DE102019211196A1 - ELECTRONIC BRAKING SYSTEM AND METHOD FOR OPERATING IT - Google Patents

Abstract

An electronic braking system of the present disclosure is disclosed. The electronic brake system may include: a container for storing a pressure medium, an integrated master cylinder including a main chamber and a simulation chamber, a container passage connecting the integrated master cylinder and the container to each other, a hydraulic pressure supply device for operating a hydraulic piston by an electrical signal output in response on a stroke of the brake pedal to generate hydraulic pressure in its pressure chambers, a hydraulic controller including a first hydraulic circuit for controlling the hydraulic pressure transmitted to two wheel cylinders and a second hydraulic circuit for controlling the hydraulic pressure transmitted to the other two wheel cylinders and an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal.

Description

BACKGROUND

Technical area

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

Description of the prior art

A brake system for braking is basically installed in a vehicle, and various types of brake systems have been proposed for the safety of a driver and a passenger.

A conventional braking system mainly employs a method of supplying hydraulic pressure necessary for braking to wheel cylinders using a mechanically connected booster when a driver depresses a brake pedal. However, as the market demand for implementing various braking functions in response to the operating environment of vehicles increases, in recent years there has been an electronic brake system for receiving an electrical signal indicative of a driver's braking force from a pedal stroke sensor that detects a stroke of the brake pedal when the driver depresses the brake pedal, and to operate a hydraulic pressure supply device based on the electric signal to supply hydraulic pressure necessary for braking to the wheel cylinders.

In the electronic brake system, an electric signal is generated and provided in accordance with the operation of the brake pedal by the driver in a normal operating mode, and the hydraulic pressure supply device is electrically operated and controlled based on the electric signal so that the hydraulic pressure necessary for braking is generated and applied the wheel cylinder is transferred. As a result, such an electronic braking system and method for its operation can be operated and controlled electronically in order to implement complex and diverse braking processes. However, the electronic brake system may impair the safety of the occupants because the hydraulic pressure necessary for braking is not stably established when a technical problem occurs in an electrical component.

As a result, if a component element fails or goes out of control, the electronic brake system enters an abnormal mode of operation, in which case a mechanism is required in which the driver's operation of the brake pedal must be directly coupled to the wheel cylinders. This means that the hydraulic pressure required for braking must be generated immediately in the abnormal operating mode of the electronic brake system while the driver is applying pressure to the brake pedal, and it must be possible to transmit this hydraulic pressure directly to the wheel cylinders.

SUMMARY

One aspect of the present disclosure is to provide an electronic brake system capable of reducing a number of components to be applied and making a product compact and lightweight.

One aspect of the present disclosure is to provide an electronic braking system that is capable of braking effectively in a variety of operating situations.

One aspect of the present disclosure is to provide an electronic braking system with improved performance and operational reliability.

One aspect of the present disclosure is to provide an electronic braking system with improved product life by reducing loads applied to components.

One aspect of the present disclosure is to provide an electronic braking system capable of improving assemblability and productivity of a product and reducing the manufacturing cost of the product.

Additional aspects of the disclosure are partially referred to in the following description and partially these become apparent from the description or can be learned through practice of the disclosure.

According to one aspect of the present disclosure, an electronic brake system may include a container for storing a print medium; an integrated master cylinder including a cylinder block configured to form a main chamber and a simulation chamber therein, a master piston provided in the main chamber and displaceable by a brake pedal, a piston spring for elastically supporting the master piston in the cylinder block, one provided in the simulation chamber and through a Displacement of the main piston displaceable simulation piston or a hydraulic pressure of the pressure medium accommodated in the main chamber, an elastic element provided between the simulation piston and the cylinder view, and a simulation spring provided together with the elastic element in the simulation chamber for elastically supporting the simulation piston; a tank passage connecting the integrated master cylinder and the tank; a hydraulic pressure supply device for generating hydraulic pressure by operating a hydraulic piston by an electrical signal output in response to a stroke of the brake pedal, the hydraulic pressure supply device comprising a first pressure chamber provided on one side of the hydraulic piston, which is movably received in a cylinder block and with at least one of the wheel cylinders is connected, and a second pressure chamber provided on the other side of the hydraulic piston and connected to at least one of the wheel cylinders; a hydraulic controller having a first hydraulic circuit for controlling the hydraulic pressure transmitted to two wheel cylinders and a second hydraulic circuit for controlling the hydraulic pressure transmitted to the other two wheel cylinders; and an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal.

Further, the cylinder block may include a step-shaped part which is formed so that it is to be attached to a part on which the simulation chamber is formed in a step-shaped manner on the main chamber, the simulation piston being provided with an extension part which is formed so that it protrudes outward and is received by the step-shaped part, the extension part restricting a stroke of the simulation piston when the simulation piston moves back after the brake pedal has been actuated.

Further, the simulation chamber may include a hydraulic port for connecting to the container, the simulation piston including a shut-off bore formed inwardly to selectively communicate with the hydraulic port, the shut-off bore connecting the simulation chamber and the hydraulic port to each other when the simulation piston is in a normal stop position, and the connection between the simulation chamber and the hydraulic connection is disconnected when the simulation piston moves.

Furthermore, the hydraulic controller may include a first hydraulic passage that communicates with the first pressure chamber; a second hydraulic passage and a third hydraulic passage branching from the first hydraulic passage; a fourth hydraulic passage communicating with the second pressure chamber; a fifth hydraulic passage in which the second hydraulic passage and the fourth hydraulic passage are merged; a sixth hydraulic passage that branches off from the fifth hydraulic passage and is connected to the first hydraulic circuit; a seventh hydraulic passage that branches off from the fifth hydraulic passage and is connected to the second hydraulic circuit; and an eighth hydraulic passage, one end of which is connected to the third hydraulic passage and the other end of which branches off to both sides and merges with the sixth hydraulic passage and the seventh hydraulic passage, respectively.

Furthermore, the hydraulic control can comprise a first valve provided in the second hydraulic passage in order to control a flow of the pressure medium; a second valve provided in the third hydraulic passage to control the flow of the pressure medium; a third valve provided in the sixth hydraulic passage to control the flow of the pressure medium; a fourth valve provided in the seventh hydraulic passage to control the flow of the pressure medium; and a fifth valve and a sixth valve provided in the eighth hydraulic passage for controlling the flow of the pressure medium.

Furthermore, the first valve, the third valve and the fourth valve can be designed as a check valve that only allows the flow of the pressure medium from the pressure chambers to the wheel cylinders, the second valve is designed as a solenoid valve to control the flow of the pressure medium in both directions , and the fifth valve and the sixth valve are designed as check valves that only allow the flow of the pressure medium from the wheel cylinders to the pressure chambers.

Furthermore, the fifth valve can be provided as a check valve that only allows the pressure medium to flow from the first hydraulic circuit to the pressure chambers, and the sixth valve is provided as a check valve that only allows the pressure medium to flow from the second hydraulic circuit to the pressure chambers.

The electronic braking system further includes a first backup passage connecting the main chamber and the first hydraulic circuit; a second replacement passage, the simulation chamber and the second connecting hydraulic circuit; a first shut-off valve provided in the first backup passage to control the flow of the pressure medium; and a second shut-off valve provided in the second backup passage to control the flow of the pressure medium.

Further, the container passage may comprise a first container passage that connects the container and the main chamber to one another, and a second container passage that connects the container and the simulation chamber to one another.

The electronic braking system further includes a first reservoir valve provided in the first reservoir passage to control the flow of the pressure medium; and a second container valve provided in the second container passage to control the flow of the pressure medium.

The electronic brake system further includes a simulation passage provided in the second tank passage for promptly connecting a front end and a rear end of the second tank valve; and a simulation valve provided in the simulation passage to control the flow of the pressure medium in both directions.

The electronic brake system further comprises a verification passage provided in the first container passage for communicating a front end and a rear end of the first container valve in a prompt manner; and a check valve provided in the check passage to control the flow of the pressure medium in both directions.

Further, the first hydraulic circuit may include a first inlet valve and a second inlet valve for respectively controlling the flow of the pressure medium supplied to the first and second wheel cylinders, and a first outlet valve and a second outlet valve for respectively controlling the flow of the first and second The second hydraulic circuit comprises a third inlet valve and a fourth inlet valve for respectively controlling the flow of the pressure medium supplied to the third and fourth wheel cylinders and a second shut-off valve for controlling the flow of the from the third wheel cylinder to the container discharged pressure medium, and the second substitute passage connects the simulation chamber to downstream sides of the third and fourth inlet valves.

The electronic braking system further comprises a drain control provided between the container and the hydraulic pressure supply device in order to control the flow of the pressure medium, the drain control comprising a first drain passage which connects the first pressure chamber and the container to one another, and a first drain check valve provided in the first drain passage , which only allows the flow of the pressure medium from the container to the first pressure chamber.

In accordance with the other aspect of the present disclosure, a method of operating an electronic braking system, in a normal operating mode, may include the first shutoff valve that is closed to seal the main chamber, the second shutoff valve that is closed, and the simulation valve that is opened is to allow the first simulation chamber and the container to communicate with each other, so that the simulation piston compresses the elastic member by operating the brake pedal and an elastic restoring force of the elastic member is supplied to the driver as a pedal feeling.

Furthermore, in the normal operating mode, the hydraulic pressure formed in the first pressure chamber by moving the hydraulic piston forward can transmit to the first hydraulic circuit first through the first hydraulic passage, then the second hydraulic passage, then the fifth hydraulic passage and finally the sixth hydraulic passage and is transmitted to the second hydraulic circuit first through the first hydraulic passage, then the second hydraulic passage, then the fifth hydraulic passage and finally the seventh hydraulic passage.

Furthermore, when the normal operating mode is released, the second valve can be switched to an open state, and the pressure medium supplied to the first hydraulic circuit and the second hydraulic circuit is transmitted to the first pressure chamber, in which a negative pressure through the eighth hydraulic passage and the third hydraulic passage is formed.

Further, in an abnormal operating mode, the first shut-off valve can be opened to allow the main chamber and the first hydraulic circuit to communicate with each other, with the simulation valve closed and the second shut-off valve opened, so that the first simulation chamber and the second hydraulic circuit communicate with each other in accordance with a pressing force of the brake pedal, the pressure medium of the main chamber through the first replacement passage to the first hydraulic circuit is transmitted and the pressure medium of the simulation chamber is transmitted through the second substitute passage to the second hydraulic circuit.

Further, in a check mode for checking whether the integrated master cylinder is leaking, the second cut-off valve and the check valve, the hydraulic pressure generated by operating the hydraulic pressure supply device is supplied to the main chamber through the hydraulic controller and the first substitute passage, the integrated master cylinder by comparing one Hydraulic pressure value of the pressure medium, which is expected to be generated by the displacement of the hydraulic piston, with a hydraulic pressure value of the pressure medium, which is measured by a pressure sensor in the first hydraulic circuit of the main chamber, determined to be leaky.

Figure list

• 1 ein Schaubild eines hydraulischen Kreislaufs ist, das ein elektronisches Bremssystem gemäß einer Ausführungsform der vorliegenden Offenbarung zeigt;
• 2 ein Schaubild eines hydraulischen Kreislaufs ist, das einen Zustand zeigt, in dem ein elektronisches Bremssystem gemäß einer Ausführungsform der vorliegenden Offenbarung einen normalen Betriebsmodus zum Bremsen durchführt;
• 3 ein Schaubild eines hydraulischen Kreislaufs ist, das einen Zustand zeigt, in dem ein elektronisches Bremssystem gemäß einer Ausführungsform der vorliegenden Offenbarung einen normalen Betriebsmodus freigibt;
• 4 ein Schaubild eines hydraulischen Kreislaufs ist, das einen Zustand zeigt, in dem ein elektronisches Bremssystem gemäß einer Ausführungsform der vorliegenden Offenbarung einen abnormalen Betriebsmodus (Reservemodus) durchführt;
• 5 ein Schaubild eines hydraulischen Kreislaufs ist, das einen Zustand zeigt, in dem ein elektronisches Bremssystem gemäß einer Ausführungsform der vorliegenden Offenbarung einen Überprüfungsmodus durchführt.

These and / or other aspects of the disclosure will be apparent and easier to recognize from the following description of the embodiments in conjunction with the accompanying drawings, wherein:

• 1 Figure 3 is a hydraulic circuit diagram showing an electronic braking system according to an embodiment of the present disclosure;
• 2 FIG. 12 is a hydraulic circuit diagram showing a state where an electronic braking system according to an embodiment of the present disclosure is performing a normal operation mode for braking;
• 3 FIG. 13 is a hydraulic circuit diagram showing a state where an electronic brake system according to an embodiment of the present disclosure enables a normal operation mode;
• 4th FIG. 12 is a hydraulic circuit diagram showing a state in which an electronic brake system according to an embodiment of the present disclosure is performing an abnormal operation mode (reserve mode);
• 5 FIG. 12 is a hydraulic circuit diagram showing a state in which an electronic brake system according to an embodiment of the present disclosure is performing a check mode.

DETAILED DESCRIPTION

In the following, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings. The following embodiments are provided in order to sufficiently convey the technical concepts of the disclosure to one of ordinary skill in the art. However, the disclosure is not limited to these embodiments and can be carried out in another form. In the drawings, parts that are irrelevant to the descriptions may not be shown in order to clarify the disclosure, and the widths, lengths, thicknesses, etc. of the components are shown more or less exaggerated for better understanding. Like numerals refer to like elements throughout this specification.

1 is a hydraulic circuit diagram that includes an electronic braking system 1000 illustrated in accordance with an embodiment of the present disclosure.

With reference to 1 can use an electronic braking system 1000 according to one embodiment of the present invention, comprise a container 1100 for storing a print medium, an integrated master cylinder 1200 for providing a reaction force in accordance with a pressing force of the brake pedal 10 to the driver and for pressurizing and releasing the pressure medium contained therein, such as brake oil, a hydraulic pressure supply device 1300 by a pedal stroke sensor 11 for detecting a stroke of the brake pedal 10 receives an electrical signal corresponding to the driver's will to brake and generates hydraulic pressure of the pressure medium through mechanical operation, a hydraulic control 1400 for controlling the from the hydraulic pressure supply device 1300 supplied hydraulic pressure, hydraulic circuits 1510 and 1520 who have favourited a wheel cylinder 20th for receiving the hydraulic pressure of the pressure medium to perform braking of each of the wheels RR, RL, FR and FL, one between the hydraulic pressure supply device 1300 and the container 1100 intended emptying control 1800 to control a flow of print media, spare passes 1610 and 1620 for the hydraulic connection of the integrated master cylinder 1200 with the hydraulic circuits 1510 and 1520 , a container passage 1700 for hydraulic connection of the container 1100 with the integrated master cylinder 1200 , and an electronic control unit (ECU; not shown) for controlling the hydraulic pressure supply device 1300 and various valves based on hydraulic pressure information and pedal displacement information.

The integrated master cylinder 1200 includes a main chamber 1220a and a simulation chamber 1230a and notifies the driver when the brake pedal 10 is applied by the driver to brake, a reaction force ready to provide a stable pedal feel, and pressurizes and discharges the pressure medium contained therein.

The integrated master cylinder 1200 may be converted into a pedal simulation part for providing a pedal feeling to the driver and a master cylinder part for transmitting the pressure medium to a first hydraulic circuit 1510 which will be described later can be divided. The integrated master cylinder 1200 can be coaxial within a cylinder block 1210 be arranged in which the master cylinder part and the pedal simulation part sequentially from the side of the brake pedal 10 are provided.

In particular, the integrated master cylinder 1200 a cylinder block forming a chamber on an inner side 1210 include, one on an intake side of the cylinder block 1210 formed main chamber 1220a with a brake pedal 10 connected, one like that in the main chamber 1220a provided and with the brake pedal 10 connected main piston 1220 , so that this by pressing the brake pedal 10 is displaceable, a piston spring 1240 for elastic support of the main piston 1220 , a simulation chamber 1230a which is formed inwardly with respect to the main chamber 1220a on the cylinder block 1210 , one in the simulation chamber 1230a provided simulation piston 1230 to by the hydraulic pressure of the pressure medium in the main chamber 1220a or a displacement of the main piston 1220 to be relocatable, one between the simulation piston 1230 and an inner wall of the cylinder block 1210 arranged and a pedal feeling by an elastic restoring force generated upon compression providing elastic element 1250 , and one common to the elastic element 1250 in the simulation chamber 1230a provided simulation spring 1270 to the simulation piston 1230 to support elastic.

The main chamber 1220a and the simulation chamber 1230a are sequential on the cylinder block 1210 of the integrated master cylinder 1200 from the side of the brake pedal 10 (with reference to 1 the right side) to the inside (referring to 1 the left side). You can also use the main piston 1220 and the simulation piston 1230 each in the main chamber 1220a and the simulation chamber 1230a be provided to develop hydraulic pressure or negative pressure on the pressure medium accommodated in each chamber in accordance with forward and backward movements.

The main chamber 1220a can be on an entry side or an outermost side (with reference to 1 the right side) of the cylinder block 1210 be formed and the via an input rod 12th with the brake pedal 10 connected main piston 1220 can be reciprocated in the main chamber 1220a be included.

The main chamber 1220a can the pressure medium through a first hydraulic connection 1280a and a second hydraulic connection 1280b receive and deliver. The first hydraulic connection 1280a is so with a first container passage 1710 , which will be described later, that the printing medium from the container 1100 in the main chamber 1220a can be introduced, the second hydraulic connection 1280b is with a first replacement pass 1610 , which will be described later, is connected to the pressure medium from the main chamber 1220a towards the first substitute run 1610 and in return the print medium from the first replacement run 1610 in the main chamber 1220a to introduce. A pair of sealing elements 1290a is on a front and a rear side of the first hydraulic port 1280a provided to prevent leakage of the pressure medium.

The main piston 1220 is in the main chamber 1220a provided and can be forwarded (with reference to 1 to the left) to increase the hydraulic pressure by pressurizing the pressure medium in the main chamber 1220a to form, and backwards (referring to 1 to the right) to reduce the negative pressure in the main chamber 1220a to build.

The simulation chamber 1230a can be found inside the main chamber 1220a on the cylinder block 1210 (with reference to 1 the left side) and the simulation piston 1230 can with the simulation chamber 1230a be provided in a reciprocable manner.

The simulation chamber 1230a can allow the pressure medium through a third hydraulic connection 1280c , a fourth hydraulic connection 1280d and a fifth hydraulic connection 1280e to receive or deliver. The third hydraulic connection 1280c is like that with a second container passage 1720 , which will be described later, that the printing medium from the container 1100 into the simulation chamber 1230a can be introduced, and the fourth hydraulic connection 1280d is like that with a second replacement pass 1620 , which will be described later, connected that the pressure medium from the simulation chamber 1230a towards the second replacement pass 1620 can be submitted and in return from the second substitute round 1620 in the Simulation chamber 1230a can be introduced. The fifth hydraulic connection 1280e is with the second container passage 1720 connected so that the print media from the container 1100 into the simulation chamber 1230a can be introduced and in return from the simulation chamber 1230a to the container 1100 can be delivered. At least one sealing element 1290b can be between a front and a rear side of the fifth hydraulic connection 1280e be provided, in particular between the inner wall of the cylinder block 1210 and an outer peripheral surface of the simulation piston 1230 to prevent the pressure medium from escaping between adjacent chambers.

The simulation piston 1230 is in the simulation chamber 1230a provided and can be moved forward to increase the hydraulic pressure of the pressure medium in the simulation chamber 1230a to form or around the elastic element 1250 to push and move backwards to reduce the negative pressure in the simulation chamber 1230a to form or the elastic element 1250 to return to its original position and shape.

The simulation piston 1230 can be a shut-off hole 1232 for selective connection of the simulation chamber 1230a with the fifth hydraulic connection 1280e exhibit. The shut-off hole 1232 is inside the simulation piston 1230 formed and connects the simulation chamber 1230a with the fifth hydraulic connection 1280e when the simulation piston 1230 is in an original position (a normal stop position) and when the simulation piston is 1230 moves the connection between the simulation chamber 1230a and the fifth hydraulic connection 1280e interrupted to block the media from moving.

A stepped part can be attached to the cylinder block 1210 be formed at a point where the simulation chamber 1230a is formed, and an extension part can so on an outer peripheral surface of the simulation piston 1230 be formed so that it protrudes outward and is received by the step-shaped part. The extension part of the simulation piston 1230 is from the stepped part of the cylinder block 1210 added to one degree of the reverse stroke of the simulation piston 1230 restrict when the simulation piston 1230 moved backwards to after moving forward by depressing the brake pedal 10 return to the original position.

Meanwhile, the integrated master cylinder includes 1200 according to the present embodiment, the main chamber 1220a and the simulation chamber 1230a to ensure safety in the event of a failure of the component elements. For example, the main chamber 1220a about the first substitute run 1610 be connected to any two wheels from the right wheel FR, the left front wheel FL, the left rear wheel RL and the right wheel RR, and the simulation chamber 1230a can use the second replacement pass 1620 which will be described later with the other two wheel cylinders 20th be connected. Accordingly, even if a problem such as leakage occurs in one of the chambers, braking of a vehicle may be possible. A detailed description thereof will be given later with reference to FIG 4th given.

The elastic element 1250 is between the simulation piston 1230 and the inner wall of the cylinder block 1210 inserted and designed to give the driver the pedal feel of the brake pedal through its elastic restoring force 10 to deliver. The elastic element 1250 can be made of a material such as compressible and inflatable rubber. By pressing the brake pedal 10 a displacement occurs in the simulation piston 1230 and the elastic element 1250 is compressed by this displacement and the elastic restoring force of the compressed elastic element 1250 allows the driver to get a stable and familiar pedal feel. A detailed description thereof will be described later.

A recess that is a shape of the elastic element 1250 corresponds to is on the rear surface (referring to 1 the left side) of the simulation piston 1230 compared to the elastic element 1250 formed so that the elastic element 1250 is easily compressed and deformed.

The simulation spring 1270 is provided to the simulation piston 1230 to support elastic. An end to the simulation pen 1270 is on the cylinder block 1210 and the other end is on the simulation piston 1230 propped to the simulation piston 1230 to support elastic. If by a forward movement of the simulation piston 1230 a displacement occurs after braking, the simulation spring 1270 compressed. The simulation spring then expands 1270 due to an elastic force when braking is released, and the simulation piston 1230 returns to its original position.

A simulation run 1260 is provided to it's simulation chamber 1230a and the container 1100 to allow to communicate with each other, and the simulation pass 1260 can with a simulation valve 1261 to control of the flow of the print medium in both directions. The simulation valve 1261 can be designed as a normally closed solenoid valve which is normally closed and which opens the valve upon receiving an electrical signal from the electronic control unit. The simulation valve 1261 can be in a normal operating mode of the electronic braking system 1000 be opened. The simulation channel 1260 may have a front end and a rear end of a second container valve 1721 on the second container passage 1720 that will be described later. A flow passage through which the pressure medium flowing into the fifth hydraulic connection 1280e flows and out of it, moves, can with a tank side of the simulation passage 1260 of the simulation valve 1261 be connected.

The following is the pedal simulation operation by the integrated master cylinder 1200 described. During normal operation, the driver depresses the brake pedal and a first shut-off valve is activated at the same time 1611 and in a first replacement round each time 1610 and a second replacement fluid passage 1620 provided second shut-off valves 1621a and 1621b switched to "closed" while the simulation valve 1261 of the simulation run 1260 is switched to "open". The main piston 1220 will while the operation of the brake pedal 10 is continued, moved forward, but the main chamber 1220a is caused by the closing of the first shut-off valve 1611 closed. As a result, the hydraulic pressure becomes that in the main chamber 1220a accommodated pressure medium to the simulation piston 1230 transferred that the simulation piston 1230 moves forward and a dislocation occurs. The displacement of the simulation piston 1230 compresses the elastic element 1250 and the elastic restoring force can be caused by the compression of the elastic element 1250 delivered to the driver as a pedal feel. At this point it will be in the simulation chamber 1230a housed print medium through the simulation pass 1260 to the container 1100 transfer. After that, when the driver depresses the brake pedal 10 releases are the piston spring 1240 , the simulation spring 1270 and the elastic element 1250 returned to their original shape and position by the elastic restoring force and the simulation chamber 1230a can with the one from the container 1100 through the simulation run 1260 and the second container passage 1720 supplied pressure medium are filled.

Because the inside of the simulation chamber 1230a is always filled with the pressure medium, the friction of the simulation piston 1230 minimized during the pedal simulation operation, so that a service life of the integrated master cylinder 1200 is improved and an inflow of foreign bodies can be blocked from the outside.

That is, if the electronic braking system 1000 is operated abnormally, the operation of the integrated master cylinder 1200 in a reserve mode later referring to FIG 4th described.

In the meantime, the container receives 1100 the print medium and stores it inside. The container 1100 is with each component element such as the integrated master cylinder 1200 , the hydraulic pressure supply device described later 1300 and a hydraulic circuit described later and can supply or receive the pressure medium. There are several containers in the figures 1100 identified by the same reference numerals. However, this is an example of how Revelation can be better understood; the container 1100 can be provided as a single part or can be provided as several separate, independent parts.

The container passage 1700 is provided to the integrated master cylinder 1200 and the container 1100 to connect with each other.

The container passage 1700 includes a first container passage 1710 who is the main chamber 1220a and the container 1100 connects together, and a second container passage 1720 who is the simulation chamber 1230a and the container 1100 connects with each other. One end of the first container passage 1710 can with the main chamber 1220a of the integrated master cylinder 1200 communicate and the other end can with the container 1100 communicate. In addition, one end of the second container passage 1720 with the simulation chamber 1230a of the integrated master cylinder 1200 communicate and the other end can with the container 1100 communicate.

The first container passage 1710 can with a first tank valve 1711 for controlling the flow of the through the first container passage 1710 transferred print medium be provided. The first tank valve 1711 can be designed as a check valve that controls the flow of the pressure medium from the container 1100 to the main chamber 1220a while allowing the flow of pressure medium from the main chamber 1220a to the container 1100 blocked.

In addition, there is a review round 1630 parallel to a front and a rear side of the first container valve 1711 with the first container passage 1710 connected and the Review pass 1630 can with a check valve 1631 for controlling the flow of pressure medium between the main chamber 1220a and the container 1100 be provided. That is, the review channel 1630 can be the front end and the rear end of the first container valve 1711 on the first container passage 1710 bypass, and the check valve 1631 can be used as a bidirectional solenoid valve to control the flow of pressure medium between the main chamber 1220a and the container 1100 be trained. The check valve 1631 may be provided with a normally open solenoid valve which is normally open and which closes the valve when it receives an electrical signal from the electronic control unit. The check valve 1631 can be closed in a checking mode to check whether the integrated master cylinder 1200 is leaking. A detailed description thereof will be described later.

The second container passage 1720 can with a second tank valve 1721 for controlling the flow of the through the second container passage 1720 transferred print medium. The second tank valve 1721 can be designed as a check valve that controls the flow of the pressure medium from the container 1100 to the simulation chamber 1230a while allowing the flow of pressure medium from the simulation chamber 1230a to the container 1100 blocked.

In addition, there is the simulation run 1260 parallel to a front and a rear side of the second container valve 1721 with the second container passage 1720 connected and the simulation run 1260 is with a simulation valve 1261 to control the flow of the pressure medium between the simulation chamber 1230a and the container 1100 provided in both directions.

The hydraulic pressure supply device 1300 is provided to generate an electrical signal from the pedal stroke sensor that corresponds to the driver's will to brake 11 to receive a brake pedal dislocation 10 detected and generated a hydraulic pressure of the pressure medium by mechanical operation.

The hydraulic pressure supply device 1300 can use a hydraulic pressure provider to provide one to the wheel cylinder 20th transmitted pressure of the pressure medium comprise a motor (not shown) for generating a rotational force by an electrical signal of the pedal stroke sensor 11 and a power converter (not shown) for converting the rotary motion of the motor into linear motion and transmitting the linear motion to the hydraulic pressure provider.

The hydraulic pressure provider can be a cylinder block 1310 , in which the pressure medium is accommodated, a hydraulic piston 1320 that is in the cylinder block 1310 is added, a sealing element 1350 that is between the hydraulic piston 1320 and the cylinder block 1310 for sealing the pressure chambers 1330 and 1340 is provided, and a drive shaft 1390 for transmitting an output power from the power converter to the hydraulic piston 1320 include.

The pressure chambers 1330 and 1340 include a first pressure chamber 1330 that is in front of the hydraulic piston 1320 located (with reference to 1 in the left direction from the hydraulic piston 1320 ) and a second pressure chamber 1330 that is behind the hydraulic piston 1320 (with reference to 1 in the right direction from the hydraulic piston 1320 ) is located. That is, the first pressure chamber 1330 is through a front surface of the cylinder block 1310 and the hydraulic piston 1320 and is designed so that its volume can be varied while the hydraulic piston is moving 1320 moved, and the second pressure chamber 1340 is through the rear surface of the cylinder block 1310 and the hydraulic piston 1320 provided so that their volume can be varied while the hydraulic piston is moving 1320 emotional.

The first pressure chamber 1330 is through one in the cylinder block 1310 formed first communication hole 1360a with a first hydraulic passage 1401 which will be described later and the second pressure chamber 1340 is through one in the cylinder block 1310 second communication hole formed 1360b with a fourth hydraulic passage 1404 which will be described later.

The sealing element 1350 can be a piston seal element 1350a include that between the hydraulic piston 1320 and the cylinder block 1310 for sealing between the first pressure chamber 1330 and the second pressure chamber 1340 is provided, and a drive shaft seal member 1350b that is between the drive shaft 1390 and the cylinder block 1310 is provided for sealing an opening of the second pressure chamber 1340 and the cylinder block 1310 . The one caused by the forward or backward movement of the hydraulic piston 1320 generated hydraulic pressure or negative pressure of the first pressure chamber 1330 and the second pressure chamber 1340 is through the piston seal element 1350a and the drive shaft seal member 1350b sealed without outlet and connected to a first hydraulic passage 1401 and a hydraulic passage 1404 which will be described later.

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

The power converter (not shown) is provided to convert the rotational force of the motor into linear motion. For example, the power converter may include a worm shaft (not shown), a worm wheel (not shown), and the drive shaft 1390 include.

The worm shaft can be formed integrally with the rotating shaft of the motor, and can rotate the worm wheel by forming a worm on an outer peripheral surface of the worm shaft so that it meshes with the worm wheel. The worm wheel meshes with the drive shaft 1390 and is connected to it to the drive shaft 1390 to move linearly, and the drive shaft 1390 is with the hydraulic piston 1320 connected so the hydraulic piston 1320 in the cylinder block 1310 can be moved slidably.

The above processes are described again below. When the displacement of the brake pedal 10 from the pedal stroke sensor 11 is detected, a detected signal is transmitted to the electronic control unit, and the electronic control unit drives the motor to rotate the worm shaft in one direction. The rotating force of the worm shaft is transmitted to the drive shaft via the worm wheel 1390 transferred and in the first pressure chamber 1330 A hydraulic pressure can be generated while the with the drive shaft 1390 connected hydraulic pistons 1320 in the cylinder block 1310 moved forward.

When the pressing force of the brake pedal 10 is released, the electronic control unit drives the motor to rotate the worm shaft in the opposite direction. Correspondingly, the worm wheel also rotates in the opposite direction and in the first pressure chamber 1330 A negative pressure can be generated while the with the drive shaft 1390 connected hydraulic pistons 1320 in the cylinder block 1310 moved backwards.

The generation of the hydraulic pressure and the negative pressure in the second pressure chamber 1340 can be achieved by reversing the operation described above. That is, when the movement of the brake pedal 10 from the pedal stroke sensor 11 is detected, a detected signal is transmitted to the electronic control unit and the electronic control unit drives the motor to rotate the worm shaft in the opposite direction. The rotating force of the worm shaft is transmitted to the drive shaft via the worm wheel 1390 transferred and in the second pressure chamber 1340 A hydraulic pressure can be generated while the with the drive shaft 1390 connected hydraulic pistons 1320 in the cylinder block 1310 moved backwards.

When the pressing force of the brake pedal 10 whereas is released, the electronic control unit drives the motor in one direction to rotate the worm shaft in one direction. Accordingly, the worm wheel also rotates in one direction and in the second pressure chamber 1340 A negative pressure can be generated while the with the drive shaft 1390 connected hydraulic pistons 1320 in the cylinder block 1310 moved forward.

Thus, the hydraulic pressure supply device generates 1300 in the first pressure chamber 1330 and the second pressure chamber 1340 a hydraulic pressure or a negative pressure in accordance with the direction of rotation of the worm shaft driven by the motor and whether braking should be done by transmitting the hydraulic pressure or whether braking should be released using the negative pressure can be determined by controlling the valves. A detailed description thereof will be described later.

Meanwhile, the power converter according to an embodiment of the present disclosure is not limited to a single structure as long as it can convert a rotary motion of the motor into linear motion, and can be configured as an apparatus having various structures and means.

The hydraulic pressure supply device 1300 can be controlled by emptying 1800 hydraulically with the tank 1100 be connected. The emptying control 1800 can make a first drainage pass 1810 include the first pressure chamber 1330 with the container 1100 connects.

The first drainage pass 1810 can with a first drainage check valve 1811 be provided for controlling the flow of the print medium. The first drain check valve 1811 can be provided to exclusively control the flow of the pressure medium from the container 1100 into the first pressure chamber 1330 to allow and block the flow of the print medium in the opposite direction.

The hydraulic control 1400 can be provided to the wheel cylinder 20th to control transmitted hydraulic pressure and the electronic control unit (ECU) is provided to control the hydraulic pressure supply device 1300 and control various valves based on hydraulic pressure information and pedal displacement information.

The hydraulic control 1400 can have a first hydraulic circuit 1510 for controlling the flow of hydraulic pressure applied to first and second wheel cylinders 21st and 22nd from the four wheel cylinders 20th and a second hydraulic circuit 1520 for controlling the flow of hydraulic pressure applied to third and fourth wheel cylinders 23 and 24 and a plurality of passages and valves for controlling the hydraulic pressure supplied by the hydraulic pressure supply device 1300 to the wheel cylinder 20th is transmitted, include.

A first hydraulic passage 1401 is intended to be connected to the first pressure chamber 1330 to communicate and can in a second hydraulic passage 1402 and a third hydraulic passage 1403 branch off. A fourth hydraulic passage 1404 is intended to be connected to the second pressure chamber 1340 to communicate and can be provided to deal with the second hydraulic passage 1402 through a fifth hydraulic passage 1405 which will be described later. The fifth hydraulic passage 1405 branches into a sixth, with the first hydraulic circuit 1510 connected hydraulic passage 1406 and a seventh, with the second hydraulic circuit 1520 connected hydraulic passage 1407 from. One end of an eighth hydraulic passage 1408 can with the third hydraulic passage 1403 be connected and the other end can be branched off and each with the sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 unite.

The second hydraulic passage 1402 can with a first valve 1411 be provided for controlling the flow of the printing medium. The first valve 1411 can be designed as a check valve that only controls the flow of the from the first pressure chamber 1330 towards the fifth hydraulic passage 1405 discharged print medium while it blocks the flow of print medium in the opposite direction.

The third hydraulic passage 1403 can with a second valve 1412 be provided for controlling the flow of the printing medium. The second valve 1412 can act as a bidirectional control valve for controlling the flow of the along the third hydraulic passage 1403 be formed transferred print medium. The second valve 1412 can be designed as a normally closed solenoid valve which is normally closed and which opens the valve upon receiving an electrical signal from the electronic control unit.

The fourth hydraulic passage 1404 and the second hydraulic passage 1402 unite on the fifth hydraulic passage 1405 and the fifth hydraulic passage 1405 branches again into the sixth, with the first hydraulic circuit 1510 connected hydraulic passage 1406 and the seventh, with the second hydraulic circuit 1520 connected hydraulic passage 1407 from.

The sixth hydraulic passage 1406 can with a third valve 1413 be provided for controlling the flow of the print medium. The third valve 1413 can be designed as a check valve, which exclusively controls the flow of the pressure medium from the pressure chamber in the direction of the fifth hydraulic circuit 1510 allowed while blocking the flow of print medium in the opposite direction. That is, the third valve 1413 allows that the hydraulic pressure of the pressure medium generated in the pressure chamber to the first hydraulic circuit 1510 is transmitted, but prevents the flow of the pressure medium in the opposite direction towards the pressure chamber through the sixth hydraulic passage 1406 exit.

The seventh hydraulic passage 1407 can with a fourth valve 1414 be provided for controlling the flow of the printing medium. The fourth valve 1414 can be designed as a check valve that only controls the flow of the pressure medium from the pressure chamber in the direction of the second hydraulic circuit 1520 allowed while blocking the flow of print medium in the opposite direction. That is, the fourth valve 1414 allows that the hydraulic pressure of the pressure medium generated in the pressure chamber to the second hydraulic circuit 1520 is transmitted, however, prevents the flow of the pressure medium in the opposite direction towards the pressure chamber through the seventh hydraulic passage 1407 exit.

One end of the eighth hydraulic passage 1408 is with a downstream side of the third, from the first hydraulic passage 1401 branching hydraulic passage 1403 connected and the other end branches off on both sides and unites with the sixth hydraulic passage 1406 and the seventh hydraulic passage 1407 .

The eighth hydraulic passage 1408 can with a fifth valve 1415 on one with the sixth hydraulic passage 1406 unified passage side and a sixth valve 1416 be provided on a passage side united with the seventh hydraulic passage. The fifth valve 1415 can be provided as a check valve that controls the flow of the pressure medium from the pressure chamber in the direction of the fifth hydraulic circuit 1510 blocked while allowing the media to flow in the opposite direction. The sixth valve 1416 can be provided as a check valve that controls the flow of the pressure medium from the pressure chamber in the direction of the second hydraulic circuit 1520 blocked while allowing the media to flow in the opposite direction. The fifth valve 1415 is on the eighth hydraulic passage 1408 that is between the one in the sixth hydraulic passage 1406 provided third valve 1413 and the first hydraulic circuit 1510 connected is provided, the sixth valve 1416 is on the eighth hydraulic passage 1408 that is between the one in the seventh hydraulic passage 1407 provided fourth valve 1414 and the second hydraulic circuit 1520 is connected, provided. Accordingly, the fifth valve allow it 1415 and the sixth valve 1416 that in the first and second hydraulic circuit 1510 and 1520 generated hydraulic pressure of the pressure medium to the first pressure chamber 1330 To be transmitted, however, prevent the flow of the pressure medium in the opposite direction to the first and the second hydraulic circuit 1510 and 1520 through the third hydraulic passage 1403 exit. The second valve 1412 which is a normally closed solenoid valve is on the third hydraulic passage 1403 provided between a partial passage of the between the fifth and the sixth valve 1415 and 1416 located eighth passage 1408 and the first hydraulic passage 1401 .

The hydraulic control 1400 having the hydraulic passages described above and the valve arrangement described above, while the hydraulic piston 1320 moved forward in the first pressure chamber 1330 hydraulic pressure formed first by the first hydraulic passage 1401 , then the second hydraulic passage 1402 , then the fifth hydraulic passage 1405 and finally the sixth hydraulic passage 1406 to the first hydraulic circuit 1510 and it first through the first hydraulic passage 1401 , then the second hydraulic passage 1402 , then the fifth hydraulic passage 1405 and finally the seventh hydraulic passage 1407 to the second hydraulic circuit 1520 transfer.

In contrast, the one in the first pressure chamber 1330 in response to the backward movement of the hydraulic piston 1320 vacuum formed the hydraulic pressure or the pressure medium of the first hydraulic circuit 1510 and the second hydraulic circuit 1520 to the first pressure chamber 1330 lead back. More precisely, if the second valve can 1412 is opened, the hydraulic pressure of the first hydraulic circuit 1510 first through the eighth hydraulic passage 1408 and then the first hydraulic passage 1401 to the first pressure chamber 1330 are transmitted and the hydraulic pressure of the second hydraulic circuit 1520 first through the eighth hydraulic passage 1408 and then the first hydraulic passage 1401 to the first pressure chamber 1330 be transmitted.

Details of the transmission and supply of hydraulic pressure through these hydraulic passages and the arrangement of the valves will be given later with reference to FIG 2 to 4th to be discribed.

The first hydraulic circuit 1510 the hydraulic control 1400 can control the hydraulic pressure of the first and second wheel cylinders 21st and 22nd who have favourited Two Wheel Cylinders 20th of the four wheels are RR, RL, FR and FL, control and the second hydraulic circuit 1520 can control the hydraulic pressure of the third and fourth wheel cylinders 23 and 24 who have favourited the other two wheel cylinders 20th are, control.

The first hydraulic circuit 1510 becomes the hydraulic pressure from the hydraulic pressure supply device 1300 through the sixth hydraulic passage 1406 and the sixth hydraulic passage 1406 branches off on both sides and is in each case with the first wheel cylinder 21st and the second wheel cylinder 22nd connected. It also becomes the second hydraulic circuit 1520 the hydraulic pressure from the hydraulic pressure supply device 1300 through the seventh hydraulic passage 1407 fed and the seventh hydraulic passage 1407 branches off on both sides and is in each case with the third wheel cylinder 23 and the fourth wheel cylinder 24 connected.

The first and second hydraulic circuits 1510 and 1520 can each have a first through fourth inlet valve 1511a , 1511b , 1521a and 1521b include the flow and hydraulic pressure of the to the first through fourth wheel cylinders 21st to 24 to control transferred print medium. The first through fourth inlet valves 1511a , 1511b , 1521a and 1521b are each on an upstream side of the first to fourth wheel cylinders 21st to 24 and may be provided as a normally open solenoid valve which is normally open and which closes the valve upon receiving an electrical signal from the electronic control unit.

The first and second hydraulic circuits 1510 and 1520 can have a first to fourth check valve 1513a , 1513b , 1523a and 1523b include parallel to the first through fourth inlet valves 1511a , 1511b , 1521ac and 1521b are connected. The check valves 1513a , 1513b , 1523a and 1523b may be provided at bypass passages, the front and rear of the respective intake valves 1511a , 1511b , 1521a and 1521b on the first and second hydraulic circuit 1510 and 1520 interconnect, and can be provided to prevent the flow of pressure medium from the wheel cylinders 20th to the hydraulic pressure supply device 1300 to allow and the flow of pressure medium from the hydraulic pressure supply device 1300 to the wheel cylinders 20th to block. The check valves 1513a , 1513b , 1523a and 1523b can allow the hydraulic pressure of the on the wheel cylinder 20th applied pressure medium is released quickly and can allow the hydraulic pressure of the on the wheel cylinder 20th applied pressure medium is returned to the hydraulic pressure provider without problems, even if the inlet valves 1511a , 1511b , 1521ac and 1521b cannot be operated normally.

The first hydraulic circuit 1510 may have a first and a second exhaust valve 1512a and 1512b to improve the performance in releasing the braking of the first and second wheel cylinders 21st and 22nd with the container 1100 are connected. The first and second exhaust valves 1512a and 1512b are between the first and second wheel cylinders, respectively 21st and 22nd and the container 1100 provided to reduce the flow of the from the first and second wheel cylinders 21st and 22nd to the container 1100 to control delivered print medium. The first and second exhaust valves 1512a and 1512b can brake pressure of the first and second wheel cylinders 21st and 22nd detect and selectively open when a pressure reduction braking in an ABS deflation mode or the like is required to reduce the pressure of the wheel cylinders 20th to control. The first and second exhaust valves 1512a and 1512b can be provided as a normally closed solenoid valve which is normally closed and which opens the valve upon receiving an electrical signal from the electronic control unit.

Meanwhile, the third wheel cylinder can 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 with a second bypass pass 1620 to be described later, and the second bypass passage 1620 can with second shut-off valves 1621a and 1621b be provided to the flow of the pressure medium between the third and the fourth wheel cylinder 23 and 24 and the integrated master cylinder 1200 to control. The second shut-off valves 1621a and 1621b will be described later.

The second hydraulic circuit 1520 can second shut-off check valves 1623a and 1623b include parallel to the second shut-off check valves 1621a and 1621b are connected. The second shut-off check valves 1623a and 1623b can be provided at bypass passages, the front and rear of the respective second cut-off check valves 1621a and 1621b on the second hydraulic circuits 1520 interconnect, and may be provided to prevent the flow of print media from the second replacement passage 1620 to the wheel cylinders 20th to allow and block the flow of media in the opposite direction. Springs in the second shut-off valves 1621a and 1621b can be omitted.

The electronic braking system 1000 according to the present embodiment, the first and second replacement passages 1610 and 1620 so that that of the integrated master cylinder 1200 discharged pressure medium directly to the wheel cylinders 20th is supplied to perform braking in a case where normal operation is impossible due to failure of a device or the like. The mode in which hydraulic pressure of the integrated master cylinder 1200 directly to the wheel cylinder 20th is referred to as abnormal operation mode, that is, reserve mode.

The first replacement round 1610 is provided to the main chamber 1220a of the integrated master cylinder 1200 and the first hydraulic circuit 1510 connect to each other and the second replacement passage 1620 is provided to the simulation chamber 1230a of the integrated master cylinder 1200 and the second hydraulic circuit 1520 to connect with each other. The second replacement round 1620 can make an additional replacement pass 1640 to move the Pressure medium that emerges from the vicinity of the drive shaft sealing element 1350b the hydraulic pressure supply device 1300 flows out and into the vicinity of the drive shaft seal member 1350b the hydraulic pressure supply device 1300 flows into it, embrace.

More precisely, an end of the first replacement pass 1610 with the main chamber 1220a and the other end can be connected to upstream sides of the first intake valve 1511a and the second intake valve 1511b on the first hydraulic circuit 1510 be connected. In addition, one end of the second replacement pass 1620 with the simulation chamber 1230a and the other end can be connected to downstream sides of the third intake valve 1521a and the fourth intake valve 1521b on the second hydraulic circuit 1520 be connected. As in 1 shown, the first substitute run is shown 1610 than with the upstream side of the first intake valve 1511a connected illustrated. When the first replacement pass 1610 branches off and between the first inlet valve 1511a and the first exhaust valve 1512a is connected, so with at least one of the upstream sides of the first exhaust valve 1512a (and / or the second exhaust valve 1512b) , this should be understood as the same.

The first replacement round 1610 is with the first shut-off valve 1611 provided for controlling the flow of the printing medium in both directions and the second spare passage 1620 can with at least one of the shut-off valves 1621a and 1621b be provided. The first shut-off valve 1611 and the second shut-off valves 1621a and 1621b are provided as a normally open solenoid valve which is normally open and which closes the valve upon receiving an electrical signal from the electronic control unit. The second replacement round 1620 can second shut-off check valves 1623a and 1623b in parallel with the second shut-off valves 1621a and 1621b are connected, include. The second shut-off check valves 1623a and 1623b may be provided at bypass passages, the front and rear of the second cut-off check valves 1621a and 1621b on the second hydraulic circuit 1520 interconnect, and may be provided to prevent the flow of print media from the second replacement passage 1620 to the wheel cylinders 20th to allow and block the flow of media in the opposite direction. Springs in the second shut-off valves 1621a and 1621b can be omitted.

This prevents when the first shut-off valve 1611 and the second shut-off valves 1621a and 1621b are closed, the pressure medium of the integrated master cylinder 1200 directly to the wheel cylinder 20th is transmitted, and that from the hydraulic pressure supply device 1300 Supplied hydraulic pressure can be controlled by the hydraulic control 1400 the first and second hydraulic circuits 1510 and 1520 are fed. When the first shut-off valve 1611 and the second shut-off valves 1621a and 1621b are opened, this is done by the integrated master cylinder 1200 pressurized pressure medium the first and the second hydraulic circuit 1510 and 1520 through the first substitute run 1610 and the second replacement pass 1620 directly supplied, whereby the braking is implemented.

The electronic braking system 1000 According to the present embodiment, a pressure sensor PS for detecting the hydraulic pressure from the first hydraulic circuit 1510 and / or the second hydraulic circuit 1520 and for sensing the hydraulic pressure of the integrated master cylinder 1200 include. Although the pressure sensor PS on the side of the second hydraulic circuit 1520 As shown in the figure, it is not limited to a position and number of the pressure sensor PS, and the pressure sensor PS may be provided in various positions and numbers as long as the hydraulic pressure of the hydraulic circuit and the integrated master cylinder 1200 can be captured.

The following is a method for operating the electric braking system 1000 according to the present embodiment.

The operation of the electronic braking system 1000 According to the present embodiment, a normal operation mode in which various devices and valves are normally operated without abnormality or failure, and an abnormal operation mode (a reserve mode) in which various devices and valves are not operated normally due to the occurrence of the abnormality or failure , include.

First, the normal operating mode is made up of the procedures for operating the electronic braking system 1000 according to the present embodiment.

2 Fig. 13 is a hydraulic circuit diagram showing a state in which the electronic brake system 1000 according to the present embodiment is operated in the normal operating mode and that in the hydraulic pressure supply device 1300 generated hydraulic pressure quickly to the wheel cylinder 20th is transmitted.

With reference to 2 when the driver depresses the brake pedal 10 at the beginning of braking is depressed, the motor (not shown) is operated to rotate in one direction, the rotational force of the motor is transmitted to the hydraulic pressure provider through the power converter, and the hydraulic piston 1320 the hydraulic pressure provider moves forward to a hydraulic pressure in the first pressure chamber 1330 to create. The one from the first pressure chamber 1330 The hydraulic pressure delivered is controlled by the hydraulic control 1400 and the first and second hydraulic circuits 1510 and 1520 to the respective wheel cylinder 20th transmitted to generate a braking force.

More precisely, it runs through the first pressure chamber 1330 hydraulic pressure formed first the first hydraulic passage 1401 , then the second hydraulic passage 1402 , then the fifth hydraulic passage 1405 and finally the sixth hydraulic passage 1406 and is attached to the first and second wheel cylinders 21st and 22nd transferred that in the first hydraulic circuit 1510 are provided. At this time, the hydraulic pressure of the pressure medium while the first valve 1411 and the third valve 1413 as a check valve that only controls the flow of the pressure medium from the first pressure chamber 1330 towards the first hydraulic circuit 1510 allowed, are provided, easily to the first and the second wheel cylinder 21st and 22nd be transmitted. Also keep the first inlet valve 1511a and the second inlet valve 1511b that are in the hydraulic circuit 1510 are provided, the open state, and the first exhaust valve 1512a and the second exhaust valve 1512b maintain the closed state, which prevents the hydraulic pressure of the pressure medium from flowing in the direction of the container 1100 exit.

It also runs through the first pressure chamber 1330 formed hydraulic pressure of the pressure medium first the first hydraulic passage 1401 , then the second hydraulic passage 1402 , then the fifth hydraulic passage 1405 and finally the seventh hydraulic passage 1407 and is attached to the side of the second hydraulic circuit 1520 provided wheel cylinder 20th transfer. As described above, the hydraulic pressure of the pressure medium while the first valve 1411 and the fourth valve 1414 as check valves, which exclusively control the flow of the pressure medium from the first pressure chamber 1330 towards the second hydraulic circuit 1520 allow, are provided, easily to the third and fourth wheel cylinders 23 and 24 be transmitted. They also retained the third inlet valve 1521a and the fourth inlet valve 1521b that is in the second hydraulic circuit 1520 are provided, the open state, and the second shut-off valves 1621a and 1621b are switched to the closed state, thereby preventing the hydraulic pressure of the pressure medium from being directed towards the second replacement passage 1620 exit.

In normal operating mode, this allows in the first emptying cycle 1810 provided and with the first pressure chamber 1330 connected first evacuation check valve 1811 the flow of media from the container 1100 to the first pressure chamber 1330 and blocks the flow of pressure medium from the first pressure chamber 1330 to the container 1100 . Accordingly, the hydraulic piston moves forward 1320 in the first pressure chamber 1330 formed hydraulic pressure of the pressure medium to the first hydraulic passage 1401 transferred to achieve quick braking.

In addition, in the normal operating mode, the wheel cylinders are used to implement the braking 20th by the hydraulic pressure supply device 1300 , the first shut-off valve 1611 and the second shut-off valve 1621a and 1621b each in the first replacement round 1610 and in the second replacement round 1620 are provided, switched to the closed state, which prevents the integrated master cylinder 1200 hydraulic pressure of the pressure medium delivered to the wheel cylinder 20th is transmitted.

More precisely, the first shut-off valve 1611 when a pushing force on the brake pedal 10 is applied, closed so that the main chamber 1220a is sealed. That means that's in the main chamber 1220a housed pressure medium is pressurized to by the pressing force of the brake pedal 10 to form a hydraulic pressure, and that in the main chamber 1220a formed hydraulic pressure of the pressure medium to a front surface of the simulation piston (with reference to 2 a right surface) and, in normal operating mode, the simulation valve 1261 is switched to the open state, causing a displacement in the simulation piston 1230 he follows. In the normal operating mode of the electronic braking system 1000 causes the simulation piston to move 1230 , as the second shut-off valves 1621a and 1621b are closed that the elastic element 1250 is compressed, and the driver is an elastic restoring force due to the compression of the elastic element 1250 delivered as a pedal feel. At this point it will be in the simulation chamber 1230a housed print medium through the simulation pass 1260 to the container 1100 submitted.

The following is a method for releasing the braking in the normal operating mode of the electric braking system 1000 according to the present embodiment.

3 Fig. 13 is a hydraulic circuit diagram showing a state in which a hydraulic piston 1320 of the electronic braking system 1000 according to the present embodiment, releases the braking while moving backward.

With reference to 3 generated by the engine when the hit the brake pedal 10 applied compressive force is released, a turning force in the other direction to transmit it to the power converter, and the power converter moves the hydraulic piston 1320 backward. Accordingly, in the first pressure chamber 1330 a negative pressure can be generated, which enables the pressure medium of the wheel cylinder 20th to the first pressure chamber 1330 is transmitted.

More precisely, the hydraulic pressures pass through the first wheel cylinder 21st and the second wheel cylinder 22nd that is in the first hydraulic circuit 1510 are provided, first the eighth hydraulic passage 1408 , then the third hydraulic pass 1403 and finally the first hydraulic passage 1401 and are in the first pressure chamber 1330 returned. At this point the second valve will 1412 opened to allow the pressure medium to pass through the eighth hydraulic passage 1408 and the first hydraulic passage 1401 to flow, and the third valve 1413 of the sixth hydraulic passage 1406 maintains the closed state to prevent the pressure medium from reaching the second pressure chamber 1340 is transmitted so that the hydraulic piston 1320 can be moved backwards quickly and easily. The first inlet valve 1511a and the second inlet valve 1511b that is in the first hydraulic circuit 1510 are provided keep the open state, and the first exhaust valve 1512a and the second exhaust valve 1512b keep the closed state.

In addition, they pass through to the third wheel cylinder 23 and the fourth wheel cylinder 24 applied hydraulic pressures of the pressure medium in the second hydraulic circuit 1520 are provided by the in the first pressure chamber 1330 generated negative pressure first the eighth hydraulic passage 1408 , then the third hydraulic pass 1403 and finally the first hydraulic passage 1401 and are in the first pressure chamber 1330 returned. The third inlet valve 1521a and the fourth inlet valve 1521b that is in the second hydraulic circuit 1520 are provided, maintain the open state and the second shut-off valves 1621a and 1621b are switched to the closed state.

The operating status of the electronic braking system is shown below 1000 according to the present embodiment when it is not operated normally, that is, the reserve mode is described.

4th Fig. 13 is a hydraulic circuit diagram showing an operating state in an abnormal operating mode (reserve mode) when the electronic brake system 1000 according to the present embodiment is not operated normally due to a failure of the device or the like.

With reference to 4th each of the valves, in the abnormal operation mode, is controlled to be in a braking initial state which is a non-operating state. At this point the one with the brake pedal moves 10 connected main piston 1220 when the driver depresses the brake pedal 10 presses down, forward and a dislocation occurs. During the first shut-off valve 1611 is provided in the open state in the non-operational state, that moves in the main chamber 1220a provided pressure medium by the forward movement of the main piston 1220 along the first replacement pass 1610 to get to the first wheel cylinder 21st and the second wheel cylinder 22nd of the first hydraulic circuit 1510 to be transmitted, whereby it implements the braking.

That in the main chamber 1220a The pressure medium accommodated moves the simulation piston 1230 forward to create a displacement so that the pressure medium is in the simulation chamber 1230a through the second replacement run 1620 to the third wheel cylinder 23 and the fourth wheel cylinder 24 of the second hydraulic circuit 1520 is transmitted, whereby it implements the braking. At this point, while the second shut-off valves 1621a and 1621b are provided in the open state in the non-operational state, this can be done in the simulation chamber 1230a stored print media to the second spare passage 1620 be transmitted.

In the abnormal operation mode, during the first through fourth intake valves 1511a , 1511b , 1521a and 1521b in the first and in the second hydraulic circuit 1510 and 1520 are provided, are controlled so that they are in the open state and the simulation valve 1261 controlled so that it is in the closed state, that of the main chamber 1220a and the simulation chamber 1230a of the integrated master cylinder 1200 transferred hydraulic pressure immediately to the respective wheel cylinder 20th are transmitted, whereby improved braking stability and quick braking can be achieved. At this point a Check valve 1631 controlled so that it is in the abnormal operating mode when open, but can be controlled by the displacement of the main piston 1220 getting closed.

The following is a check mode of the electric brake system 1000 according to the present embodiment.

5 Fig. 13 is a hydraulic circuit diagram showing the check mode state of the electronic braking system 1000 according to the present embodiment. With reference to 5 can use the electronic braking system 1000 according to the present embodiment, the check mode for checking whether an integrated master cylinder 1200 is leaking. In the verification mode, the electrical control unit controls the one from the hydraulic pressure supply device 1300 generated hydraulic pressure that of the main chamber 1220a of the integrated master cylinder 1200 should be fed.

More specifically, since each of the valves is controlled to be in a braking initial state which is an inoperative state, and the electronic control unit controls the hydraulic piston 1320 moved forward to the hydraulic pressure in the first pressure chamber 1330 will generate the check valve 1631 and the second shut-off valves 1621a and 1621b switched to the closed state and the first shut-off valve 1611 maintains the open state. Accordingly, it passes through the first pressure chamber 1330 hydraulic pressure formed first the first hydraulic passage 1401 , then the second hydraulic passage 1402 and finally the sixth hydraulic passage 1406 and is attached to the first hydraulic circuit 1510 transfer. As the first inlet valve 1511a and the second inlet valve 1511b are normally open, this is connected to the first hydraulic circuit 1510 transferred print media through the first replacement pass 1610 in the main chamber 1220a introduced. At this point the simulation valve stops 1261 the closed state, so that the simulation chamber 1230a is sealed and the print medium does not move in it.

By comparing a hydraulic pressure value of the pressure medium, which is likely due to the displacement of the hydraulic piston 1320 is generated with a hydraulic pressure value of the first hydraulic circuit measured by the pressure sensor PS 1510 or the main chamber 1220a , in the state described above, there may be a leak in the master cylinder 1200 to be established. More specifically, a based on the displacement amount of the hydraulic piston 1320 Compare the calculated prospective hydraulic pressure value or the angle of rotation measured by the engine control sensor (not shown) and an actual hydraulic pressure value measured by the pressure sensor PS, and if the values match, it can be determined that there is no leakage in the integrated master cylinder 1200 is available. On the other hand, when the actual hydraulic pressure value measured by the pressure sensor PS is smaller than the anticipated hydraulic pressure value based on the displacement amount of the hydraulic piston 1320 or the rotation angle measured by the engine control sensor (not shown), part of it goes to the integrated master cylinder 1200 applied hydraulic pressure of the pressure medium is lost and it can be determined that there is a leak in the integrated master cylinder 1200 is present and it can be communicated to the driver.

As can be seen from the foregoing, the electronic brake system according to the embodiment of the present disclosure can reduce a number of components and enable a compact and lightweight product.

The electronic braking system according to the embodiment of the present disclosure can effectively implement braking in various operating situations.

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

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

The electronic braking system according to the embodiment of the present disclosure can improve the life of a product by reducing loads applied to components.

The electronic brake system according to the embodiment of the present disclosure can improve assemblability and productivity of a product, and can reduce manufacturing cost of the product.

While several embodiments of the present disclosure have been shown and described, it would be advantageous to those skilled in the art if changes could be made in these embodiments without departing from the spirit and spirit of the disclosure, the scope of which is defined in the claims and their equivalents.

Claims (19)

An electronic braking system (1000) comprising: a container (1100) for storing a print medium; an integrated master cylinder (1200) including a cylinder block (1210) which is designed to form a main chamber (1220a) and a simulation chamber (1230a) therein, a master piston provided in the main chamber (1220a) and displaceable by a brake pedal (10) (1220), a piston spring (1240) for elastically supporting the main piston (1220) in the cylinder block (1210), a simulation piston (1230) provided in the simulation chamber (1230a) and displaceable by displacing the main piston (1220) or a hydraulic pressure of the pressure medium accommodated in the main chamber (1220a), an elastic element (1250) provided between the simulation piston (1230) and the cylinder block (1210), and a simulation spring (1270) provided in the simulation chamber (1230a) together with the elastic element (1250) for resiliently supporting the simulation piston (1230); a container passage (1700) interconnecting the integrated master cylinder (1200) and the container (1100); a hydraulic pressure supply device (1300) for generating hydraulic pressure by operating a hydraulic piston (1320) by an electrical signal output in response to a stroke of the brake pedal (10), the hydraulic pressure supply device (1300) being one on a side of the hydraulic piston (1320 ) provided first pressure chamber (1330) which is movably received in a cylinder block (1210) and is connected to at least one of the wheel cylinders (20), and a second pressure chamber (1340) provided on the other side of the hydraulic piston (1320), which is connected to at least one of the wheel cylinders (20); a hydraulic controller (1400) having a first hydraulic circuit (1510) for controlling the hydraulic pressure transmitted to two wheel cylinders (20) and a second hydraulic circuit (1520) for controlling the hydraulic pressure transmitted to the other two wheel cylinders (20) ; and an electronic control unit for controlling valves based on hydraulic pressure information and displacement information of the brake pedal (10). Electronic braking system (1000) according to Claim 1 wherein the cylinder block (1210) comprises a step-shaped part which is formed so that it is to be attached to a part where the simulation chamber (1230a) is formed in a step-like manner on the main chamber (1220a), the simulation piston (1230) is provided with an extension part which is formed so that it protrudes outward and is received by the step-shaped part, the extension part restricting a stroke of the simulation piston (1230) when the simulation piston (1230) moves after the brake pedal (10 ) moved back. Electronic braking system (1000) according to one of the Claims 1 or 2 wherein the simulation chamber (1230a) comprises a hydraulic port (1280e) for connecting to the container (1100), wherein the simulation piston (1230) includes a shut-off bore (1232) formed inwardly to selectively connect to the hydraulic port (1280e ), the shut-off bore (1232) connecting the simulation chamber (1230a) and the hydraulic connection (1280e) to one another when the simulation piston (1230) is in a normal stop position, and the connection between the simulation chamber (1230a) and the hydraulic Connection (1280e) disconnects when the simulation piston (1230) moves. Electronic braking system (1000) according to one of the Claims 1 to 3 wherein the hydraulic controller (1400) comprises: a first hydraulic passage (1401) communicating with the first pressure chamber (1330); a second hydraulic passage (1402) and a third hydraulic passage (1403) branching off from the first hydraulic passage (1401); a fourth hydraulic passage communicating with the second pressure chamber (1340); a fifth hydraulic passage (1405) in which the second hydraulic passage (1402) and the fourth hydraulic passage (1404) merge; a sixth hydraulic passage (1406) which branches off from the fifth hydraulic passage (1405) and is connected to the first hydraulic circuit (1510); a seventh hydraulic passage (1407) which branches off from the fifth hydraulic passage (1405) and is connected to the second hydraulic circuit (1520); and an eighth hydraulic passage (1408), one end of which is connected to the third hydraulic passage (1403) and the other end of which branches off to both sides and connects to the sixth hydraulic passage (1406). and the seventh hydraulic passage (1407) combined. Electronic braking system (1000) according to Claim 4 wherein the hydraulic controller (1400) comprises: a first valve (1411) provided in the second hydraulic passage (1402) to control a flow of the pressure medium; a second valve (1412) provided in the third hydraulic passage (1403) to control the flow of the pressure medium; a third valve (1413) provided in the sixth hydraulic passage (1406) to control the flow of the pressure medium; a fourth valve (1414) provided in the seventh hydraulic passage (1407) to control the flow of the pressure medium; a fifth valve (1415) and sixth valve (1416) provided in the eighth hydraulic passage (1408) to control the flow of the pressure medium. Electronic braking system (1000) according to Claim 5 , wherein the first valve (1411), the third valve (1413) and the fourth valve (1414) are designed as a check valve, which only allows the flow of the pressure medium from the pressure chambers (1330, 1340) in the direction of the wheel cylinder (20), the second valve (1412) is designed as a solenoid valve to control the flow of the pressure medium in both directions, and the fifth valve (1415) and the sixth valve (1416) are designed as a check valve that exclusively controls the flow of the pressure medium from the wheel cylinders (20) in the direction of the pressure chambers (1330, 1340). Electronic braking system (1000) according to one of the Claims 5 or 6 , wherein the fifth valve (1415) is designed as a check valve, which only allows the flow of the pressure medium from the first hydraulic circuit (1510) to the pressure chambers (1330, 1340), and the sixth valve (1416) is designed as a check valve, which exclusively enables the flow of the pressure medium from the second hydraulic circuit (1520) in the direction of the pressure chambers (1330, 1340). Electronic braking system (1000) according to one of the Claims 1 to 7th further comprising: a first spare passage (1610) interconnecting the main chamber (1220a) and the first hydraulic circuit (1510); a second substitute passage (1620) connecting the simulation chamber (1230a) and the second hydraulic circuit (1520); a first shut-off valve (1611) provided in the first backup passage (1610) to control the flow of the pressure medium; and a second shut-off valve (1621a, 1621b) provided in the second backup passage (1620) to control the flow of the pressure medium. Electronic braking system (1000) according to one of the Claims 1 to 8th wherein the container passage (1700) comprises a first container passage (1710) interconnecting the container (1100) and the main chamber (1220a), and a second container passage (1720) connecting the container (1100) and the simulation chamber (1230a) connects with each other. Electronic braking system (1000) according to Claim 9 further comprising: a first container valve (1711) provided in the first container passage (1710) to control the flow of the pressure medium; and a second tank valve (1721) provided in the second tank passage (1720) to control the flow of the pressure medium. Electronic braking system (1000) according to Claim 10 further comprising: a simulation passage (1260) provided in the second container passage (1720) for promptly connecting a front end and a rear end of the second container valve (1721); and a simulation valve (1261) provided in the simulation passage (1260) to control the flow of the printing medium in both directions. Electronic braking system (1000) according to one of the Claims 10 or 11 further comprising: an inspection passage (1630) provided in the first container passage (1710) for promptly connecting a front end and a rear end of the first container valve (1711) to each other; and a check valve (1631) provided in the check passage (1630) to control the flow of the printing medium in both directions. Electronic braking system (1000) according to Claim 8 or one of the Claims 9 to 12th as far as this from Claim 8 are dependent, the first hydraulic circuit (1510) having a first inlet valve (1511a) and a second inlet valve (1511b) for respectively controlling the flow of the pressure medium supplied to the first and second wheel cylinders (21, 22), and a first outlet valve ( 1512a) and a second outlet valve (1512b) for controlling the flow of the from the first and second wheel cylinders (21, 22) to the, respectively Container (1100), the second hydraulic circuit (1520) having a third inlet valve (1521a) and a fourth inlet valve (1521b) for respectively controlling the flow of the pressure medium supplied to the third and fourth wheel cylinders (23, 24) and a second shut-off valve (1621a) for controlling the flow of the pressure medium discharged from the third wheel cylinder (23) to the container (1100), and the second substitute passage (1620) comprises the simulation chamber (1230a) with downstream sides of the third and fourth inlet valves ( 1521a, 1521b) connects. Electronic braking system (1000) according to Claim 13 further comprising: an evacuation controller (1800) provided between the reservoir (1100) and the hydraulic pressure supply device (1300) to control the flow of the pressure medium, the evacuation controller (1800) including a first evacuation passage (1810) that encompasses the first pressure chamber (1330) and the container (1100) connects to one another, and a first evacuation check valve (1811) provided in the first evacuation passage (1810), which only allows the flow of the pressure medium from the container (1100) to the first pressure chamber (1330). Method for operating the electronic brake system (1000) according to Claim 11 as far as this from Claim 8 are dependent, or after one of the Claims 12 or 13 , provided this is from Claim 11 and 8th are dependent, in which in a normal operating mode the first shut-off valve (1611) is closed to seal the main chamber (1220a), the second shut-off valve (1621a, 1621b) is closed and the simulation valve (1261) is open in order to connect it to the simulation chamber ( 1230a) and the container (1100) to communicate with each other, so that the simulation piston (1230) compresses the elastic element (1250) by pressing the brake pedal (10) and delivers an elastic restoring force of the elastic element (1250) to the driver as a pedal feeling becomes. Procedure according to Claim 15 , in which in the normal operating mode the hydraulic pressure formed in the first pressure chamber (1330) by moving the hydraulic piston (1320) forward first through the first hydraulic passage (1401), then the second hydraulic passage (1402), then the fifth hydraulic passage ( 1405) and finally the sixth hydraulic passage (1406) is transmitted to the first hydraulic circuit (1510) and first through the first hydraulic passage (1401), then the second hydraulic passage (1402), then the fifth hydraulic passage (1405) and finally the seventh hydraulic passage (1407) is transmitted to the second hydraulic circuit (1520). Method according to one of the Claims 15 or 16 in which, when the normal operating mode is released, the second valve (1412) is switched to an open state and the pressure medium supplied to the first hydraulic circuit (1510) and the second hydraulic circuit (1520) is transferred to the first pressure chamber (1330), in which a negative pressure is formed through the eighth hydraulic passage (1408) and through the third hydraulic passage (1403). Method according to one of the Claims 15 to 17th , in which in an abnormal operating mode the first shut-off valve (1611) is opened to allow the main chamber (1220a) and the first hydraulic circuit (1510) to communicate with each other, the simulation valve (1261) is closed and the second shut-off valve (1621a , 1621b) is opened so that the simulation chamber (1230a) and the second hydraulic circuit (1520) communicate with each other, in accordance with a pressing force of the brake pedal (10), the pressure medium of the main chamber (1220a) through the first substitute passage (1610) to the first hydraulic circuit (1510) is transmitted and the pressure medium of the simulation chamber (1230a) is transmitted through the second substitute passage (1620) to the second hydraulic circuit (1520). Method according to one of the Claims 15 to 18th , in which in a check mode for checking whether the integrated master cylinder (1200) is leaking, the second shut-off valve (1621a, 1621b) and the check valve (1631) are closed, the hydraulic pressure generated by operating the hydraulic pressure supply device (1300) to the Main chamber (1220a) is supplied by the hydraulic control (1400) and the first substitute passage (1610), the integrated master cylinder (1200) by comparing a hydraulic pressure value of the pressure medium predicted to be generated by the stroke of the hydraulic piston (1320), with a hydraulic pressure value of the pressure medium, which is measured by a pressure sensor (PS) in the first hydraulic circuit (1510) of the main chamber (1220a), is determined to be leaky.

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