High frequency ball valve

Abstract

The application discloses a high-frequency ball valve and relates to the technical field of fluid control valves.The high-frequency ball valve comprises a valve body, a ball, a valve rod and a valve seat, the valve body comprises a middle valve body and a side valve body, the ball is installed in the middle valve body, the valve rod is in transmission connection with the ball through the middle valve body, the valve seat is installed in the side valve body and is in sealing cooperation with the ball, an ash discharging groove is arranged in the side valve body, the ash discharging groove is connected with the valve seat and is provided with a 45-degree flow guide inclined surface at an end portion, a first disc spring is arranged between the valve seat and the side valve body, an upper cover is arranged at the top of the middle valve body, a graphite packing group is arranged between the valve rod and the upper cover, a packing pressing sleeve and a packing pressing plate are arranged above the graphite packing group, a second disc spring is arranged above the packing pressing plate, the upper end face and the lower end face of the ball are both provided with a second bearing, a first bearing and a thrust washer are arranged at the lower end of the valve rod, and the flow channel of the side valve body is lined with a lining pipe.The high-frequency ball valve effectively solves the problems of valve jamming, locking and internal leakage under high-frequency opening and closing conditions, and greatly improves the service life and reliability of the valve.

Description

Technical Field

[0001] This invention relates to the field of valve technology, and specifically to a high-frequency ball valve for high-frequency switching and solid media conditions. Background Technology

[0002] In industrial systems such as polyethylene / polypropylene (PDS) plants, coal chemical plants, and pneumatic conveying systems, high-frequency shut-off valves need to complete hundreds of thousands to millions of frequent opening and closing cycles within a short period of time (e.g., switching cycles of less than 10 seconds). Simultaneously, the media often contains suspended solids such as hard dust and catalyst particles. Under these demanding conditions, existing high-frequency ball valves are highly susceptible to jamming, packing loosening and leakage, and severe bearing wear due to dust entering the sealing surface. These conditions place extremely stringent requirements on the ball valve's wear resistance, sealing reliability, and resistance to media accumulation.

[0003] In the prior art, Chinese invention patent with publication number CN109812595B discloses a high-frequency actuated programmable ball valve, which includes a side valve body, a main valve body, a valve seat assembly, a valve ball, and a valve stem. The upper end of the main valve body is connected to the stuffing box through a top cover. The valve stem is provided with bushings at the top and bottom to decompose the lateral unbalanced force. A packing seal is provided between the stuffing box and the valve stem, and a graphite ring seal is provided between the top cover and the valve stem to form a double-layer redundant sealing structure. The valve seat assembly includes a valve seat, a support ring, and a disc spring. The valve seat has an inner conical cavity at the tail end to avoid powder accumulation, and a scraping tip is provided at the front end of the valve seat to scrape off the adhering material on the surface of the ball. However, this technical solution has the following drawbacks: First, although the inner conical cavity at the tail of the valve seat can alleviate the accumulation of medium to a certain extent, solid particles can still easily accumulate in the disc spring cavity under high-frequency operation. After long-term operation, the elasticity of the disc spring will decrease, resulting in insufficient pre-tightening force of the valve seat seal and causing internal leakage. Second, the compensation of the packing seal depends on the static stress of the packing gland bolts and lacks a dynamic adaptive compensation mechanism. When the packing has gaps due to high-frequency wear, it cannot be automatically compensated in time, which can easily lead to external leakage at the valve stem. Third, the valve ball is positioned only by the limiting plate and lacks independent bearing support on the upper and lower end faces. Under high-frequency operation, the positioning accuracy and wear resistance of the ball are insufficient.

[0004] Chinese utility model patent CN213628985U discloses a high-frequency ball valve for a PDS system. It incorporates a push ring, a disc spring, and a guide ring between the valve seat and body to keep the disc spring open and prevent media accumulation and failure. A spiral groove is provided on the valve seat to prevent scale buildup in the gaps. The packing uses a wedge-shaped combination seal and is compensated for by the disc spring on the bolts. This solution improves the problems of dust accumulation in the disc spring cavity and packing compensation to some extent, but it still has the following shortcomings: the guide ring structure requires precise matching with multiple parts such as the push ring, disc spring, and valve seat notch, resulting in a complex structure, cumbersome assembly, and high processing costs; the disc spring loading at the packing pressure plate is achieved through bolt sleeve, meaning the disc spring acts on the bolts rather than directly between the packing pressure plate and the top cover, resulting in a long transmission path for the compensation force and insufficient response sensitivity and uniformity; furthermore, this solution does not provide hardening protection for the side valve body flow channel, leading to severe wear on the inner wall of the flow channel under long-term scouring by solid media, affecting the overall lifespan of the valve.

[0005] In summary, existing high-frequency ball valves generally suffer from problems such as easy dust accumulation in the disc spring cavity leading to sealing failure, delayed response or complex structure of the packing compensation mechanism, lack of effective wear-resistant protection in the flow channel, and insufficient ball support and positioning accuracy. There is an urgent need for a high-frequency ball valve with a compact structure, strong self-cleaning ability, sensitive sealing compensation response, and excellent overall wear resistance and life. Summary of the Invention

[0006] The present invention provides a high-frequency ball valve to solve at least one of the problems mentioned in the background art.

[0007] To achieve the above objectives, the present invention provides the following technical solution: A high-frequency ball valve includes a valve body, a ball, a valve stem, and a valve seat. The valve body includes a middle valve body and a side valve body. The ball is installed in the middle valve body. The valve stem passes through the middle valve body and is connected to the ball in a driving connection. The valve seat is installed in the side valve body and is sealed to the ball.

[0008] The side valve body is provided with an ash discharge groove, which is connected to the valve seat and has a 45° guide slope at its end; a first disc spring is provided between the valve seat and the side valve body; the top of the middle valve body is provided with an upper cover, and a graphite packing group is provided between the valve stem and the upper cover. A packing sleeve and a packing pressure plate are provided above the graphite packing group, and a second disc spring is provided above the packing pressure plate; a second bearing is provided on both the upper and lower end faces of the ball, and a first bearing and a thrust washer are provided at the lower end of the valve stem; the flow channel of the side valve body is lined with a liner.

[0009] Furthermore, a graphite ring is provided between the ash discharge trough and the valve seat.

[0010] Furthermore, the lower end of the valve stem has a flat rectangular structure, which engages with the ball for transmission.

[0011] Furthermore, the surface of the sphere is provided with a DLC wear-resistant coating.

[0012] Furthermore, when the nominal diameter DN of the high-frequency ball valve is ≤50mm, the axial preload of the first disc spring is 50N-80N; when the nominal diameter is 100mm≤DN≤200mm, the axial preload of the first disc spring is 120N-200N.

[0013] Furthermore, the packing pressure plate is connected to the packing pressure sleeve via a second stud and a second nut.

[0014] Furthermore, the sphere is restricted from axial movement by a fixed shaft, which is fixed to the bottom of the valve body by an internal hexagon screw.

[0015] Furthermore, the preload of the first disc spring is 50-200N.

[0016] Furthermore, the liner is made of tungsten carbide; Both the first and second bearings are ceramic bearings.

[0017] Furthermore, the ash discharge groove is arranged in a ring-shaped tangential angle on the valve seat sealing surface, and the angle between the ash discharge groove and the normal of the valve seat sealing surface is 30°-45°.

[0018] Compared with the prior art, the present invention has at least the following beneficial effects: By setting an ash discharge groove in the side valve body and a guide slope at the end of the ash discharge groove, the solid particle medium entering the gap between the valve seat and the side valve body can be smoothly discharged along the guide slope, avoiding the accumulation of particles and scale in the first disc spring cavity, thereby preventing the disc spring from losing its elasticity due to medium accumulation and ensuring that the valve seat maintains a stable sealing preload for a long time.

[0019] The combination of the ash discharge trough and the graphite ring not only achieves directional guidance and removal of accumulated ash, but also allows the valve seat to have axial micro-displacement floating capability when heated or impacted by particles due to the slight elastic deformation of the graphite ring in conjunction with the first disc spring (0.1-0.3mm floating gap). The pulsating pressure generated during high-frequency switching of the medium forms a self-flushing flow field in the ash discharge trough, which significantly reduces the wear of the sealing surface.

[0020] By directly installing a second disc spring between the packing pressure plate and the top cover, the elastic compensation force of the disc spring acts directly on the packing pressure plate. This results in a short transmission path and sensitive response. When the graphite packing assembly wears or loosens due to high-frequency operation, the second disc spring can automatically compensate for the clamping force in real time, maintaining a constant sealing pressure on the packing and effectively preventing leakage at the valve stem. Compared to the indirect loading method in CN213628985U, where the disc spring is sleeved on a bolt, the disc spring arrangement of this invention provides more direct and uniform compensation force transmission.

[0021] The second disc spring is placed directly between the packing pressure plate and the second nut. Compared with the traditional indirect compensation method that is sleeved on a long bolt, it significantly shortens the force transmission path and reduces the response time, effectively overcoming the micro-leakage problem caused by packing relaxation under high-frequency vibration.

[0022] By installing second bearings on both the upper and lower ends of the ball, and a first bearing and thrust washer at the lower end of the valve stem, a composite positioning system is formed, consisting of double-bearing positioning of the ball and bearing support of the valve stem. This effectively improves the positioning accuracy and coaxiality of the ball under high-frequency operation, reduces operating torque, and minimizes uneven wear between the ball and the valve seat. The ceramic bearings possess excellent self-lubricating and wear-resistant properties, further extending the valve's service life.

[0023] By lining the flow channel of the side valve body with a tungsten carbide liner, the inner wall of the flow channel is hardened and protected, effectively resisting the high-speed scouring of solid media, solving the problem of severe wear of the inner wall of the flow channel in the prior art, and significantly extending the service life of the valve body.

[0024] The surface of the ball is coated with a DLC (diamond-like carbon) wear-resistant coating, which has extremely high surface hardness and extremely low coefficient of friction. This significantly improves the wear resistance and anti-metal adhesion between the ball and the valve seat sealing surface, meeting the requirements of high-frequency switching conditions of hundreds of thousands of cycles per year.

[0025] A graphite ring is installed between the ash discharge trough and the valve seat, which has both sealing and wear-resistant functions, preventing the medium from leaking from the side of the ash discharge trough to the back of the valve seat. At the same time, the self-lubricating properties of graphite reduce the frictional resistance when the valve seat floats.

[0026] The lower end of the valve stem adopts a flat square structure that engages with the ball for transmission. Compared with the cylindrical pin connection method, the flat square structure has a larger contact area and higher impact resistance, which can effectively avoid connection fatigue deformation under high-frequency operation and ensure stable and reliable transmission torque.

[0027] The graphite packing assembly adopts a redundant design with two sets of packing, upper and lower. When the lower packing has gaps due to wear, the upper packing can still maintain an effective seal under the compensation of the second disc spring, which greatly extends the packing replacement cycle and improves the reliability and maintenance economy of the valve. Attached Figure Description

[0028] Figure 1 This is a schematic diagram of the structure of the high-frequency ball valve of the present invention; Figure 2 This is an enlarged schematic diagram of the valve seat structure of the high-frequency ball valve of the present invention; Figure 3 This is an enlarged schematic diagram of the connection between the ball and the valve stem of the high-frequency ball valve of the present invention.

[0029] In the diagram: 1. Middle valve body; 2. Side valve body; 3. Ball; 4. Valve seat; 5. First disc spring; 6. Ash discharge trough; 7. Graphite ring; 8. Valve stem; 9. Fixed shaft; 10. Top cover; 11. First stud; 12. First nut; 13. Hex socket head cap screw; 14. First bearing; 15. Graphite packing assembly; 16. Packing sleeve; 17. Packing pressure plate; 18. Second stud; 19. Second nut; 20. Second disc spring; 21. Third stud; 22. Third nut; 23. Liner; 24. Thrust washer; 25. Second bearing. Detailed Implementation

[0030] In this invention, the terms "first," "second," etc., are used for descriptive purposes only and do not specifically refer to any order or sequence, nor are they intended to limit the invention. They are merely used to distinguish components or operations described using the same technical terms and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Furthermore, the technical solutions and features of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0031] Example 1: As Figure 1 As shown, this embodiment provides a high-frequency ball valve, including a valve body, a ball 3, a valve stem 8, and a valve seat 4. The valve body adopts a split structure, consisting of a central valve body 1 and two side valve bodies 2. The two sides of the central valve body 1 are fixedly connected to the side valve bodies 2 by a third stud 21 and a third nut 22, respectively. The ball 3 is installed in the inner cavity of the central valve body 1. The upper and lower end faces of the ball 3 are provided with second bearings 25, preferably ceramic bearings, which provide double bearing positioning support for the ball 3, ensuring the coaxiality and stability of the ball 3 during high-frequency rotation and reducing rotational friction resistance.

[0032] The outer circumferential surface of the valve seat 4 and the inner wall of the side valve body 2 are fitted with a clearance, with a 0.1mm-0.3mm axial floating clearance. Within this clearance range, the valve seat 4 can produce a slight axial displacement under external force. The ash discharge groove is opened on the end face of the side valve body 2, and its groove opening is in fluid communication with the back space of the valve seat 4, and a 45° guide slope is provided at the groove opening.

[0033] During high-frequency operation, the valve seat 4 floats axially within the aforementioned micro-gap due to the combined effect of the elastic restoring force of the first disc spring and the medium pressure. The medium enters the mating gap between the valve seat 4 and the side valve body 2 through the floating gap, forming a micro self-flushing flow field. This flow field can flush away solid particles accumulated around the sealing surface and carry them into the ash discharge trough, where they are guided to the main channel for discharge via a 45° guide slope. Thus, the floating action achieves real-time automatic cleaning of the mating gap.

[0034] The valve body 1 is machined from a forging, and the valve cavity inside the valve body is polished to reduce the resistance to medium flow and improve the sealing performance and service life of the valve.

[0035] The valve stem 8 extends into the inner cavity of the middle valve body 1 through the mounting hole at the top of the middle valve body 1. The lower end of the valve stem 8 has a flat rectangular structure, which engages with the corresponding flat rectangular groove on the upper end of the ball 3 for transmission connection. Compared with the traditional cylindrical pin connection method, the flat rectangular structure has a larger torque transmission area and higher impact fatigue strength, and can withstand repeated impact loads under high-frequency switching action, ensuring transmission accuracy and reliability. The lower end of the valve stem 8 is also provided with a first bearing 14 and a thrust washer 24. The first bearing 14 is preferably a ceramic bearing, and the thrust washer 24 bears the axial thrust of the valve stem 8. The first bearing 14 and the thrust washer 24 cooperate to form a double support and positioning for the lower end of the valve stem, effectively reducing the operating torque and preventing valve stem wear.

[0036] The bottom of the ball 3 is axially limited by the fixed shaft 9, which is fixed to the bottom of the valve body 1 by the internal hexagon screw 13, thus limiting the axial movement of the ball 3 under the action of medium pressure and ensuring the sealing fit accuracy between the ball 3 and the valve seat 4.

[0037] The valve seat 4 is installed in the inner cavity of the side valve body 2, and the front sealing surface of the valve seat 4 is in sealing fit with the spherical surface of the ball 3. A first disc spring 5 is provided between the valve seat 4 and the side valve body 2. The preload of the first disc spring 5 is set to 50-200N, providing the valve seat 4 with an elastic preload in the direction of the ball 3, so that the valve seat 4 maintains a reliable seal with the ball 3 under the conditions of medium pressure fluctuation and temperature change. At the same time, the elasticity of the first disc spring 5 gives the valve seat 4 a certain floating ability. During the valve opening and closing process, a small gap change can be formed between the valve seat 4 and the ball 3, generating a self-flushing effect and flushing out solid particles on the sealing surface.

[0038] like Figure 2As shown, a ash discharge groove 6 is provided inside the side valve body 2. The ash discharge groove 6 is located behind the valve seat 4 (on the side away from the ball 3). The ash discharge groove 6 is connected to the valve seat 4, and its end (on the side near the flow channel) is provided with a 45° guide slope. When a medium containing solid particles enters the gap between the valve seat 4 and the side valve body 2, the particles slide into the ash discharge groove 6 along the 45° guide slope under the action of gravity and fluid, and are discharged with the flow of the medium. This effectively prevents the particles from accumulating and scaling in the mounting cavity of the first disc spring 5, and avoids the disc spring from losing elasticity or becoming stuck due to the accumulation of medium. A graphite ring 7 is also provided between the ash discharge groove 6 and the valve seat 4. The graphite ring 7 plays a dual role of sealing and wear resistance. On the one hand, it prevents the medium from leaking from the side of the ash discharge groove 6 to the back of the valve seat 4. On the other hand, the self-lubricating properties of graphite reduce the frictional resistance when the valve seat 4 floats.

[0039] The flow channel of the side valve body 2 is lined with a liner 23, which is preferably made of tungsten carbide. Tungsten carbide has extremely high hardness (HV 1100-1300) and excellent resistance to abrasive wear, which can effectively resist the high-speed erosion of the inner wall of the flow channel of the side valve body by solid media, significantly extending the service life of the valve body. The liner 23 can be fixed to the inner wall of the flow channel of the side valve body 2 by heat fitting or bonding.

[0040] The surface of the ball 3 is coated with a DLC (diamond-like carbon) wear-resistant coating. The DLC coating has extremely high surface hardness (HV 2000-5000) and extremely low coefficient of friction (0.05-0.1), which can significantly improve the wear resistance between the sealing surfaces of the ball 3 and the valve seat 4, prevent metal adhesion under high-frequency friction, and extend the service life of the sealing pair.

[0041] The axial floating clearance between the valve seat and the valve body is set to 0.1mm-0.3mm; the upper and lower ceramic bearings are made of silicon nitride or zirconium oxide ceramic, and their radial clearance with the valve stem is 0.02mm-0.05mm; the hard alloy coating (such as tungsten carbide or DLC) sprayed on the sealing surface of the valve seat and the ball has a thickness of 0.03mm-0.05mm and a surface roughness Ra≤0.2μm.

[0042] like Figure 1 and Figure 3As shown, the top of the middle valve body 1 is fixedly connected to the top of the upper cover 10 by the first stud 11 and the first nut 12, and the upper cover 10 closes the packing installation cavity at the top of the middle valve body 1. A graphite packing assembly 15 is provided between the valve stem 8 and the upper cover 10. The graphite packing assembly 15 is wound around the outer circumference of the valve stem 8 to achieve a seal between the valve stem 8 and the upper cover 10. The graphite packing assembly 15 includes two sets of packing, forming a redundant sealing design: the lower packing (closer to the inner cavity of the middle valve body 1) serves as the main seal, and the upper packing (closer to the outer side) serves as the auxiliary seal. When the lower packing wears due to long-term high-frequency operation, the upper packing can still maintain an effective seal, greatly extending the packing replacement cycle.

[0043] A packing sleeve 16 is provided above the graphite packing assembly 15. The packing sleeve 16 is fitted onto the valve stem 8 and presses the graphite packing assembly 15 tightly. A packing pressure plate 17 is provided above the packing sleeve 16. The packing pressure plate 17 is connected and fixed to the packing sleeve 16 by a second stud 18 and a second nut 19. A second disc spring 20 is provided between the packing pressure plate 17 and the second nut 19. The second disc spring 20 acts directly on the surface of the packing pressure plate 17. When the graphite packing assembly 15 wears due to high-frequency operation or loosens due to high temperature, the second disc spring 20 can release elastic potential energy in real time, pushing the packing pressure plate 17 to move downward. The compensating force is transmitted to the graphite packing assembly 15 through the packing sleeve 16, automatically compensating for the packing volume loss, maintaining a constant sealing pressure, and realizing dynamic adaptive sealing compensation.

[0044] Working process: When the valve is opened, the external drive device (such as a pneumatic actuator) drives the valve stem 8 to rotate. The valve stem 8 engages with the ball 3 through the lower flat square structure, driving the ball 3 to rotate 90° around its vertical axis. The flow channel of the ball 3 is aligned with the flow channel of the side valve body 2. The medium flows out from the inlet side valve body 2 through the liner 23, the flow channel of the ball 3, and the outlet side liner 23. During the instantaneous process of opening and closing, the first disc spring 5 provides elastic preload to the valve seat 4, so that the valve seat 4 always fits against the surface of the ball 3. The small floating gap between the valve seat 4 and the ball 3 produces a self-flushing effect, flushing the particles on the sealing surface to the ash discharge groove 6. The particles are discharged along the 45° guide slope, avoiding accumulation in the cavity of the first disc spring 5.

[0045] When the valve is closed, the valve stem 8 drives the ball 3 to rotate 90° back to the closed position. The spherical surface of the ball 3 blocks the flow path, and the valve seat 4, under the preload of the first disc spring 5, fits tightly against the ball 3 to achieve a seal. During long-term high-frequency operation, the second disc spring 20 automatically and passively compensates for the wear of the graphite packing assembly 15, maintaining a reliable seal at the valve stem 8.

[0046] Example 2: This example is basically the same as Example 1 in structure and working principle, the difference being: The material of the liner 23 is replaced by silicon carbide ceramic instead of tungsten carbide. Silicon carbide ceramic also has extremely high hardness (HV2200-2800) and excellent wear resistance, and its corrosion resistance is better than that of tungsten carbide, making it suitable for use in highly corrosive solid media conditions. The liner 23 can be fixed to the inner wall of the flow channel of the side valve body 2 by mechanical press-fitting or high-temperature bonding.

[0047] The first bearing 14 and the second bearing 25 are replaced with cemented carbide bearings (such as tungsten carbide-based cemented carbide bearings) to reduce manufacturing costs while meeting wear resistance requirements, making them suitable for cost-sensitive applications.

[0048] The DLC wear-resistant coating on the surface of sphere 3 can be replaced with a physical vapor deposition (PVD) chromium nitride (CrN) coating or a titanium nitride (TiN) coating, which also have good wear resistance and friction reduction properties, and the process is mature and the cost is low.

[0049] The preload of the first disc spring needs to be set according to the nominal diameter DN of the valve and the medium pressure: For valves with DN50 (inclusive) and below, the preload of the first disc spring should be adjusted to 50N-80N to avoid excessive opening and closing torque while ensuring sealing; For valves with DN100-DN200, the preload of the first disc spring should be adjusted to 120N-200N to counteract the axial thrust of the high-pressure medium on the ball.

[0050] The upper and lower packing groups in the graphite packing group 15 are each composed of alternating layers of pure graphite rings and stainless steel spiral wound graphite rings to balance sealing flexibility and compressive strength.

[0051] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A high-frequency ball valve, comprising a valve body, a ball, a valve stem, and a valve seat, wherein the valve body comprises a central valve body and a side valve body, the ball is installed in the central valve body, the valve stem passes through the central valve body and is drively connected to the ball, and the valve seat is installed in the side valve body and is sealingly fitted with the ball, characterized in that: The side valve body is provided with an ash discharge groove, which is connected to the valve seat and has a 45° guide slope at its end; A first disc spring is provided between the valve seat and the side valve body; The valve body is provided with a top cover, and a graphite packing group is provided between the valve stem and the top cover. A packing sleeve and a packing pressure plate are provided above the graphite packing group, and a second disc spring is provided above the packing pressure plate. The upper and lower surfaces of the ball are each provided with a second bearing, and the lower end of the valve stem is provided with a first bearing and a thrust washer. The flow channel of the side valve body is lined with a liner.

2. A high-frequency ball valve according to claim 1, characterized in that: A graphite ring is provided between the ash discharge trough and the valve seat.

3. A high-frequency ball valve according to claim 1, characterized in that: The lower end of the valve stem has a flat rectangular structure, which engages with the ball for transmission.

4. A high-frequency ball valve according to claim 1, characterized in that: The surface of the sphere is coated with a DLC wear-resistant coating.

5. A high-frequency ball valve according to claim 1, characterized in that: When the nominal diameter DN of the high-frequency ball valve is ≤50mm, the axial preload of the first disc spring is 50N-80N; when the nominal diameter is 100mm≤DN≤200mm, the axial preload of the first disc spring is 120N-200N.

6. A high-frequency ball valve according to claim 1, characterized in that: The packing pressure plate is connected to the packing pressure sleeve via a second stud and a second nut.

7. A high-frequency ball valve according to claim 1, characterized in that: The ball is restricted from axial movement by a fixed shaft, which is fixed to the bottom of the valve body by an internal hexagon screw.

8. A high-frequency ball valve according to claim 1, characterized in that: The preload of the first disc spring is 50-200N.

9. A high-frequency ball valve according to claim 1, characterized in that: The liner is made of tungsten carbide. Both the first and second bearings are ceramic bearings.

10. A high-frequency ball valve according to claim 1, characterized in that: The ash discharge groove is arranged in a ring-shaped tangential angle on the valve seat sealing surface, and the angle between the ash discharge groove and the normal of the valve seat sealing surface is 30°-45°.

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