged from the second pressure chamber 1340 and blocks the flow of pressurized medium in the opposite direction.

[0093] The fourth hydraulic flow path 1404 is configured to branch again from the third hydraulic flow path 1403, which merges with the first hydraulic flow path 1401 and the second hydraulic flow path 1402, and connect to the first hydraulic circuit 1510. The fourth hydraulic flow path 1404 may be provided with a third valve 1433 to control the flow of pressurized medium. The third valve 1433 may be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the first hydraulic circuit 1510 and blocks the flow of pressurized medium in the opposite direction.

[0094] The fifth hydraulic flow path 1405 is configured to branch again from the third hydraulic flow path 1403, which merges with the first hydraulic flow path 1401 and the second hydraulic flow path 1402, and connect to the second hydraulic circuit 1520. The fifth hydraulic flow path 1405 may be equipped with a fourth valve 1434 to control the flow of pressurized medium. The fourth valve 1434 may be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520 and blocks the flow of pressurized medium in the opposite direction.

[0095] The sixth hydraulic flow path 1406 connects to the first hydraulic circuit 1510, and the seventh hydraulic flow path 1407 connects to the second hydraulic circuit 1520. The sixth and seventh hydraulic flow paths 1406 and 1407 are configured to merge into the eighth hydraulic flow path 1408. The sixth hydraulic flow path 1406 may be equipped with a fifth valve 1435 to control the flow of the pressurized medium. The fifth valve 1435 may be configured as a check valve that only allows the flow of pressurized medium discharged from the first hydraulic circuit 1510 and blocks the flow of pressurized medium in the opposite direction. Additionally, the seventh hydraulic flow path 1407 may be equipped with a sixth valve 1436 to control the flow of the pressurized medium. The sixth valve 1436 may be configured as a check valve that only allows the flow of pressurized medium discharged from the second hydraulic circuit 1520 and blocks the flow of pressurized medium in the opposite direction.

[0096] The ninth hydraulic flow path 1409 is configured to branch off from the eighth hydraulic flow path 1408, which is formed by the convergence of the sixth and seventh hydraulic flow paths 1406 and connect to the first pressure chamber 1330. The ninth hydraulic flow path 1409 may be equipped with a seventh valve 1437 for controlling the flow of the pressurized medium. The seventh valve 1437 may be configured as a bidirectional control valve for controlling the flow of the pressurized medium transmitted along the ninth hydraulic flow path 1409. The seventh valve 1437 may be configured as a normally closed solenoid valve that is normally closed and operates to open when receiving an electrical signal from the electronic control unit.

[0097] The tenth hydraulic flow path 1410 is configured to branch off from the eighth hydraulic flow path 1408, which is formed by the convergence of the sixth and seventh hydraulic flow paths 1406 and connect to the second pressure chamber 1340. The tenth hydraulic flow path 1410 may be equipped with an eighth valve 1438 for controlling the flow of the pressurized medium. The eighth valve 1438 may be configured as a bidirectional control valve for controlling the flow of the pressurized medium transmitted along the tenth hydraulic flow path 1410. Similar to the seventh valve 1437, the eighth valve 1438 may be configured as a normally closed solenoid valve that is normally closed and operates to open when receiving an electrical signal from the electronic control unit.

[0098] The hydraulic control unit 1400, through the hydraulic flow path and valve arrangement described above, allows the hydraulic pressure generated in the first pressure chamber 1330 due to the forward movement of the hydraulic piston 1320 to be transmitted sequentially through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404 to the first hydraulic circuit 1510, and sequentially through the first hydraulic flow path 1401 and the fifth hydraulic flow path 1405 to the second hydraulic circuit 1520. Furthermore, the hydraulic pressure generated in the second pressure chamber 1340 due to the backward movement of the hydraulic piston 1320 can be transmitted sequentially through the second hydraulic flow path 1402 and the fourth hydraulic flow path 1404 to the first hydraulic circuit 1510, and sequentially through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405 to the second hydraulic circuit 1520.

[0099] Conversely, the negative pressure formed in the first pressure chamber 1330 due to the rearward movement of the hydraulic piston 1320 can return the pressurized medium supplied to the first hydraulic circuit 1510 to the first pressure chamber 1330 by sequentially passing through the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and the ninth hydraulic flow path 1409. Similarly, the pressurized medium supplied to the second hydraulic circuit 1520 can return to the first pressure chamber 1330 by sequentially passing through the seventh hydraulic flow path 1407, the eighth hydraulic flow path 1408, and the ninth hydraulic flow path 1409. Furthermore, the negative pressure formed in the second pressure chamber 1340 due to the forward movement of the hydraulic piston 1320 can sequentially return the pressurized medium supplied to the first hydraulic circuit 1510 to the first pressure chamber 1340 through the sixth hydraulic flow path 1406, the eighth hydraulic flow path 1408, and the tenth hydraulic flow path 1410, and can also return the pressurized medium supplied to the second hydraulic circuit 1520 to the second pressure chamber 1340 through the seventh hydraulic flow path 1407, the eighth hydraulic flow path 1408, and the tenth hydraulic flow path 1410.

[0100] The first hydraulic circuit 1510 of the hydraulic control unit 1400 can control the hydraulic pressure of the first wheel cylinder 21 and the second wheel cylinder 22, which are two wheel cylinders 20 in four wheels (RR, RL, FR and FL), and the second hydraulic circuit 1520 can control the hydraulic pressure of the third wheel cylinder 23 and the fourth wheel cylinder 24, which are two other wheel cylinders 20.

[0101] The first hydraulic circuit 1510 can receive hydraulic pressure through the fourth hydraulic flow path 1404 and discharge hydraulic pressure through the sixth hydraulic flow path 1406. Therefore, as follows... Figure 1As shown, the fourth hydraulic flow path 1404 and the sixth hydraulic flow path 1406 can be configured to branch into two flow paths connecting to the first wheel cylinder 21 and the second wheel cylinder 22 after merging. Additionally, the second hydraulic circuit 1520 can receive hydraulic pressure through the fifth hydraulic flow path 1405 and discharge hydraulic pressure through the seventh hydraulic flow path 1407, for this purpose, as... Figure 1 As shown, the fifth hydraulic flow path 1405 and the seventh hydraulic flow path 1407 can be configured to branch into two flow paths connecting to the third wheel cylinder 23 and the fourth wheel cylinder 24 after merging. However, Figure 1 The hydraulic flow path connections shown are merely an example to aid in understanding the invention and are not limited to this structure. They should also be understood in various ways and structures as follows: for example, the fourth hydraulic flow path 1404 and the sixth hydraulic flow path 1406 can be connected to the first hydraulic circuit 1510 side, and independently branch and connect to the first wheel cylinder 21 and the second wheel cylinder 22. Similarly, the fifth hydraulic flow path 1405 and the seventh hydraulic flow path 1407 can be connected to the second hydraulic circuit 1520 side, and independently branch and connect to the third wheel cylinder 23 and the fourth wheel cylinder 24.

[0102] The first hydraulic circuit 1510 and the second hydraulic circuit 1520 may include first inlet valves to fourth inlet valves 1511a, 1511b, 1521a, and 1521b, respectively, controlling the flow of pressurized medium to the first to fourth cylinders 21, 22, 23, and 24. The first inlet valves to fourth inlet valves 1511a, 1511b, 1521a, and 1521b may be located upstream of the first to fourth cylinders 21, 22, 23, and 24, and may be configured as normally open solenoid valves that operate as closed valves when receiving an electrical signal from the electronic control unit.

[0103] The first hydraulic circuit 1510 and the second hydraulic circuit 1520 may include a first check valve to a fourth check valve 1513a, 1513b, 1523a, 1523b connected in parallel with the first inlet valve to the fourth inlet valve 1511a, 1511b, 1521a, 1521b. The check valves 1513a, 1513b, 1523a, 1523b may be provided in bypass flow paths in the first hydraulic circuit 1510 and the second hydraulic circuit 1520, connecting the first inlet valve to the fourth inlet valve 1511a, 1511b, 1521a, 1521b, and may allow only the flow of pressurized medium from each wheel cylinder 20 to the hydraulic supply device 1300, while blocking the flow of pressurized medium from the hydraulic supply device 1300 to the wheel cylinder 20. Hydraulic pressure applied to each wheel cylinder 20 can be quickly discharged through the first check valve to the fourth check valve 1513a, 1513b, 1523a, 1523b. In the event that the first inlet valve to the fourth inlet valve 1511a, 1511b, 1521a, 1521b cannot operate normally, the hydraulic pressure applied to the wheel cylinder 20 can also be smoothly returned to the hydraulic supply unit.

[0104] The second hydraulic circuit 1520 may be equipped with a first outlet valve 1522a and a second outlet valve 1522b to control the flow of pressurized medium discharged from the third wheel cylinder 23 and the fourth wheel cylinder 24, thereby improving performance when releasing the brakes of the third wheel cylinder 23 and the fourth wheel cylinder 24. The first outlet valve 1522a and the second outlet valve 1522b are respectively located on the discharge side of the third wheel cylinder 23 and the fourth wheel cylinder 24 to control the flow of pressurized medium transmitted from the third wheel cylinder 23 and the fourth wheel cylinder 24 to the reservoir 1100. The first outlet valve 1522a and the second outlet valve 1522b may be configured as normally closed solenoid valves that open when receiving an electrical signal from the electronic control unit. The first outlet valve 1522a and the second outlet valve 1522b may selectively release the hydraulic pressure applied to the pressurized medium of the third wheel cylinder 23 and the fourth wheel cylinder 24 to the reservoir 1100 side during the vehicle's ABS (anti-lock braking system) braking mode.

[0105] The first backup flow path 1610 described below can branch and connect to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510. The first backup flow path 1610 can be provided with at least one first shut-off valve 1611 to control the flow of pressurized medium between the first wheel cylinder 21, the second wheel cylinder 22 and the integrated master cylinder 1200.

[0106] The electronic braking system 1000 according to a first embodiment of the present invention may include a first backup flow path 1610 and a second backup flow path 1620, so that when normal operation is impossible due to device failure or other reasons, the pressurized medium discharged from the integrated master cylinder 1200 can be directly supplied to the wheel cylinder 20 to achieve braking. The mode in which the hydraulic pressure of the integrated master cylinder 1200 is directly transmitted to the wheel cylinder 20 is called the abnormal operation mode, i.e., the fallback mode.

[0107] The first backup flow path 1610 can be configured to connect the first main chamber 1220a and the first hydraulic circuit 1510 of the integrated master cylinder 1200, and the second backup flow path 1620 can be configured to connect the second main chamber 1230a and the second hydraulic circuit 1520 of the integrated master cylinder 1200.

[0108] One end of the first backup flow path 1610 can be connected to the first main chamber 1220a, and the other end can branch on the first hydraulic circuit 1510 and connect to the downstream side of the first inlet valve 1511a and the second inlet valve 1511b. One end of the second backup flow path 1620 can be connected to the second main chamber 1230a, and the other end can be connected between the third inlet valve 1521a and the first outlet valve 1522a on the second hydraulic circuit 1520. Figure 1 Although the diagram shows the second backup flow path 1620 connected between the third inlet valve 1521a and the first outlet valve 1522a, the same understanding should be made if the second backup flow path 1620 branches and connects to at least one of the upstream sides of the first outlet valve 1522a and the second outlet valve 1522b.

[0109] The first backup flow path 1610 may be provided with at least one first shut-off valve 1611 for controlling the bidirectional flow of the pressurized medium, and the second backup flow path 1620 may be provided with a second shut-off valve 1621 for controlling the bidirectional flow of the pressurized medium. The first shut-off valve 1611 and the second shut-off valve 1621 may be configured as normally open solenoid valves that are normally open and operate to close when receiving an electrical signal from the electronic control unit.

[0110] like Figure 1 As shown, a pair of first shut-off valves 1611 can also be provided on the first wheel cylinder 21 and the second wheel cylinder 22 respectively. The first shut-off valves 1611 can selectively release the hydraulic pressure applied to the first wheel cylinder 21 and the second wheel cylinder 22 during the vehicle's ABS braking mode, allowing it to be discharged to the reservoir 1100 side via the first backup flow path 1610, the first main chamber 1220a, the second branch flow path 1920 described below, and the discharge control unit 1800. This will be explained in detail below.

[0111] When the first shut-off valve 1611 and the second shut-off valve 1621 are closed, the pressurized medium from the integrated master cylinder 1200 can be prevented from being directly transmitted to the wheel cylinder 20, while also preventing hydraulic leakage from the hydraulic supply device 1300 to the integrated master cylinder 1200 side. Conversely, when the first shut-off valve 1611 and the second shut-off valve 1621 are opened, the pressurized medium pressurized in the integrated master cylinder 1200 can be directly supplied to the first hydraulic circuit 1510 and the second hydraulic circuit 1520 side through the first backup flow path 1610 and the second backup flow path 1620 to achieve braking.

[0112] The inspection flow path 1900 is configured to connect the integrated master cylinder 1200 and the hydraulic supply device 1300, and is configured to check for leaks in various components installed in the integrated master cylinder 1200 and the simulator valve 1711.

[0113] One end of the inspection flow path 1900 can be connected to the second pressure chamber 1340, and the other end can branch into a first branch flow path 1910 and a second branch flow path 1920, which are connected to the first main chamber 1220a via a third hydraulic port 1280c and a fourth hydraulic port 1280d, respectively. One end of the inspection flow path 1900 can be directly connected to the second pressure chamber 1340, or as... Figure 1 As shown, it can also be connected to the second pressure chamber 1340 via the second discharge path 1820.

[0114] The first branch flow path 1910 may be equipped with a check valve 1911 that controls the bidirectional flow of the pressurized medium between the first main chamber 1220a and the second pressure chamber 1340. The second branch flow path 1920 may be equipped with a check check valve 1921 that only allows the flow of the pressurized medium from the first main chamber 1220a to the second pressure chamber 1340, while blocking the flow of the pressurized medium in the opposite direction. The check valve 1911 may be configured as a normally open solenoid valve that is open under normal conditions and closes when it receives an electrical signal from the electronic control unit. The check valve 1911 may be controlled to be closed in a first check mode of the electronic braking system 1000 and open in a second check mode. This will be described in detail below.

[0115] The electronic braking system 1000 may include: a circuit pressure sensor PS1, which senses the hydraulic pressure of the pressurized medium supplied by the hydraulic supply device 1300; and a cylinder pressure sensor PS2, which senses the hydraulic pressure of the second main chamber 1230a. The circuit pressure sensor PS1 may be disposed on the first hydraulic circuit 1510 side to sense the hydraulic pressure of the pressurized medium generated, supplied, and transmitted to the hydraulic circuit 1510 from the hydraulic supply device 1300 during the inspection mode. The cylinder pressure sensor PS2 may be disposed between the second main chamber 1230a and the second shut-off valve 1621 on the second backup flow path 1620 to sense the hydraulic pressure of the pressurized medium contained in the second main chamber 1230a. During the first inspection mode described below, the pressure values ​​of the pressurized medium sensed by the circuit pressure sensor PS1 and the cylinder pressure sensor PS2 can be sent to the electronic control unit. The electronic control unit can compare the hydraulic pressure value sensed by the circuit pressure sensor PS1 and the hydraulic pressure value sensed by the cylinder pressure sensor PS2, and determine whether the integrated master cylinder 1200 or the simulator valve 1711 is leaking. Additionally, the electronic braking system 1000 may include a displacement sensor (not shown) that measures the displacement of the hydraulic piston 1320 of the hydraulic supply device 1300. This displacement sensor can check for leaks in the integrated master cylinder 1200 based on the displacement information of the hydraulic piston 1320 during the second inspection mode described below. This will be explained in more detail below. Figure 2 and Figure 3 Provide a detailed description.

[0116] The operation method of the electronic braking system 1000 according to the first embodiment of the present invention will be described below.

[0117] The electronic braking system 1000 according to a first embodiment of the present invention may include: a check mode for checking whether the integrated master cylinder 1200 and the simulator valve 1711 are leaking; a normal operation mode in which various components operate normally to perform braking without fault or abnormality; and an abnormal operation mode (standby mode) for emergency vehicle braking in the event of a fault or abnormality in the braking system.

[0118] First, the inspection mode of the electronic braking system 1000 according to the first embodiment of the present invention will be described.

[0119] Before checking for leaks in the integrated master cylinder 1200 or simulator valve 1711, the electronic control unit can discharge the hydraulic pressure applied to the first through fourth cylinders 21, 22, 23, and 24 into the reservoir 1100 to improve the accuracy of the inspection. Afterward, the electronic control unit can enter the first inspection mode to check for leaks in the integrated master cylinder 1200 and simulator valve 1711.

[0120] Figure 2This is a hydraulic circuit diagram showing the state of the electronic braking system 1000 according to a first embodiment of the present invention performing a first inspection mode. (Refer to...) Figure 2 The electronic control unit operates the motor to move the hydraulic piston 1320 forward, generating hydraulic pressure in the first pressure chamber 1330. Simultaneously, the simulator valve 1711, check valve 1911, third inlet valve 1521a, fourth inlet valve 1521b, and second shut-off valve 1621 are closed, while the first inlet valve 1511a, second inlet valve 1511b, and first shut-off valve 1611 are opened. Thus, the hydraulic pressure formed in the first pressure chamber 1330 flows sequentially through the hydraulic control unit 1400, the first inlet valve 1511a and second inlet valve 1511b of the first hydraulic circuit 1510, and the first backup flow path 1610, into the first main chamber 1220a. At this time, the second shut-off valve 1621 is closed, and the second main chamber 1230a is sealed.

[0121] In this state, the electronic control unit can compare the pressure values ​​measured by the loop pressure sensor PS1 and the pressure values ​​measured by the cylinder pressure sensor PS2 to check for leaks in the integrated master cylinder 1200 and the simulator valve 1711. Specifically, if there are no leaks in the components installed in the integrated master cylinder 1200 and the simulator valve 1711, the hydraulic pressure value of the hydraulic supply device 1300 measured by the loop pressure sensor PS1 reaches the target pressure, and this hydraulic pressure flows into the first main chamber 1220a through the first backup flow path 1610, thereby pressurizing the second master piston 1230 forward. Thus, the hydraulic pressure value of the second main chamber 1230a sensed by the cylinder pressure sensor PS2 and the hydraulic pressure value sensed by the loop pressure sensor PS1 can be synchronized with each other. When the hydraulic pressure values ​​sensed by the loop pressure sensor PS1 and the cylinder pressure sensor PS2 are synchronized for a predetermined time, the electronic control unit can determine that it is in a normal state and end the first check mode.

[0122] In contrast, when the hydraulic pressure value measured by the cylinder pressure sensor PS2 is lower than that measured by the loop pressure sensor PS1, it can be determined that there is a leak in the integrated master cylinder 1200 and the simulator valve 1711. Specifically, if the hydraulic pressure value of the pressurized medium pressurized by the hydraulic supply device 1300, as measured by the loop pressure sensor PS1, reaches the target pressure and is maintained for a predetermined time, but the hydraulic pressure value sensed by the cylinder pressure sensor PS2 in the second main chamber 1220a is lower than that sensed by the loop pressure sensor PS1, or if the hydraulic pressure value sensed by the loop pressure sensor PS1 also gradually decreases, the electronic control unit can consider that there is a leak in the integrated master cylinder 1200 and the simulator valve 1711, causing the hydraulic pressure in the second main chamber 1230a to fail to reach the target pressure, and therefore it can be determined as an abnormal state.

[0123] As described above, the electronic braking system 1000 according to the first embodiment of the present invention can determine whether various components installed in the integrated master cylinder 1200 are normal by means of a first inspection mode. Specifically, it can determine whether the first sealing member 1290a, the second sealing member 1290b, the fourth sealing member 1290d, and the first inspection valve 1911 are normal, and can also determine whether the simulator valve 1711 is normal. Furthermore, it can also determine whether peripheral components connected to the integrated master cylinder 1200, such as the second shut-off valve 1621, are normal.

[0124] When the first inspection mode determines that there is a leak in the components of the integrated master cylinder 1200 or the simulator valve 1711, the electronic control unit can notify the driver of the abnormal state through a display or prompt tone, and can guide the driver to restrict the operation of the vehicle.

[0125] When the result of executing the first check mode is that the first check mode is judged to be normal, the electronic control unit can enter the second check mode.

[0126] Figure 3 This is a hydraulic circuit diagram showing the state of the electronic braking system 1000 according to a first embodiment of the present invention performing a second inspection mode. (Refer to...) Figure 3The electronic control unit operates the motor to move the hydraulic piston 1320 backward, generating hydraulic pressure in the second pressure chamber 1340. Simultaneously, the second discharge valve 1841 can be closed to disconnect the hydraulic connection between the second pressure chamber 1340 and the reservoir 1100, and the inspection valve 1911 can be opened to allow the hydraulic connection between the second pressure chamber 1340 and the inspection flow path 1900. Thus, the hydraulic pressure generated in the second pressure chamber 1340 sequentially passes through the inspection flow path 1900, the first branch flow path 1910, and is transmitted to the third hydraulic port 1280c. At this time, the first inlet valve to the fourth inlet valves 1511a, 1511b, 1521a, and 1521b are switched to the closed state to quickly initiate the inspection mode.

[0127] The third sealing component 1290c is configured to block the flow of pressurized medium from the first branch flow path 1910 to the first main chamber 1220a. When the third sealing component 1290c is in normal condition, as the third hydraulic port 1280c is sealed, hydraulic pressure can no longer be formed in the second pressure chamber 1340 after the hydraulic piston 1320 moves backward by a predetermined displacement.

[0128] Therefore, when the displacement of the hydraulic piston measured by the displacement sensor (not shown) is within a predetermined range, the electronic control unit can determine that the third sealing component 1290c is in a normal state and end the second inspection mode. Conversely, when the displacement of the hydraulic piston measured by the displacement sensor (not shown) exceeds the predetermined range or gradually increases, the electronic control unit can assume that there is a leak in the third sealing component 1290c, thus determining it as an abnormal state, and notifying the user via a display or audible alert, and can guide and restrict vehicle operation.

[0129] The normal operating mode of the electronic braking system 1000 according to the first embodiment of the present invention will be described below.

[0130] The normal operating mode of the electronic braking system 1000 according to the first embodiment of the present invention can be divided into a first braking mode to a third braking mode as the hydraulic pressure transmitted from the hydraulic supply device 1300 to the wheel cylinder 20 increases. Specifically, in the first braking mode, hydraulic pressure is initially supplied to the wheel cylinder 20 by the hydraulic supply device 1300; in the second braking mode, hydraulic pressure is supplied to the wheel cylinder 20 a second time by the hydraulic supply device 1300 to transmit a braking pressure higher than that in the first braking mode; and in the third braking mode, hydraulic pressure is supplied to the wheel cylinder 20 a third time by the hydraulic supply device 1300 to transmit a braking pressure higher than that in the second braking mode.

[0131] The first braking mode can be changed to the third braking mode through different operations of the hydraulic supply device 1300 and the hydraulic control unit 1400. By utilizing the first to third braking modes, the hydraulic supply device 1300 can provide a sufficiently high hydraulic pressure for the pressurized medium even without a high-configuration motor, further preventing unnecessary loads on the motor. Thus, stable braking force can be ensured while reducing the cost and weight of the braking system, and the durability and operational reliability of the device can be improved.

[0132] Figure 4 This is a hydraulic circuit diagram showing the state of the electronic braking system 1000 executing a first braking mode according to a first embodiment of the present invention.

[0133] Reference Figure 4 When the driver initially depresses the brake pedal 10, the motor (not shown) rotates in one direction. The rotational force of the motor is transmitted to the hydraulic supply unit through the power conversion unit. As the hydraulic piston 1320 of the hydraulic supply unit moves forward, 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, thereby generating braking force.

[0134] Specifically, the hydraulic pressure generated in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404, and is initially transmitted to the first cylinder 21 and the second cylinder 22 located in the first hydraulic circuit 1510. At this time, the first valve 1431 only allows the flow of pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 can be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the first hydraulic circuit 1510. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the first cylinder 21 and the second cylinder 22. In addition, the first inlet valve 1511a and the second inlet valve 1511b located in the first hydraulic circuit 1510 remain open, and the first shut-off valve 1611 remains closed, thus preventing the hydraulic pressure of the pressurized medium from leaking to the first backup flow path 1610 side.

[0135] Furthermore, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401 and the fifth hydraulic flow path 1405, and is first transmitted to the third and fourth cylinders 23 and 24 provided in the second hydraulic circuit 1520. As described above, the first valve 1431 only allows the flow of the pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 can be configured as a check valve that only allows the flow of the pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 remain open, and the first outlet valve 1522a and the second outlet valve 1522b remain closed, thus preventing the hydraulic pressure of the pressurized medium from leaking to the reservoir 1100 side.

[0136] In the first braking mode, the eighth valve 1438 is controlled to be closed, thus preventing hydraulic leakage of the pressurized medium formed in the first pressure chamber 1330 into the second pressure chamber 1340. Additionally, the first discharge valve 1831 provided in the first bypass flow path 1830 remains closed, thus preventing hydraulic leakage of the hydraulic medium formed in the first pressure chamber 1330 into the reservoir 1100.

[0137] On the other hand, as the hydraulic piston 1320 moves forward, a negative pressure is generated in the second pressure chamber 1340. The hydraulic pressure of the pressurizing medium is transferred from the reservoir 1100 to the second pressure chamber 1340 through the second discharge passage 1820, thereby preparing for the second braking mode described below. The second discharge check valve 1821 provided in the second discharge passage 1820 allows the flow of the pressurizing medium from the reservoir 1100 to the second pressure chamber 1340, so the pressurizing medium can be stably supplied to the second pressure chamber 1340. Furthermore, the second discharge valve 1841 provided in the second bypass passage 1840 is switched to the open state, thereby allowing the pressurizing medium to be quickly supplied from the reservoir 1100 to the second pressure chamber 1340.

[0138] In the first braking mode where the wheel cylinder 20 is braked by the hydraulic supply device 1300, the first shut-off valve 1611 and the second shut-off valve 1621, which are respectively set in the first backup flow path 1610 and the second backup flow path 1620, are switched to closed, thereby preventing the pressurized medium discharged from the integrated master cylinder 1200 from being transmitted to the wheel cylinder 20 side.

[0139] Specifically, while the driver operates the brake pedal 10, the first shut-off valve 1611 and the second shut-off valve 1621, respectively provided in the first backup flow path 1610 and the second backup flow path 1620, are closed. On the other hand, the simulator valve 1711 of the first reservoir flow path 1710 is opened. With the operation of the brake pedal 10, the first master piston 1220 moves forward, but because the second shut-off valve 1621 is closed, the second main chamber 1230 is sealed, and therefore the second master piston 1230 cannot move. At this time, according to the closing operation of the first shut-off valve 1611 and the opening operation of the simulator valve 1711, the pressurized medium contained in the first main chamber 1220a flows in along the first reservoir flow path 1710. The second master piston 1230 cannot move forward, while the first master piston 1220 continues to move forward, thereby compressing the pedal simulator 1240, and the elastic restoring force of the pedal simulator 1240 can be provided to the driver as a pedal feel.

[0140] According to the first embodiment of the present invention, the electronic braking system 1000 can switch from the first braking mode to a mode that requires a higher braking pressure than the first braking mode. Figure 5 The second braking mode is shown.

[0141] Figure 5 This is a hydraulic circuit diagram showing the state of the electronic braking system 1000 executing the second braking mode according to the first embodiment of the present invention, with reference to... Figure 5 When the displacement or operating speed of the brake pedal 10 sensed by the pedal displacement sensor is higher than a preset level, or the hydraulic pressure sensed by the pressure sensor is higher than a preset level, the electronic control unit determines that a higher braking pressure is required, and thus switches from the first braking mode to the second braking mode.

[0142] When switching from the first braking mode to the second braking mode, the motor operates by rotating in the opposite direction. The rotational force of the motor is transmitted to the hydraulic supply unit through the power conversion unit, causing the hydraulic piston 1320 to move backward, thereby generating hydraulic pressure in the second pressure chamber 1340. The hydraulic pressure discharged from the second pressure chamber 1340 is transmitted to each wheel cylinder 20 through the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520, generating braking force.

[0143] Specifically, the hydraulic pressure generated in the second pressure chamber 1340 is sequentially transmitted through the second hydraulic flow path 1402 and the fourth hydraulic flow path 1404, and then a second time to the first wheel cylinder 21 and the second wheel cylinder 22 located in the first hydraulic circuit 1510. At this time, the second valve 1432 located in the second hydraulic flow path 1402 only allows the flow of pressurized medium discharged from the second pressure chamber 1340, and the third valve 1433 located in the fourth hydraulic flow path 1404 can be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the first hydraulic circuit 1510. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the first wheel cylinder 21 and the second wheel cylinder 22. The first inlet valve 1511a and the second inlet valve 1511b located in the first hydraulic circuit 1510 remain open, and the first shut-off valve 1611 remains closed, thus preventing the hydraulic pressure of the pressurized medium from leaking to the first backup flow path 1610 side.

[0144] Furthermore, the hydraulic pressure generated in the second pressure chamber 1340 sequentially passes through the second hydraulic flow path 1402, the third hydraulic flow path 1403, and the fifth hydraulic flow path 1405, and is then transmitted a second time to the third and fourth cylinders 23 and 24 located in the second hydraulic circuit 1520. As described above, the second valve 1432 located in the second hydraulic flow path 1403 only allows the flow of pressurized medium discharged from the second pressure chamber 1340, and the fourth valve 1434 located in the fifth hydraulic flow path 1405 can be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b in the second hydraulic circuit 1520 are kept open, while the first outlet valve 1522a and the second outlet valve 1522b are kept closed, thus preventing hydraulic leakage of the pressurized medium to the reservoir 1100 side.

[0145] In the second braking mode, the seventh valve 1437 is controlled to be closed, thus preventing hydraulic leakage of the pressurized medium formed in the second pressure chamber 1340 into the first pressure chamber 1330. Additionally, since the second discharge valve 1841 is switched to the closed state, hydraulic leakage of the pressurized medium formed in the second pressure chamber 1340 into the reservoir 1100 side is also prevented.

[0146] On the other hand, as the hydraulic piston 1320 moves backward, a negative pressure is generated in the first pressure chamber 1330. The hydraulic pressure of the pressurizing medium is transferred from the reservoir 1100 to the first pressure chamber 1330 through the first discharge passage 1810, thereby preparing for the third braking mode described below. The first discharge check valve 1811 provided in the first discharge passage 1810 allows the flow of the pressurizing medium from the reservoir 1100 to the first pressure chamber 1330, so the pressurizing medium can be stably supplied to the first pressure chamber 1330. Furthermore, the first discharge valve 1831 provided in the first bypass passage 1830 is switched to the open state, thereby allowing the pressurizing medium to be quickly supplied from the reservoir 1100 to the first pressure chamber 1330.

[0147] The operation of the integrated master cylinder 1200 in the second braking mode is the same as that of the integrated master cylinder 1200 in the first braking mode of the electronic braking system described above. To avoid repetition, the description will be omitted.

[0148] According to the first embodiment of the present invention, the electronic braking system 1000 can switch from the second braking mode when a higher braking pressure than the second braking mode is required. Figure 6 The third braking mode is shown.

[0149] Figure 6 This is a hydraulic circuit diagram illustrating the state of the electronic braking system 1000 according to a first embodiment of the present invention executing a third braking mode. (Refer to...) Figure 6 When the displacement or operating speed of the brake pedal 10 sensed by the pedal displacement sensor is higher than a preset level, or the hydraulic pressure sensed by the pressure sensor is higher than a preset level, the electronic control unit determines that a higher braking pressure is required, and thus switches from the second braking mode to the third braking mode.

[0150] 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 supply unit through the power conversion unit. As the hydraulic piston 1320 of the hydraulic supply unit 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, generating braking force.

[0151] Specifically, a portion of the hydraulic pressure generated in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404, and is initially transmitted to the first cylinder 21 and the second cylinder 22 located in the first hydraulic circuit 1510. At this time, the first valve 1431 only allows the flow of pressurized medium discharged from the first pressure chamber 1330, and the third valve 1433 can be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the first hydraulic circuit 1510. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the first cylinder 21 and the second cylinder 22. Furthermore, the first inlet valve 1511a and the second inlet valve 1511b located in the first hydraulic circuit 1510 remain open, and the first shut-off valve 1611 remains closed, thus preventing hydraulic leakage of the pressurized medium to the first backup flow path 1610 side.

[0152] Furthermore, a portion of the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 sequentially passes through the first hydraulic flow path 1401 and the fifth hydraulic flow path 1405, and is initially transmitted to the third and fourth cylinders 23 and 24 provided in the second hydraulic circuit 1520. As described above, the first valve 1431 only allows the flow of pressurized medium discharged from the first pressure chamber 1330, and the fourth valve 1434 can be configured as a check valve that only allows the flow of pressurized medium from the third hydraulic flow path 1403 to the second hydraulic circuit 1520. Therefore, the hydraulic pressure of the pressurized medium can be smoothly transmitted to the third and fourth cylinders 23 and 24. In addition, the third inlet valve 1521a and the fourth inlet valve 1521b provided in the second hydraulic circuit 1520 remain open, and the first outlet valve 1522a and the second outlet valve 1522b remain closed, thus preventing the hydraulic pressure of the pressurized medium from leaking to the reservoir 1100 side.

[0153] On the other hand, in the third braking mode, a high-pressure hydraulic pressure is supplied. Therefore, as the hydraulic piston 1320 moves forward, the force exerted by the hydraulic pressure in the first pressure chamber 1330 to move the hydraulic piston 1320 backward also increases, resulting in a sharp increase in the load applied to the motor. Therefore, in the third braking mode, the seventh valve 1437 and the eighth valve 1438 can be operated open, allowing the pressurized medium to flow through the ninth hydraulic flow path 1409 and the tenth hydraulic flow path 1410. In other words, a portion of the hydraulic pressure formed in the first pressure chamber 1330 can be supplied to the second pressure chamber 1340 sequentially through the ninth hydraulic flow path 1409 and the tenth hydraulic flow path 1410, thereby connecting the first pressure chamber 1330 and the second pressure chamber 1340 to each other and synchronizing the hydraulic pressure, thereby reducing the load applied to the motor and improving the durability and reliability of the device.

[0154] In the third braking mode, the first discharge valve 1831 is switched to the closed state, thereby preventing the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 from leaking into the reservoir 1100 along the first bypass flow path 1830. The second discharge valve 1841 is also controlled to the closed state, so that a negative pressure can be quickly formed in the second pressure chamber 1340 according to the forward movement of the hydraulic piston 1320, thereby smoothly receiving the pressurized medium provided from the first pressure chamber 1330.

[0155] In the third braking mode, the operation of the integrated master cylinder 1200 is the same as that of the integrated master cylinder 1200 in the first and second braking modes of the electronic braking system described above. To avoid repetition, the description will be omitted.

[0156] The following describes the situation where the electronic braking system 1000 according to the first embodiment of the present invention cannot operate normally, i.e., the operation state of the standby mode.

[0157] Figure 7 This is a hydraulic circuit diagram showing the operating state in an abnormal operating mode (standby mode) when the electronic braking system 1000 according to the first embodiment of the present invention cannot operate normally due to device malfunction or the like.

[0158] Reference Figure 7 In the abnormal operating mode, each valve is controlled to the initial braking state as a non-operating state. At this time, when the driver applies pedal force to the brake pedal 10, the first master piston 1220 connected to the brake pedal 10 moves forward and is displaced. In the non-operating state, the first shut-off valve 1611 is set to the open state, so the pressurized medium contained in the first main chamber 1220a can be transmitted along the first backup flow path 1610 to the first wheel cylinder 21 and the second wheel cylinder 22 of the first hydraulic circuit 1510 according to the forward movement of the first master piston 1220, thus achieving braking.

[0159] In addition, as the first main piston 1220 moves forward, the second main piston 1230 also moves forward and is displaced. In the non-operating state, the second shut-off valve 1621 is also set to the open state. Thus, the pressurized medium contained in the second main chamber 1230a can be transmitted along the second backup flow path 1620 to the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 and achieve braking.

[0160] The electronic braking system 2000 according to the second embodiment of the present invention will be described below.

[0161] Figure 8 This is a hydraulic circuit diagram illustrating an electronic braking system 2000 according to a second embodiment of the present invention, with reference to... Figure 8The electronic braking system 2000 according to the second embodiment may further include: a first circuit pressure sensor PS11 for sensing the hydraulic pressure of the pressurized medium transmitted to the first hydraulic circuit 1510; and a second circuit pressure sensor PS12 for sensing the hydraulic pressure of the pressurized medium transmitted to the second hydraulic circuit 1520.

[0162] In the following description of the electronic braking system 2000 according to a second embodiment of the present invention, except where further explanation is given by additional reference numerals, the remainder is the same as the description of the electronic braking system 1000 according to the first embodiment of the present invention described above, and therefore the description will be omitted to prevent repetition.

[0163] The first-loop pressure sensor PS11 senses the hydraulic pressure generated by the hydraulic supply device 1300 and supplied to the first hydraulic circuit 1510, and sends the pressure value information to the electronic control unit. Similarly, the second-loop pressure sensor PS12 senses the hydraulic pressure generated by the hydraulic supply device 1300 and supplied to the second hydraulic circuit 1520, and sends the pressure value information to the electronic control unit. The electronic control unit can receive the hydraulic pressure value information for each hydraulic circuit from the first-loop pressure sensor PS11 and the second-loop pressure sensor PS12, and thereby control the operation of the hydraulic supply device 1300, thus assisting in vehicle autonomous driving and braking, such as highway driving assistance and emergency braking.

[0164] As an example, the first wheel cylinder 21 and the second wheel cylinder 22, located in the first hydraulic circuit 1510, can be allocated to the right front wheel (FR) and the left front wheel (FL), respectively. Similarly, the third wheel cylinder 23 and the fourth wheel cylinder 24, located in the second hydraulic circuit 1520, can be allocated to the left rear wheel (RL) and the right rear wheel (RR), respectively. Thus, the first circuit pressure sensor PS11 can sense and transmit the hydraulic pressure applied to the front wheel cylinders, and the second circuit pressure sensor PS12 can sense and transmit the hydraulic pressure applied to the rear wheel cylinders. The electronic control unit can automatically adjust and control the vehicle's braking pressure based on the hydraulic information received from the first circuit pressure sensor PS11 and the second circuit pressure sensor PS12, thereby ensuring driver convenience.

[0165] The electronic braking system 3000 according to the third embodiment of the present invention will be described below.

[0166] Figure 9 This is a hydraulic circuit diagram illustrating an electronic braking system 3000 according to a third embodiment of the present invention, with reference to... Figure 9 According to the third embodiment, the electronic braking system 3000 can perform assisted control for regenerative braking mode.

[0167] In the following description of the electronic braking system 3000 according to a third embodiment of the present invention, except where further explanation is given by additional reference numerals, the remainder is the same as the description of the electronic braking system 1000 according to the first embodiment of the present invention described above, and therefore the description will be omitted to prevent repetition.

[0168] Recently, with the increasing market demand for environmentally friendly vehicles, hybrid vehicles, which improve vehicle fuel economy, have become increasingly popular. Hybrid vehicles utilize a method where kinetic energy is recovered into electrical energy during vehicle braking and stored in a battery, while the motor is used as an auxiliary drive source. Typically, hybrid vehicles recover energy during braking operations using a generator (not shown) to improve energy recovery rate. This braking operation is called regenerative braking mode. According to this embodiment, the electronic braking system 3000, in order to achieve regenerative braking mode, distributes the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 to the left rear wheel (RL) and the right rear wheel, thereby allowing the generator (not shown) to be installed. The generators of the third wheel cylinder 23 and the fourth wheel cylinder 24, and the ninth valve 3439 described below, can assist in controlling the execution of regenerative braking mode.

[0169] The hydraulic control unit 3400 of the electronic braking system 3000 according to a third embodiment of the present invention may further include a ninth valve 3439 for adjusting the hydraulic pressure of the pressurized medium transmitted to the second hydraulic circuit 1520. The ninth valve 3439 may be disposed at the inlet end of the second hydraulic circuit 1520, for example, on the rear end of the fourth valve 1434 in the fifth hydraulic flow path 1405, and may be configured as a bidirectional control valve for controlling the flow of the pressurized medium transmitted to the second hydraulic circuit 1520. The ninth valve 3439 may be configured as a normally closed solenoid valve that is normally closed and opens upon receiving an electrical signal from the electronic control unit. The ninth valve 3439 may be controlled to open in the normal operating mode of the electronic braking system 3000, and switched to a closed state when entering a regenerative mode based on a generator (not shown) disposed in the third wheel cylinder 23 and the fourth wheel cylinder 24.

[0170] The regenerative braking mode of the electronic braking system 3000 according to the third embodiment of the present invention will be described. In the case of the first cylinder 21 and the second cylinder 22 of the first hydraulic circuit 1510 of the front wheels, the braking force that the driver wants to achieve is formed by the hydraulic pressure of the pressurized medium according to the operation of the hydraulic supply device 1300. Conversely, in the case of the third cylinder 23 and the fourth cylinder 24 of the second hydraulic circuit 1520 of the rear wheels, which are equipped with a power recovery device such as a generator, the sum of the overall braking pressure of the brake pressure of the pressurized medium according to the hydraulic supply device 1300 and the regenerative braking pressure according to the generator should be the same as the overall braking force of the first cylinder 21 and the second cylinder 22.

[0171] Therefore, when entering the regenerative braking mode, the braking pressure applied to the third wheel cylinder 23 and the fourth wheel cylinder 24 by the hydraulic supply device 1300 is eliminated or a predetermined level of braking pressure is maintained by closing the ninth valve 3439. At the same time, the regenerative braking pressure according to the generator is increased, so that the overall braking force of the third wheel cylinder 23 and the fourth wheel cylinder 24 can be the same as the braking force of the first wheel cylinder 21 and the second wheel cylinder 22.

[0172] Specifically, during vehicle braking, when the driver presses the brake pedal 10, the motor operates by rotating in one direction. The rotational force of the motor is transmitted to the hydraulic supply unit through the power transmission unit. The hydraulic piston 1320 of the hydraulic supply unit generates hydraulic pressure in the first pressure chamber 1330 as it moves forward. The hydraulic pressure discharged from the first pressure chamber 1330 is transmitted to each wheel cylinder 20 via the hydraulic control unit 1400, the first hydraulic circuit 1510, and the second hydraulic circuit 1520, generating braking force.

[0173] In the absence of an energy recovery device such as a generator in the first hydraulic circuit 1510, the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 flows sequentially through the first hydraulic flow path 1401, the third hydraulic flow path 1403, and the fourth hydraulic flow path 1404, thereby achieving braking of the first wheel cylinder 21 and the second wheel cylinder 23. As described above, the first valve 1411 and the third valve 1413 allow the flow of the pressurized medium from the first pressure chamber 1330 to the first hydraulic circuit 1510, thus the hydraulic pressure of the pressurized medium formed in the first pressure chamber 1330 can be transmitted to the first hydraulic circuit 1510 side.

[0174] On the other hand, when a second hydraulic circuit 1520 with a generator is provided, if the electronic control unit determines that regenerative braking mode can be entered by sensing the vehicle's speed, deceleration, etc., it can close the ninth valve 3439 to block the hydraulic pressure transmission of the pressurized medium to the third wheel cylinder 23 and the fourth wheel cylinder 24, and regenerative braking can be achieved according to the generator. Subsequently, if the electronic control unit determines that the vehicle is in a state unsuitable for regenerative braking, or determines that the braking pressure of the first hydraulic circuit 1510 and the second hydraulic circuit 1520 are different, it can simultaneously open the ninth valve 3439 to control the hydraulic pressure transmission of the pressurized medium to the second hydraulic circuit 1520 side, while synchronizing the braking pressure of the first hydraulic circuit 1510 and the second hydraulic circuit 1520. Thus, the braking pressure or braking force applied to the first to fourth wheel cylinders 20 can be uniformly controlled, thereby ensuring the vehicle's braking stability while preventing oversteering or understeering, and improving the vehicle's driving stability.

[0175] As described above, although the present invention has been described by way of limited embodiments and drawings, the present invention is not limited thereto. Obviously, those skilled in the art to which this invention pertains can make various modifications and changes within the equivalent scope of the technical concept of the present invention and the appended claims.

Claims

1. An electronic braking system, characterized in that, include: A liquid reservoir that stores pressurized media; An integrated master cylinder is provided with a master piston connected to the brake pedal, a main chamber whose volume changes according to the displacement of the master piston, and a sealing component for sealing the main chamber; The hydraulic supply device operates a hydraulic piston to generate hydraulic pressure based on an electrical signal output corresponding to the displacement of the brake pedal. A hydraulic control unit is disposed between the hydraulic supply device and the plurality of wheel cylinders, and controls the flow of the pressurized medium supplied to the plurality of wheel cylinders; A circuit pressure sensor senses the hydraulic pressure supplied through the hydraulic supply device; A cylinder pressure sensor senses the hydraulic pressure in the main chamber; Inspect the flow path and connect the main chamber to the hydraulic supply device; as well as A check valve is provided in the check flow path to control the flow of the pressurized medium. The integrated master cylinder includes: The first master piston is connected to the brake pedal; as well as The volume of the first main chamber changes according to the displacement of the first main piston. The first main piston is provided with a first stop hole, which communicates with the first main chamber and, in the non-operating state, communicates with the inspection flow path. On the outer peripheral surface of the first main piston and on the inner peripheral surface of the cylinder body forming a chamber inside the integrated main cylinder, there are: a first sealing member that seals the first main chamber relative to the outside; and a third sealing member that blocks the flow of pressurized medium from the inspection flow path into the first main chamber. The first sealing component is disposed on the rear side of the third sealing component, and the inspection flow path is connected between the first sealing component and the third sealing component of the integrated master cylinder.

2. The electronic braking system according to claim 1, wherein, One end of the inspection flow path is connected to the hydraulic supply device side, and the other end branches into a first branch flow path and a second branch flow path, which are respectively connected to the first main chamber. The inspection valve is located in the first branch flow path. The second branch flow path is provided with a check valve that allows only the flow of pressurized medium from the first main chamber to the hydraulic supply device.

3. The electronic braking system according to claim 2, wherein, The hydraulic supply device includes a first pressure chamber located in front of the hydraulic piston and a second pressure chamber located behind the hydraulic piston. One end of the inspection flow path is connected to the second pressure chamber.

4. The electronic braking system according to claim 3, characterized in that, Further includes: A discharge control unit is disposed between the liquid reservoir and the hydraulic supply device to control the flow of the pressurized medium. The discharge control unit includes a first discharge control unit that controls the flow of pressurized medium between the first pressure chamber and the reservoir, and a second discharge control unit that controls the flow of pressurized medium between the second pressure chamber and the reservoir.

5. The electronic braking system according to claim 3, wherein, The integrated master cylinder further includes: The second main piston is configured to move in response to the displacement of the first main piston; and The volume of the second main chamber changes according to the displacement of the second main piston. The cylinder pressure sensor senses the hydraulic pressure in the second main chamber.

6. The electronic braking system according to claim 5, wherein, The integrated master cylinder further includes: The second sealing component seals the first main chamber relative to the second main chamber.

7. The electronic braking system according to claim 5, characterized in that, Further includes: The first liquid reservoir flow path connects the liquid reservoir and the first main chamber; as well as A simulator valve is installed in the flow path of the first reservoir to control the flow of the pressurized medium between the reservoir and the first main chamber.

8. The electronic braking system according to claim 7, wherein, The hydraulic control unit includes: The first hydraulic circuit controls the flow of the pressurized medium supplied to the first and second wheel cylinders; and The second hydraulic circuit controls the flow of pressurized medium supplied to the third and fourth wheel cylinders. The electronic braking system further includes: A first backup flow path connects the first main chamber and the first hydraulic circuit; and The second backup flow path connects the second main chamber and the second hydraulic circuit.

9. The electronic braking system according to claim 8, characterized in that, Further includes: A first shut-off valve is installed in the first backup flow path to control the flow of the pressurized medium; as well as The second shut-off valve is installed in the second backup flow path to control the flow of the pressurized medium.

10. The electronic braking system according to claim 5, wherein, The integrated master cylinder further includes: A pedal simulator is positioned between the first master piston and the second master piston to provide pedal feel through the elastic restoring force generated during compression.

11. The electronic braking system according to claim 6, characterized in that, Further includes: The second liquid reservoir flow path connects the liquid reservoir and the second main chamber. The integrated master cylinder further includes: The fourth sealing component blocks the flow of pressurized medium from the second main chamber to the flow path of the second reservoir.

12. The electronic braking system according to claim 11, wherein, The second main piston includes: The second shut-off hole connects the second main chamber and the flow path of the second reservoir when not in operation.

13. The electronic braking system according to claim 7, wherein, The hydraulic control unit includes: The first hydraulic circuit controls the flow of the pressurized medium supplied to the first and second wheel cylinders; and The second hydraulic circuit controls the flow of pressurized medium supplied to the third and fourth wheel cylinders. The third and fourth wheel cylinders are each equipped with a generator. The hydraulic control unit further includes: The solenoid valve blocks the transmission of hydraulic pressure from the pressurized medium to the third and fourth wheel cylinders during regenerative braking mode.

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