Bidirectional sealing structure and eccentric C-shaped ball valve

Abstract

The utility model relates to a bidirectional sealing structure and an eccentric C type ball valve, the bidirectional sealing structure comprises a valve seat and a C type ball body, the C type ball body is arranged to be an eccentric structure, the rotating center line of the C type ball body is not intersected with the central axis of a flow channel in the valve seat, and the rear end of the valve seat abuts against a valve body to form limit. A valve seat sealing surface matched with the spherical surface of the C-shaped ball body in shape is arranged at the front end of the valve seat, and a valve seat sealing piece is arranged between the front end of the valve seat and the valve body; in a forward pressure-bearing working state, the valve seat moves forwards and compresses the valve seat sealing piece, so that the valve seat sealing surface is in close contact with the spherical surface, and forward sealing is realized; in the reverse pressure-bearing working state, the C-shaped ball body rotates around the rotating center line of the C-shaped ball body, the spherical surface is promoted to make gradual contact with the sealing face of the valve seat, reverse sealing is achieved, and the technical problems that an existing eccentric C-shaped ball valve does not have the two-way sealing function and cannot meet the two-way pressure-bearing requirement of a complex pipe network system can be solved.

Description

Technical Field

[0001] This utility model belongs to the field of valve technology, specifically relating to a bidirectional sealing structure and an eccentric C-type ball valve. Background Technology

[0002] Valves, as key components in pipeline systems, are primarily used for the shut-off and regulation of media. Given their importance in the overall system structure and their widespread use, the basic requirements for valves include high durability and excellent cost-effectiveness. Especially in complex and multifunctional pipeline systems, changes in the direction of media flow are a common phenomenon. These changes require valves not only to adapt to different operating conditions but also to possess bidirectional pressure-bearing capacity to ensure that the valves maintain good sealing performance regardless of the direction of media flow.

[0003] However, the eccentric C-type ball valves commonly used in the market have certain limitations in practical applications. These valves typically only provide reliable pressure resistance in one predetermined direction, failing to guarantee the same pressure resistance in the opposite direction, thus preventing the achievement of ideal bidirectional sealing. This deficiency limits the widespread application of eccentric C-type ball valves in piping systems requiring higher flexibility and reliability. Utility Model Content

[0004] To address the shortcomings of existing technologies, a bidirectional sealing structure and an eccentric C-type ball valve are proposed to solve the technical problem that existing eccentric C-type ball valves do not have bidirectional sealing function and cannot meet the bidirectional pressure requirements of complex pipeline systems.

[0005] To achieve the above objectives, this utility model provides the following technical solution:

[0006] In a first aspect, this utility model provides a bidirectional sealing structure, including a valve seat and a C-shaped ball. The C-shaped ball is configured as an eccentric structure, and the rotation center line of the C-shaped ball does not intersect with the central axis of the internal flow channel of the valve seat. The rear end of the valve seat abuts against the valve body to form a limit. The front end of the valve seat is provided with a valve seat sealing surface adapted to the spherical shape of the C-shaped ball, and a valve seat sealing element is provided between the front end of the valve seat and the valve body.

[0007] Under positive pressure, the valve seat moves forward and compresses the valve seat seal, causing the valve seat sealing surface to come into close contact with the spherical surface, thus achieving a positive seal. Under negative pressure, the C-shaped ball rotates around its rotation center line, causing the spherical surface to gradually come into contact with the valve seat sealing surface, thus achieving a negative seal.

[0008] The technical solution is further configured such that a first notch is provided at the rear end of the valve seat, and a boss is provided on the valve body, wherein the first notch and the boss engage to form a limiting position.

[0009] The technical solution is further configured such that a first flow guiding gap is left between the rear end of the valve seat and the valve body, and a second flow guiding gap is left between the front end of the valve seat and the C-shaped ball, wherein the second flow guiding gap is located between the first flow guiding gap and the sealing surface of the valve seat.

[0010] The technical solution is further configured such that the first guide gap and the second guide gap are respectively connected to the valve body inlet;

[0011] Under positive pressure, the area of ​​the medium acting on the rear end of the valve seat from the first guide gap is greater than the area acting on the front end of the valve seat from the second guide gap, so as to generate a force difference. The force difference pushes the valve seat forward and compresses the valve seat seal, causing the valve seat sealing surface to come into close contact with the spherical surface, thereby achieving positive sealing.

[0012] The technical solution is further configured such that a second notch is provided at the front end of the valve seat, the valve seat seal is located inside the second notch, and a clamping assembly is provided between the valve seat seal and the valve body.

[0013] The technical solution is further configured such that the clamping assembly includes a pressure cap, a baffle, and a fixing member. The first end of the pressure cap is embedded in the second notch and abuts against the valve seat seal. The second end of the pressure cap extends to the outside of the second notch. The fixing member is disposed inside the annular groove of the valve body. The baffle engages with the second end of the pressure cap and is fixed to the fixing member by a connector.

[0014] Secondly, this utility model provides an eccentric C-type ball valve, which includes a valve body, and the valve body is provided with the aforementioned bidirectional sealing structure.

[0015] The technical solution is further configured such that a lower support shaft is provided at the bottom of the valve body, a valve cover is provided at the top of the valve body, an upper support shaft is provided inside the valve cover, and the C-shaped ball is connected to the lower support shaft and the upper support shaft respectively.

[0016] The technical solution is further configured such that a valve stem is provided inside the upper support shaft, the end of the valve stem is connected to the C-shaped ball, the valve stem, the upper support shaft and the lower support shaft are arranged collinearly, and this line serves as the rotation center line of the C-shaped ball.

[0017] The beneficial effects of this utility model are:

[0018] Under forward pressure, the medium pushes the valve seat forward, compressing the valve seat seal. During this process, the valve seat sealing surface and the spherical surface are in close contact, thus achieving a good forward seal. Under reverse pressure, utilizing the eccentric design of the C-shaped ball, the medium pushes the C-shaped ball to rotate around its rotation center line. During this process, the spherical surface and the valve seat sealing surface are pressed tighter and tighter, thus achieving a good reverse seal. The double eccentric design, combined with the slight compensation of the valve seat, achieves a reliable bidirectional seal, meeting the requirements of complex pipeline systems. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the eccentric C-type ball valve in an embodiment of this utility model;

[0020] Figure 2 yes Figure 1 Partial schematic diagram at point A in the middle;

[0021] Figure 3 This is a partial schematic diagram of the valve body in an embodiment of this utility model;

[0022] Figure 4 This is a schematic diagram of the fixing component in an embodiment of this utility model;

[0023] Figure 5 This is a schematic diagram of the assembly of the C-shaped ball and the valve seat in an embodiment of this utility model.

[0024] In the attached diagram: 1. Valve seat; 2. C-shaped ball; 3. Valve body; 4. Valve cover; 5. Lower support shaft; 6. Upper support shaft; 7. Valve stem; 8. Valve seat seal; 9. Gland; 10. Fixing element; 11. Baffle; 12. Connecting element; 13. Boss; 14. Annular groove; 15. Mounting groove; 16. Threaded hole; 17. First notch; 18. Second notch; 19. First guide gap; 20. Second guide gap; 21. Valve seat sealing surface. Detailed Implementation

[0025] To enable those skilled in the art to better understand the technical solution of this utility model, the technical solution of this utility model will be clearly and completely described below with reference to the accompanying drawings. Based on the embodiments in this application, other similar embodiments obtained by those skilled in the art without creative effort should all fall within the scope of protection of this application. Furthermore, directional terms mentioned in the following embodiments, such as "up," "down," "left," and "right," are only for reference to the directions in the accompanying drawings; therefore, the directional terms used are for illustrative purposes and not for limiting the invention.

[0026] The present invention will be further described below with reference to the accompanying drawings and preferred embodiments.

[0027] Example 1

[0028] This embodiment provides a bidirectional sealing structure; please refer to [link / reference]. Figures 1 to 5 The valve includes a valve seat 1 and a C-shaped ball 2. The C-shaped ball 2 is configured with an eccentric structure, and the rotation center line of the C-shaped ball does not intersect with the central axis of the flow channel inside the valve seat. The rear end of the valve seat 1 abuts against the valve body 3 to form a limit. The front end of the valve seat 1 is provided with a valve seat sealing surface 21 that matches the spherical shape of the C-shaped ball 2, and a valve seat sealing element 8 is provided between the front end of the valve seat 1 and the valve body 3.

[0029] Furthermore, the valve seat 1 has an annular structure, with its inner diameter matching the outer diameter of the C-shaped ball 2. The front end of the valve seat faces the spherical surface of the C-shaped ball 2 and is designed with a valve seat sealing surface 21 that matches the shape of the spherical surface to ensure a tight fit with the spherical surface in the sealed state. The rear end of the valve seat 1 abuts against the inner wall of the valve body 3, forming a limit on the valve seat 1 to prevent it from retracting when closed or under reverse pressure, which would cause a drop in sealing pressure and leakage.

[0030] Furthermore, the C-shaped ball 2 adopts an eccentric structure, and its rotation center line does not intersect with the central axis of the flow channel inside the valve seat, i.e., the two are offset. This double eccentric design makes the rotation radius of the C-shaped ball 2 divided into long-radius rotation and short-radius rotation. The movement trajectory of the C-shaped ball 2 is a two-vector motion, i.e., rotation + translation. When closed, the short-radius ball enters the valve seat 1 first. As the closure continues, the rotation radius gradually increases, and the spherical surface gradually presses against the valve seat sealing surface 21 to achieve progressive contact. Since the rear end of the valve seat 1 is in direct contact with the valve body 3 for limiting, the valve seat 1 will not move backward, so it becomes tighter and tighter as it closes, thereby improving the sealing effect and reducing the operating torque. When opened, the C-shaped ball 2 rotates in the opposite direction, and the spherical surface gradually separates from the valve seat sealing surface 21.

[0031] Specifically, the C-shaped sphere 2 is made of corrosion-resistant and wear-resistant alloy material, and its surface is precision machined and polished to ensure that the smoothness of the sphere meets the sealing requirements.

[0032] Furthermore, the valve seat seal 8 is disposed between the front end of the valve seat 1 and the valve body 3, and is made of elastic material, such as fluororubber, polytetrafluoroethylene, etc., which has good elastic recovery performance and resistance to media corrosion.

[0033] In operation, under forward pressure, the medium enters from the valve body inlet, exerting pressure on the valve seat 1. This causes the valve seat 1 to move forward and compress the valve seat seal 8, resulting in tight contact between the valve seat sealing surface 21 and the spherical surface of the C-shaped ball 2, forming a reliable forward seal. At this time, the greater the medium pressure, the greater the force that causes the valve seat 1 to move forward, and the better the sealing effect, thus achieving a forward seal. Under reverse pressure, the medium enters from the valve body outlet, exerting pressure on the C-shaped ball 2. Because the C-shaped ball 2 is designed with an eccentric structure, as the C-shaped ball 2 rotates around its rotation center line, the gap between the spherical surface and the valve seat sealing surface 21 gradually decreases until they are completely fitted, thus achieving a reverse seal. The double eccentric design, combined with the slight compensation of the valve seat 1, achieves a reliable bidirectional seal, meeting the requirements of complex pipeline systems.

[0034] In the bidirectional sealing structure of this embodiment, please refer to Figures 1 to 5 The valve seat 1 has a first notch 17 at its rear end and a boss 13 on its valve body 3. The first notch 17 and the boss 13 engage to form a limit, preventing the valve seat 1 from retracting when closed or under reverse pressure, which would cause the sealing pressure to drop and leakage to occur.

[0035] Specifically, the first notch 17 is distributed in a ring around the rear end of the valve seat 1, forming a locking structure with the ring-shaped boss 13 on the valve body 3. Through long-term practice, the inventors discovered that when a spring or valve seat seal is placed at the rear end of the valve seat, the valve seat will retract under closed or reverse pressure conditions, leading to a decrease in sealing pressure and leakage. To solve this technical problem, the inventors placed the valve seat seal 8 at the front end of the valve seat 1, with the rear end of the valve seat 1 in rigid contact with the valve body 3. When the hemispherical valve is closed or under reverse pressure, the position of the valve seat 1 remains unchanged, and the spherical surface and the valve seat sealing surface 21 always maintain a constant sealing pressure, ensuring reliable sealing.

[0036] In the bidirectional sealing structure of this embodiment, please refer to Figures 1 to 5 A first flow guide gap 19 is provided between the rear end of the valve seat 1 and the valve body 3, and a second flow guide gap 20 is provided between the front end of the valve seat 1 and the C-shaped ball 2. The second flow guide gap 20 is located between the first flow guide gap 19 and the valve seat sealing surface 21.

[0037] Furthermore, the boss 13 is formed by connecting a transverse platform and a longitudinal platform. The width of its transverse platform is greater than the transverse width of the first notch 17. The difference in width between the two creates a first flow guide gap 19 between the rear end of the valve seat 1 and the valve body 3. The valve seat sealing surface 21 is connected to the inner wall of the valve seat 1 by a transition slope, thereby creating a second flow guide gap 20 between the front end of the valve seat 1 and the C-shaped ball 2. The purpose of designing the two flow guide gaps is to utilize the pressure difference of the medium to generate a force that pushes the valve seat 1 forward under positive pressure, thereby enhancing the sealing effect.

[0038] Specifically, the first guide gap 19 and the second guide gap 20 are connected to the valve body inlet. Under positive pressure working conditions, a slight deformation of the C-shaped ball support shaft may occur, causing the spherical surface to tend to leave the valve seat sealing surface 21. At the same time, the medium acts on the rear and front ends of the valve seat 1 through these two guide gaps. The area of ​​the first guide gap 19 is larger than the area of ​​the second guide gap 20. Therefore, the area S1 of the medium acting on the rear end of the valve seat 1 from the first guide gap 19 is larger than the area S2 of the medium acting on the front end of the valve seat 1 from the second guide gap 20, thereby generating a force difference along the flow channel direction. This force difference pushes the valve seat 1 forward slightly and further compresses the valve seat seal 8, causing the valve seat sealing surface 21 to contact the spherical surface of the C-shaped ball more closely, achieving positive sealing. At this time, the closing force and the force difference of the medium acting on the valve seat 1 together form the positive sealing force. Under reverse pressure, the area A1 of the medium acting on the long radius of the C-shaped ball 2 is greater than the area A2 of the medium acting on the short radius of the C-shaped ball 2, thereby generating an eccentric force. This causes the C-shaped ball 2 to tend to rotate clockwise around its rotation center line, making the spherical surface press tightly against the valve seat sealing surface 21. At the same time, since the rear end of the valve seat 1 is in direct contact with the valve body 3 for limiting, no displacement will occur, thus achieving reverse sealing. At this time, the closing force and the eccentric force of the medium acting on the C-shaped ball 2 together form the reverse sealing force.

[0039] In the bidirectional sealing structure of this embodiment, please refer to Figures 1 to 5 The valve seat 1 has a second notch 18 at its front end, the valve seat seal 8 is located inside the second notch 18, and a clamping assembly is provided between the valve seat seal 8 and the valve body 3.

[0040] Furthermore, the second notch 18 has an annular structure and is formed on the outer peripheral surface of the front end of the valve seat 1. The valve seat seal 8 is embedded in the second notch 18, with its outer side in contact with the clamping assembly and its inner side in contact with the valve seat body, forming a stable sealing structure.

[0041] Specifically, the thickness of the valve seat seal 8 is designed according to the actual working pressure and temperature conditions to ensure that it can provide sufficient sealing force under compression.

[0042] In the bidirectional sealing structure of this embodiment, please refer to Figures 1 to 5 The clamping assembly includes a pressure cap 9, a baffle 11, and a fixing member 10. The first end of the pressure cap 9 is embedded in the second notch 18 and abuts against the valve seat seal 8. The second end of the pressure cap 9 extends outside the second notch 18. The fixing member 10 is disposed inside the annular groove 14 of the valve body 1. The baffle 11 engages with the second end of the pressure cap 9 and is fixed to the fixing member 10 by a connector 12. This design allows the clamping assembly to apply a stable preload to the valve seat seal 8, while allowing the valve seat 1 to move forward to a limited extent during operation to adapt to different working conditions.

[0043] Furthermore, the gland 9 has an annular structure, and the shape of its first end is adapted to the second notch 18, so that it can be embedded in the second notch 18 and in close contact with the valve seat seal 8, applying a pre-tightening force to the valve seat seal 8. The second end of the gland 9 extends to the outside of the second notch 18, and at the same time, the second end extends in a direction perpendicular to the gland body to form a flange, which engages with the baffle 11.

[0044] Furthermore, the fastener 10 is installed in the annular groove 14 on the inner wall of the valve body 3. The fastener 10 is preferably a four-open ring, which is composed of four arc-shaped segments. These arc-shaped segments can be installed into the annular groove 14 respectively, and then squeezed together by elastic force to form a complete annular structure. The fastener 10 is usually made of an elastic alloy material, which has a certain elastic deformation capacity and sufficient strength.

[0045] Furthermore, the first end of the baffle 11 engages with the flange of the pressure cap 9, forming an axial limit on the pressure cap 9. The second end of the baffle 11 presses against the outside of the fixing member 10, and simultaneously, the second end abuts against the mounting groove 15 to form a limit. Then, it is fixed to the fixing member 10 by the connector 12. The mounting groove 15 is annular and is arranged circumferentially along the valve body 3. The radius of the mounting groove 15 is smaller than the radius of the annular groove 14, and the junction of the two forms a limit on the fixing member 10. Preferably, the connector 12 is a bolt, and the fixing member 10 has a threaded hole 16 adapted to the bolt.

[0046] Example 2

[0047] This embodiment provides an eccentric C-type ball valve. Please refer to [link / reference]. Figures 1 to 5 It includes a valve body 3, and the valve body 3 is provided with the bidirectional sealing structure described in Embodiment 1.

[0048] Furthermore, the valve body 3 is manufactured using a casting process, and the material can be carbon steel, stainless steel, or cast iron, selected according to the actual working medium and environmental conditions. The internal space of the valve body 3 is designed to accommodate a bidirectional sealing structure. Both ends of the valve body are equipped with flanges or threaded connections for connection to piping systems.

[0049] In the eccentric C-type ball valve of this embodiment, please refer to Figures 1 to 5 The bottom of the valve body 3 is provided with a lower support shaft 5, the top of the valve body 3 is provided with a valve cover 4, and the inside of the valve cover 4 is provided with an upper support shaft 6. The C-shaped ball 2 is connected to the lower support shaft 5 and the upper support shaft 6 respectively.

[0050] Furthermore, the lower support shaft 5 is fixed to the bottom of the valve body 3 and is made of wear-resistant alloy material with a hardened surface to improve wear resistance and service life.

[0051] Furthermore, the valve cover 4 is bolted to the top of the valve body 3, and a sealing gasket is placed between the valve cover 4 and the valve body 3 to ensure the sealing of the connection. An upper support shaft 6 is installed inside the valve cover 4, and the upper support shaft 6 and the lower support shaft 5 are collinear, jointly supporting the rotation of the C-shaped ball 2. The upper support shaft 6 is made of the same material as the lower support shaft 5 and has also undergone hardening treatment to improve wear resistance. The C-shaped ball 2 is connected to the lower support shaft 5 and the upper support shaft 6 respectively via key or spline connection.

[0052] In the eccentric C-type ball valve of this embodiment, please refer to Figures 1 to 5 The upper support shaft 6 is equipped with a valve stem 7. The end of the valve stem 7 is connected to the C-shaped ball 2. The valve stem 7, the upper support shaft 6 and the lower support shaft 5 are arranged collinearly, and this line serves as the rotation center line of the C-shaped ball 2.

[0053] Furthermore, the valve stem 7 is made of high-strength alloy steel with an anti-corrosion surface treatment. The diameter of the valve stem 7 is determined according to the valve size and operating torque. The lower end of the valve stem 7 is connected to the C-type ball 2 by a keyed or splined connection to ensure reliable torque transmission. The upper end of the valve stem 7 extends to the outside of the valve cover 4, connecting to the operating mechanism such as a handwheel, electric actuator, or pneumatic actuator. A packing seal structure is provided at the position where the valve stem 7 passes through the valve cover 4 to prevent media leakage from the gap between the valve stem 7 and the valve cover 4. The packing seal structure includes components such as packing, packing gland, and clamping bolts. The packing material is selected according to the working medium and temperature conditions; commonly used materials include graphite and polytetrafluoroethylene (PTFE).

[0054] Furthermore, the valve stem 7, the upper support shaft 6, and the lower support shaft 5 are arranged collinearly to form the rotation centerline of the C-shaped ball 2. Since the C-shaped ball 2 is designed with an eccentric structure, its geometric center does not coincide with the rotation centerline. This eccentric design allows the C-shaped ball 2 to achieve progressive contact or separation with the valve seat sealing surface 21 during rotation, thereby improving the sealing effect and reducing the operating torque.

[0055] During valve opening, the valve stem 7 is rotated via the operating mechanism. The valve stem 7 drives the C-shaped ball 2 to rotate around its center line, gradually separating the spherical surface from the valve seat sealing surface 21, forming a medium flow channel, allowing the medium to flow through the valve. During valve closing, the C-shaped ball 2 rotates in the opposite direction, and the spherical surface gradually and tightly contacts the valve seat sealing surface 21, blocking the medium flow. Simultaneously, due to the adoption of a bidirectional sealing structure, this eccentric C-shaped ball valve can achieve reliable sealing under both forward and reverse pressure.

[0056] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0057] Optionally, specific examples in this embodiment can refer to the examples described in the above embodiments, and will not be repeated here.

[0058] The sequence numbers of the embodiments in this application are for descriptive purposes only and do not represent the superiority or inferiority of the embodiments.

[0059] In the above embodiments of this application, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions of other embodiments.

[0060] The above description is only a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. A bidirectional seal structure, characterized by, The valve seat and the C-shaped ball are arranged in an eccentric structure, and the rotation center line of the C-shaped ball does not intersect with the axis in the internal flow channel of the valve seat, the rear end of the valve seat is limited by the valve body, the front end of the valve seat is provided with a valve seat sealing surface matched with the spherical surface of the C-shaped ball, and the valve seat sealing element is arranged between the front end of the valve seat and the valve body. In the forward pressure-bearing working state, the valve seat moves forward and compresses the valve seat sealing element, so as to make the valve seat sealing surface closely contact with the spherical surface, thereby realizing the forward sealing; in the reverse pressure-bearing working state, the C-shaped ball rotates around the rotation center line, so as to make the spherical surface gradually contact with the valve seat sealing surface, thereby realizing the reverse sealing.

2. The bidirectional seal structure of claim 1, wherein, The rear end of the valve seat is provided with a first notch, the valve body is provided with a boss, and the first notch is limited by the boss.

3. The bidirectional seal structure of claim 1, wherein, The rear end of the valve seat is provided with a first notch, the valve body is provided with a boss, and the first notch is limited by the boss.

4. The bidirectional seal structure of claim 3, wherein, The first flow guide gap and the second flow guide gap are respectively communicated with the valve body inlet. In the forward pressure-bearing state, the area of the medium acting on the rear end of the valve seat from the first flow guide gap is greater than the area of the medium acting on the front end of the valve seat from the second flow guide gap, so as to generate a force difference, the force difference drives the valve seat to move forward and compresses the valve seat sealing element, so as to make the valve seat sealing surface closely contact with the spherical surface, thereby realizing the forward sealing.

5. The bidirectional seal structure of claim 1, wherein, The front end of the valve seat is provided with a second notch, the valve seat sealing element is located in the second notch, and the valve seat sealing element is provided with a compression assembly between the valve body.

6. The bidirectional seal structure of claim 5, wherein, The compression assembly comprises a gland, a baffle and a fixing element, the first end of the gland is embedded in the second notch and abuts against the valve seat sealing element, the second end of the gland extends to the outside of the second notch, the fixing element is arranged in the annular groove of the valve body, the baffle is limited by the second end of the gland, and the baffle is fixed on the fixing element through a connecting element.

7. An eccentric C-type ball valve, characterized by The valve body is internally provided with the bidirectional sealing structure of any one of claims 1-6.

8. The eccentric C-ball valve according to claim 7, wherein The bottom of the valve body is provided with a lower support shaft, the top of the valve body is provided with a valve cover, the valve cover is internally provided with an upper support shaft, and the C-shaped ball is connected with the lower support shaft and the upper support shaft respectively.

9. The eccentric C-ball valve according to claim 8, wherein The upper support shaft is internally provided with a valve rod, the end of the valve rod is connected with the C-shaped ball, the valve rod, the upper support shaft and the lower support shaft are arranged in a line, and the line serves as the rotation center line of the C-shaped ball.

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