Hard sealing ball valve for high-pressure hydrogen and slurry

Abstract

The utility model discloses a hard sealing ball valve for high-pressure hydrogen and slurry, and relates to the field of ball valves. In high-pressure hydrogen and slurry-containing working conditions, in an existing high-pressure ball valve, soft sealing is prone to being corroded and abraded to cause sealing failure, hard sealing has the problems of large structure and operation torque, sealing and the like, hydrogen is prone to leaking, and a reliable hard sealing ball valve adapting to the working conditions is needed urgently. The ball valve comprises a left valve body, a right valve body, a left valve seat, a right valve seat, a valve cover, a valve rod, a ball body, a packing sealing assembly, a supporting frame and a pneumatic actuator, sealing faces between the left valve seat and the ball body and between the right valve seat and the ball body are rigidly sealed through hard alloy, and the left valve seat is pushed through a belleville spring sealing assembly to achieve dynamic sealing. And three sliding bearings are arranged between the valve rod and the left valve body as well as between the valve rod and the lower end and the upper part of the valve cover. The abrasion resistance and the corrosion resistance are remarkably improved, meanwhile, thermal deformation and abrasion can be effectively compensated, long-term sealing reliability is ensured, and the problem that a traditional hard ball valve is large in torque is solved.

Description

Technical Field

[0001] This utility model relates to the field of ball valves, and more particularly to a hard-seal ball valve for high-pressure hydrogen and slurry applications. Background Technology

[0002] In industries such as petrochemicals, high-pressure hydrogen-containing and slurry-containing media are extremely common. Under these conditions, valves, as key components controlling fluid flow, directly affect the safe and stable operation of the entire system. Currently, ball valves for high-pressure applications are mainly divided into two types: soft-seal and hard-seal.

[0003] While soft-seal valves offer good sealing performance, they are susceptible to corrosion or wear in high-temperature, highly corrosive, or particulate-containing slurry media, leading to seal failure. Hard-seal ball valves, although capable of withstanding higher temperatures and pressures, often suffer from issues such as non-compact structure, high operating torque, complex sealing systems, and difficult manufacturing and assembly. They are particularly prone to leakage under high-pressure hydrogen conditions, impacting safety and stability. Therefore, there is an urgent need for a hard-seal ball valve that is compact, easy to operate, has reliable sealing performance, and can adapt to high-pressure hydrogen and slurry conditions. Utility Model Content

[0004] The technical problem to be solved and the technical task proposed by this utility model is to improve and refine the existing technical solutions, and to provide a hard-seal ball valve for high-pressure hydrogen and slurry applications, with the aim of improving the sealing reliability and operational flexibility of the ball valve. To this end, this utility model adopts the following technical solution.

[0005] A high-pressure hard-seal ball valve for hydrogen and slurry applications includes a left valve body with an inlet flow channel, a right valve body with an outlet flow channel, a valve cover with a vertical through hole, a valve stem, a ball with a horizontal through flow channel hole, a support frame, and a pneumatic actuator. The right valve body is connected and fixed to the right side of the left valve body. The valve cover is connected and fixed to the upper end of the left valve body. The support frame is located on the upper end of the valve cover. The pneumatic actuator is located on top of the support frame and is connected to the upper end of the valve stem via a connecting short shaft. The valve stem passes downward through the support frame and the valve cover, and its lower end passes through the left valve body and is connected and fixed to the ball inside the left valve body. A packing seal assembly is provided between the upper end of the valve cover and the valve stem. A left valve seat is located at the right end of the inlet flow channel, and a right valve seat is located at the left end of the outlet flow channel. By rotating the ball, the left valve seat and the right valve seat... A flow channel blocking and opening adjustment structure is formed between the valve seat and the ball. The right valve seat is fixed to the left end of the right valve body. The left valve seat and the left valve step hole provided at the right end of the inlet flow channel have a left-right sliding mating structure. A disc spring sealing assembly is provided on the left side of the left valve seat. The disc spring sealing assembly pushes the sealing surface between the left valve seat and the ball to the right to seal. The sealing surfaces between the right valve seat and the ball, and between the left valve seat and the ball, are all made of hard alloy sealing surfaces. A first sliding bearing is provided between the valve stem and the through hole at the top of the valve body. A second sliding bearing is provided between the lower end of the valve cover and the valve stem. A third sliding bearing is provided on the valve cover below the packing sealing assembly. The valve stem passes through the center hole of the third sliding bearing, the second sliding bearing, and the first sliding bearing. Sealing packing is provided between the upper part of the valve body and the valve stem.

[0006] Dynamic sealing is achieved by using a rigid sealing surface of hard alloy combined with a disc spring sealing assembly to push the left valve seat. This significantly improves wear resistance and corrosion resistance while effectively compensating for thermal deformation and wear, ensuring long-term sealing reliability. By setting three-stage sliding bearings at the valve stem, the friction and torque generated by the valve stem control ball can be greatly reduced, solving the problem of high torque in traditional hard ball valves. This greatly improves the flexibility and durability of ball valve operation, reduces the energy consumption of the drive device, and is suitable for slurry media containing particles and highly corrosive environments, extending its service life in high-temperature and highly corrosive slurry media.

[0007] As a preferred technical approach: the left side of the right valve body is embedded in the right side of the inner cavity of the left valve body. The inner side of the right end face of the left valve body is provided with a sealing ring groove, and a metal spiral wound washer is placed within the sealing ring groove. The right valve body is provided with an annular pressure strip that matches the sealing ring groove. The annular pressure strip extends into the sealing ring groove and presses the metal spiral wound washer to the left. The right and left valve bodies are fastened together by a circumferentially distributed fully threaded stud nut assembly. The combined sealing structure of the metal spiral wound washer and the annular pressure strip embedded and pressed between the left and right valve bodies enhances the sealing reliability under high pressure and effectively prevents leakage. The modular structure of the right valve body embedded in the left valve body and fastened by the fully threaded stud nut assembly facilitates assembly and maintenance while ensuring connection strength and sealing performance.

[0008] As a preferred technical approach, the left and right valve bodies are connected by a hard-seal welding. This hard-seal welding further strengthens the connection and sealing performance, eliminating the leakage risk that may exist with flange connections, and is particularly suitable for high-pressure hydrogen-containing environments.

[0009] As a preferred technical approach: the right valve seat is embedded in the right valve step hole at the left end of the right valve body. The left end of the right valve seat is provided with an annular pressure step, and a pressure ring is provided on the annular pressure step. The right valve seat is fastened to the right valve body by the pressure ring and screws. Fastening the right valve seat to the right valve body by the pressure ring and screws ensures accurate valve seat positioning, prevents loosening caused by media erosion, and extends service life.

[0010] As a preferred technical means: the disc spring sealing assembly includes a graphite sealing ring, a spring seat, and a disc spring assembly. The spring seat includes an inner ring portion located on the left inner side, a flat ring portion located on the right side of the inner ring portion, and an outer ring portion located on the right outer side of the flat ring portion. The graphite sealing ring is located on the right side of the outer ring portion. The inner circumference of the outer ring portion and the inner circumference of the graphite sealing ring abut against the left outer circumference of the left valve seat. The right side of the graphite sealing ring abuts against the inclined step of the outer circumference of the left valve seat. The outer circumference of the outer ring portion and the outer circumference of the graphite sealing ring abut against the hole wall of the left valve step hole. The disc spring assembly is sleeved on the outer circumference of the inner ring portion. The left side of the disc spring assembly abuts against the stepped surface of the left valve step hole. The right side of the disc spring assembly abuts against the left side surface of the flat ring portion. The left valve body has a radially open sealing groove on the left inner wall of the stepped surface of the left valve step hole, and a graphite semi-open ring sealing ring is provided inside. The inner circumference of the graphite semi-open ring sealing ring abuts against the outer circumference of the inner ring portion. The combination of disc spring assembly and graphite sealing ring forms a multi-stage seal. The disc spring assembly provides continuous elastic force, and the graphite sealing ring achieves radial and axial dual sealing, effectively resisting high-pressure media. The graphite semi-open ring sealing ring is easy to install.

[0011] As a preferred technical means: the lower end of the valve stem is provided with a square connector, which is embedded into a matching connecting groove on the upper end of the ball. A hard alloy layer is welded to the inner circumference of the connecting groove. The hard alloy layer welded to the square connector of the valve stem and the connecting groove of the ball improves the hardness and wear resistance of the contact surface, avoiding wear and loosening caused by frequent operation.

[0012] As a preferred technical means: a stepped shaft portion is provided on the valve stem above the square connector; the sealing packing is disposed on the step of the stepped shaft portion; the first sliding bearing is disposed on top of the sealing packing; and the outer peripheral wall of the first sliding bearing is interference-fitted with the left valve body. The sealing packing disposed on the stepped shaft portion effectively prevents the medium from leaking upwards along the valve stem.

[0013] As a preferred technical means: the valve body has an annular stepped hole at the upper end of the first sliding bearing, and a thrust washer is provided on the stepped surface of the annular stepped hole. The lower end of the valve cover has a downwardly protruding extension, the outer periphery of which matches the wall of the annular stepped hole. The lower inner side of the valve cover has a bearing groove, and the second sliding bearing is interference-fitted into the bearing groove. The lower end of the second sliding bearing abuts against the upper end of the thrust washer. The thrust washer, located at the lower end of the second sliding bearing, effectively provides axial support, withstands the axial force during valve operation, reduces friction between the valve stem and the valve body, and improves operational stability.

[0014] As a preferred technical approach: the lower end of the valve cover has an annular groove on the outer side of the extended portion, with a metal spiral wound gasket inside; the upper end face of the left valve body has an annular protrusion that matches the annular groove, and the annular protrusion presses the metal spiral wound gasket upward. The annular groove and the annular protrusion, in conjunction with the metal spiral wound gasket, effectively enhance the sealing performance between the valve cover and the valve body.

[0015] As a preferred technical means: the packing sealing assembly is disposed in the stuffing groove on the inner circumference of the upper end of the valve cover, and consists of a graphite packing group, a packing gland, and a packing pressure plate from bottom to top. The packing pressure plate and the upper valve cover plate disposed on the upper end of the valve cover are fastened by fully threaded studs and nuts. A disc spring washer group is provided below the nut. The disc spring washer group provides constant clamping force, automatically compensates for packing wear, avoids overpressure or loosening problems caused by traditional bolt tightening, and extends the service life of the packing.

[0016] Beneficial effects: The rigid sealing surface of the hard alloy combined with the disc spring sealing assembly pushes the left valve seat to achieve dynamic sealing, which significantly improves wear resistance and corrosion resistance while effectively compensating for thermal deformation and wear, ensuring long-term sealing reliability. By setting three-stage sliding bearings at the valve stem, the friction and torque generated by the valve stem control ball can be greatly reduced, solving the problem of high torque in traditional hard ball valves. This greatly improves the flexibility and durability of ball valve operation, reduces the energy consumption of the drive device, and is suitable for slurry media containing particles and highly corrosive environments, extending the service life in high-temperature and highly corrosive slurry media. The packing seal assembly provides constant clamping force through the disc spring gasket group, automatically compensating for packing wear, avoiding overpressure or loosening problems caused by traditional bolt tightening, and extending the service life of the packing. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of this utility model.

[0018] Figure 2 This is a top view of the present invention.

[0019] Figure 3 This is a utility model Figure 2 Schematic diagram of sectional view AA.

[0020] Figure 4 This is a utility model Figure 3 Enlarged schematic diagram of section B in the middle.

[0021] Figure 5 This is a utility model Figure 3 Enlarged schematic diagram of section C.

[0022] Figure 6 This is a utility model Figure 5 A cross-sectional schematic diagram of the middle spring seat.

[0023] Figure 7 This is a utility model Figure 3 Enlarged schematic diagram of section D in the middle.

[0024] In the diagram: 1. Left valve body; 2. Right valve body; 3. Valve cover; 4. Valve stem; 5. Ball; 6. Support frame; 7. Pneumatic actuator; 8. Connecting short shaft; 9. Packing seal assembly; 10. Left valve seat; 11. Right valve seat; 12. Disc spring seal assembly; 13. First sliding bearing; 14. Second sliding bearing; 15. Third sliding bearing; 16. Sealing packing; 17. Metal spiral wound gasket; 18. Pressure ring; 19. Graphite semi-open ring seal; 20. Thrust gasket; 21. Valve cover upper plate; 22. Disc spring gasket assembly; 101. Inlet flow channel; 102. Left valve. Stepped hole; 103, annular protrusion; 201, outlet flow channel; 202, annular pressure strip; 301, extension part; 401, square connector; 402, stepped shaft part; 601, lower plate of bracket; 602, bracket support plate; 603, side plate of bracket; 604, upper plate of bracket; 901, graphite packing assembly; 902, packing gland; 903, packing pressure plate; 1001, inclined step; 1201, graphite sealing ring; 1202, spring seat; 120201, inner ring part; 120202, flat ring part; 120203, outer ring part; 1203, disc spring assembly. Detailed Implementation

[0025] The technical solution of this utility model will be further described in detail below with reference to the accompanying drawings.

[0026] Example 1

[0027] like Figures 1-3 and Figure 7As shown, a high-pressure hard-seal ball valve for hydrogen and slurry applications includes a left valve body 1 with an inlet flow channel 101, a right valve body 2 with an outlet flow channel 201, a valve cover 3 with a vertical through hole, a valve stem 4, a ball 5 with a horizontal through flow channel hole, a support frame 6, and a pneumatic actuator 7. The right valve body 2 is connected and fixed to the right side of the left valve body 1, the valve cover 3 is connected and fixed to the upper end of the left valve body 1, the support frame 6 is located at the upper end of the valve cover 3, and the pneumatic actuator 7 is located on top of the support frame 6. The valve stem 4 is connected to the upper end of the short shaft 8. After the valve stem 4 passes downward through the support frame 6 and the valve cover 3, its lower end passes through the left valve body 1 and is fixedly connected to the ball 5 in the inner cavity of the left valve body 1. A packing seal assembly 9 is provided between the upper end of the valve cover 3 and the valve stem 4. The packing seal assembly 9 is set in the stuffing groove on the inner circumference of the upper end of the valve cover 3. From bottom to top, it consists of a graphite packing group 901, a packing gland 902, and a packing pressure plate 903. A left valve seat 10 is provided at the right end of the inlet flow channel 101, and the outlet flow channel 201... A right valve seat 11 is provided at the left end. By rotating the ball 5, an adjustment structure for flow channel blocking and opening is formed between the left valve seat 10 and the right valve seat 11 and the ball 5. The right valve seat 11 is fixed to the left end of the right valve body 2. The left valve seat 10 and the left valve step hole 102 provided at the right end of the inlet flow channel 101 have a left-right sliding mating structure. A disc spring sealing assembly 12 is provided on the left side of the left valve seat 10. The disc spring sealing assembly 12 pushes the sealing surface between the left valve seat 10 and the ball 5 to the right to seal. The sealing surfaces between valve stem 1 and ball 5, and between left valve seat 10 and ball 5, are all made of hard alloy. A first sliding bearing 13 is provided between valve stem 4 and the through hole at the top of valve body. A second sliding bearing 14 is provided between the lower end of valve cover 3 and valve stem 4. A third sliding bearing 15 is provided on valve cover 3 below packing seal assembly 9. Valve stem 4 passes through the center hole of the third sliding bearing 15, the second sliding bearing 14 and the first sliding bearing 13. Sealing packing 16 is provided between the upper part of valve body and valve stem 4.

[0028] To enhance sealing reliability under high pressure, such as Figure 4 As shown, the left side of the right valve body 2 is embedded in the right side of the inner cavity of the left valve body 1. A sealing ring groove is provided on the inner side of the right end face of the left valve body 1, and a metal spiral wound washer 17 is placed inside the sealing ring groove. An annular pressure strip 202, matching the sealing ring groove, extends into the sealing ring groove and presses the metal spiral wound washer 17 to the left. The right valve body 2 and the left valve body 1 are fastened together by a circumferentially distributed fully threaded stud nut assembly. The combined sealing structure of the metal spiral wound washer 17 and the annular pressure strip 202, used between the left and right valve bodies 2, enhances the sealing reliability under high pressure and effectively prevents leakage. The modular structure of the right valve body 2 embedded in the left valve body 1 and fastened by the fully threaded stud nut assembly facilitates assembly and maintenance while ensuring connection strength and sealing performance.

[0029] To achieve the fixation of the right valve seat 11, such as Figure 3 As shown, the right valve seat 11 is fitted into the right valve step hole at the left end of the right valve body 2. The left end of the right valve seat 11 is provided with an annular pressure step, and a pressure ring 18 is provided on the annular pressure step. The right valve seat 11 is fastened to the right valve body 2 by the pressure ring 18 and screws. The right valve seat 11 is fastened to the right valve body 2 by the pressure ring 18 and screws to ensure the positioning and firm fixation of the valve seat, prevent the medium from eroding and causing loosening, and extend the service life.

[0030] To achieve a flexible push and sealing combination structure, such as Figure 5 , 6 As shown, the disc spring sealing assembly 12 includes a graphite sealing ring 1201, a spring seat 1202, and a disc spring assembly 1203. The spring seat 1202 includes an inner ring portion 120201 located on the left inner side, a flat ring portion 120202 located to the right of the inner ring portion 120201, and an outer ring portion 120203 located to the right outer side of the flat ring portion 120202. The graphite sealing ring 1201 is located on the right side of the outer ring portion 120203. The inner circumference of the outer ring portion 120203 and the inner circumference of the graphite sealing ring 1201 abut against the left outer circumference of the left valve seat 10. The right side of the graphite sealing ring 1201 abuts against the inclined step 1001 of the outer circumference of the left valve seat 10. The outer ring portion 120203... The outer periphery of 203 and the outer periphery of graphite sealing ring 1201 abut against the hole wall of left valve step hole 102. Disc spring assembly 1203 is sleeved on the outer periphery of inner ring portion 120201. The left side of disc spring assembly 1203 abuts against the stepped surface of left valve step hole 102, and the right side of disc spring assembly 1203 abuts against the left side surface of flat ring portion 120202. In this embodiment, disc spring assembly 1203 is composed of three disc springs stacked left and right. A radially open sealing groove is provided on the left inner wall of the stepped surface of left valve step hole 102 on the left valve body 1. A graphite semi-open ring sealing ring 19 is provided inside. The inner periphery of graphite semi-open ring sealing ring 19 abuts against the outer periphery of inner ring portion 120201. The combination of the disc spring assembly and the graphite sealing ring 1201 forms a multi-stage seal. The disc spring assembly 1203 provides continuous elastic force, and the graphite sealing ring achieves radial and axial dual sealing, effectively resisting high-pressure media. The graphite semi-open ring sealing ring 19 is easy to embed into the radially slotted sealing groove, making installation convenient.

[0031] To prevent wear and loosening of the connection, such as Figure 3 As shown, the lower end of the valve stem 4 is provided with a square connector 401, which is embedded into the connecting groove at the upper end of the ball 5. The inner circumference of the connecting groove is overlaid with a hard alloy layer. The hard alloy layer overlaid on the square connector 401 of the valve stem 4 and the connecting groove of the ball 5 improves the hardness and wear resistance of the contact surface, and avoids wear and loosening caused by frequent operation.

[0032] To prevent the medium from leaking upwards along valve stem 4, such as Figure 7As shown, a stepped shaft portion 402 is provided on the valve stem 4 above the square connector 401. A sealing packing 16 is disposed on the step of the stepped shaft portion 402, and a first sliding bearing 13 is disposed above the sealing packing 16. The outer peripheral wall of the first sliding bearing 13 is interference-fitted with the left valve body 1. The sealing packing 16, disposed on the stepped shaft portion 402, effectively prevents the medium from leaking upwards along the valve stem 4.

[0033] like Figure 7 As shown, to provide axial support for the second sliding bearing 14, an annular stepped hole is provided on the valve body above the first sliding bearing 13. A thrust washer 20 is provided on the stepped surface of the annular stepped hole. The lower end of the valve cover 3 has a downwardly protruding extension 301, the outer periphery of which matches the hole wall of the annular stepped hole. A bearing groove is provided on the inner side of the lower end of the valve cover 3. The second sliding bearing 14 is interference-fitted into the bearing groove, and the lower end of the second sliding bearing 14 abuts against the upper end of the thrust washer 20. The thrust washer 20 is located at the lower end of the second sliding bearing 14, effectively providing axial support for the second sliding bearing 14, bearing the axial force during valve operation, reducing friction between the valve stem 4 and the valve body, and improving operational stability.

[0034] To enhance the sealing performance between the valve cover 3 and the valve body, such as Figure 7 As shown, the lower end of the valve cover 3 has an annular groove on the outer side of the extension portion 301, and a metal spiral wound gasket 17 is installed inside. The upper end face of the left valve body 1 has an annular protrusion 103 that matches the annular groove, and the annular protrusion 103 presses the metal spiral wound gasket 17 upward. The annular groove and the annular protrusion 103, in conjunction with the metal spiral wound gasket 17, effectively enhance the sealing performance between the valve cover 3 and the valve body.

[0035] This ball valve achieves dynamic sealing by using a rigid sealing surface of hard alloy combined with a disc spring sealing assembly 12 to push the left valve seat 10. This significantly improves wear resistance and corrosion resistance while effectively compensating for thermal deformation and wear, ensuring long-term sealing reliability. By setting three-stage sliding bearings at the valve stem 4, the friction and torque generated by the valve stem 4 controlling the ball 5 can be greatly reduced, solving the problem of high torque in traditional hard ball valves. This greatly improves the flexibility and durability of the ball valve's on / off operation, reduces the energy consumption of the drive device, and is suitable for high-pressure hydrogen-containing media, slurry media, and highly corrosive environments, extending its service life in high-temperature and highly corrosive slurry media.

[0036] Example 2

[0037] Unlike the previous embodiment, a hard seal weld is added between the left valve body 1 and the right valve body 2. The addition of a hard seal weld to the left and right valve bodies 2 further enhances the connection strength and sealing performance, eliminating the leakage risk that may exist in flange connections, and is especially suitable for high-pressure hydrogen-containing environments.

[0038] Example 3

[0039] Unlike Embodiment 1 or 2 above, as Figure 1 , 3 As shown, the upper end of the valve cover 3 is provided with a valve cover upper plate 21, which is interference-fitted with the upper end of the valve cover 3. An annular weld is provided at the adjacent position of the valve cover upper plate 21 and the upper end of the valve cover 3, forming a robust integrated structure through annular welding. After welding, the surface is ground smooth. By providing a valve cover upper plate 21 at the upper end of the valve cover 3 to fix the support frame 6, there is no need to leave a fixing position for the support frame 6 at the upper end of the valve cover 3, which can reduce the diameter of the upper part of the valve cover 3 and reduce material usage.

[0040] Example 4

[0041] Unlike embodiments one, two, or three above, as Figure 3 As shown, the support frame 6 includes a lower support plate 601, a support plate 602, a side plate 603, and an upper support plate 604. The lower support plate 601 is symmetrically connected and fixed to the upper valve cover plate 21 by four sets of bolts and anti-loosening washers. The support plate 602 and the side plate 603 are divided into two groups and are symmetrically welded and fixed to the left and right sides of the lower support plate 601. The support plate 602 is vertically arranged inside the side plate 603, forming a T-shaped layout structure. The support plate 602 and the side plate 603 are welded and fixed together. The upper support plate 604 is welded and fixed to the upper ends of the two sets of support plates 602 and side plates 603. The lower end of the pneumatic actuator 7 is connected and fixed to the upper support plate 604 by eight evenly distributed bolts and anti-loosening washers. The upper support plate 604 has a through hole in the middle to allow the connecting short shaft 8 to pass through. This support frame 6 is constructed by welding sheet metal, eliminating the need for mold making and saving mold costs, resulting in a simpler structure.

[0042] Example 5

[0043] Unlike embodiments one, two, three, or four above, as Figure 1 As shown, the packing pressure plate 903 and the valve cover upper plate 21 are fastened by two sets of symmetrically arranged fully threaded studs and nuts. Each set of nuts has a disc spring washer assembly 22 underneath it. In this embodiment, the disc spring washer assembly 22 includes eight disc spring washers. The disc spring washer assembly 22 provides a constant clamping force, automatically compensates for packing wear, avoids overpressure or loosening problems caused by traditional bolt tightening, and extends the service life of the packing.

[0044] The above-described high-pressure hydrogen-sealed ball valve for slurries is a specific embodiment of this utility model, demonstrating its substantial features and advancements. Based on actual usage needs, equivalent modifications in shape, structure, etc., can be made to it under the guidance of this utility model, all of which are within the scope of protection of this solution.

Claims

1. A hard sealing ball valve for high pressure and slurry with hydrogen, comprising a left valve body provided with an inlet flow channel, a right valve body provided with an outlet flow channel, a valve cover provided with a vertical through hole, a valve stem, a ball provided with a horizontal through flow channel hole, a support frame and a pneumatic actuator, the right valve body is connected and fixed to the right side of the left valve body, the valve cover is connected and fixed to the upper end of the left valve body, the support frame is arranged on the upper end of the valve cover, the pneumatic actuator is arranged on the upper surface of the support frame, the pneumatic actuator is connected with the upper end of the valve stem through a connecting short shaft, the valve stem passes through the support frame and the valve cover downwardly, and the lower end of the valve stem is connected and fixed with the ball in the inner cavity of the left valve body, a packing seal assembly is arranged between the upper end of the valve cover and the valve stem, the right end of the inlet flow channel is provided with a left valve seat, the left end of the outlet flow channel is provided with a right valve seat, and the left valve seat and the right valve seat form a flow channel blocking and opening adjusting structure with the ball through rotation of the ball, characterized in that: The right valve seat is fixed to the left end of the right valve body, the left valve seat and the left valve step hole arranged at the right end of the inlet flow channel are in left-right sliding matching structure, the left side of the left valve seat is provided with a disc spring sealing assembly, the disc spring sealing assembly pushes the sealing surface between the left valve seat and the ball to the right for sealing, the sealing surface between the right valve seat and the ball and the sealing surface between the left valve seat and the ball are both made of hard alloy sealing surface; the first sliding bearing is arranged between the valve stem and the perforation of the upper part of the valve body, the second sliding bearing is arranged between the lower end of the valve cover and the valve stem, the third sliding bearing is arranged below the packing sealing assembly on the valve cover, the valve stem passes through the central holes of the third sliding bearing, the second sliding bearing and the first sliding bearing, and the sealing packing is arranged between the upper part of the valve body and the valve stem.

2. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 1, characterized in that: The right side of the right valve body is embedded into the right side of the inner cavity of the left valve body, the inner side of the right end surface of the left valve body is provided with a sealing ring groove, a metal winding gasket is arranged in the sealing ring groove, the right valve body is provided with an annular pressing strip part matched with the sealing ring groove, the annular pressing strip part extends into the sealing ring groove and presses the metal winding gasket to the left, and the right valve body and the left valve body are tightly connected through the full thread stud nut assembly uniformly arranged around.

3. A high pressure hard sealed ball valve for hydrogen and slurry service according to claim 2, characterized in that: The left valve body and the right valve body are welded by hard sealing.

4. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 3, characterized in that: The right valve seat is embedded into the right valve step hole of the left end of the right valve body, the left end of the right valve seat is provided with an annular pressing step, a pressing ring is arranged on the annular pressing step, and the right valve seat is tightly arranged on the right valve body through the pressing ring and the screw.

5. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 4, characterized in that: The disc spring sealing assembly comprises a graphite sealing ring, a spring seat and a disc spring group, the spring seat comprises an inner ring part on the left inner side, a flat ring part on the right side of the inner ring part and an outer ring part on the right outer side of the flat ring part, the graphite sealing ring is arranged on the right side of the outer ring part, the inner periphery of the outer ring part and the inner periphery of the graphite sealing ring are in abutment with the outer periphery of the left side of the left valve seat, the right side of the graphite sealing ring is in abutment with the inclined step of the outer periphery of the left valve seat, the outer periphery of the outer ring part and the outer periphery of the graphite sealing ring are in abutment with the hole wall of the left valve step hole, the disc spring group is sleeved on the outer periphery of the inner ring part, the left side of the disc spring group is in abutment with the step surface of the left valve step hole, and the right side of the disc spring group is in abutment with the left side surface of the flat ring part.

6. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 5, characterized in that: The lower end of the valve stem is provided with a square connector, the square connector is embedded into a connecting slot matched with the square connector on the upper end of the ball, and a hard alloy layer is built up on the inner periphery of the connecting slot.

7. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 6, characterized in that: The upper part of the valve stem is provided with a stepped shaft part above the square connector, the sealing packing is arranged on the step of the stepped shaft part, the first sliding bearing is arranged above the sealing packing, and the outer periphery wall of the first sliding bearing is in interference matching with the left valve body.

8. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 7, characterized in that: The upper end of the first sliding bearing of the valve body is provided with an annular stepped hole, and a thrust washer is arranged on the stepped surface of the annular stepped hole; the lower end of the valve cover is provided with a downward protruding insertion part, the outer periphery of the insertion part is matched with the hole wall of the annular stepped hole, the inner side of the lower end of the valve cover is provided with a bearing groove hole, the second sliding bearing is interference fitted in the bearing groove hole, and the lower end of the second sliding bearing abuts against the upper end of the thrust washer.

9. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 8, characterized in that: The outer side of the lower end of the valve cover located at the insertion part is provided with an annular groove, and a metal winding gasket is arranged in the annular groove; the upper end surface of the left valve body is provided with an annular convex part matched with the annular groove, and the annular convex part presses the metal winding gasket upward.

10. A high pressure hard sealed ball valve for use in hydrogen and slurry service according to claim 9, characterized in that: The packing seal assembly is arranged in the packing box groove of the inner periphery of the upper end of the valve cover, and is sequentially provided with a graphite packing group, a packing gland and a packing plate from bottom to top; the packing plate and the upper cover plate arranged on the upper end of the valve cover are fastened through all-thread studs and nuts, and the lower surface of the nut is provided with a disc spring washer group.

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