Inner rail forced sealing ball valve

Abstract

The invention discloses an inner rail forced sealing ball valve, belongs to the technical field of valves, and aims to solve the technical problems of insufficient sealing performance and service life of a ball valve in the prior art. The inner rail forced sealing ball valve comprises a valve body, a ball body is arranged in the valve body, a support is assembled on the top of the valve body, and an actuator is installed on the top of the support. A valve rod is vertically arranged in the support in a penetrating mode, and the valve rod is connected with the ball body and an actuator power output shaft. A pair of valve seats and a pair of thrust gears are further arranged in the valve body, the valve seats are distributed on the two sides of the ball body, the thrust gears are distributed on the top and the bottom of the ball body, and the valve rod is connected with the thrust gears and drives the thrust gears to rotate. The inner rail forced sealing ball valve comprises the valve body, forced sealing can be achieved, the output torque of an actuator can be increased, the sealing force of the ball valve can be increased, the stability of the valve is improved, in addition, friction-free movement of the ball body and the valve seat can be achieved, and the service life of the valve is greatly prolonged.

Description

Technical Field

[0001] This invention belongs to the field of valve technology, specifically relating to an internal track forced sealing ball valve. Background Technology

[0002] Ball valves, as an important fluid control device, have wide and crucial applications in many industrial fields such as petroleum, chemical, natural gas, power, and water treatment, as well as in civil applications. With their advantages of simple structure, convenient operation, rapid switching, and low fluid resistance, they have become a commonly used valve type for controlling fluid flow and regulating flow in various pipeline systems.

[0003] However, existing ball valves have many problems in terms of sealing performance and service life that urgently need to be solved. Currently, most ball valves adopt a self-sealing structure. In this structure, when the valve is closed, the sealing force between the valve seat and the ball mainly relies on the pre-tightening force and the force of the medium inside the valve. However, this sealing method has obvious defects. Once the valve seat has micro-leakage or micro-wear, the sealing effect of the valve will drop sharply, making it difficult to guarantee long-term stable sealing performance. This may lead to medium leakage, causing safety accidents, resource waste, and environmental pollution. During the opening and closing process of the ball valve and valve seat, existing ball valves also have another serious problem: the ball and valve seat are always in contact, and a lot of friction will be generated between them. This friction not only accelerates the wear of the sealing surface and affects the sealing effect of the valve, but the wear problem is more prominent for large-diameter and high-pressure ball valves. With the increase of service time, the wear of the sealing surface will lead to an increase in valve leakage, or even failure to close properly, seriously affecting the safe operation of the pipeline system and production efficiency. To this end, this application proposes an internal track forced sealing ball valve. Summary of the Invention

[0004] In view of the shortcomings of the prior art, the purpose of this invention is to provide an internal track forced sealing ball valve, which aims to solve the technical problems of insufficient sealing performance and service life of ball valves under the prior art.

[0005] Technical solution

[0006] To address the aforementioned technical problems, this invention provides an internal track forced sealing ball valve, comprising a valve body, inside which a ball is disposed, and a bracket is mounted on the top of the valve body, with an actuator installed on the top of the bracket; a valve stem is vertically inserted through the bracket, connecting the ball and the actuator's power output shaft; the valve body also contains a pair of valve seats and a pair of thrust gears, with the pair of valve seats distributed on both sides of the ball, and the pair of thrust gears distributed on the top and bottom of the ball, the valve stem being connected to the thrust gears, the valve stem driving the thrust gears to rotate, thereby causing the valve seats to move toward the ball.

[0007] Preferably, a curved track is formed on the outer circular surface of the valve seat, and a pin is inserted through the thrust gear into the curved track.

[0008] Preferably, a lower ball bearing is provided at the bottom of the valve body, and an upper ball bearing is provided at the top of the valve body.

[0009] Preferably, a valve stem bearing and a valve stem thrust bearing are provided at the bottom of the bracket, and a packing assembly and a packing pressure plate are provided between the inside of the bracket and the valve stem, with the packing pressure plate pressing the packing assembly.

[0010] Preferably, a lower support plate is provided at the bottom of the valve body, an upper support plate is provided at the top of the valve body, a lower ball bearing and an upper ball bearing are respectively embedded in the lower support plate and the upper support plate, and a pair of thrust gears are respectively mounted on the lower support plate and the upper support plate.

[0011] Preferably, the valve body is provided with a valve seat energy storage ring and a thrust bearing, which are located outside the thrust gear.

[0012] Preferably, the cross-section at the connection between the valve stem and the ball is square, and the square cross-section of the valve stem is larger than that of the ball.

[0013] Preferably, a leaf spring is provided on the side of the ball, and the leaf spring makes elastic contact with the inner wall of the valve stem and the ball sleeve joint.

[0014] Preferably, the maximum angle of the curved track is 90°, and the rotation angle range of the sphere is 0 to 90°.

[0015] Beneficial effects

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows: This invention, through the rational design of the curved track on the valve seat, utilizes gear transmission to transfer the actuator's torque to the valve seat, thereby increasing the ball valve's sealing force by increasing the actuator's output torque. During valve closing, when the valve stem rotates to a certain angle, the sliding of the pin within the curved track pushes the valve seat towards the ball, achieving forced sealing. This significantly improves the valve's sealing performance and stability, effectively solving the problem of a sharp decline in sealing effect in existing self-sealing ball valves due to micro-leakage of impurities or micro-wear on the valve seat.

[0017] In this invention, the movement of the ball and valve seat is divided into two processes by utilizing the curved track design on the valve seat. During the 90° rotation of the ball, a gap exists between the valve seat and the ball, resulting in frictionless contact and ensuring the fluid capacity of the ball valve and fixing the ball in the closed position. When the ball has rotated 90°, the valve seat contacts the ball. At this point, the valve stem continues to rotate, compressing the leaf spring and stopping the ball's rotation. Meanwhile, the valve seat continues to move towards the ball under the action of the pin, achieving a frictionless seal. This design significantly reduces friction between the ball and valve seat, reduces wear on the sealing surface, and significantly increases the service life of the valve, making it particularly suitable for large-diameter and high-pressure ball valves.

[0018] In this invention, by transmitting the power of the actuator to the valve seat, a large sealing force can be achieved in a relatively small space. Compared with existing externally sealed ball valves, this ball valve has a more compact structure, reduced manufacturing difficulty, and correspondingly lower cost, while also saving space and facilitating installation and use. Attached Figure Description

[0019] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the internal structure of the valve body in this invention; Figure 3 This is a schematic diagram of the valve stem structure in this invention; Figure 4 This is a schematic diagram of the structure when the ball and the valve seat just come into contact in this invention; Figure 5 This is a schematic diagram of the structure when the ball and valve seat are completely sealed in this invention; Figure 6 This is a schematic diagram of the thrust gear in this invention; Figure 7 This is a schematic diagram of the valve seat structure in this invention.

[0021] The labels in the attached diagram are as follows: 1. Valve body; 2. Valve seat accumulator ring; 3. Thrust bearing; 4. Valve seat; 5. Thrust gear; 6. Pin; 7. Lower support plate; 8. Ball; 9. Lower ball bearing; 10. Valve stem; 11. Upper ball bearing; 12. Leaf spring; 13. Valve stem bearing; 14. Valve stem thrust bearing; 15. Packing assembly; 16. Packing pressure plate; 17. Bracket; 18. Actuator; 19. Curved track. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] This embodiment provides an internal track forced sealing ball valve, the structural schematic diagram of which is shown below. Figures 1-7 As shown, it includes valve body 1 and valve stem 10.

[0024] In this embodiment, the valve body 1 serves as the main structure of the entire ball valve, and a ball 8 is disposed inside it. The ball 8 can rotate within the valve body 1 to open and close the valve. A bracket 17 is mounted on the top of the valve body 1, and an actuator 18 is mounted on the top of the bracket 17, providing power for the valve's movement. A valve stem 10 is vertically inserted through the bracket 17. The lower end of the valve stem 10 is connected to the ball 8, and the upper end is connected to the power output shaft of the actuator 18. The actuator 18 drives the valve stem 10 to rotate, thereby driving the ball 8 to rotate. The cross-section at the connection between the valve stem 10 and the ball 8 is square, and the square cross-section of the valve stem 10 is larger than that of the ball 8. A leaf spring 12 is disposed between them, and the leaf spring 12 makes elastic contact with the inner wall of the connection between the valve stem 10 and the ball 8, playing a buffering and positioning role during the opening and closing of the valve.

[0025] Furthermore, in this embodiment, the valve body 1 is also provided with a pair of valve seats 4 and a pair of thrust gears 5. The pair of valve seats 4 are distributed on both sides of the ball 8, and the pair of thrust gears 5 are distributed on the top and bottom of the ball 8. The valve stem 10 is connected to the thrust gears 5. When the valve stem 10 rotates, it drives the thrust gears 5 to rotate. A pin 6 passes through the thrust gear 5, and the other end of the pin 6 is inserted into the curved track 19 on the valve seat 4. During the rotation of the thrust gear 5, the sliding of the pin 6 in the curved track 19 drives the valve seat 4 to move towards the ball 8, thereby achieving valve sealing.

[0026] Furthermore, in this embodiment, a lower support plate 7 and a lower ball bearing 9 are provided at the bottom of the valve body 1, and an upper support plate and an upper ball bearing 11 are provided at the top of the valve body 1. The lower ball bearing 9 and the upper ball bearing 11 are respectively embedded in the lower support plate 7 and the upper support plate. A pair of thrust gears 5 are respectively fitted on the lower support plate 7 and the upper support plate, providing support and positioning for the rotation of the ball 8 and the thrust gears 5. Inside the valve body 1, a valve seat energy storage ring 2 and a thrust bearing 3 are provided on the outer side of the valve seat 4. The valve seat energy storage ring 2 can provide a certain preload when the valve is closed, enhancing the sealing effect; the thrust bearing 3 can reduce the friction when the valve seat 4 rotates.

[0027] Furthermore, in this embodiment, a valve stem bearing 13 and a valve stem thrust bearing 14 are provided at the bottom of the bracket 17 to support and position the valve stem 10 and reduce friction when the valve stem 10 rotates. A packing assembly 15 and a packing pressure plate 16 are provided inside the bracket 17 and between it and the valve stem 10. The packing pressure plate 16 presses the packing assembly 15 to prevent the medium from leaking from the valve stem 10 and to ensure the sealing performance of the valve.

[0028] As a preferred technical solution in this embodiment, the maximum angle of the curved track 19 is 90°, and the rotation angle range of the ball 8 is 0 to 90°. By reasonably designing the shape and angle of the curved track 19, a specific motion relationship between the ball 8 and the valve seat 4 is achieved, thereby realizing the forced sealing and frictionless movement of the valve.

[0029] Working principle: When the valve transitions from the open state to the closed state: When the valve is fully open, there is a very small gap between the valve seat 4 and the ball 8. When the actuator 18 receives the closing signal, it drives the valve stem 10 to rotate. Since the valve stem 10 is connected to both the ball 8 and the thrust gear 5, and the leaf spring 12 at the connection between the valve stem 10 and the ball 8, as well as the ball 8 and the valve seat 4, are not in contact, there is no friction, and the ball 8 moves with the valve stem 10. At the same time, the valve stem 10 drives the thrust gear 5 to rotate, and one end of the pin 6 is fixed to the thrust gear 5, while the other end slides on the curved track 19 of the valve seat 4.

[0030] When the valve stem 10 rotates 0-88°, the ball 8 also rotates 0-88°. Since the gear ratio between the thrust gear 5 and the valve stem 10 is 1:1, the thrust gear 5 also rotates 0-88°. Because the curved track 19 on the valve seat 4 is circular from 0-89°, and both the valve seat 4 and the valve body 1 have anti-rotation structures, the valve seat 4 does not move during this process.

[0031] When the valve stem 10 rotates from 88-90°, the pin 6 changes from a circular shape to a curved surface on the curved track 19 of the valve seat 4. Simultaneously, the valve seat 4 is restricted from rotation. During rotation, the valve seat 4 moves towards the ball 8, eliminating the gap between them, and they begin to contact. As the valve stem 10 continues to rotate, because the square cross-section of the valve stem 10 is larger than that of the ball 8, and the ball 8 is already in contact with the valve seat 4, the medium force pushes the valve seat 4 into contact with the medium. The friction between the ball 8 and the valve seat 4 is significant. Continued rotation of the valve stem 10 merely compresses the leaf spring 12, while the ball 8 remains stationary relative to the valve seat 4. The continued rotation of the valve stem 10 causes the pin 6 to slide on the curved surface, pushing the valve seat 4 and the ball 8 into tight contact, thus ensuring a valve seal and placing the valve in a fully closed state. This process achieves both forced sealing and frictionless closure of the ball 8 and valve seat 4 during valve closing.

[0032] When the ball valve transitions from the closed state to the open state: When the valve stem 10 rotates 0-2°, it eliminates the compression between the valve seat 4 and the ball 8 and causes them to separate. At this time, the ball 8 is relatively stationary.

[0033] During the rotation of valve stem 10 from 2 to 90 degrees, since ball 8 and valve seat 4 have separated, ball 8 and valve seat 4 achieve frictionless opening.

[0034] All technical features in this embodiment can be freely combined according to actual needs.

[0035] Finally, it should be noted that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. An inner track forced sealing ball valve, comprising a valve body (1), characterized in that: a ball (8) is arranged inside the valve body (1), a support (17) is arranged on the top of the valve body (1), and an actuator (18) is arranged on the top of the support (17); a valve rod (10) is vertically arranged in the support (17), and the valve rod (10) is connected with the ball (8) and the power output shaft of the actuator (18); a pair of valve seats (4) are arranged on both sides of the ball (8), and a pair of thrust gears (5) are arranged on the top and bottom of the ball (8), the valve rod (10) is connected with the thrust gears (5), the valve rod (10) drives the rotation of the thrust gears (5), and the valve seats (4) are driven to move towards the ball (8).

2. A ball valve with an internal track positive seal according to claim 1, wherein, A curved track (19) is arranged on the outer surface of the valve seat (4), and a pin shaft (6) is arranged on the thrust gear (5), and the pin shaft (6) is inserted into the curved track (19).

3. A ball valve with an internal track positive seal according to claim 1, wherein, A ball lower bearing (9) is arranged at the bottom of the valve body (1), and a ball upper bearing (11) is arranged at the top of the valve body (1).

4. An inner track forced seal ball valve according to claim 1, wherein, A valve rod bearing (13) and a valve rod thrust bearing (14) are arranged at the bottom of the support (17), a packing group (15) and a packing pressing plate (16) are arranged between the inside of the support (17) and the valve rod (10), and the packing pressing plate (16) compresses the packing group (15).

5. A ball valve with an internal track positive seal according to claim 3, wherein, A lower support plate (7) is arranged at the bottom of the valve body (1), an upper support plate is arranged at the top of the valve body (1), the ball lower bearing (9) and the ball upper bearing (11) are respectively embedded in the lower support plate (7) and the upper support plate, and a pair of the thrust gears (5) are respectively sleeved on the lower support plate (7) and the upper support plate.

6. A ball valve with an internal track positive seal according to claim 1, wherein, A valve seat energy storage ring (2) and a thrust bearing (3) are arranged in the valve body (1), and the valve seat energy storage ring (2) and the thrust bearing (3) are located outside the thrust gear (5).

7. A ball valve with an internal track positive seal according to claim 1, wherein, The cross section of the connection between the valve rod (10) and the ball (8) is a quadrilateral structure, and the cross section of the valve rod (10) is larger than that of the ball (8).

8. A ball valve with an internal track positive seal according to claim 1, wherein, A leaf spring (12) is arranged on the side surface of the ball (8), and the leaf spring (12) is in elastic contact with the inner wall of the sleeve joint of the valve rod (10) and the ball (8).

9. An inner track forced seal ball valve as defined in claim 2 wherein, The maximum angle of the curved track (19) is 90°, and the rotation angle range of the ball (8) is 0-90°.

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