A zero-leak one-way valve

Abstract

The utility model belongs to one -way valve field discloses a kind of zero leakage one-way valves, including valve body, spring and valve core, the front end of valve core is equipped with cone head, the front end inner surface of valve body is equipped with taper face, cone head and taper face can face contact between, the outer periphery of cone head is equipped with annular groove, sealing element is installed in annular groove, the outer ring of sealing element is with the outer surface of cone head, sealing element and annular groove are sealed state between, the inside of valve core is equipped with valve core passage, one end of valve core passage is connected to the groove bottom of annular groove, another end of valve core passage is connected to valve body export.The utility model cooperates sealing element and valve core passage, controls using reverse pressure, can effectively reduce the fatigue damage of sealing element, prolong the service life of sealing element, improve the zero leakage effect of one-way valve.

Description

Technical Field

[0001] This utility model relates to the field of one-way valve technology, and in particular to a zero-leakage one-way valve. Background Technology

[0002] Hydraulic check valves are a common component in hydraulic transmission applications. The function of a hydraulic check valve is to allow pressurized oil to flow from one port to another while preventing oil from flowing from one port to another, ensuring zero leakage and maintaining the pressure at the other port.

[0003] Hydraulic systems require high performance, demanding precise control and pressure maintenance while ensuring safe and stable operation. Therefore, check valves are subject to stringent requirements, necessitating zero leakage to maintain the stability and reliability of the hydraulic system. Traditional check valves, such as ball-type and cone-type valves, suffer from poor sealing performance and are prone to leakage. For example, typical pilot-operated check valves use a hard metal cone seal, resulting in relatively large leakage, and the sealing performance deteriorates with each opening and closing cycle. Traditional dual-pilot-operated check valves rely on a rigid seal between the valve disc and valve body; regardless of machining precision, pressure leakage will occur, making absolute zero pressure leakage impossible.

[0004] CN 202972035 U discloses a zero-leakage reverse check valve, including a valve body, a valve core installed in the cavity of the valve body, and an irregularly shaped groove with a smaller outer surface and a larger inner surface on the inclined surface of the valve body. A sealing ring is installed in the irregularly shaped groove, and the sealing ring can fit against the smooth conical surface of the valve body. The check valve uses a metal-to-metal line seal or a metal conical surface seal, which may result in a slight leakage in one direction. By adding a sealing ring that fits against the smooth conical surface of the valve body, and applying one-way pressure to press the sealing ring against the smooth conical surface of the valve body, zero reverse leakage can be achieved, enabling long-term pressure maintenance and preventing hydraulic oil leakage. This patent achieves a double-seal effect through a combination of conical surface sealing and sealing ring sealing. While this improves the sealing effect, it presents several problems: First, to ensure stable installation of the sealing ring, a small annular groove is typically created on the conical surface of the valve core. The sealing ring is then squeezed and secured within this groove. However, the inner ring of the sealing ring is constantly compressed within the groove. When the outer ring is compressed against the conical surface by a spring or reverse pressure, the uneven deformation between the inner and outer rings makes them prone to breakage, especially during repeated compression. First, the sealing ring is broken. Second, in order to achieve a seal, the outer ring of the sealing ring must extend beyond the annular groove. When the valve core seals in the reverse direction, the sealing ring will first be squeezed onto the conical surface of the valve body, and then the conical surface between the valve core and the valve body can make contact and fit. This sealing sequence is very critical. The sealing ring must deform and seal first, and then the conical surface must make contact and seal rigidly. Therefore, regardless of whether there is reverse pressure, the valve core will cause the sealing ring to deform first under the action of the spring. Therefore, as long as the valve core is closed, the sealing ring will always be squeezed. The sealing ring is always involved in the squeezing and deformation sealing, which is prone to fatigue damage and leads to sealing failure, making it impossible to achieve zero leakage of the one-way valve. Summary of the Invention

[0005] The technical problem to be solved by this utility model is to provide a zero-leakage one-way valve with better sealing effect and longer service life.

[0006] To solve the above-mentioned technical problems, the technical solution of this utility model is: a zero-leakage one-way valve, comprising a valve body, a spring, and a valve core. The valve body has a valve body inlet at its front end and a valve body outlet at its side end. The valve core is assembled within the valve body and can move along a direction away from or towards the front end of the valve body. The spring drives the valve core to move towards the front end of the valve body. The front end of the valve core has a conical head, and the inner surface of the front end of the valve body has a conical surface. The conical head and the conical surface can be in surface contact. The outer circumferential surface of the conical head has an annular groove, and a sealing element is installed within the annular groove. The outer ring of the seal is flush with the outer surface of the cone, and the seal is in a sealing relationship with the annular groove. The valve core has a valve core channel inside, one end of which is connected to the bottom of the annular groove, and the other end of which is connected to the valve body outlet.

[0007] As a preferred technical solution, there is an oil-filled gap between the inner ring of the seal and the bottom of the annular groove.

[0008] As a preferred technical solution, the valve core includes a cylinder with a valve core cavity and a cone. The outer circumferential surface of the cylinder is provided with a valve core oil port, which connects the valve body outlet and the valve core cavity. The cone is provided with a valve core main oil hole that communicates with the valve core cavity. The cone is also provided with a plurality of valve core support oil holes, each of which connects the annular groove to the valve core main oil hole.

[0009] As a preferred technical solution, the annular groove is perpendicular to the conical surface of the valve core.

[0010] As a preferred technical solution, the annular groove is perpendicular to the rotation axis of the valve core.

[0011] As a preferred technical solution, the sealing element is an O-ring, and the wire diameter of the O-ring is larger than the width of the annular groove to achieve a sealing installation.

[0012] As a preferred technical solution, the sealing element includes an O-ring and a support ring frame supported on the inner ring of the O-ring. The wire diameter of the O-ring is equal to the width of the annular groove, and the support ring frame is sealed and installed in the annular groove.

[0013] Due to the adoption of the above technical solution, the beneficial effects of this utility model are: 1. When there is reverse pressure in the valve core channel, the seal will be squeezed and deformed. When there is no reverse pressure in the valve core channel, the seal will not deform. Therefore, the deformation of the seal is affected by the reverse pressure. When the valve core is closed, the seal does not need to be squeezed and deformed all the time. Compared with the seals in the prior art that need to participate in the squeezing and deformation, the seal of this application is squeezed in an intermittent manner. The seal is matched with the valve core channel and controlled by the reverse pressure, which can achieve the effect of active sealing, effectively reduce the fatigue damage of the seal, extend the service life of the seal, and improve the zero leakage effect of the check valve.

[0014] Second, because the seal and the annular groove are sealed together, reverse hydraulic oil located on the inner ring side of the seal can be prevented from entering the outer ring side of the seal, thus avoiding the situation where the pressure on both the inner and outer rings of the seal is the same, preventing the reverse hydraulic oil from pushing the seal outward. Simultaneously, when reverse pressure is first applied, the reverse hydraulic oil will also flow through the conical surface, resulting in a slight leakage. There will be a pressure loss on the outer ring side of the seal. Due to the seal and the annular groove being sealed together, the pressure on the inner ring of the seal will be greater than the pressure on the outer ring, creating a significant pressure difference between the inner and outer rings. This allows the seal to be better pushed outward by the reverse pressure oil. In summary, the seal and the annular groove are sealed together, effectively ensuring the seal is pushed outward, achieving zero leakage of reverse pressure. Furthermore, because the compression on the upper and lower sides of the seal is fixed, it will not fatigue, is less prone to breakage, and also provides a fixing function. Attached Figure Description

[0015] The following figures are intended only to illustrate and explain the present invention and do not limit the scope of the present invention. Wherein: Figure 1 This is a structural cross-sectional view of Embodiment 1 of this utility model; Figure 2 This is a schematic diagram of the one-way valve in the open state according to Embodiment 1 of this utility model; Figure 3 This is a schematic diagram of the one-way valve in the closed state according to Embodiment 1 of this utility model; Figure 4 yes Figure 3 Enlarged view of point I in the middle; Figure 5 This is a structural cross-sectional view of Embodiment 2 of this utility model; Figure 6 This is a structural cross-sectional view of Embodiment 3 of this utility model; Figure 7 This is a structural cross-sectional view of Embodiment 4 of this utility model; In the diagram: 1-Valve body; 2-Spring; 3-Valve core; 4-Valve cap; 5-Valve body inlet; 6-Valve body outlet; 7-Annular groove; 8-O-ring; 9-Oil filling gap; 10-Valve core oil port; 11-Valve core main oil hole; 12-Valve core branch oil hole; 13-Support ring frame; A-Multi-way valve; B-Oil passage; C-Oil port. Detailed Implementation

[0016] The present invention will be further described below with reference to the accompanying drawings and embodiments. In the following detailed description, only certain exemplary embodiments of the present invention are described by way of illustration. Undoubtedly, those skilled in the art will recognize that various modifications can be made to the described embodiments without departing from the spirit and scope of the present invention. Therefore, the drawings and description are illustrative in nature and not intended to limit the scope of the claims.

[0017] Example 1: like Figure 1 As shown, an active sealing zero-leakage check valve includes a valve body 1, a spring 2, a valve core 3, and a valve cap 4.

[0018] The valve body 1 has a valve body inlet 5 at its front end and a valve body outlet 6 at its side end. The valve core 3 is assembled inside the valve body 1 and can move in a direction away from or close to the front end of the valve body 1. The spring 2 is located between the valve core 3 and the valve cap 4, providing elastic force to drive the valve core 3 to move toward the front end of the valve body 1.

[0019] The valve core 3 has a conical head at its front end, and the inner surface of the front end of the valve body 1 has a conical surface. The conical head and the conical surface can be in surface contact. The outer circumferential surface of the conical head has an annular groove 7. A sealing element is installed in the annular groove 7. The outer ring of the sealing element is flush with the outer surface of the conical head. There is an oil-filled gap 9 between the inner ring of the sealing element and the bottom of the annular groove 7. The sealing element and the annular groove 7 are in a sealing relationship. In this embodiment, the sealing element is an O-ring. The O-ring 8 is directly sealed by having a wire diameter greater than the width of the annular groove 7. The valve core 3 has a valve core channel inside. One end of the valve core channel is connected to the bottom of the annular groove 7, and the other end of the valve core channel is connected to the valve body outlet 6.

[0020] The working principle of this embodiment is as follows: When the one-way valve of this application is installed on a multi-way valve A, the hydraulic oil in the oil passage B enters through the valve body inlet 5. The pressure increases, overcoming the elastic force of the spring 2, and pushes the valve core 3 to move away from the valve body inlet 5, opening the valve body inlet 5. The hydraulic oil enters through the gap between the cone head and the cone surface, then flows out through the valve body outlet 6, and enters the actuator through the oil port C, providing power for the actuator's operation. See the status section. Figure 2 ; When the oil supply to the valve body inlet 5 is stopped, the valve core 3 moves to reset towards the valve body inlet 5 under the action of the spring 2. The cone head and the cone surface are in a rigid sealing fit with surface contact. The outer ring of the O-ring 8 is in contact with the cone surface. In this state, if only the cone surface is in contact with the rigid seal, there will actually be a slight leakage. However, at this time, the outer ring of the O-ring 8 is in contact with the cone surface. Although the O-ring 8 is not squeezed and deformed, its outer ring is in contact with the cone surface and also participates in the sealing. At this time, compared with the single cone surface contact rigid seal, the sealing effect is effectively improved, and zero leakage is achieved. After the actuator moves, it generates a certain pressure. For example, when the hydraulic cylinder pushes a heavy object and then stops, the heavy object will compress the hydraulic cylinder, generating a certain pressure. Hydraulic oil will flow from the valve body outlet 6 and act in the opposite direction on the check valve. The hydraulic oil, as a pressure signal, enters the oil filling gap 9 through the valve body outlet 6, the valve core channel, and the annular groove 7, filling the oil filling gap 9 with hydraulic oil. The hydraulic oil acts evenly on the inner ring of the O-ring 8, pushing the O-ring 8 to deform outward as a whole. The outer ring of the O-ring 8 is tightly pressed against the conical surface, achieving zero leakage of the check valve. See the status section. Figure 3 and Figure 4 In this state, in addition to the rigid seal of the conical surface, the O-ring 8 deforms and is pressed more tightly against the conical surface for sealing. The sealing effect is better in this state. As long as pressure is applied to the inner ring of the O-ring 8, the sealing effect of the O-ring 8 is further improved, achieving zero leakage. When the actuator is released and there is no longer pressure at the valve body outlet 6, the O-ring 8 returns to its original shape under its own elastic deformation, no longer pressing against the conical surface but only contacting it. At this time, the zero leakage of the one-way valve can still be guaranteed.

[0021] When there is reverse pressure in the valve core channel, the O-ring 8 will be squeezed and deformed. When there is no reverse pressure in the valve core channel, the O-ring 8 will not deform. Therefore, the deformation of the O-ring 8 is affected by the reverse pressure. So, when the valve core 3 is closed, the O-ring 8 does not need to be squeezed and deformed all the time. Compared with the sealing rings in the prior art that need to participate in the squeezing and deformation, the O-ring 8 of this application is squeezed in an intermittent manner. The O-ring 8 is matched with the valve core channel and controlled by the reverse pressure, which can achieve the effect of active sealing, effectively reduce the fatigue damage of the sealing ring, extend the service life of the sealing ring, and improve the zero leakage effect of the one-way valve.

[0022] Because there is an oil-filled gap 9 between the O-ring 8 and the bottom of the annular groove 7, when reverse pressure enters the oil-filled gap 9 in the valve core channel, the oil-filled gap 9 is filled with hydraulic oil. The hydraulic oil then evenly contacts the inner surface of the O-ring 8. The large and uniform contact area between the hydraulic oil and the O-ring 8 allows the O-ring 8 to deform outwards as a whole, causing it to be compressed from a circle into a shape resembling a rectangle. (See attached image for details.) Figure 4 When the O-ring 8 is pushed outward and deformed, the force acting on the inner surface of the O-ring 8 is uniform, so the O-ring 8 is not easy to roll, but will move outward instead, which can avoid breakage due to rolling. At the same time, since the surface deformation of the O-ring 8 is very uniform, it is not easy to have local damage, which can extend the service life of the O-ring 8.

[0023] Because the wire diameter of the O-ring 8 is larger than the width of the annular groove 7, the upper and lower sides of the O-ring 8 are compressed against the inner wall of the annular groove 7. This prevents reverse hydraulic oil located on the inner ring side of the O-ring from entering the outer ring side of the O-ring 8 through the upper and lower sides, thus avoiding the situation where the pressure on both the inner and outer rings of the O-ring 8 is the same, preventing the reverse hydraulic oil from pushing the O-ring 8 outward. Simultaneously, when reverse pressure is just beginning to appear, the reverse hydraulic oil will also flow through the conical surface, resulting in a slight leakage on the conical surface. The reverse hydraulic oil will then flow on the outer ring side of the O-ring 8. Pressure loss occurs because the upper and lower sides of the O-ring 8 press and seal the inner wall of the annular groove 7. Therefore, the pressure on the inner ring of the O-ring 8 is greater than the pressure on the outer ring side, resulting in a large pressure difference between the inner and outer rings. At this time, the O-ring can be better pushed outward by the reverse pressure oil. In summary, since the wire diameter of the O-ring 8 is larger than the width of the annular groove 7, it can effectively ensure that the O-ring 8 is pushed outward, achieving zero leakage of reverse pressure. Furthermore, since the compression of the upper and lower sides of the O-ring 8 is fixed, it will not fatigue, is not prone to breakage, and can also play a fixing role.

[0024] In this embodiment, the wire diameter of the O-ring 8 is slightly larger than the width of the annular groove 7, which can ensure that the O-ring 8 is stably sealed and installed, while the extrusion deformation is not serious.

[0025] See Figure 4The valve core 3 includes a cylinder with a valve core cavity and a conical head. The outer circumferential surface of the cylinder is provided with a valve core oil port 10, which connects the valve body outlet 6 to the valve core cavity. The conical head is provided with a valve core main oil hole 11 communicating with the valve core cavity, and also with multiple valve core support oil holes 12. Each valve core support oil hole 12 connects the annular groove 7 to the valve core main oil hole 11. The valve core oil port 10, the valve core main oil hole 11, and the valve core support oil holes 12 cooperate to form the valve core channel. When there is reverse hydraulic oil at the valve body outlet 6, the hydraulic oil sequentially passes through the valve body outlet 6, the valve core oil port 10, the valve core 3 cavity, the valve core main oil hole 11, and the valve core support oil holes 12 to enter the bottom of the annular groove 7, and then enters the oil filling gap 9 to push the O-ring 8.

[0026] In this embodiment, the annular groove 7 is perpendicular to the conical surface of the cone head, and the axis of the valve core oil support hole 12 is also perpendicular to the conical surface of the cone head. The valve core main oil hole 11 is located on the rotation axis of the valve core 3.

[0027] Example 2: This embodiment is basically the same in structure as Embodiment 1, the difference being the installation method between the O-ring 8 and the annular groove 7. In Embodiment 1, the O-ring 8 and the annular groove 7 are directly sealed. In this embodiment, the sealing element includes the O-ring 8 and a support ring 13 supported on the inner ring of the O-ring. The wire diameter of the O-ring 8 is equal to the width of the annular groove 7. The two sides of the O-ring 8 do not need to be compressed. The support ring 13 can be a sealing ring rubber ring, which is slightly harder than the O-ring 8, used to support the O-ring 8 and keep the O-ring 8 as round as possible. The two sides of the support ring 13 are in close contact with the annular groove 7, sealing the annular groove 7 to achieve the sealing purpose. The oil filling gap 9 is located between the inner ring of the support ring 13 and the bottom of the annular groove 7. See the structural principle diagram. Figure 5 .

[0028] When there is no reverse hydraulic oil, the O-ring 8 remains undeformed. When there is reverse hydraulic oil, it enters the oil filling gap 9 and acts on the inner ring of the support ring frame 13. The support ring frame 13 deforms outward evenly, causing the O-ring 8 to deform outward, thus achieving an active sealing effect. Since the deformation of the O-ring 8 only occurs when there is a reverse pressure signal, the O-ring 8 participates in sealing deformation for a shorter period of time, resulting in a longer lifespan for the O-ring 8.

[0029] Example 3: This embodiment is basically the same in structure as Embodiment 1, with the main difference being that the structure of the annular groove 7 is slightly different. In this embodiment, the annular groove 7 is perpendicular to the rotation axis of the valve core 3, and the axis of the valve core oil support hole 12 is also perpendicular to the rotation axis of the valve core 3. See [link to documentation]. Figure 6 The working principle of this embodiment is exactly the same as that of Embodiment 1. The main difference is that when the hydraulic oil flows, the resistance is slightly greater when the hydraulic oil flows between the main oil hole 11 of the valve core and the branch oil hole 12 of the valve core, but it does not affect the control of the O-ring 8, which is within the protection scope of this application.

[0030] Example 4: This embodiment is an improvement on Embodiments 2 and 3. A support ring frame 13 with the same structure as in Embodiment 2 is added to the annular groove 7 in Embodiment 3. The support ring frame 13 is used in conjunction with the O-ring 8. See the structural schematic diagram. Figure 7 Its working principle is basically the same as that of Example 2, and will not be repeated here.

[0031] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A zero-leakage one-way valve, comprising a valve body, a spring, and a valve core, wherein the valve body has a valve body inlet at its front end and a valve body outlet at its side end; the valve core is assembled within the valve body and is movable in a direction away from or towards the front end of the valve body; the spring drives the valve core to move toward the front end of the valve body; the front end of the valve core has a conical head; the inner surface of the front end of the valve body has a conical surface; the conical head and the conical surface are in surface contact; the outer circumferential surface of the conical head has an annular groove; a sealing element is installed in the annular groove. Its features are: The outer ring of the seal is flush with the outer surface of the cone, and the seal is in a sealing relationship with the annular groove. The valve core has a valve core channel inside, one end of which is connected to the bottom of the annular groove, and the other end of which is connected to the valve body outlet.

2. The zero-leakage check valve as described in claim 1, characterized in that: There is an oil-filled gap between the inner ring of the seal and the bottom of the annular groove.

3. A zero-leakage check valve as described in claim 1, characterized in that: The valve core includes a cylinder with a valve core cavity and a cone. The outer circumferential surface of the cylinder is provided with a valve core oil port, which connects the valve body outlet and the valve core cavity. The cone is provided with a valve core main oil hole that communicates with the valve core cavity. The cone is also provided with a plurality of valve core branch oil holes, each of which connects the annular groove to the valve core main oil hole.

4. A zero-leakage check valve as described in claim 1, characterized in that: The annular groove is perpendicular to the conical surface of the valve core.

5. A zero-leakage check valve as described in claim 1, characterized in that: The annular groove is perpendicular to the rotation axis of the valve core.

6. A zero-leakage check valve as described in any one of claims 1 to 5, characterized in that: The sealing element is an O-ring, and the wire diameter of the O-ring is larger than the width of the annular groove to achieve a sealing installation.

7. A zero-leakage check valve as described in any one of claims 1 to 5, characterized in that: The sealing element includes an O-ring and a support ring frame supported on the inner ring of the O-ring. The wire diameter of the O-ring is equal to the width of the annular groove, and the support ring frame is sealed and installed in the annular groove.

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