Integrated ball valve

Abstract

The invention provides an integrated ball valve which comprises a valve body and an actuator, a ball body is arranged in the valve body, the actuator is in driving connection with the ball body through a valve rod, the integrated ball valve is characterized by further comprising an electromagnetic valve, a first piston cylinder and a second piston cylinder, a first piston is arranged in the first piston cylinder, and a second piston is arranged in the second piston cylinder. A first piston is arranged in the first piston cylinder, a second piston is arranged in the second piston cylinder, the first piston and the second piston are in meshed connection with the valve rod, and the electromagnetic valve is used for introducing medium pressure on the high-pressure side of the valve body into the first piston cylinder and / or the second piston cylinder so that the first piston cylinder and / or the second piston cylinder can act. The piston cylinder is arranged on the valve body, medium pressure is introduced, driving force is formed at the two ends of the piston through medium pressure difference, the driving force and the actuator are combined to drive the valve rod to achieve rapid opening and closing of the valve, and the problems that an actuator of an existing high-pressure working condition integrated ball valve is large in size and weight and long in opening and closing time are solved.

Description

Technical Field

[0001] This invention relates to the field of ball valve control technology, and more specifically, to an integrated ball valve. Background Technology

[0002] Ball valves are widely used in pipeline transportation of various fluids. Large-diameter ball valves are mostly used for long-distance pipeline transportation or industrial pipeline bus. Due to the characteristics of high pressure and large flow of liquid in pipelines, higher requirements are placed on the opening and closing performance and sealing safety of ball valves.

[0003] Currently, ball valves on the market are usually opened and closed manually or driven by electric, electro-hydraulic, or pneumatic actuators to achieve valve opening and closing. If they are opened and closed rapidly (≤5s) under high pressure conditions (≥900Lb), the instantaneous torque output by the ball valve actuator will increase significantly. This will lead to a significant increase in the size of the actuator and the entire ball valve, making it difficult to meet the installation requirements in confined spaces.

[0004] To address this, some ball valves employ a frictionless ball valve structure to achieve low opening and closing torque. For example, Chinese Patent Publication No. CN119084609A discloses an electro-hydraulic driven low-torque ball valve and its control method. The ball valve includes a valve body unit, a valve core unit installed inside the valve body unit, valve seat units symmetrically installed on both sides of the valve core unit, an upper support seat and a lower support seat mounted opposite each other on the valve body unit, and a valve stem drive unit mounted on the upper support seat for driving the valve core unit to rotate within the valve body unit. This solution uses a deformation mechanism to achieve disengagement or engagement between these components, thus solving the problem of high opening and closing resistance. However, the complex structure results in lower valve sealing performance and longer opening and closing times.

[0005] Chinese patent CN221880298U discloses a frictionless pneumatic ball valve with dust removal function. It uses a spring between the radially outer step on the back of the valve seat and the radially inner step of the valve body channel to form a floating valve seat. An annular groove is provided in the middle of the valve seat sealing surface, dividing the valve seat sealing surface into an outer annular sealing surface and an inner annular sealing surface. The annular groove is connected to the air source inlet of the pneumatic device through air holes and pressure taps on the valve seat and valve body. This solution synchronously introduces air into the valve seat, pushing the valve seat sealing surface away from the ball sealing surface to achieve a lower opening and closing torque. However, it requires an air source and cannot be implemented without one.

[0006] In view of this, the present invention is hereby proposed. Summary of the Invention

[0007] The problem solved by this invention is that existing ball valves cannot simultaneously meet the requirements of being installed in confined spaces and achieving rapid opening and closing under high-pressure conditions.

[0008] To address the aforementioned problems, this invention provides an integrated ball valve, comprising a valve body and an actuator. A ball is disposed within the valve body, and the actuator is drivenly connected to the ball via a valve stem. The integrated ball valve further includes a solenoid valve and a first piston cylinder and a second piston cylinder located on both sides of the valve stem. A first piston is disposed within the first piston cylinder, and a second piston is disposed within the second piston cylinder. The first piston and the second piston are respectively engaged with the valve stem. The solenoid valve is used to connect the high-pressure side of the valve body to the first piston cylinder or the second piston cylinder to activate it.

[0009] This application uses a solenoid valve to guide the medium pressure on the high-pressure side of the valve to the first and / or second piston cylinders, which then drive the corresponding piston. The piston engages with the valve stem, converting the enormous linear thrust generated by the medium pressure into torque that drives the ball to rotate. This is equivalent to providing a "hydraulic booster" for the actuator, enabling a smaller power actuator to easily operate large-diameter valves with high pressure differentials, significantly reducing the actuator's energy consumption and manufacturing costs. The piston cylinder, solenoid valve, and other booster components are compactly integrated with the valve body, eliminating the need for bulky external booster devices, saving space and making the entire valve structure very compact. The booster energy comes directly from the medium, eliminating the need for an external hydraulic station or compressed air or other auxiliary energy sources, simplifying system configuration, reducing installation and maintenance complexity, and solving the problems of large size, weight, and long opening and closing times in existing high-pressure integrated ball valves.

[0010] Preferably, the valve body is provided with a front pressure port and a rear pressure port on both sides of the ball, the solenoid valve is a three-position four-way structure, the solenoid valve is connected to the front pressure port through the front pressure pipe, the solenoid valve is connected to the rear pressure port through the rear pressure pipe, the solenoid valve is connected to the first piston cylinder through the opening pressure pipe, and the solenoid valve is connected to the second piston cylinder through the closing pressure pipe.

[0011] This setup derives energy from the medium and uses it to drive the valve itself, forming a self-circulating closed-loop system that eliminates the need for an external hydraulic power source, minimizing energy loss and maximizing efficiency. The pressure difference between the valve's upstream and downstream sides captures the potential energy of the fluid in the pipeline in real time, providing a free and perfectly matched energy source to drive the assist piston. The greater the pressure difference between the upstream and downstream sides of the valve, the greater the torque required to open and close the valve, and the greater the assistance provided by the system, achieving a perfect "on-demand assistance" match.

[0012] Preferably, the solenoid valve is connected to the first end of the first piston cylinder and the second end of the second piston cylinder via an opening pressure pipe, and the solenoid valve is connected to the second end of the first piston cylinder and the first end of the second piston cylinder via a closing pressure pipe.

[0013] This configuration ensures that the first and second piston cylinders always operate simultaneously and in opposite directions. The two engagement points on the valve stem generate equal and opposite forces, forming a torque couple. This means the valve stem bears only pure torque, without any lateral bending moment, significantly reducing friction and wear, and ensuring smooth valve stem movement and a long service life. Furthermore, compared to single-cylinder drive, under the same oil pressure, the total effective working area of ​​the two piston cylinders is doubled, and the total thrust generated is also nearly doubled. This allows for driving valves with higher torque or faster valve opening and closing speeds with lower system pressure.

[0014] Preferably, the valve stem is equipped with a gear, the first piston has a first rack on the side near the gear, and the second piston has a second rack on the side near the gear. The first and second racks are symmetrically arranged on both sides of the gear. This arrangement drives the first and second pistons to move by introducing high pressure from the medium, thereby causing the valve stem to rotate to open or close the ball. The structure is simple and the transmission is stable and reliable.

[0015] Preferably, the first rack and the second rack are parallel to each other and are centrally symmetrical with respect to the central axis of the valve stem. This arrangement ensures that the movement of the first rack and the second rack will not interfere with each other, but will instead drive the valve stem to rotate based on the pressure difference between the two ends of the first piston cylinder and the two ends of the second piston cylinder, corresponding to the pressure difference between the inlet and outlet ends of the valve.

[0016] Preferably, the lengths of the first rack and the second rack are L1 and L2, respectively, and the circumference of the gear is L3, where L1 = L2 = 0.25 * L3. This arrangement ensures that the length of the rack exactly meets the requirement of the gear rotating 90°, eliminating unnecessary travel and making the entire transmission mechanism compact, minimizing size and weight while fulfilling functional requirements.

[0017] Preferably, the pressure taps before, after, and when the valve is closed are all metal pipes assembled by welding. This configuration facilitates equipment miniaturization, ensures that sealing performance does not degrade over time, adapts to high-pressure media, and provides stable and reliable operation. The welding process connects the disparate pipes and valve body into a rigid whole, effectively suppressing pipeline vibration and preventing fatigue fracture caused by vibration, making it particularly suitable for use in industrial environments with high vibration.

[0018] Preferably, the valve body is integrally cast or forged. This design completely eliminates the possibility of external leakage points easily forming at the connection points of existing two-piece or three-piece ball valves, making it particularly suitable for flammable, explosive, toxic, or expensive media conditions; ensuring that the valve body has extremely high structural strength and rigidity, better withstanding pipeline stress, thermal stress caused by temperature changes, and high-pressure conditions, thereby protecting the integrity of the internal seal.

[0019] Preferably, the lower end of the valve stem is fitted with the ball for limiting, and the upper end of the valve stem is connected to the actuator. This arrangement allows the torque output by the actuator to be directly transmitted to the ball through the valve stem without any intermediate links, resulting in high transmission efficiency and rapid response. This ensures that the valve can quickly and accurately execute opening or closing commands; it also precisely controls the rotation of the ball by 90° to achieve full opening, full closing, or adjustment of the flow channel, ensuring accurate sealing position and avoiding sealing failure or equipment damage caused by over-opening or over-closing.

[0020] Preferably, the actuator is electric or electro-hydraulic. This configuration enables extremely precise control of the valve stem rotation angle, with an accuracy of up to 0.1°, achieving fine adjustment of the valve opening; the huge output torque and powerful load capacity can drive the valve operation under large-diameter, high-pressure differential conditions.

[0021] Compared with the prior art, the integrated ball valve of the present invention has the following advantages: 1) By setting a piston assembly at the valve body and introducing medium pressure, the driving force is formed by the pressure difference of the medium, realizing the dual driving effect of medium pressure and actuator; 2) The driving force formed by the medium pressure difference can be automatically adjusted according to the pressure difference on both sides of the ball. When the pressure difference on both sides of the ball increases, the required driving force increases accordingly. At this time, the driving force formed by the medium pressure difference in the piston cylinder also increases, realizing the opening and closing of the valve under different pressure differences, which is especially suitable for the operating conditions of valve pressure difference changes; 3) By converting the medium pressure into driving force, the driving torque of the actuator can be reduced, thereby reducing the size, weight and output power of the actuator, which is especially suitable for installation in confined spaces; 4) The solenoid valve used in the present invention is a three-position four-way structure. Its initial position is that the pressure inlet pipes are not connected. At this time, the medium in the piston cylinder cannot flow, and the piston position remains stationary, realizing the hydraulic self-locking function of the valve stem and the ball. Attached Figure Description

[0022] Figure 1 This is an overall schematic diagram of the integrated ball valve described in an embodiment of the present invention;

[0023] Figure 2 This is a schematic diagram of the integrated ball valve described in an embodiment of the present invention after being cut across the piston cylinder;

[0024] Figure 3 This is a schematic diagram of the integrated ball valve described in an embodiment of the present invention after being cut across the valve body.

[0025] Explanation of reference numerals in the attached figures:

[0026] 1-Valve body, 201-Pre-valve pressure tap, 202-Post-valve pressure tap, 3-Solenoid valve, 401-Close valve pressure tap, 402-Open valve pressure tap, 501-First piston cylinder, 502-Second piston cylinder, 6-Control line, 7-Actuator, 801-First piston, 802-Second piston, 9-Valve stem, 1001-Pre-valve pressure tap, 1002-Post-valve pressure tap, 11-Ball. Detailed Implementation

[0027] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Without conflict, the technical features of the embodiments of the present invention can be combined with each other.

[0028] Existing electric ball valves use an actuator to drive the valve stem to open or close the valve. Under low to medium pressure conditions, the torque required for valve opening and closing is relatively small, and the actuator output is also relatively small, allowing the ball valve size and opening / closing time to meet requirements. However, for rapid (≤5s) opening and closing of the ball valve under high pressure (≥900Lb) conditions, if the actuator output remains unchanged, rapid valve opening and closing cannot be achieved. Significantly increasing the actuator output would result in a substantial increase in the overall valve size, making it difficult to meet installation requirements in confined spaces. Therefore, the applicant proposes the following technical solution:

[0029] like Figure 1-3 As shown, an integrated ball valve includes a valve body 1 and an actuator 7. A ball 11 is disposed inside the valve body 1. The actuator 7 is connected to the ball 11 via a valve stem 9 and is used to drive the ball 11 to rotate. The integrated ball valve also includes a solenoid valve 3 and a first piston cylinder 501 and a second piston cylinder 502 located on both sides of the valve stem 9. A first piston 801 is disposed inside the first piston cylinder 501, and a second piston 802 is disposed inside the second piston cylinder 502. The first piston 801 and the second piston 802 are respectively engaged with the valve stem 9. The solenoid valve 3 is used to selectively connect the high-pressure side of the valve body 1 to the first piston cylinder 501 and / or the second piston cylinder 502.

[0030] This design, by incorporating a piston assembly on the valve body 1, introduces high-pressure media into the first piston cylinder 501 and / or the second piston cylinder 502. The pressure difference of the media generates a driving force within the corresponding piston assembly, which, together with the actuator 7, drives the rotation of the valve stem 9 to achieve rapid valve opening and closing. This solves the problems of large size and weight, and long opening and closing times in existing high-pressure integrated ball valves, making it particularly suitable for critical valve applications in marine or confined spaces. Compared to the previous ball valve, the integrated ball valve described in this application reduces the opening and closing time to 20-30% of the original time for the same size, significantly shortening the opening and closing time.

[0031] As an example of the present invention, the valve body 1 is provided with a front pressure port 1001 and a rear pressure port 1002 on both sides of the ball 11, respectively. The solenoid valve 3 is a three-position four-way structure. The solenoid valve 3 is connected to the front pressure port 1001 through the front pressure pipe 201. The solenoid valve 3 is connected to the rear pressure port 1002 through the rear pressure pipe 202. The solenoid valve 3 is connected to the first piston cylinder 501 through the valve opening pressure pipe 402. The solenoid valve 3 is connected to the second piston cylinder 502 through the valve closing pressure pipe 401.

[0032] This setup can introduce the high pressure of the medium into the first piston cylinder 501, thereby cooperating with the actuator 7 to achieve rapid valve closure, or introduce the high pressure of the medium into the second piston cylinder 502, thereby cooperating with the actuator 7 to achieve rapid valve opening. It has a simple structure and occupies little space.

[0033] Preferably, the solenoid valve 3 is connected to the first end of the first piston cylinder 501 and the second end of the second piston cylinder 502 respectively via the valve opening pressure pipe 402, and the solenoid valve 3 is connected to the second end of the first piston cylinder 501 and the first end of the second piston cylinder 502 respectively via the valve closing pressure pipe 401.

[0034] This configuration ensures that the first piston cylinder 501 and the second piston cylinder 502 always operate simultaneously and in opposite directions. The two engagement points on the valve stem 9 generate forces of equal magnitude and opposite direction, forming a torque couple. This allows the valve stem 9 to bear only pure torque, without any lateral bending moment, significantly reducing friction and wear, and ensuring smooth movement and a long service life for the valve stem 9. Furthermore, compared to single-cylinder drive, under the same oil pressure, this configuration doubles the total effective working area of ​​the two piston cylinders, and nearly doubles the total thrust. This allows for driving valves with higher torque using less system pressure or enabling faster valve opening and closing speeds.

[0035] Specifically, when the solenoid valve 3 is in position I, the pressure pipe 201 before the valve is connected to the pressure pipe 401 for closing the valve, and the pressure pipe 202 after the valve is connected to the pressure pipe 402 for opening the valve. If it is in position II, the pressure pipe 201 before the valve is connected to the pressure pipe 402 for opening the valve, and the pressure pipe 202 after the valve is connected to the pressure pipe 401 for closing the valve. If it is in position III, the pressure pipe 201 before the valve, the pressure pipe 202 after the valve, the pressure pipe 401 for closing the valve, and the pressure pipe 402 for opening the valve are not connected.

[0036] As an example of the present invention, the solenoid valve 3 is connected to the actuator 7 via a control line 6. This arrangement allows the control signal to be provided by the actuator 7, which provides instructions to control the position switching of the solenoid valve 3 via the control line 6, ensuring that the driving force generated by the medium pressure difference is aligned with the driving force provided by the actuator 7.

[0037] As an example of the present invention, the valve stem 9 is provided with a gear, the first piston 801 has a first rack on the side near the gear, and the second piston 802 has a second rack on the side near the gear. The first rack and the second rack are symmetrically arranged on both sides of the gear. This arrangement drives the first piston 801 and / or the second piston 802 to move by introducing high pressure of the medium, thereby driving the valve stem 9 to rotate to open or close the ball 11. The structure is simple and the transmission is stable and reliable. As an example of the present invention, the gear is located on the outer periphery of the valve stem 9 and is integrally formed with the valve stem.

[0038] Preferably, the first rack and the second rack are parallel to each other and centrally symmetrical with respect to the central axis of the valve stem 9. This arrangement ensures that the movement of the first rack and the second rack will not interfere with each other, but will instead drive the valve stem 9 to rotate based on the pressure difference between the two ends of the first piston cylinder 501 and the two ends of the second piston cylinder 502, corresponding to the pressure difference between the inlet and outlet ends of the valve. That is, when the first end of the first rack moves closer to the gear towards the second end, the second end of the second rack moves closer to the gear towards the first end.

[0039] As an example of the present invention, the lengths of the first rack and the second rack are L1 and L2, respectively, and the circumference of the gear is L3, where L1 = L2 = 0.25 * L3. This arrangement ensures that the length of the rack exactly meets the requirement of the gear rotating 90°, eliminating unnecessary travel and making the entire transmission mechanism compact. While fulfilling the functional requirements, the size and weight are minimized. Due to the bidirectional symmetrical motion, there is meshing force between the gear and the rack in both directions, which helps reduce unilateral wear and extend the service life of the mechanism.

[0040] Preferably, the pressure difference between the medium on both sides of the ball 11 is at least 900 Lb. At this point, the torque generated by the actuator 7 is relatively small, while this application can generate force on the valve stem 9 through the first piston cylinder 501 or the second piston cylinder 502, causing it to open or close quickly. In fact, this application can be used for any medium pressure. When the medium pressure is high, the integrated ball valve of this application generates a large driving force through the solenoid valve 3; while when the medium pressure is low, the required opening and closing torque is small, and the driving force generated by the solenoid valve 3 can compensate for the torque shortfall.

[0041] As an example of the present invention, the pre-valve pressure tap 201, post-valve pressure tap 202, valve-closing pressure tap 401, and valve-opening pressure tap 402 are all metal pipes assembled by welding. This arrangement contributes to the miniaturization of the equipment, ensures that the sealing performance does not degrade over time, is adaptable to high-pressure media, and operates stably and reliably. The welding process connects the dispersed pipes and valve body 1 into a rigid whole, effectively suppressing pipeline vibration and preventing fatigue fracture caused by vibration, making it particularly suitable for use in industrial environments with high vibration.

[0042] As an example of the present invention, the valve body 1 is integrally cast or forged. This design completely eliminates the possibility of external leakage points easily forming at the connection points of existing two-piece or three-piece ball valves, making it particularly suitable for flammable, explosive, toxic, or expensive media conditions; it ensures that the valve body 1 has extremely high structural strength and rigidity, better withstanding pipeline stress, thermal stress caused by temperature changes, and high-pressure conditions, thereby protecting the integrity of the internal seal; at the same time, the flow channel wall of the valve body 1 is continuous and smooth, reducing fluid turbulence and resistance, achieving lower pressure loss and higher flow coefficient, resulting in significant energy savings.

[0043] As an example of the present invention, the lower end of the valve stem 9 is fitted with the ball 11 for limiting, and the upper end of the valve stem 9 is connected to the actuator 7. This arrangement allows the torque output by the actuator 7 to be directly transmitted to the ball 11 through the valve stem 9 without any intermediate links, resulting in high transmission efficiency and rapid response. This ensures that the valve can quickly and accurately execute opening or closing commands; it also precisely controls the rotation of the ball 11 by 90° to achieve full opening, full closing, or adjustment of the flow channel, ensuring accurate sealing position and avoiding sealing failure or equipment damage caused by over-opening or over-closing.

[0044] The actuator 7 is either electric or electro-hydraulic. This setup can control the rotation angle of the valve stem 9 with extremely high precision, up to 0.1°, enabling fine adjustment of the valve opening; its huge output torque and powerful load capacity can drive valves operating under large-diameter, high-pressure differential conditions.

[0045] In use, the solenoid valve 3 is initially in position III, meaning all pressure pipes are disconnected. At this time, the medium in the first piston cylinder 501 and the second piston cylinder 502 cannot flow, and the corresponding positions of the first piston 801 and the second piston 802 remain stationary, thus providing a hydraulic locking function for the ball 11. When it is necessary to close the ball 11, the actuator 7 sends a command to the solenoid valve 3 to move it to position I while outputting the valve-closing torque. At this time, the valve-front pressure pipe 201 is connected to the valve-closing pressure pipe 401. The pressure tap 202 after the valve is connected to the pressure tap 402 after the valve is opened, and the valve closing torque is formed by the medium pressure, realizing the dual driving effect of medium pressure and actuator 7. When it is necessary to open the ball 11, the actuator 7 outputs the valve opening torque and sends a command to the solenoid valve 3 to move to position II. At this time, the pressure tap 201 before the valve is connected to the pressure tap 402 after the valve is opened, and the pressure tap 202 after the valve is connected to the pressure tap 401 after the valve is closed, and the valve opening torque is formed by the medium pressure, realizing the dual driving effect of medium pressure and actuator 7.

[0046] Conversely, when the medium flows from the rear flange to the front flange, and when the ball 11 needs to be closed, the actuator 7 outputs the valve closing torque and simultaneously sends a command to the solenoid valve 3 to move it to position II. At this time, the valve front pressure pipe 201 is connected to the valve opening pressure pipe 402, and the valve rear pressure pipe 202 is connected to the valve closing pressure pipe 401. The valve closing torque is formed by the medium pressure. When the ball 11 needs to be opened, the actuator 7 outputs the valve opening torque and simultaneously sends a command to the solenoid valve 3 to move it to position I. At this time, the valve front pressure pipe 201 is connected to the valve closing pressure pipe 401, and the valve rear pressure pipe 202 is connected to the valve opening pressure pipe 402. The valve closing torque is formed by the medium pressure.

[0047] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. An integrated ball valve, comprising a valve body (1) and an actuator (7), wherein a ball (11) is disposed within the valve body (1), and the actuator (7) is drivenly connected to the ball (11) via a valve stem (9), characterized in that, The integrated ball valve also includes a solenoid valve (3), a first piston cylinder (501), and a second piston cylinder (502). The first piston cylinder (501) is provided with a first piston (801), and the second piston cylinder (502) is provided with a second piston (802). The first piston (801) and the second piston (802) are respectively engaged with the valve stem (9). The solenoid valve (3) is used to introduce the high-pressure side medium pressure of the valve body (1) into the first piston cylinder (501) and / or the second piston cylinder (502) to make it actuate.

2. The integrated ball valve according to claim 1, characterized in that, The valve body (1) is provided with a front pressure port (1001) and a rear pressure port (1002) on both sides of the ball (11). The solenoid valve (3) is a three-position four-way structure. The solenoid valve (3) is connected to the front pressure port (1001) through the front pressure pipe (201). The solenoid valve (3) is connected to the rear pressure port (1002) through the rear pressure pipe (202). The solenoid valve (3) is connected to the first piston cylinder (501) through the opening pressure pipe (402). The solenoid valve (3) is connected to the second piston cylinder (502) through the closing pressure pipe (401).

3. The integrated ball valve according to claim 2, characterized in that, The solenoid valve (3) is connected to the first end of the first piston cylinder (501) and the second end of the second piston cylinder (502) respectively through the valve opening pressure pipe (402), and the solenoid valve (3) is connected to the second end of the first piston cylinder (501) and the first end of the second piston cylinder (502) respectively through the valve closing pressure pipe (401).

4. The integrated ball valve according to claim 1, characterized in that, The first piston cylinder (501) and the second piston cylinder (502) are located on both sides of the valve stem (9). The valve stem (9) is provided with a gear. The first piston (801) is provided with a first rack on the side close to the gear, and the second piston (802) is provided with a second rack on the side close to the gear. The first rack and the second rack are symmetrically arranged on both sides of the gear.

5. The integrated ball valve according to claim 4, characterized in that, The first rack and the second rack are parallel to each other and are centrally symmetrical with respect to the central axis of the valve stem (9).

6. The integrated ball valve according to claim 5, characterized in that, The lengths of the first rack and the second rack are L1 and L2, respectively, and the circumference of the gear is L3, where L1=L2=0.25*L3.

7. The integrated ball valve according to claim 1, characterized in that, The valve pre-pressure pipe (201), valve post-pressure pipe (202), valve closing pressure pipe (401), and valve opening pressure pipe (402) are all metal pipes assembled by welding.

8. The integrated ball valve according to claim 1, characterized in that, The valve body (1) is integrally cast or forged.

9. The integrated ball valve according to claim 1, characterized in that, The lower end of the valve stem (9) is fitted to the ball (11) for limiting, and the upper end of the valve stem (9) is connected to the actuator (7).

10. The integrated ball valve according to claim 9, characterized in that, The actuator (7) is electric or electro-hydraulic.

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