High-pressure straight-through valve

Abstract

The utility model discloses a high-pressure straight-through valve which comprises a valve body and a movable valve rod arranged in the valve body, first sealing pieces are arranged between the upper portion of the movable valve rod and a lining and between the lower end of the movable valve rod and the valve body respectively, and a first balance groove and a second balance groove are annularly formed in the position, between the two first sealing pieces, of the movable valve rod. Two stress surfaces which are oppositely arranged and have the same axial projection area are formed on the upper side surface of the first balance groove and the lower side surface of the second balance groove, and the axial projection areas of the two stress surfaces are the same. After the movable valve rod is sealed, high-pressure fluid can only act on the movable valve rod through the two stress faces, it is guaranteed that the pressure borne by the movable valve rod in the two directions is the same, the self-balancing effect is achieved, it is guaranteed that the movable valve rod is not affected by the pressure of the high-pressure fluid, and adaptability to the high-pressure fluid is higher.

Description

Technical Field

[0001] The utility model relates to the technical field of fluid control, and particularly relates to a high-pressure straight-through valve. Background Art

[0002] A high-pressure straight-through valve is an automatic valve relying on electromagnetic force as the power source, that is, an electromagnetic force is generated after the electromagnetic coil of the solenoid valve is energized, and the relevant parts of the solenoid valve are driven to move to realize the opening, closing or switching functions of the valve. It is widely used in various fields such as metallurgy, petrochemical industry, pharmaceuticals, food, medical treatment, and textiles.

[0003] At present, various existing high-pressure straight-through valves are not highly adaptable to high-pressure environments, that is, high-pressure fluids exert a huge pressure on the moving valve stem. If the valve lacks a self-balancing mechanism, this pressure will cause the fluid pressures on both ends of the moving valve stem to be different, resulting in excessive force on one direction of the moving valve stem, and further making the opening and closing forces exerted by the electromagnetic coil / spring insufficient to offset, causing the valve to be unable to open and close normally. Summary of the Invention

[0004] The utility model provides a high-pressure straight-through valve, which can achieve pressure self-balancing to effectively overcome the technical problem that the moving valve stem is subjected to excessive force in one direction in the prior art, resulting in the valve being unable to open and close normally.

[0005] In order to achieve the above purpose, the technical solution of the utility model is as follows:

[0006] A high-pressure straight-through valve includes a valve body and a moving valve stem. An installation cavity penetrating through the upper and lower ends is provided in the center of the valve body, and the moving valve stem is inserted into the installation cavity. A fluid inlet and two fluid outlets communicating with the installation cavity are provided on the valve body. A bushing, an upper support sleeve, an upper inner valve seat, a middle support sleeve, a lower inner valve seat, and a lower support sleeve are sequentially sleeved on the moving valve stem in the installation cavity from top to bottom. First seals are provided between the upper part of the moving valve stem and the bushing and between the lower end of the moving valve stem and the valve body. A first balance groove and a second balance groove are circumferentially formed on the moving valve stem between the two first seals. A sealing protrusion that is hermetically fitted with the upper inner valve seat and the lower inner valve seat is formed on the moving valve stem between the first balance groove and the second balance groove. The inlet end of the fluid inlet communicates with the installation cavity at the sealing protrusion through a through hole provided in the middle support sleeve. Two opposite and axially projected area-identical stress surfaces are formed on the upper side surface of the first balance groove and the lower side surface of the second balance groove. The inlet end of one fluid outlet communicates with the first balance groove through a through hole provided in the upper support sleeve, and the inlet section of the other fluid outlet communicates with the second balance groove through a through hole provided in the lower support sleeve.

[0007] Further, a bottom sealing seat is installed at the bottom of the installation cavity, an electromagnetic coil is fixed at the top of the valve body, the upper part of the moving valve rod extends into the electromagnetic coil, a support step is formed on the upper part of the moving valve rod, a spring is sleeved on the moving valve rod above the support step, a fixed valve rod is arranged in the electromagnetic coil above the moving valve rod, the upper end of the fixed valve rod is fixed by a valve cover, both ends of the spring abut between the support step and the lower end face of the fixed valve rod, and a wire is electrically connected to the top of the electromagnetic coil.

[0008] Further, a groove adapted to the sealing protrusion is formed on the inner wall of the intermediate support sleeve.

[0009] Further, the axial cross-section of the groove is C-shaped.

[0010] Further, the opening position of the fluid inlet is adapted to the position of the sealing protrusion, and the opening positions of the two fluid outlets are respectively adapted to the positions of the first balance groove and the second balance groove.

[0011] Further, anti-rotation through pipes are installed in both the fluid inlet and the fluid outlet, and the inner ends of the anti-rotation through pipes extend into the through holes opened in the upper support sleeve, the intermediate support sleeve, and the lower support sleeve.

[0012] Further, the axial cross-sections of both the first balance groove and the second balance groove are C-shaped.

[0013] Further, second sealing members are provided between the upper inner valve seat, the lower inner valve seat and the valve body.

[0014] Further, the second sealing member is a Gleitring.

[0015] Further, the first sealing member is an O-ring.

[0016] Beneficial effects:

[0017] In the high-pressure direct-through valve of the present utility model, the upper and lower ends of the moving valve rod are sealed and slidably sleeved through the first sealing member, so that the high-pressure fluid can only apply unidirectional pressure to one end of the moving valve rod; at the same time, through two force-receiving surfaces with the same structure and axial projection area, after the moving valve rod is sealed, the high-pressure fluid can only act on the moving valve rod through the two force-receiving surfaces, ensuring that the pressures received by the moving valve rod in two directions are the same, achieving a self-balancing effect, ensuring that the moving valve rod itself will not be affected by the pressure of the high-pressure fluid, thereby avoiding the phenomenon that the switching force applied by the electromagnetic coil / spring is not enough to offset due to excessive force on one direction of the moving valve rod, resulting in the valve being unable to be normally switched, and having stronger adaptability to high-pressure fluids. Description of the Drawings

[0018] Figure 1Structural schematic diagram of the present utility model;

[0019] Figure 2 is Figure 1 A - A cross - sectional view of Specific embodiments

[0020] The present utility model will be further described below in conjunction with embodiments and drawings.

[0021] As Figure 1 and Figure 2 shown, this embodiment proposes a high - pressure straight - through valve, which includes a valve cover 1, a fixed valve rod 2, a spring 3, a moving valve rod 4, a bushing 5, a bottom seal seat 13, a valve body 14, an electromagnetic coil 19, and a wire 20. An installation cavity penetrating the upper and lower ends is provided in the center of the valve body 14. The bottom seal seat 13 is installed at the bottom of the installation cavity. On the moving valve rod 4 in the installation cavity, a bushing 5, an upper support sleeve 18, an upper inner valve seat 8, an intermediate support sleeve 9, a lower inner valve seat 11, and a lower support sleeve 15 are sequentially sleeved from top to bottom. First sealing members 6 are provided between the upper part of the moving valve rod 4 and the bushing 5 and between the lower end of the moving valve rod 4 and the valve body 14. The electromagnetic coil 19 is fixed at the top of the valve body 14. The upper part of the moving valve rod 4 extends into the electromagnetic coil 19. A support step is formed on the upper part of the moving valve rod 4. A spring 3 is sleeved on the moving valve rod 4 above the support step. A fixed valve rod 2 is provided in the electromagnetic coil 19 above the moving valve rod. The upper end of the fixed valve rod 2 is fixed by the valve cover 1. Both ends of the spring 3 abut between the support step and the lower end face of the fixed valve rod 2. A wire 20 is electrically connected to the top of the electromagnetic coil 19. A fluid inlet 16 and two fluid outlets 7 communicating with the installation cavity are provided on the valve body 14.

[0022] In this example, the outer and inner diameters of the upper support sleeve 18, the upper inner valve seat 8, the intermediate support sleeve 9, the lower inner valve seat 11, and the lower support sleeve 15 are the same, so that the entire movement process of the solenoid valve is not affected by the fluid pressure, but only affected by the electromagnetic force and the reset spring force, ensuring that the solenoid valve can be normally opened and closed under the action of the spring force and the electromagnetic force, thereby achieving high pressure or even ultra - high pressure.

[0023] Preferably, the upper support sleeve 18, the upper inner valve seat 8, the intermediate support sleeve 9, the lower inner valve seat 11, and the lower support sleeve 15 are all made of PEEK material, and the PEEK material specifications of the upper inner valve seat 8 and the lower inner valve seat 11 are higher. Therefore, in this example, the above - mentioned split - type structure is adopted, which can not only ensure the processability of the upper inner valve seat 8 and the lower inner valve seat 11, making them stress - free and wear - resistant, but also ensure the convenience of processing.

[0024] In this example, anti-rotation through pipes 17 are installed in both the fluid inlet 16 and the fluid outlet 7. The inner ends of the anti-rotation through pipes 17 extend into the through holes opened in the upper support sleeve 18, the intermediate support sleeve 9, and the lower support sleeve 15. By providing the anti-rotation through pipes 17, it is possible to prevent the upper support sleeve 18, the intermediate support sleeve 9, and the lower support sleeve 15 from rotating during the entire movement of the solenoid valve and blocking the inlet ends of the fluid inlet 16 or the fluid outlet 7, ensuring that the solenoid valve can be normally opened and closed.

[0025] In this embodiment, second seals 10 are provided between the upper inner valve seat 8, the lower inner valve seat 11, and the valve body 14. A first balance groove 4a and a second balance groove 4b are circumferentially formed on the moving valve stem 4 between the two first seals 6. A sealing protrusion 4c that is in sealing cooperation with the upper inner valve seat 8 and the lower inner valve seat 11 is formed on the moving valve stem 4 between the first balance groove 4a and the second balance groove 4b. After the moving valve stem 4 moves upward or downward, the on-off control between the fluid inlet 16 and the two fluid outlets 7 can be achieved through the sealing cooperation between the sealing protrusion 4c and the upper inner valve seat 8 and the lower inner valve seat 11. The inlet end of the fluid inlet 16 is communicated with the installation cavity at the sealing protrusion 4c through the through hole opened in the intermediate support sleeve 9. Two force-receiving surfaces s that are oppositely arranged and have the same axial projection area are formed on the upper side surface of the first balance groove 4a and the lower side surface of the second balance groove 4b. The inlet end of one of the fluid outlets 7 is communicated with the first balance groove 4a through the through hole opened in the upper support sleeve 18, and the inlet end of the other fluid outlet 7 is communicated with the second balance groove 4b through the through hole opened in the lower support sleeve 15.

[0026] Through the two force-receiving surfaces s, after the moving valve stem 4 is sealed, the high-pressure fluid can only act on the moving valve stem 4 through the two force-receiving surfaces, ensuring that the pressures received by the moving valve stem 4 in both directions are the same, achieving a self-balancing effect, and ensuring that the moving valve stem 4 itself is not affected by the pressure of the high-pressure fluid, thereby avoiding the phenomenon that the on-off force applied by the electromagnetic coil / spring is not sufficient to offset the excessive force received by the moving valve stem 4 in one direction, resulting in the valve being unable to be normally opened and closed.

[0027] From Figure 2 it can also be seen that the axial cross-sections of the first balance groove 4a and the second balance groove 4b are both C-shaped, so that the force-receiving surface s can be more conveniently formed by grooving, improving the processing convenience.

[0028] Preferably, the opening position of the fluid inlet 16 is adapted to the position of the sealing protrusion 4c, and the opening positions of the two fluid outlets 7 are respectively adapted to the positions of the first balance groove 4a and the second balance groove 4b.

[0029] See attached Figure 2, a groove adapted to the sealing projection 4c is formed inside the inner support 9, and the longitudinal section of the groove is C-shaped, so as to avoid collision with the sealing projection 4c on the moving valve stem 4 and affect the opening and closing effect of the valve.

[0030] In this embodiment, the first seal 6 is an O-ring seal; the second seal 10 is a Gleitring.

[0031] An organized gas spring area 12 is formed between the moving valve stem 4 and the bottom seal seat 13. Through such a setting, the negative impact of the gas spring effect is reduced.

[0032] Based on the above structure, the high-pressure direct-through valve described in this example can be used as a normally closed valve or an open valve. The specific principle is as follows:

[0033] When used as a normally closed valve, the fluid outlet at the upper right is blocked by a plug; if the electromagnetic coil 19 is not energized, the moving valve stem 4 relies on the downward pre-tightening force from the spring 3. In this state, the high-pressure fluid flows in from the fluid inlet 16 on the left and accumulates in the area above the moving valve stem 4, and the valve is in the closed position; if the electromagnetic coil 19 is energized, the upward force provided by the electromagnetic coil 19 overcomes the pre-tightening force of the upper spring 3, and the moving valve stem 4 is lifted, so that the high-pressure fluid enters from the left and flows out through the fluid outlet 7 at the lower right. That is, in the energized state, the valve is in the open position;

[0034] When used as an open valve, the fluid outlet 7 at the lower right is blocked by a plug; if the electromagnetic coil 19 is not energized, the moving valve stem 4 relies on the downward pre-tightening force from the spring 3. In this state, the high-pressure fluid flows in from the left fluid inlet 16 and flows out through the fluid outlet 7 at the upper right. That is, in the energized state, the valve is in the open position; if the electromagnetic coil 19 is energized, the upward force provided by the electromagnetic coil 19 overcomes the pre-tightening force of the upper spring 3, and the moving valve stem 4 is lifted, so that the high-pressure fluid enters from the left and accumulates in the area above the moving valve stem 4, and the valve is in the closed position.

[0035] In addition, when no plug is installed on the high-pressure direct-through valve described in this example, due to the self-balancing structure, the valve can still work normally. At this time, the valve will become a two-position three-way reversing valve: when the electromagnetic coil 19 is not energized, the downward pre-tightening force from the spring 3 causes the high-pressure fluid to flow in from the fluid inlet 16 on the left and flow out through the fluid outlet 7 at the upper right; when the electromagnetic coil 19 is energized, the downward pre-tightening force from the spring 3 will be overcome by the electromagnetic force, resulting in the gas entering from the fluid inlet 16 on the left and flowing out through the fluid outlet 7 at the lower right.

[0036] Beneficial effects: In the high-pressure through valve described in this embodiment, the upper and lower ends of the moving valve stem 4 are sealed and slidably fitted through the first seal 6, so that the high-pressure fluid can only exert a unidirectional pressure on one end of the moving valve stem 4. At the same time, through two force-receiving surfaces s with the same structure and axial projection area, after the moving valve stem is sealed, the high-pressure fluid can only act on the moving valve stem 4 through the two force-receiving surfaces s, ensuring that the pressures received by the moving valve stem 4 in two directions are the same, achieving a self-balancing effect. That is, regardless of the position of the moving valve stem 4, the pressures at both ends always remain balanced. The only external force affecting the moving valve stem 4 is the force exerted on the moving valve stem 4 by the spring 3 or the electromagnetic coil 17, ensuring that the moving valve stem 4 itself is not affected by the pressure of the high-pressure fluid, thereby avoiding the phenomenon that the switching force exerted by the electromagnetic coil / spring is not sufficient to offset the excessive force on one direction of the moving valve stem 4, resulting in the valve being unable to be normally opened and closed, and having stronger adaptability to high-pressure fluids.

[0037] Finally, it should be noted that the above description is only the preferred embodiment of the present invention. Under the inspiration of the present invention, those of ordinary skill in the art can make various similar representations without violating the purpose and claims of the present invention. Such transformations all fall within the protection scope of the present invention.

Claims

1. A high-pressure through-valve, comprising a valve body (14) and a movable valve stem (4), wherein a mounting cavity penetrating the upper and lower ends of the valve body (14) is provided at the center thereof, the movable valve stem (4) is inserted into the mounting cavity, and a fluid inlet (16) and two fluid outlets (7) communicating with the mounting cavity are provided on the valve body (14), characterized in that: A bushing (5), an upper support sleeve (18), an upper inner valve seat (8), an intermediate support sleeve (9), a lower inner valve seat (11), and a lower support sleeve (15) are sequentially mounted on the movable valve stem (4) in the mounting cavity from top to bottom. A first sealing member (6) is arranged between the upper portion of the movable valve stem (4) and the bushing (5) and between the lower end of the movable valve stem (4) and the valve body (14). A first balancing groove (4a) and a second balancing groove (4b) are circumferentially formed on the movable valve stem (4) between the two first sealing members (6). A balancing groove (4a) and a balancing groove (4b) are formed on the movable valve stem (4) between the first balancing groove (4a) and the second balancing groove (4b). The lower inner valve seat (11) is sealed with a sealing protrusion (4c), the inlet end of the fluid inlet (16) is connected to the installation cavity at the sealing protrusion (4c) through a through hole opened in the middle support sleeve (9), and two force-bearing surfaces (s) arranged opposite to each other and having the same axial projection area are formed on the upper side surface of the first balancing groove (4a) and the lower side surface of the second balancing groove (4b), wherein the inlet end of one fluid outlet (7) is connected to the first balancing groove (4a) through a through hole opened in the upper support sleeve (18), and the inlet section of the other fluid outlet (7) is connected to the second balancing groove (4b) through a through hole opened in the lower support sleeve (15).

2. The high-pressure through valve according to claim 1, characterized in that: A bottom sealing seat (13) is installed at the bottom of the installation cavity, an electromagnetic coil (19) is fixed on the top of the valve body (14), the upper part of the movable valve stem (4) extends into the electromagnetic coil (19), a support step is formed on the upper part of the movable valve stem (4), a spring (3) is mounted on the movable valve stem (4) above the support step, a fixed valve stem (2) is arranged in the electromagnetic coil (19) above the movable valve stem, the upper end of the fixed valve stem (2) is fixed by a valve cover (1), both ends of the spring (3) are abutted between the support step and the lower end surface of the fixed valve stem (2), and a wire (20) is electrically connected to the top of the electromagnetic coil (19).

3. The high-pressure through valve according to claim 1, characterized in that: The inner wall of the intermediate support sleeve (9) is formed with a groove adapted to the sealing protrusion (4c).

4. The high-pressure through valve according to claim 3, characterized in that: The axial cross section of the groove is C-shaped.

5. The high-pressure through valve according to claim 1, characterized in that: The opening position of the fluid inlet (16) is adapted to the position of the sealing protrusion (4c), and the opening positions of the two fluid outlets (7) are adapted to the positions of the first balancing groove (4a) and the second balancing groove (4b), respectively.

6. The high-pressure through valve according to claim 5, characterized in that: Anti-rotation through tubes (17) are installed in the fluid inlet (16) and the fluid outlet (7), and the inner ends of the anti-rotation through tubes (17) extend into the through holes formed in the upper support sleeve (18), the middle support sleeve (9), and the lower support sleeve (15).

7. The high-pressure through valve according to claim 1, characterized in that: The axial cross-sections of the first balancing groove (4a) and the second balancing groove (4b) are both C-shaped.

8. The high-pressure through valve according to claim 1, characterized in that: A second sealing member (10) is provided between the upper inner valve seat (8), the lower inner valve seat (11) and the valve body (14).

9. The high-pressure through valve according to claim 8, characterized in that: The second sealing member (10) is a Gly ring.

10. The high-pressure through valve according to any one of claims 1 to 9, characterized in that: The first sealing member (6) is an O-ring.

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