CN114321063B - Piston valve and vehicle - Google Patents

Abstract

The embodiment of the application provides a piston valve and a vehicle. The piston valve comprises a cylinder body, the annular side wall is provided with a fluid inlet and a fluid outlet; a piston movable in an axial direction within the cylinder; the reversing mechanism is arranged at the gap between the cylinder body and the piston around the circumferential direction of the piston, is positioned between the fluid inlet and the fluid outlet along the axial direction and is communicated with the fluid outlet, and when the piston moves along the axial direction, the reversing mechanism is switched between a one-way conduction state and a two-way conduction state, and can seal the gap in one direction, prevent fluid from flowing from the fluid inlet to the fluid outlet and enable the fluid to flow back from the fluid outlet to the fluid inlet; in a bi-directional conducting state, the reversing mechanism enables bi-directional fluid flow between the fluid inlet and the fluid outlet. The embodiment of the application realizes the function of integrating the check valve on the piston valve, ensures that the high-pressure fluid at the fluid outlet can flow back to the fluid inlet when the pressure of the fluid inlet is reduced, has less parts, reduces the leakage risk, improves the reliability and reduces the cost.

Description

Piston valve and vehicle

Technical Field

The present application relates to the field of transportation vehicles, and in particular to a piston valve and a vehicle.

Background Art

The electro-mechanical brake (EMB) is a braking system in a vehicle that uses an electronic mechanical system instead of a hydraulic device. It has an extremely fast response speed and greatly shortens the braking distance. In addition, since there is no hydraulic system, the layout is simple, the weight is lighter, and it is easy to integrate functions such as electronic parking, anti-lock braking, and brake force distribution. However, EMB has no mechanical failure protection device, and the system safety and reliability are insufficient.

In order to solve the safety and reliability problems of EMB, a hybrid braking system based on hydraulics and electromechanical has been formed. In this hybrid braking system, a piston valve such as a two-position three-way solenoid valve can be used to switch between hydraulic braking and electromechanical braking. When braking by hydraulic braking, the brake fluid in the hydraulic component flows into the brake wheel cylinder to provide braking force; when braking by electromechanical braking, the electronic equipment obtains the brake signal to control the wheel to provide braking force, and the brake fluid in the hydraulic component flows into the pedal feel simulator to provide feedback force to avoid stepping on air.

In addition, in order to prevent the brake fluid pressure in the brake wheel cylinder and the pedal feel simulator from being greater than the brake fluid pressure in the hydraulic assembly, a first one-way valve is separately arranged between the brake wheel cylinder and the hydraulic assembly, and a second one-way valve is separately arranged between the pedal feel simulator and the hydraulic assembly. On the one hand, the one-way valve can assist the system in quickly releasing pressure, and on the other hand, it can ensure that when the pressure in the hydraulic assembly is reduced, the high-pressure fluid in the brake wheel cylinder and the pedal feel simulator can flow back to the hydraulic assembly smoothly, thereby reducing the probability of danger.

Since the one-way valve and the piston valve are independently arranged, the number of system parts and flow channels is large, which increases the risk of leakage and is not conducive to reducing costs. At the same time, the system occupies a large volume, which is not conducive to miniaturization.

Summary of the invention

The embodiments of the present application provide a piston valve and a vehicle, which realize the function of integrating a one-way valve on the piston valve, thereby ensuring that when the pressure at the fluid inlet is reduced, the high-pressure fluid at the fluid outlet can flow back to the fluid inlet, so that the pressure at the fluid outlet in a stable state will not be greater than the pressure at the fluid inlet. At the same time, the number of parts and the number of channels are reduced, the risk of leakage is reduced, the reliability is improved, and the cost is reduced, which is conducive to miniaturization.

To this end, the embodiments of the present application adopt the following technical solutions:

In a first aspect, an embodiment of the present application provides a piston valve, which includes: a cylinder body, on which an annular side wall is arranged a fluid inlet and at least one fluid outlet at intervals along an axial direction; a piston, which can move along the axial direction in the cylinder body; at least one reversing mechanism, which is arranged at the gap between the cylinder body and the piston in a circumferential direction around the piston, the reversing mechanism is located between the fluid inlet and the fluid outlet along the axial direction and is connected to the fluid outlet, and when the piston moves along the axial direction, the reversing mechanism can switch between a unidirectional conductive state and a bidirectional conductive state, wherein: in the unidirectional conductive state, the reversing mechanism can unidirectionally seal the gap to prevent the fluid from flowing from the fluid inlet through the reversing mechanism to the fluid outlet, and can enable the fluid to flow back from the fluid outlet to the fluid inlet through the reversing mechanism; in the bidirectional conductive state, the reversing mechanism can enable the fluid to flow from the fluid inlet through the reversing mechanism to the fluid outlet or can enable the fluid to flow back from the fluid outlet to the fluid inlet through the reversing mechanism.

The piston valve of the embodiment of the present application can achieve unidirectional or bidirectional conduction between the fluid inlet and the fluid outlet through a reversing mechanism, thereby realizing the function of integrating a one-way valve on the piston valve, ensuring that when the pressure at the fluid inlet is reduced, the high-pressure fluid at the fluid outlet can flow back to the fluid inlet, so that the pressure at the fluid outlet in a stable state is not greater than the pressure at the fluid inlet, thereby reducing the probability of danger, reducing the number of parts and the number of flow channels, reducing the risk of leakage, improving reliability, and reducing costs, which is conducive to miniaturization.

In a possible implementation, the reversing mechanism includes: an annular groove and a one-way seal, wherein the annular groove is arranged on one of the inner wall of the cylinder body and the outer wall of the piston, and the one-way seal is arranged in the annular groove; an annular outer wall and an annular groove channel, which are adjacently arranged on the other of the inner wall of the cylinder body and the outer wall of the piston, and the fluid inlet and the annular groove channel are located on both sides of the annular outer wall along the axial direction, and the fluid outlet is connected to the annular groove channel, wherein: in the one-way conduction state, the one-way seal contacts the annular outer wall, the one-way seal can seal the gap along the direction from the fluid inlet to the annular groove channel, and can make the fluid flow through the gap along the direction from the annular groove channel to the fluid inlet to flow back to the fluid inlet; in the two-way conduction state, the one-way seal corresponds to the annular groove channel, so that the fluid can flow through the annular groove channel along the direction from the fluid inlet to the annular groove channel to flow to the fluid outlet or flow through the annular groove channel along the direction from the annular groove channel to the fluid inlet to flow back to the fluid inlet.

That is to say, in this implementation, an annular outer wall and an annular groove channel may be arranged adjacent to each other on the inner wall of the cylinder body, an annular groove may be arranged on the outer wall of the piston, and a one-way seal may be arranged in the annular groove. Alternatively, an annular outer wall and an annular groove channel may be arranged adjacent to each other on the outer wall of the piston, an annular groove may be arranged on the inner wall of the cylinder body, and a one-way seal may be arranged in the annular groove. When the one-way seal contacts the annular outer wall, a one-way seal may be achieved, preventing the fluid flow at the fluid inlet from flowing to the fluid outlet through the one-way seal, and allowing the fluid at the fluid outlet to flow back to the fluid inlet through the gap between the one-way seal and the annular outer wall; when the one-way seal contacts the annular groove channel, the fluid can achieve bidirectional flow through the annular groove channel at the one-way seal.

In a possible implementation, the one-way seal includes a lip seal ring, the lip of the lip seal ring faces the side where the fluid inlet is located, wherein: when the one-way seal is in corresponding contact with the annular outer wall, when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the opposite side of the lip, the lip expands outward, so that the lip edge of the lip seal ring is close to the annular outer wall, thereby sealing the gap along the direction from the fluid inlet to the annular groove channel; when the fluid pressure on the lip side is less than the fluid pressure on the opposite side of the lip, the lip contracts, so that the lip edge of the lip seal ring is close to the annular outer wall. The outer walls are separated to form a gap, so that the fluid can flow from the opposite side of the lip to the lip side through the gap, thereby realizing one-way sealing or one-way conduction; when the one-way seal corresponds to the annular groove channel, when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the lip side to the opposite side of the lip through the annular groove channel; when the pressure of the fluid on the lip side is less than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the opposite side of the lip to the lip side through the annular groove channel, thereby realizing two-way conduction.

That is to say, in this implementation, the one-way seal can be a lip seal ring. The sealing of the lip seal ring is achieved by deforming its lip under the action of the hydraulic pressure, so that the lip edge is close to the sealing surface. The higher the hydraulic pressure, the tighter the lip edge is to the sealing surface. After the sealing lip edge is worn, it has a certain ability to automatically compensate. Since the O-ring needs an interference fit to seal, that is, it needs to be pre-compressed, which makes the movement resistance larger, requires more power consumption, and leads to a larger volume of the driving mechanism. In addition, the size of the O-ring itself in the axial direction is larger than that of the lip seal ring. After the O-ring seal is pre-compressed, the size in the axial direction is further increased, which makes the piston move larger when switching between the sealing state and the conducting state, resulting in a larger structural volume. The lip seal ring is not pre-compressed, the movement resistance is small, and the sliding resistance of the piston valve is reduced. At the same time, the lip seal ring relies on the lip seal and has a small axial size, thereby reducing the movement stroke of the piston valve, so that the power consumption of the driving mechanism that drives the piston to move is reduced.

In one possible implementation, the annular groove channel includes a plurality of groove bodies spaced apart in a circumferential direction around the inner wall of the cylinder body and the other of the outer walls of the piston, and when the one-way seal corresponds to the annular groove channel, the outer walls between adjacent groove bodies can support and contact the one-way seal.

That is to say, in this implementation, the annular groove channel is a discontinuous groove design along the circumferential direction, which can reliably support the large lip edge of the lip seal ring, so that the lip seal ring can achieve liquid flow without significant deformation, effectively prevent overturning, and also increase the service life of the lip seal ring.

In one possible implementation, the dimension of the groove body along the axial direction is greater than, less than, or equal to the dimension along the circumferential direction; and/or the longitudinal section or cross section of the groove body is arc-shaped, and the two ends of the arc along the bending direction are away from the central axis of the piston relative to the middle of the arc.

That is to say, in this implementation, the size of the slot body in the axial direction may be greater than the size in the circumferential direction. For example, the slot body is a narrow and long slot, and its length is in the axial direction, which is consistent with the flow direction of the fluid. In this way, more slot bodies can be set in the circumferential direction, so that the fluid can flow through multiple slot bodies in multiple ways, so that the force is more uniform; or, the size of the slot body in the axial direction may be smaller than the size in the circumferential direction, so that the slot body is wider and can accommodate more fluid, allowing the fluid to pass through the slot body faster. Of course, the size of the slot body in the axial direction may also be equal to the size in the circumferential direction. In addition, the cross-section of the slot body can be selected according to work needs. For example, the cross-section of the slot body is arc-shaped, so that the flow channel formed by the slot body is relatively smooth, which is convenient for the fluid to enter and flow out of the slot body, that is, the fluid can pass through relatively smoothly, and it is not easy for the fluid to be retained, which is conducive to accelerating the fluid speed. Of course, other shapes of slot bodies can also be selected, such as a rectangular cross-section of the slot body.

In a possible implementation, two fluid outlets are provided on the cylinder body, the fluid inlet is located between the two fluid outlets along the axial direction, and the two fluid outlets are a first fluid outlet and a second fluid outlet, and the piston valve includes two reversing mechanisms, and the two reversing mechanisms are a first reversing mechanism and a second reversing mechanism; the first reversing mechanism is located between the fluid inlet and the first fluid outlet along the axial direction and is connected to the first fluid outlet, and the second reversing mechanism is located between the fluid inlet and the second fluid outlet along the axial direction and is connected to the second fluid outlet; the piston can move between a first position and a second position, wherein: in the first position, the first reversing mechanism is in the bidirectional conductive state, and the second reversing mechanism is in the unidirectional conductive state; in the second position, the first reversing mechanism is in the unidirectional conductive state, and the second reversing mechanism is in the bidirectional conductive state.

That is to say, in this implementation, the piston valve may include a fluid inlet and two fluid outlets. The piston valve may be a two-position three-way solenoid valve. Two reversing mechanisms are provided on the piston valve, and the conduction states of the two reversing mechanisms are different. Specifically, when the piston is in the first position, the first reversing mechanism may be in a two-way conduction state, and the second reversing mechanism may be in a unidirectional conduction state; when the piston moves to the second position, the first reversing mechanism may be in a unidirectional conduction state, and the second reversing mechanism may be in a two-way conduction state. Among them, the first reversing mechanism can realize unidirectional or bidirectional conduction between the fluid inlet and the first fluid outlet, ensuring that when the pressure at the fluid inlet is reduced, the high-pressure fluid at the first fluid outlet can flow back to the fluid inlet, so that the pressure at the first fluid outlet in a stable state will not be greater than the pressure at the fluid inlet. The second reversing mechanism can realize unidirectional or bidirectional conduction between the fluid inlet and the second fluid outlet, ensuring that when the pressure at the fluid inlet is reduced, the high-pressure fluid at the second fluid outlet can flow back to the fluid inlet, so that in a stable state the pressure at the second fluid outlet will not be greater than the pressure at the fluid inlet, thereby reducing the probability of danger. At the same time, there is no need to set up a one-way valve separately, reducing the number of parts and the number of channels, reducing the risk of leakage, improving reliability, and reducing costs, which is conducive to miniaturization.

In a possible implementation, an annular channel is provided on the other of the inner wall of the cylinder body and the outer wall of the piston, the fluid inlet is connected to the annular channel, and the annular channel has the same or different structure as the annular groove channel of the reversing mechanism.

That is, in this implementation, in order to allow the liquid at the fluid inlet to flow into the gap between the cylinder and the piston as quickly as possible, the size of the gap at the fluid inlet can be increased, specifically, an annular channel can be provided on the outer wall of the piston, or an annular channel can be provided on the inner wall of the cylinder. The annular channel can be located between the annular outer wall of the first reversing mechanism and the annular outer wall of the second reversing mechanism.

In a possible implementation, the piston valve also includes: a first sealing ring, located at the first end of the piston, and capable of sealing the circumferential gap between the cylinder body and the piston along the direction from the second end of the piston to the first end of the piston; a second sealing ring, located at the second end of the piston, and capable of sealing the circumferential gap between the cylinder body and the piston along the direction from the first end of the piston to the second end of the piston; the fluid inlet, the fluid outlet, and the reversing mechanism are located between the first sealing ring and the second sealing ring along the axial direction.

That is to say, in this implementation, in order to ensure that the fluid does not flow out from both ends of the piston along the gap between the piston and the cylinder body, sealing rings can be set at both ends of the piston for sealing, and the sealing rings at both ends of the piston need to seal the gap at least in the direction toward the outside. Here, "the direction toward the outside" refers to the direction away from the fluid inlet along the axial direction at the end of the piston. Specifically, at the first end of the piston, "the direction toward the outside" refers to the direction from the fluid inlet/the second end of the piston to the first end of the piston; at the second end of the piston, "the direction toward the outside" refers to the direction from the fluid inlet/the first end of the piston to the second end of the piston.

In a possible implementation, the first sealing ring and the second sealing ring are respectively one of an O-ring and a lip sealing ring, wherein: the O-ring can seal the gap in both directions from the first end of the piston to the second end of the piston and from the second end of the piston to the first end of the piston; the opening of the lip sealing ring faces the side where the fluid inlet is located, and the lip sealing ring can seal the gap in one direction from the lip side to the opposite side of the lip.

That is to say, in this implementation, the sealing rings at both ends of the piston can seal the gap in two directions along the axial direction. Here, "bidirectional sealing" refers to the direction from the first end to the second end of the piston and the direction from the second end to the first end of the piston. In this case, an O-type sealing ring can be used to achieve bidirectional sealing; or, the sealing rings at both ends of the piston can seal the gap in one direction in the direction toward the outside. Here, "one-way sealing" refers to sealing the gap only in the direction toward the outside. In this case, a lip-shaped sealing ring such as a U-shaped sealing ring or a V-shaped sealing ring can be used to achieve one-way sealing.

In a possible implementation, the piston valve also includes a driving mechanism, which is used to drive the piston to move along the axial direction, and the driving mechanism is one of a manual operating mechanism, an electromagnetic driving mechanism, a pneumatic driving mechanism, a hydraulic driving mechanism and an electro-hydraulic driving mechanism; and the electromagnetic driving mechanism includes a static iron, a moving iron, an elastic part connecting the static iron and the moving iron, and an electromagnetic coil arranged on the moving iron and the periphery of the static iron, and the moving iron is connected to the piston, wherein: when the electromagnetic coil is not energized, the moving iron and the static iron are spaced apart, and the piston is located in the first position; when the electromagnetic coil is energized, the moving iron and the static iron are magnetized, so that the moving iron drives the piston to move toward the static iron and compress the elastic part, and the piston is located in the second position.

That is to say, in this implementation, a variety of methods can be used to drive the piston to move in the axial direction. When an electromagnetic drive mechanism is used to drive the piston to move, the piston valve is an electromagnetic valve. When the electromagnetic coil is not energized, the static iron and the moving iron are spaced apart, and the piston is located in the first position. When the electromagnetic coil is energized, the static iron and the moving iron are magnetized by the electromagnetic coil, and the moving iron moves toward the static iron under the action of suction, driving the piston to move at the same time until the dynamic and static contacts are made. At this time, the piston is located in the second position, thereby realizing the movement of the piston between the first position and the second position.

In a possible implementation, the lip seal ring includes one of a U-shaped seal ring, a V-shaped seal ring and a Y-shaped seal ring. It is understandable that other lip seal rings that can achieve similar functions, or other seal rings or other sealing structures that can achieve similar functions can also be selected as needed.

In a second aspect, an embodiment of the present application provides a vehicle, comprising: a piston valve having a first fluid outlet and a second fluid outlet provided in the first aspect above; a brake master cylinder connected to the fluid inlet of the piston valve; a wheel and a brake wheel cylinder, wherein the brake wheel cylinder is connected to the first fluid outlet of the piston valve to provide a braking force for braking the wheel when the fluid is received; a pedal feel simulator connected to the second fluid outlet of the piston valve to simulate the pedaling force when the fluid is received; wherein: in the first position, the brake master cylinder is bidirectionally connected to the brake wheel cylinder through the first reversing mechanism; the brake master cylinder and the pedal feel simulator are unidirectionally connected through the second reversing mechanism; in the second position, the brake master cylinder is unidirectionally connected to the brake wheel cylinder through the first reversing mechanism; the brake master cylinder and the pedal feel simulator are bidirectionally connected through the second reversing mechanism.

Other features and advantages of the present invention will be described in detail in the following specific embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS

The following is a brief introduction to the drawings required for describing the embodiments or prior art.

FIG1A is a schematic structural diagram of a braking system of a vehicle in a first working position;

FIG1B is a schematic structural diagram of the brake system shown in FIG1A in a second working position;

FIG1C is a schematic diagram and an actual structural diagram of a one-way valve in the brake system shown in FIG1A ;

FIG2 is a schematic cross-sectional view of a piston valve provided in the first embodiment of the present application;

FIG3A is a schematic diagram of an exemplary structure of a piston of the piston valve shown in FIG2 ;

FIG3B is another exemplary structural schematic diagram of the piston of the piston valve shown in FIG2 ;

FIG3C is another exemplary structural schematic diagram of the piston of the piston valve shown in FIG2 ;

FIG4 is a schematic cross-sectional view of a piston valve provided in a second embodiment of the present application;

FIG5A is a schematic diagram of an exemplary structure of a piston of the piston valve shown in FIG4 ;

FIG5B is another exemplary structural schematic diagram of the piston of the piston valve shown in FIG4 ;

FIG. 5C is another exemplary structural schematic diagram of the piston of the piston valve shown in FIG. 4 .

DETAILED DESCRIPTION

The technical solutions in the embodiments of the present application will be described below in conjunction with the drawings in the embodiments of the present application.

In the description of the present application, the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

In the description of the present application, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, a conflicting connection or an integrated connection. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

In the description of this specification, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

In order to solve the safety and reliability problems of EMB, a hybrid brake system based on hydraulic pressure and electronic machinery is formed. The hybrid brake system is specifically introduced below in conjunction with Figures 1A, 1B and 1C.

FIG. 1A is a schematic diagram of the structure of a braking system of a vehicle in a first working position. FIG. 1B is a schematic diagram of the structure of the braking system shown in FIG. 1A in a second working position. As shown in FIG. 1A and FIG. 1B, the vehicle includes a pedal assembly 1, a hydraulic assembly 2, a reversing assembly 3, a front wheel assembly 4, a rear wheel assembly 5, a pedal feel simulator 6, and a first electronic control unit ECU 7. The pedal assembly 1 may include a brake pedal 101 and a pedal travel sensor 102. The hydraulic assembly 2 may include a fluid reservoir 201, a brake master cylinder 202, and an input push rod 203. The pedal travel sensor 102 is mounted on the brake pedal 101, or the pedal travel sensor 102 is mounted on the input push rod 203. The front wheel assembly 4 may include two front wheels 401 and a first EMB brake actuator 402. The first EMB brake actuator 402 is respectively mounted on the two front wheels 401. The rear wheel assembly 5 includes two rear wheels 501 and a second EMB brake actuator 502, and each wheel of the two rear wheels 501 is respectively mounted with a second EMB brake actuator 502.

As shown in FIG1A , in the first working position, the vehicle is in a completely failed condition. When the driver steps on the pedal 101, the input push rod 203 is displaced under the action of the pedal assembly 1, so that the brake fluid in the brake master cylinder 202 of the hydraulic assembly 2 flows into the brake wheel cylinder of the first EMB actuator 402 of the front wheel assembly 4 through the reversing assembly 3. The brake wheel cylinder provides braking force to the wheel, such as the front wheel 401, driven by the brake fluid.

As shown in FIG1B , in the second working position, when the vehicle is in a normal working condition or a non-completely failed condition, when the driver steps on the pedal 101, the input push rod 203 is displaced under the action of the pedal assembly 1, so that the brake fluid in the hydraulic assembly 2 flows into the pedal feeling simulator 6 through the reversing assembly 3. The pedal feeling simulator 6 is used to generate feedback force of the pedal assembly, so that the driver can easily perceive and control the magnitude of the applied braking force. In addition, the first ECU 7 controls the front wheel assembly 4 and the rear wheel assembly 5 to provide braking force according to the obtained braking signal.

In the above hybrid brake system, the reversing assembly 3 can be a two-position three-way solenoid valve, that is, the two-position three-way solenoid valve 3 can be used as a guide mechanism for the output hydraulic pressure of the brake master cylinder 202, so as to realize the switching of the brake master cylinder 202 between being connected with the front wheel assembly 4 and being connected with the pedal feeling simulator 6. When the electrical state is normal (i.e., the second working position), the driver steps on the pedal 101, and the hydraulic pressure in the brake master cylinder 202 is introduced into the pedal feeling simulator 6 through the two-position three-way solenoid valve, giving the driver a feedback of force and displacement; when the electrical state fails (i.e., the first working position), the driver steps on the pedal 101, and the hydraulic two-position three-way solenoid valve in the brake master cylinder 202 is guided to the two front wheel brakes 401, forming an emergency backup brake.

In addition, as shown in FIG. 1A and FIG. 1B , the brake system may further include a one-way valve 8 and a one-way valve 9. The one-way valve 8 is arranged on the pipeline between the hydraulic assembly 2 and the front wheel assembly 4, and the conducting direction of the one-way valve 8 is the direction of flowing from the front wheel assembly 4 to the hydraulic assembly 2. The one-way valve 9 is arranged on the pipeline between the hydraulic assembly 2 and the pedal feeling simulator 6, and the conducting direction of the one-way valve 9 is the direction of flowing from the pedal feeling simulator 6 to the hydraulic assembly 2. In this way, when the brake pedal 101 is released in the first working position, the liquid in the brake wheel cylinder of the first EMB actuator 402 can not only flow back to the brake master cylinder 202 through the hydraulic assembly 2, but the one-way valve 8 can assist the system to release pressure quickly; when the brake pedal 101 is released in the second working position, the liquid in the pedal feeling simulator 6 can not only flow back to the brake master cylinder 202 through the hydraulic assembly 2, but the one-way valve 9 can assist the system to release pressure quickly.

In addition, no matter in the first working position or the second working position, the one-way valve 8 can ensure that the pressure in the brake wheel cylinder of the first EMB actuator 402 of the front wheel assembly 4 in a stable state will not be greater than the pressure in the hydraulic assembly 2, that is, when the pressure in the hydraulic assembly 2 decreases, the high-pressure liquid in the brake wheel cylinder can flow back to the hydraulic assembly 2; the one-way valve 9 can ensure that the pressure in the pedal feel simulator 6 in a stable state will not be greater than the pressure in the hydraulic assembly 2, that is, when the pressure in the hydraulic assembly 2 decreases, the high-pressure liquid in the pedal feel simulator 6 can flow back to the hydraulic assembly 2. In other words, the one-way valve 8 and the one-way valve 9 can ensure the so-called "driver intention priority", that is, when the driver releases the pedal under any circumstances and the hydraulic pressure in the brake master cylinder 202 decreases, the hydraulic pressure in the brake wheel cylinder of the first EMB actuator 402 of the front wheel assembly 4 can flow back through the one-way valve 8, and the hydraulic pressure in the pedal feel simulator 6 can flow back through the one-way valve 9, thereby ensuring that their pressures follow the driver's intention.

FIG1C is a schematic diagram and an actual structural diagram of a one-way valve in the brake system shown in FIG1A. In FIG1C, FIG(a) is two schematic diagrams of a one-way valve, and FIG(b1), FIG(b2), FIG(b3) and FIG(b4) are four actual structural diagrams of a one-way valve. As shown in FIG1C, a one-way valve is generally composed of a sphere or a cone disposed at a conical nozzle, and the fluid can only flow from the top of the cone to the bottom of the cone. Otherwise, the fluid will push the sphere or cone to press the conical nozzle, and the fluid will be locked, forming a one-way flow. The one-way valve generally exists as a single component.

As can be seen from Figures 1A, 1B and 1C, the above solution requires a separate one-way valve to be provided outside the reversing component 3, such as a two-position three-way valve, which results in a large number of parts and flow channels, a high risk of leakage, which is not conducive to reducing costs, and a large volume, which is not conducive to miniaturization.

In view of this, the embodiment of the present application provides a piston valve and a vehicle. The fluid inlet and the fluid outlet of the piston valve can be unidirectionally or bidirectionally connected through a reversing mechanism, so as to realize the function of integrating a one-way valve on the piston valve, avoid using a single one-way valve, and ensure that when the pressure at the fluid inlet is reduced, the high-pressure fluid at the fluid outlet can flow back to the fluid inlet, so that the pressure at the fluid outlet in a stable state will not be greater than the pressure at the fluid inlet, thereby reducing the probability of danger, reducing the number of parts, reducing the risk of leakage, improving reliability, and reducing costs, which is conducive to miniaturization. Among them, the piston valve may include a fluid inlet, a fluid outlet and a reversing mechanism, in which case the piston valve is a two-position two-way valve; or, the piston valve may include a fluid inlet, two fluid outlets and two reversing mechanisms, in which case the piston valve is a two-position three-way valve. In addition, the number of positions and the number of openings of the piston valve can be increased as needed, for example, the piston valve can be a three-position five-way valve, in which case a reversing mechanism can be added accordingly.

Fig. 2 is a schematic cross-sectional structure diagram of a piston valve provided in the first embodiment of the present application. As shown in Fig. 2, the piston valve includes a cylinder body 1, a piston 2 and a reversing mechanism 3. The piston 2 is arranged in the cylinder body 1 and can move in the axial direction in the cylinder body 1. A fluid inlet R and a fluid outlet C are arranged at intervals in the axial direction on the annular side wall of the cylinder body 1, that is, the piston valve is a two-position two-way valve. In addition, the fluid inlet R can be arranged along the entire circumferential direction of the cylinder body 1, and the fluid outlet C can also be arranged along the entire circumferential direction of the cylinder body 1, that is, the fluid inlet R and the fluid outlet C can be arranged around the outer wall of the cylinder body 1. At this time, the piston valve also includes a valve seat (not shown in Fig. 2), and a plurality of channels are arranged on the valve seat, and the plurality of channels are respectively connected to the fluid inlet R and the fluid outlet C.

In FIG. 2 , the fluid inlet R in the entire circumferential direction has the same axial position on the cylinder body 1, and the fluid outlet C in the entire circumferential direction has the same axial position on the cylinder body 1, that is, the fluid inlet R and the fluid outlet C can be respectively arranged around the periphery of the "cross section" of the cylinder body 1, and the "cross section" is perpendicular to the central axis of the cylinder body 1. Of course, it can be understood that the structures of the fluid inlet R and the fluid outlet C can also be changed as needed. For example, the fluid inlet R and the fluid outlet C are arranged along part of the circumferential direction. For another example, when necessary, the fluid inlet R can also be designed so that different parts in the circumferential direction have different axial positions on the cylinder body 1, and the fluid outlet C can be designed so that different parts in the circumferential direction have different axial positions on the cylinder body 1, that is, the fluid inlet R and the fluid outlet C can be respectively arranged around the periphery of the "transverse section" of the cylinder body 1, and the "transverse section" has an angle with the above-mentioned "cross section" and is not perpendicular to the central axis of the cylinder body 1.

Herein, the main explanation is given by taking “the fluid inlet R and the fluid outlet C are respectively arranged along the entire circumferential direction on the cylinder body 1 and the axial positions of different parts along the circumferential direction are the same” as an example.

As shown in FIG2 , the reversing mechanism 3 can be arranged at the gap between the cylinder body 1 and the piston 2 in the circumferential direction around the piston 2, and the reversing mechanism 3 is located between the fluid inlet R and the fluid outlet C in the axial direction, and is connected to the fluid outlet C. When the piston 2 moves in the axial direction, the reversing mechanism 3 can switch between a unidirectional conductive state and a bidirectional conductive state.

In the unidirectional conduction state, the reversing mechanism 3 can unidirectionally seal the circumferential gap between the cylinder body 1 and the piston 2, that is, the reversing mechanism 3 unidirectionally seals the gap along the entire circumferential direction to prevent the fluid from flowing from the fluid inlet R to the fluid outlet C through the reversing mechanism 3, and can enable the fluid to flow back from the fluid outlet C to the fluid inlet R through the reversing mechanism 3.

In the bidirectional conduction state, the reversing mechanism 3 can make the fluid flow from the fluid inlet R to the fluid outlet C through the reversing mechanism 3, or can make the fluid flow back from the fluid outlet C to the fluid inlet R through the reversing mechanism 3. It should be noted that the "bidirectional conduction state" here means that in the first time period, the fluid can flow from the fluid inlet R to the fluid outlet C through the reversing mechanism 3, and in the second time period, the fluid can flow back from the fluid outlet C to the fluid inlet R through the reversing mechanism 3, that is, the same channel can be conducted in different directions in different time periods.

The fluid may be liquid or gas, etc. In addition, since the reversing mechanism 3 is in a unidirectional conduction state or a bidirectional conduction state, the reversing mechanism 3 (specifically, the annular groove channel 34 of the reversing mechanism 3 to be described below) is connected to the fluid outlet C, thereby ensuring that the liquid at the fluid outlet C can flow back to the fluid inlet R through the reversing mechanism 3, that is, when the pressure at the fluid inlet R decreases, the high-pressure fluid at the fluid outlet C can flow back to the fluid inlet R, so that the pressure at the fluid outlet C will not be greater than the pressure at the fluid inlet R in a stable state, thereby reducing the probability of danger.

2, the reversing mechanism 3 may include an annular groove 31, a one-way seal 32, an annular outer wall 33, and an annular groove channel 34. The annular groove 31 is provided on one of the inner wall of the cylinder body 1 and the outer wall of the piston 2, and the one-way seal 32 is provided in the annular groove 31. The annular outer wall 33 and the annular groove channel 34 are adjacently provided on the other of the inner wall of the cylinder body 1 and the outer wall of the piston 2, and the fluid inlet R and the annular groove channel 34 are located on both sides of the annular outer wall 33 in the axial direction, and the fluid outlet C is communicated with the annular groove channel 34.

In FIG. 2 and FIG. 4 to be described below, the annular outer wall 33 and the annular groove channel 34 are adjacently arranged on the outer wall of the piston 2, the annular groove 31 is arranged on the inner wall of the cylinder body 1, and the one-way seal 32 can be arranged in the annular groove 31. It can be understood that the annular outer wall and the annular groove channel can also be adjacently arranged on the inner wall of the cylinder body 1, and the annular groove can be arranged on the outer wall of the piston 2, and the one-way seal 32 can be arranged in the annular groove at the outer wall of the piston 2.

As shown in FIG2 , when the reversing mechanism 3 is in a bidirectional conduction state, the one-way seal 32 is misaligned with the annular outer wall 33 and corresponds to the annular groove channel 34. The fluid entering the gap between the cylinder body 1 and the piston 2 from the fluid inlet R can flow through the annular groove channel 34 along the direction from the fluid inlet R to the annular groove channel 34 to flow to the fluid outlet C; or the fluid entering the gap between the cylinder body 1 and the piston 2 from the fluid outlet C can flow through the annular groove channel 34 along the direction from the annular groove channel 34 to the fluid inlet R to flow back to the fluid inlet R. That is to say, when the one-way seal 32 is in contact with the annular groove channel 34, the fluid can achieve bidirectional flow through the annular groove channel 34 at the one-way seal 32.

In addition, in the two-way conduction state shown in FIG2 , when the piston 2 moves in the axial direction so that the one-way seal 32 contacts the annular outer wall 33, the reversing mechanism 3 is in the one-way conduction state. At this time, the one-way seal 32 can seal the gap along the direction from the fluid inlet R to the annular groove channel 34, and the fluid entering the gap between the cylinder body 1 and the piston 2 from the fluid inlet R cannot flow to the fluid outlet C through the reversing mechanism 3, and the one-way seal 32 can make the fluid entering the gap between the cylinder body 1 and the piston 2 through the fluid outlet C flow through the gap along the direction from the annular groove channel 34 to the fluid inlet R, so as to flow back to the fluid inlet R. That is to say, when the one-way seal 32 contacts the annular outer wall 33, one-way sealing/one-way conduction can be achieved, and the fluid at the fluid inlet R can be prevented from flowing through the one-way seal 32, and the fluid at the fluid outlet can flow back to the fluid inlet R through the gap between the one-way seal 32 and the annular outer wall 33.

The one-way seal 32 may include a lip seal ring, and the lip of the lip seal ring faces the side where the fluid inlet R is located. The lip side is the side where the fluid inlet R is located; the side opposite to the lip is the side where the fluid outlet C is located. In this way, when the one-way seal 32 is in corresponding contact with the annular outer wall 33, when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the side opposite to the lip, the lip expands outward, so that the lip edge of the lip seal ring can be close to the annular outer wall 33, and the sealing gap from the fluid inlet R to the annular groove channel 34 is achieved. When the fluid pressure on the lip side is less than the fluid pressure on the side opposite to the lip, the lip shrinks, so that the lip edge of the lip seal ring can be separated from the annular outer wall 33 to form a gap, so that the fluid can flow from the side opposite to the lip through the gap to the lip side, thereby achieving one-way sealing or one-way conduction. Furthermore, when the one-way seal 32 corresponds to the annular groove channel 34, when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the lip side to the opposite side of the lip through the annular groove channel 34; when the pressure of the fluid on the lip side is less than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the opposite side of the lip to the lip side through the annular groove channel 34, thereby achieving two-way conduction. Among them, the lip seal ring may include one of a U-shaped seal ring, a V-shaped seal ring and a Y-shaped seal ring. In Figures 2 and 4, the one-way seal 32 is a U-shaped seal ring. It can be understood that other lip seal rings, other types of seal rings or other sealing structures that can achieve similar functions can also be selected as needed.

The piston of the conventional piston valve is provided with grooves and high points, and an O-type sealing ring is provided on the high point. The cylinder body matched with the piston is also provided with grooves and high points, but the high point of the cylinder body does not need to be provided with a sealing ring. When the high point of the piston is aligned with the high point of the cylinder body, the O-type sealing ring can seal the circumferential gap between the cylinder body and the piston, so that the hydraulic pressure is isolated; when the driving mechanism pushes the piston to move in the axial direction, when the high point of the piston and the high point of the cylinder body are staggered, the O-type sealing ring cannot seal the circumferential gap between the cylinder body and the piston, and the liquid can be conducted. Since the O-type sealing ring needs an interference fit to seal, that is, it needs to be pre-compressed when sealing, which makes the movement resistance larger. Furthermore, the size of the O-type sealing ring itself in the axial direction is larger than that of the lip sealing ring, and after the O-type sealing ring is pre-compressed, the size in the axial direction is further increased, which makes the piston 2 have a larger movement stroke when switching between the sealing state and the conducting state, resulting in higher power consumption and requiring a driving mechanism with higher power. For example, when an electromagnetic driving mechanism is used, the spring and electromagnetic valve required to match are relatively large, resulting in a larger volume, which is not conducive to miniaturization.

The one-way seal 32 in the reversing mechanism 3 of the embodiment of the present application can be a lip seal. The sealing of the lip seal is achieved by deforming its lip under the action of the liquid pressure, so that the lip is close to the sealing surface. The higher the liquid pressure, the tighter the lip is to the sealing surface, and the sealing lip has a certain ability to automatically compensate after wear. Since the lip seal is not pre-compressed, the movement resistance is small, which reduces the sliding resistance of the piston valve. At the same time, the lip seal relies on the lip seal and has a small axial size, thereby reducing the movement stroke of the piston valve, reducing the power consumption of the driving mechanism that drives the piston 2 to move, and can reduce the volume, which is conducive to miniaturization.

In addition, in order to ensure that the fluid does not flow out from both ends of the piston 2 along the gap between the piston 2 and the piston 2, sealing rings can be provided at both ends of the piston 2 for sealing. Continuing to refer to FIG. 2, the piston valve can also include a first sealing ring M1 and a second sealing ring M2. Two annular grooves can be provided on the inner wall of the cylinder body 1, and the first sealing ring M1 and the second sealing ring M2 are respectively provided in the two annular grooves. At this time, the annular groove 31 accommodating the one-way seal 32 is located between the first sealing ring M1 and the second sealing ring M2 in the axial direction.

Specifically, the first sealing ring M1 may be located at the first end of the piston 2, and can seal the circumferential gap between the cylinder body 1 and the piston 2 at the first end of the piston 2 in the direction from the second end to the first end of the piston 2. The second sealing ring M2 is located at the second end of the piston 2, and can seal the circumferential gap between the cylinder body 1 and the piston 2 at the second end of the piston 2 in the direction from the first end to the second end of the piston 2. The fluid inlet R, the fluid outlet C, and the reversing mechanism 3 are located between the first sealing ring M1 and the second sealing ring M2 in the axial direction.

The first sealing ring M1 and the second sealing ring M2 need to seal the gap at least in the direction toward the outside at both ends of the piston 2. That is, the function of the first sealing ring M1 and the second sealing ring M2 is to prevent the fluid from flowing out of the piston valve. Here, "the direction toward the outside" refers to the direction away from the fluid inlet along the axial direction at the end of the piston 2. For example, at the first end of the piston 2, "the direction toward the outside" refers to the direction from the fluid inlet/the second end of the piston 2 to the first end of the piston 2; at the second end of the piston 2, "the direction toward the outside" refers to the direction from the fluid inlet/the first end of the piston 2 to the second end of the piston 2.

The first sealing ring M1 and the second sealing ring M2 can be in the following two forms but are not limited to:

Method 1: Both the first sealing ring M1 and the second sealing ring M2 are lip-shaped sealing rings, which can seal the gap unidirectionally from the lip side to the opposite side of the lip. As shown in Figure 2 and Figure 4 to be introduced below, the opening of the lip-shaped sealing ring as the first sealing ring M1 faces the side where the fluid inlet R is located, so that the circumferential gap between the cylinder body 1 and the piston 2 can be sealed from the lip side, i.e., the fluid inlet R, to the opposite side of the lip, i.e., the first end of the piston 2; the opening of the lip-shaped sealing ring as the second sealing ring M1 faces the side where the fluid inlet R is located, so that the circumferential gap between the cylinder body 1 and the piston 2 can be sealed from the lip side, i.e., the fluid inlet R, to the opposite side of the lip, i.e., the second end of the piston 2.

Since the lip seal is not pre-compressed, the movement resistance is small, which reduces the sliding resistance of the piston valve. At the same time, the lip seal relies on lip sealing and has a small axial dimension, thereby reducing the movement stroke of the piston valve, thereby reducing the power consumption of the driving mechanism that drives the piston 2 to move. If the driving mechanism is an electromagnetic driving mechanism, the power consumption of the electromagnetic coil can be reduced, the volume can be reduced, and miniaturization can be achieved.

Mode 2: Both the first sealing ring M1 and the second sealing ring M2 are O-rings, wherein the O-rings can seal the gap in both directions from the first end of the piston 2 to the second end of the piston 2 and from the second end of the piston 2 to the first end of the piston 2. In other words, the first sealing ring M1 and the second sealing ring M2 can seal the circumferential gap between the cylinder body 1 and the piston 2 in both directions along the axial direction at both ends of the piston 2, respectively. Here, "bidirectional sealing" refers to the direction from the first end of the piston 2 to the second end and from the second end of the piston 2 to the first end. At this time, the first sealing ring M1 and the second sealing ring M2 can use O-rings to achieve bidirectional sealing.

In addition, in addition to the above two methods, the first sealing ring M1 may be an O-ring and the second sealing ring M2 may be a lip-shaped sealing ring. Alternatively, the first sealing ring M1 may be a lip-shaped sealing ring and the second sealing ring M2 may be an O-ring.

Further, the piston valve may also include a driving mechanism, which is used to drive the piston 2 to move in the axial direction, and the driving mechanism is one of a manual operating mechanism, an electromagnetic driving mechanism 4, a pneumatic driving mechanism, a hydraulic driving mechanism and an electro-hydraulic driving mechanism. The electromagnetic driving mechanism 4 is mainly used as an example for introduction herein. In this case, the piston valve may be an electromagnetic valve. As shown in FIG. 2 and FIG. 4 to be introduced below, the electromagnetic driving mechanism 4 may include a stationary iron 41, a moving iron 42, an elastic member 43 connecting the stationary iron 41 and the moving iron 42, and an electromagnetic coil 44 arranged on the periphery of the moving iron 42 and the stationary iron 41, and the moving iron 42 is connected to the piston 2. For example, the moving iron 42 and the piston 2 are fixed together by a tight fit of a hole shaft, and the movement of the moving iron 42 can pull the piston 2 to move up and down in the cylinder body 1.

The elastic member 43 may be a spring, one end of which is connected to the stationary iron 41, and the other end is connected to the moving iron 42. As shown in FIG2 , when the electromagnetic coil 44 is not energized, the moving iron 42 and the stationary iron 41 are spaced apart, and the piston 2 is located at the first position, at which time the elastic member 43 may be in a compressed state; when the electromagnetic coil 44 is energized, the moving iron 42 and the stationary iron 41 are magnetized, and under the attraction generated between the moving iron 42 and the stationary iron 41, the moving iron 42 drives the piston 2 to move toward the stationary iron 41 and further compresses the elastic member 43 until the interval between the moving iron 42 and the stationary iron 41 disappears, that is, the moving iron 42 and the stationary iron 41 are in contact, and the piston 2 is located at the second position. The interval is the stroke of the moving iron 42.

In addition, in order to allow the liquid at the fluid inlet R to flow into the gap between the cylinder body 1 and the piston 2 as quickly as possible, the size of the gap at the fluid inlet R can be increased. Specifically, an annular channel T can be provided on the other of the inner wall of the cylinder body 1 and the outer wall of the piston 2. As shown in FIG2 , the annular groove 31 is provided on the inner wall of the cylinder body 1, and the annular channel T can be provided on the outer wall of the piston 2. Alternatively, if the annular groove 31 is provided on the outer wall of the piston 2, the annular channel T can be provided on the inner wall of the cylinder body 1. Furthermore, the fluid inlet R can be communicated with the annular channel T, and the structure of the annular channel T and the annular groove channel 34 of the reversing mechanism 3 can be the same or different.

Fig. 3A is a schematic diagram of an exemplary structure of the piston of the piston valve shown in Fig. 2. As shown in Fig. 3A, the annular groove channel 34 has the same structure as the annular channel T, and both are continuous grooves extending along the circumferential direction. This reduces the processing difficulty and saves time.

FIG3B is another exemplary structural schematic diagram of the piston of the piston valve shown in FIG2 . The difference from the piston 2 shown in FIG3A is that in the piston 2 shown in FIG3B , the annular groove channel 34 is a discontinuous groove design along the circumferential direction. Specifically, the annular groove channel 34 includes a plurality of groove bodies G spaced in the circumferential direction around the inner wall of the cylinder body 1 and the outer wall of the piston 2, wherein the plurality of groove bodies G can be spaced evenly or unevenly along the circumferential direction. When the one-way seal 32 corresponds to the annular groove channel 34, the outer wall W between the adjacent groove bodies G can support the one-way seal 32, that is, can reliably support the lip edge of the lip seal ring, so that the lip seal ring can realize the on-off of the liquid without significant deformation, which can effectively prevent the one-way seal 32 from turning over, and also has the effect of increasing the life of the lip seal ring. In addition, in FIG3B , the annular channel T is still a continuous groove extending in the circumferential direction.

Furthermore, the size of the groove body G in the axial direction may be larger than the size in the circumferential direction. For example, the groove body G may be a narrow and long groove, and the length of the narrow and long groove is in the axial direction, which is consistent with the flow direction of the fluid. In this way, more groove bodies G may be arranged in the circumferential direction, so that the fluid can flow from more groove bodies G in multiple ways, so that the force is more balanced. In addition, the size of the groove body G in the axial direction may also be smaller than the size in the circumferential direction, so that the groove body G can accommodate more fluid and allow the fluid to pass through the groove body G faster. Of course, the size of the groove body G in the axial direction may also be equal to the size in the circumferential direction.

In addition, the longitudinal section or cross section of the groove body G is an arc. Among them, the "cross section of the groove body G" refers to the transverse section perpendicular to the central axis of the piston 2. The "longitudinal section of the groove body G" refers to the longitudinal section passing through the central axis of the piston 2. In addition, the arc can be away from the central axis of the piston 2 at both ends of the arc along the bending direction. That is, the arc is bent away from the central axis of the piston 2, so that the middle space of the groove body G is larger and the space at both ends is smaller, which is convenient for processing and manufacturing. Moreover, when the cross section of the groove body G is an arc, the flow channel formed is relatively smooth, which is convenient for the fluid to enter the groove body G and flow out of the groove body G, that is, the fluid can pass through more smoothly, and it is not easy for the fluid to be retained, which is conducive to speeding up the fluid speed. It can be understood that the cross section of the groove body G can also be other shapes, for example, the cross section of the groove body G is rectangular.

Fig. 3C is another exemplary structural schematic diagram of the piston of the piston valve shown in Fig. 2. The difference from the piston 2 shown in Fig. 3B is that in the piston 2 shown in Fig. 3C, the structure of the annular channel T is the same as the structure of the annular groove channel 34, both of which are discontinuous groove designs along the circumferential direction.

The piston valve of the embodiment of the present application can conduct unidirectional or bidirectional flow between the fluid inlet R and the fluid outlet C through the reversing mechanism 3, realizing the function of integrating a one-way valve on the piston valve, ensuring that when the pressure at the fluid inlet R is reduced, the high-pressure fluid at the fluid outlet C can flow back to the fluid inlet R, so that in a stable state the pressure at the fluid outlet C will not be greater than the pressure at the fluid inlet R, thereby reducing the probability of danger. At the same time, it avoids the use of a single one-way valve, reduces the number of parts and the number of flow channels, reduces the risk of leakage, improves reliability, and reduces costs, which is conducive to miniaturization.

In addition, the one-way seal 32 can be a lip seal. Since the lip seal is not pre-compressed, the movement resistance is small, which reduces the sliding resistance of the piston valve. At the same time, the lip seal relies on lip sealing and has a small axial dimension, thereby reducing the movement stroke of the piston valve, reducing the power consumption of the driving mechanism that drives the piston 2 to move, and can reduce the volume, which is conducive to miniaturization.

In addition, the piston 2 can adopt the design of "intermittent groove". The "intermittent groove" means that the groove is intermittent in the annular direction and no continuous annular groove is formed. The complete circular ring, i.e., the annular outer wall and the lip seal ring, such as the lip edge of the U-shaped seal ring, arranged adjacent to the "intermittent groove" can cooperate to form a one-way seal, and block the flow of fluids such as liquids in one direction; when the lip edge of the U-shaped seal ring fits on the "intermittent groove", the liquid can flow in both directions from the groove. The intermittent groove can ensure that the piston 2 can slide smoothly in both directions relative to the U-shaped seal ring, can reliably support the lip edge of the lip seal ring, so that the lip seal ring can realize the on-off of the liquid without significant deformation, can effectively prevent the one-way seal 32 from flipping, and can also be used to increase the life of the lip seal ring. The step of the continuous groove is easy to cause the rubber lip edge to flip and be damaged when it slides in the opposite direction relative to the U-shaped seal ring.

FIG4 is a schematic cross-sectional view of a piston valve provided in the second embodiment of the present application. The difference from the piston valve shown in FIG2 is that in the piston valve shown in FIG4, two fluid outlets C are provided on the cylinder body 1, and the fluid inlet R is located between the two fluid outlets C in the axial direction. The two fluid outlets C are the first fluid outlet C1 and the second fluid outlet C2. The piston valve is a two-position three-way valve, and the piston valve includes two reversing mechanisms 3, and the two reversing mechanisms 3 are the first reversing mechanism 3a and the second reversing mechanism 3b. The first reversing mechanism 3a is located between the fluid inlet R and the first fluid outlet C1 in the axial direction, and is connected to the first fluid outlet C1. Specifically, the annular groove channel 34 of the first reversing mechanism 3a is connected to the first fluid outlet C1. The first reversing mechanism 3a can realize unidirectional or bidirectional communication between the fluid inlet R and the first fluid outlet C1, ensuring that when the pressure at the fluid inlet R is reduced, the high-pressure fluid at the first fluid outlet C1 can flow back to the fluid inlet R, so that the pressure at the first fluid outlet C1 will not be greater than the pressure at the fluid inlet R in a stable state. The second reversing mechanism 3b is located between the fluid inlet R and the second fluid outlet C2 in the axial direction and is connected to the second fluid outlet C2. Specifically, the annular groove channel 34 of the second reversing mechanism 3b is connected to the second fluid outlet C2. The second reversing mechanism 3b can achieve unidirectional or bidirectional communication between the fluid inlet R and the second fluid outlet C2, ensuring that when the pressure at the fluid inlet R is reduced, the high-pressure fluid at the second fluid outlet C2 can flow back to the fluid inlet R, so that in a stable state, the pressure at the second fluid outlet C2 will not be greater than the pressure at the fluid inlet R.

The piston 2 can move between a first position and a second position. In the first position, the first reversing mechanism 3a is in a two-way conduction state, and the second reversing mechanism 3b is in a one-way conduction state; in the second position, the first reversing mechanism 3a is in a one-way conduction state, and the second reversing mechanism 3b is in a two-way conduction state. That is, the conduction states of the first reversing mechanism 3a and the second reversing mechanism 3b are different at the first position and the second position.

The form of the driving mechanism for driving the piston 2 to move in the axial direction can be found in the relevant description of the piston valve of the first embodiment. As shown in FIG4 , when the electromagnetic driving mechanism is used to drive the piston 2 to move, when the electromagnetic coil 44 is not energized, the elastic member 43 pushes the moving iron 42 and the piston 2 to the lowest position, and the piston 2 is located in the first position. When the electromagnetic coil 44 is energized, the stationary iron 41 and the moving iron 42 are magnetized by the electromagnetic coil 44, and the moving iron 42 is moved toward the stationary iron 41 by the electromagnetic force, and at the same time drives the piston 2 to move until the moving iron 42 contacts the stationary iron 41, and the piston 2 can move to the second position, thereby realizing the movement of the piston 2 between the first position and the second position.

4, in the piston valve of the second embodiment of the present application, the annular channel T connected to the fluid inlet R may be located between the annular outer wall 33 of the first reversing mechanism 3a and the annular outer wall 33 of the second reversing mechanism 3b. In addition, the annular channel T may have the same or different structure as the annular groove channel 34 of the reversing mechanism 3.

Fig. 5A is a schematic diagram of an exemplary structure of the piston of the piston valve shown in Fig. 4. As shown in Fig. 5A, the annular groove channel 34 of the first reversing mechanism 3a and the annular groove channel 34 of the second reversing mechanism 3b have the same structure as the annular channel T, and are both continuous grooves extending along the circumferential direction. This reduces the processing difficulty and saves time.

FIG5B is another exemplary structural diagram of the piston of the piston valve shown in FIG4. The difference from the piston 2 shown in FIG5A is that in the piston 2 shown in FIG5B, the annular groove channel 34 of the first reversing mechanism 3a and the annular groove channel 34 of the second reversing mechanism 3b are intermittent groove designs, and the specific contents of the intermittent grooves can be referred to the relevant description of FIG3B. In addition, in FIG5B, the annular channel T is still a continuous groove extending in the circumferential direction.

Fig. 5C is another exemplary structural schematic diagram of the piston of the piston valve shown in Fig. 4. The difference from the piston 2 shown in Fig. 5B is that in the piston 2 shown in Fig. 5C, the structure of the annular channel T is the same as the structure of the annular groove channel 34, both of which are discontinuous groove designs along the circumferential direction.

The application scenario of the piston valve of the second embodiment of the present application is the occasion where a two-position three-way valve is required to direct one hydraulic input selection to two output passages, and when the pressure of the input passage is reduced, the high-pressure liquid at the two output passages can flow back to the input passage, so that the pressure of the two output passages will not be greater than the pressure of the input passage in a stable state, wherein the input passage is connected to the fluid inlet, and the output passage is connected to the fluid outlet. Specifically, the two one-way valves and the two-position three-way valve are designed as one body, and the two-position three-way valve is connected in parallel with the two one-way valves to avoid the appearance of a single one-way valve, and it is ensured that the pressure of the two output ends/fluid outlets can flow back to the input end, that is, when the pressure at the fluid inlet is reduced, the high-pressure fluid at the fluid outlet can flow back to the fluid inlet, so that the pressure at the fluid outlet in a stable state will not be greater than the pressure at the fluid inlet, which reduces the probability of danger, reduces the number of parts and the number of flow channels, reduces the risk of leakage, improves reliability, and reduces costs, which is conducive to miniaturization.

Furthermore, the embodiment of the present application uses a lip seal ring such as a U-shaped seal ring instead of an O-shaped seal ring, and utilizes the one-way conduction function of the lip seal ring to replace the one-way valve, thereby realizing the function of a two-position three-way valve in parallel with a one-way valve. Since the lip seal ring is not pre-compressed, the movement resistance is small, which reduces the sliding resistance of the piston valve. At the same time, the lip seal ring relies on the lip seal and has a small axial dimension, thereby reducing the movement stroke of the piston valve, reducing the power consumption of the driving mechanism that drives the piston 2 to move, and can reduce the volume, which is conducive to miniaturization.

In addition, the piston 2 can adopt the design of "intermittent groove". The "intermittent groove" means that the groove is intermittent in the annular direction and no continuous annular groove is formed. The complete circular ring, i.e., the annular outer wall and the lip seal ring, such as the lip edge of the U-shaped seal ring, arranged adjacent to the "intermittent groove" can cooperate to form a one-way seal, and block the flow of fluids such as liquids in one direction; when the lip edge of the U-shaped seal ring fits on the "intermittent groove", the liquid can flow in both directions from the groove. The intermittent groove can ensure that the piston 2 can slide smoothly in both directions relative to the U-shaped seal ring, can reliably support the lip edge of the lip seal ring, so that the lip seal ring can realize the on-off of the liquid without significant deformation, can effectively prevent the one-way seal 32 from flipping, and can also be used to increase the life of the lip seal ring. The step of the continuous groove is easy to cause the rubber lip edge to flip and be damaged when it slides in the opposite direction relative to the U-shaped seal ring.

The embodiment of the present application also provides a vehicle, which includes a piston valve, a brake master cylinder, a wheel and a brake wheel cylinder, and a pedal feel simulator. Among them, the piston valve of the vehicle can be the piston valve of the second embodiment of the present application mentioned above. The brake master cylinder is connected to the fluid inlet R of the piston valve. The brake wheel cylinder is connected to the first fluid outlet C1 of the piston valve, and provides braking force for the brake wheel when receiving the fluid. The pedal feel simulator is connected to the second fluid outlet C2 of the piston valve, and simulates the pedaling force when receiving the fluid.

In the first position, the master cylinder is bidirectionally connected to the wheel cylinder through the first reversing mechanism 3a; the master cylinder is unidirectionally connected to the pedal feel simulator through the second reversing mechanism 3b. In this way, when the driver steps on the pedal, the fluid pressure in the master cylinder increases, so that the fluid in the master cylinder enters the wheel cylinder through the fluid inlet R, the first reversing mechanism 3a, and the first fluid outlet C1 in sequence, applying braking force to the wheel; and the one-way seal 32 of the second reversing mechanism 3b one-way seals the gap between the piston 2 and the cylinder body 1, which can prevent the fluid in the master cylinder from passing through, and the fluid will not enter the pedal feel simulator; when the driver releases the pedal, the fluid pressure in the master cylinder decreases, and the fluid in the wheel cylinder can flow back to the master cylinder through the first fluid outlet C1, the first reversing mechanism 3a, and the fluid inlet R in sequence.

Specifically, as shown in FIG4 , in the first position, for the first reversing mechanism 3a, the one-way seal 32 such as a U-shaped seal ring in the annular groove 31 of the cylinder body 1 is in contact with the intermittent groove, i.e., the annular groove channel 34, and the one-way seal 32 does not circumferentially seal the gap between the piston 2 and the cylinder body 1. After the high-pressure liquid in the brake master cylinder connected to the fluid inlet R enters the cylinder body 1, it can continue to flow through the intermittent groove at the piston 2, flow to the first fluid outlet C1, and enter the brake wheel cylinder to form a backup brake. In addition, when the liquid pressure in the brake wheel cylinder is higher than the fluid pressure in the brake master cylinder, the liquid in the brake wheel cylinder can enter the cylinder body 1 through the first fluid outlet C1, and flow back to the fluid inlet R through the one-way seal 32, and then enter the brake master cylinder. For the second reversing mechanism 3b, the annular outer wall 33 on the piston 2 and the one-way seal 32 such as a U-shaped seal ring in the annular groove 31 of the cylinder body 1 are one-way sealed. After the fluid in the brake master cylinder connected to the fluid inlet R enters the gap between the cylinder body 1 and the piston 2, it cannot pass through the one-way seal 32 of the second reversing mechanism 3b to reach the second fluid outlet C2, so it cannot enter the pedal feeling simulator. However, when the fluid pressure in the pedal feeling simulator is higher than the fluid pressure in the brake master cylinder, the fluid in the pedal feeling simulator can enter the cylinder body 1 through the second fluid outlet C2, and flow back to the fluid inlet R through the one-way seal 32, and then enter the brake master cylinder.

When the piston valve is energized, the wheel braking force can be provided by the first ECU shown in FIG. 1A and FIG. 1B, and the fluid in the master cylinder can be used to enter the pedal simulator to simulate the pedaling force. At this time, the piston 2 is in the second position, and the master cylinder is unidirectionally connected to the wheel cylinder through the first reversing mechanism 3a; the master cylinder and the pedal feeling simulator are bidirectionally connected through the second reversing mechanism 3b. When the driver steps on the pedal, the fluid pressure in the master cylinder increases, so that the fluid in the master cylinder enters the pedal feeling simulator through the fluid inlet R, the second reversing mechanism 3b, and the second fluid outlet C2 in sequence, and the one-way seal 32 of the first reversing mechanism 3a seals the gap between the piston 2 and the cylinder body 1 in one direction, which can prevent the fluid in the master cylinder from passing through, and the fluid will not enter the wheel cylinder; when the driver releases the pedal, the hydraulic pressure in the master cylinder decreases, and the fluid in the pedal feeling simulator can flow back to the master cylinder through the second fluid outlet C2, the second reversing mechanism 3b, and the fluid inlet R in sequence.

Specifically, in the second position, for the first reversing mechanism 3a, the annular outer wall 33 on the piston 2 and the one-way seal 32 such as a U-shaped seal ring are in contact with each other to form a one-way seal, so that after the liquid in the brake master cylinder enters the cylinder body 1 through the fluid inlet R, it cannot flow to the first fluid outlet C1 through the first reversing mechanism 3a, and therefore cannot enter the brake wheel cylinder; but when the liquid pressure in the brake wheel cylinder is higher than the fluid pressure in the brake master cylinder, the liquid in the brake wheel cylinder can enter the gap between the cylinder body 1 and the piston 2 through the first fluid outlet C1, and flow back to the fluid inlet R through the one-way seal 32, and then enter the brake master cylinder. For the second reversing mechanism 3b, the one-way seal 32 such as a U-shaped seal ring in the annular groove 31 of the cylinder body 1 is in contact with the intermittent groove, that is, the annular groove channel 34, and the high-pressure liquid in the brake master cylinder connected to the fluid inlet R, after entering the gap between the cylinder body 1 and the piston 2, can continue to flow through the intermittent groove at the piston 2, flow to the second fluid outlet C2, and enter the pedal feeling simulator to form pedal feedback. In addition, when the fluid pressure in the pedal feel simulator is higher than the fluid pressure in the brake master cylinder, the fluid in the pedal feel simulator can enter the gap between the cylinder body 1 and the piston 2 through the second fluid outlet C2, and flow back to the fluid inlet R through the one-way seal 32 of the second reversing mechanism 3b, and then enter the brake master cylinder.

In summary, in the embodiment of the present application, a lip seal ring such as a U-shaped seal ring is used to replace an O-shaped seal ring, which plays a role of one-way conduction, avoids the setting of a split one-way valve, and realizes the function of a parallel one-way valve on a piston valve, which can reduce the number of parts and the number of channels, reduce the risk of leakage, improve reliability, and reduce costs, which helps to reduce the volume and achieve miniaturization. Furthermore, the intermittent groove design can not only form a fluid such as a liquid channel, but also support the lip edge of a lip seal ring such as a U-shaped seal ring, so that the liquid can be turned on and off without significant deformation, which is beneficial to improving the life of the U-shaped seal ring and is beneficial to the bidirectional movement of the piston relative to the U-shaped seal ring. In addition, there is no need to use the height H of the entire U-shaped seal ring to achieve sealing, and only the smooth section between its lip edge and the intermittent groove is used for sealing, which can reduce friction resistance and make the solenoid valve stroke smaller. In addition, since the lip seal ring is not pre-compressed, the movement resistance is small, and the piston 2 moves smoothly in both directions, which helps to reduce power consumption.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, and do not limit it. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present application.

Claims (13)

1. A piston valve, comprising: A cylinder body (1), wherein a fluid inlet (R) and at least one fluid outlet (C) are arranged at intervals along the axial direction on the annular side wall thereof, wherein the fluid inlet (R) is at least used for connecting to a brake master cylinder, and the fluid outlet (C) is at least used for connecting to a brake wheel cylinder and/or a pedal feeling simulator; A piston (2) capable of moving along the axial direction in the cylinder (1); At least one reversing mechanism (3) is arranged at a gap between the cylinder body (1) and the piston (2) in a circumferential direction around the piston, the reversing mechanism (3) is located between the fluid inlet (R) and the fluid outlet (C) along the axial direction and is in communication with the fluid outlet (C), and when the piston (2) moves along the axial direction, the reversing mechanism (3) can switch between a unidirectional conductive state and a bidirectional conductive state, wherein: In the one-way conduction state, the reversing mechanism (3) can unidirectionally seal the gap to prevent the fluid from flowing from the fluid inlet (R) through the reversing mechanism (3) to the fluid outlet (C), and can allow the fluid to flow back from the fluid outlet (C) through the reversing mechanism (3) to the fluid inlet (R); In the bidirectional conduction state, the reversing mechanism (3) can allow the fluid to flow from the fluid inlet (R) to the fluid outlet (C) through the reversing mechanism (3), or can allow the fluid to flow back from the fluid outlet (C) to the fluid inlet (R) through the reversing mechanism (3). 2. The piston valve according to claim 1, characterized in that the reversing mechanism (3) comprises: an annular groove (31) and a one-way seal (32), wherein the annular groove (31) is arranged on one of the inner wall of the cylinder body (1) and the outer wall of the piston (2), and the one-way seal (32) is arranged in the annular groove (31); The annular outer wall (33) and the annular groove channel (34) are adjacently arranged on the other of the inner wall of the cylinder body (1) and the outer wall of the piston (2), and the fluid inlet (R) and the annular groove channel (34) are located on both sides of the annular outer wall (33) along the axial direction, and the fluid outlet (C) is communicated with the annular groove channel (34), wherein: In the one-way conduction state, the one-way seal (32) contacts the annular outer wall (33), and the one-way seal (32) can seal the gap along the direction from the fluid inlet (R) to the annular groove channel (34), and can allow the fluid to flow through the gap along the direction from the annular groove channel (34) to the fluid inlet (R) to flow back to the fluid inlet (R); In the bidirectional conductive state, the one-way seal (32) corresponds to the annular groove channel (34), so that the fluid can flow through the annular groove channel (34) in the direction from the fluid inlet (R) to the annular groove channel (34) to flow to the fluid outlet (C) or flow through the annular groove channel (34) in the direction from the annular groove channel (34) to the fluid inlet (R) to flow back to the fluid inlet (R). 3. The piston valve according to claim 2, characterized in that the one-way seal (32) comprises a lip seal ring, the lip of the lip seal ring faces the side where the fluid inlet (R) is located, wherein: When the one-way seal (32) is in corresponding contact with the annular outer wall (33), when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the opposite side of the lip, the lip expands outward, so that the lip edge of the lip-shaped sealing ring is in close contact with the annular outer wall (33), thereby sealing the gap along the direction from the fluid inlet (R) to the annular groove channel (34); when the fluid pressure on the lip side is less than the fluid pressure on the opposite side of the lip, the lip contracts, so that the lip edge of the lip-shaped sealing ring is separated from the annular outer wall (33) to form a gap, so that the fluid flows from the opposite side of the lip through the gap to the lip side, thereby achieving one-way sealing or one-way conduction; When the one-way seal (32) corresponds to the annular groove channel (34), when the pressure of the fluid on the lip side is greater than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the lip side to the opposite side of the lip through the annular groove channel (34); when the pressure of the fluid on the lip side is less than the pressure of the fluid on the opposite side of the lip, the fluid can flow from the opposite side of the lip to the lip side through the annular groove channel (34), thereby achieving two-way conduction. 4. The piston valve according to claim 2 or 3 is characterized in that the annular groove channel (34) includes a plurality of groove bodies (G) arranged at intervals in the circumferential direction around the inner wall of the cylinder body (1) and the other of the outer walls of the piston (2), and when the one-way seal (32) corresponds to the annular groove channel (34), the outer wall (W) between adjacent groove bodies (G) can support and contact the one-way seal (32). 5. The piston valve according to claim 4, characterized in that: The dimension of the groove body (G) along the axial direction is greater than, less than or equal to the dimension along the circumferential direction; and/or, The longitudinal section or cross section of the groove body (G) is arc-shaped, and the two ends of the arc along the bending direction are away from the central axis of the piston (2) relative to the middle of the arc. 6. A piston valve according to any one of claims 1 to 3, characterized in that two fluid outlets (C) are provided on the cylinder body (1), the fluid inlet (R) is located between the two fluid outlets (C) along the axial direction, the two fluid outlets (C) are a first fluid outlet (C1) and a second fluid outlet (C2), the piston valve comprises two reversing mechanisms (3), the two reversing mechanisms (3) are a first reversing mechanism (3a) and a second reversing mechanism (3b); the first reversing mechanism (3a) is located between the fluid inlet (R) and the first fluid outlet (C1) along the axial direction and is communicated with the first fluid outlet (C1), the second reversing mechanism (3b) is located between the fluid inlet (R) and the second fluid outlet (C2) along the axial direction and is communicated with the second fluid outlet (C2); the piston (2) is capable of moving between a first position and a second position, wherein: When in the first position, the first reversing mechanism (3a) is in the bidirectional conduction state, and the second reversing mechanism (3b) is in the unidirectional conduction state; When in the second position, the first reversing mechanism (3a) is in the unidirectional conductive state, and the second reversing mechanism (3b) is in the bidirectional conductive state. 7. A piston valve according to any one of claims 1-3, characterized in that an annular channel (T) is provided on the other of the inner wall of the cylinder body (1) and the outer wall of the piston (2), the fluid inlet (R) is connected to the annular channel (T), and the annular channel (T) has the same or different structure as the annular groove channel (34) of the reversing mechanism (3). 8. The piston valve according to any one of claims 1 to 3, characterized in that the piston valve further comprises: A first sealing ring (M1) is located at the first end of the piston (2) and is capable of sealing the circumferential gap between the cylinder body (1) and the piston (2) in the direction from the second end of the piston (2) to the first end of the piston (2); A second sealing ring (M2) is located at the second end of the piston (2) and is capable of sealing the circumferential gap between the cylinder body (1) and the piston (2) along the direction from the first end of the piston (2) to the second end of the piston (2); The fluid inlet (R), the fluid outlet (C), and the reversing mechanism (3) are located between the first sealing ring (M1) and the second sealing ring (M2) along the axial direction. 9. The piston valve according to claim 8, characterized in that the first sealing ring (M1) and the second sealing ring (M2) are respectively one of an O-ring and a lip sealing ring, wherein: The O-ring can seal the gap in both directions from the first end of the piston (2) to the second end of the piston (2) and from the second end of the piston (2) to the first end of the piston (2); The opening of the lip seal ring faces the side where the fluid inlet (R) is located, and the lip seal ring can unidirectionally seal the gap from the lip side to the opposite side of the lip. 10. The piston valve according to claim 6, characterized in that the piston valve further comprises a driving mechanism, the driving mechanism is used to drive the piston (2) to move along the axial direction, and the driving mechanism is one of a manual operating mechanism, an electromagnetic driving mechanism (4), a pneumatic driving mechanism, a hydraulic driving mechanism and an electro-hydraulic driving mechanism; Furthermore, the electromagnetic drive mechanism (4) comprises a stationary iron (41), a moving iron (42), an elastic member (43) connecting the stationary iron (41) and the moving iron (42), and an electromagnetic coil (44) arranged on the periphery of the moving iron (42) and the stationary iron (41), and the moving iron (42) is connected to the piston (2), wherein: When the electromagnetic coil (44) is not energized, the moving iron (42) and the stationary iron (41) are spaced apart, and the piston (2) is located at a first position; When the electromagnetic coil (44) is energized, the moving iron (42) and the stationary iron (41) are magnetized, so that the moving iron (42) drives the piston (2) to move toward the stationary iron (41) and compresses the elastic member (43), and the piston (2) is located at the second position. 11. The piston valve according to claim 7, characterized in that the piston valve further comprises a driving mechanism, the driving mechanism is used to drive the piston (2) to move along the axial direction, and the driving mechanism is one of a manual operating mechanism, an electromagnetic driving mechanism (4), a pneumatic driving mechanism, a hydraulic driving mechanism and an electro-hydraulic driving mechanism; Furthermore, the electromagnetic drive mechanism (4) comprises a stationary iron (41), a moving iron (42), an elastic member (43) connecting the stationary iron (41) and the moving iron (42), and an electromagnetic coil (44) arranged on the periphery of the moving iron (42) and the stationary iron (41), and the moving iron (42) is connected to the piston (2), wherein: When the electromagnetic coil (44) is not energized, the moving iron (42) and the stationary iron (41) are spaced apart, and the piston (2) is located at a first position; When the electromagnetic coil (44) is energized, the moving iron (42) and the stationary iron (41) are magnetized, so that the moving iron (42) drives the piston (2) to move toward the stationary iron (41) and compresses the elastic member (43), and the piston (2) is located at the second position. 12. The piston valve according to any one of claims 3 or 9, characterized in that the lip seal ring comprises one of a U-shaped seal ring, a V-shaped seal ring and a Y-shaped seal ring. 13. A vehicle, comprising: The piston valve according to any one of claims 6 to 12; a brake master cylinder, connected to a fluid inlet (R) of the piston valve; a wheel and a wheel cylinder, the wheel cylinder being in communication with a first fluid outlet (C1) of the piston valve to provide a braking force for braking the wheel upon receiving fluid; a pedal feel simulator in communication with the second fluid outlet (C2) of the piston valve to simulate a pedaling force upon receiving the fluid; wherein: When in the first position, the master brake cylinder is bidirectionally connected to the wheel brake cylinder via a first reversing mechanism (3a); the master brake cylinder is unidirectionally connected to the pedal feel simulator via a second reversing mechanism (3b); When in the second position, the master brake cylinder is unidirectionally connected to the brake wheel cylinder through the first reversing mechanism (3a); and the master brake cylinder is bidirectionally connected to the pedal feel simulator through the second reversing mechanism (3b).