A large differential pressure operated semi-sphere valve

Abstract

The application relates to the technical field of ball valves, in particular to a large-pressure-difference-operated half-ball valve, which comprises a valve body, flanges are fixedly connected to two ends of the valve body, an upper pressure cover is fixedly connected in communication with the top of the valve body, an upper actuator is fixedly connected to the top of the upper pressure cover, and a lower shaft sleeve is fixedly connected in communication with the bottom of the valve body; through the design of staged pressure reduction and step-by-step opening and closing, the actuator load is significantly reduced, the service life of the valve is prolonged, and the manufacturing cost is reduced; specifically, channel two is first opened to balance the pressure of the upstream and downstream, then channel one is opened, the staged pressure reduction is realized, the medium force required to be overcome by the actuator is greatly reduced, meanwhile, double actuators are adopted to replace a single actuator, two small-torque actuators are used to control two valve cores, the total cost is much lower than that of a single large-torque actuator, and two valve seat rings are independently arranged, bidirectional sealing is realized by matching corresponding half spheres and O-shaped small ball valve cores, and the sealing reliability is effectively improved.

Description

Technical Field

[0001] This application relates to the field of ball valve technology, and in particular to a semi-ball valve for operation with large differential pressure. Background Technology

[0002] A hemispherical valve is a type of valve that uses a rotating hemispherical valve core to open or close fluid or regulate flow. It belongs to the category of rotary valves. Its core structure includes a valve body, valve seat, hemispherical valve core, and actuator. By rotating the valve core 90 degrees, the pipeline can be quickly opened or closed, achieving efficient fluid control. Hemispherical valves operating under high differential pressure usually adopt a double eccentric or unidirectional eccentric design, which allows the valve core to quickly disengage from or contact the valve seat during the opening and closing process, reducing the operating torque by 30% to 50% compared to ordinary ball valves and extending the life of the actuator.

[0003] A prior art patent application with publication number CN221443372U discloses a top-mounted eccentric hemispherical valve, including a valve body, a valve seat, and a hemisphere. The valve body has a first port and a second port for water inlet and outlet. A groove for accommodating the valve seat is provided within the valve body, forming a receiving space between the groove and the valve seat. A sealing element is installed within the receiving space. Two elastic components are symmetrically arranged between the inner side of the valve seat and the valve body. A groove for accommodating the elastic components is provided at one end of the valve body near the inner side of the valve seat. One end of the elastic component abuts against the end face of the valve body near the inner side of the valve seat, and the other end abuts against the inner side of the valve seat. A limiting component for limiting the valve seat is provided between the outer end of the valve seat and the valve body. The hemisphere is rotatably connected to the inside of the valve body and is used to close and open the valve seat. This ball valve adopts a micro-floating valve seat structure, which is not only suitable for high-pressure systems but also achieves bidirectional full differential pressure sealing requirements.

[0004] Existing high-pressure differential valves mostly use a single actuator to drive the valve core. During the opening and closing process, they need to overcome the enormous force of the medium and the differential pressure load, resulting in high actuator torque requirements, high cost, easy wear, and short life. In addition, the valve opening and closing impact is large under high-pressure differential conditions, which can easily cause damage to the sealing surface and leakage.

[0005] Therefore, this application provides a ball valve for operation with large differential pressure. Summary of the Invention

[0006] The purpose of this application is to solve at least one technical problem raised in the background art.

[0007] This application provides a large differential pressure operating hemispherical valve, comprising: a valve body, both ends of which are fixedly connected to flanges; an upper pressure cover is fixedly connected to the top of the valve body; an upper actuator is fixedly connected to the top of the upper pressure cover; a lower bushing is fixedly connected to the bottom of the valve body; and a lower actuator is fixedly connected to the bottom of the lower bushing. It also includes a graded pressure reducing mechanism and a safety locking mechanism. The graded pressure reducing mechanism includes a hemispherical body, an O-shaped small ball, a first channel, a second channel, an upper valve stem, and a lower valve stem. The top of the hemispherical body is fixedly connected to the end of the upper valve stem, and the bottom of the hemispherical body is rotatably sleeved onto the end of the lower valve stem. The top of the O-shaped small ball is rotatably connected to the end of the upper valve stem, and the bottom of the O-shaped small ball is fixedly connected to the end of the lower valve stem. The outer ends of the upper and lower valve stems are respectively fixed to the upper and lower actuators. The valve body has a first channel in the middle, and the hemispherical body has a second channel in the middle.

[0008] By adopting the above technical solution, the impact and wear problems caused by traditional single valve core opening and closing valves are solved. Since the lower actuator operates the O-ring ball to connect the upstream and downstream, the pressure difference between the upstream and downstream is balanced. In this way, during the entire opening process, the lower actuator only needs to overcome the medium force in channel one, the spring preload force, the friction force of the first O-ring and the friction force of the lower valve stem, and the upper valve stem needs to overcome the friction force, the friction force of the first valve seat ring and the spring preload force. Therefore, the upper and lower actuators can be downgraded by several levels, saving costs, and the service life of the valve is also greatly improved.

[0009] Preferably, the graded pressure reduction mechanism further includes a first valve seat cover fixed to the edge of the valve body, and the end of the first valve seat cover is elastically connected to a first support ring.

[0010] Preferably, the first support ring abuts against the inner cavity of the valve body through a plurality of first O-rings, and the end of the first support ring abuts against the outer wall of the hemisphere through a first valve seat ring.

[0011] By adopting the above technical solution, the problem of the impact of the large pressure difference on the system when the valve is opened is solved. During the valve closing process, the upper actuator is closed first, driving the upper valve stem to close the hemisphere. At this time, because the second channel is still in the open position and the upstream and downstream are connected, there is no pressure difference, and the closing is effortless. Then the lower actuator is closed. The lower actuator overcomes the medium force, spring preload, friction of the second O-ring and friction of the lower valve stem at the second channel to close the valve, effectively adapting to the operating environment of large pressure difference.

[0012] Preferably, a second valve seat cover is fixed to the inner edge of the hemisphere, and a second support ring is elastically connected to the middle of the second valve seat cover. The outer wall of the second support ring abuts against the second valve seat cover through a second O-ring.

[0013] Preferably, a second valve seat ring is fixed to the end of the second support ring, and the end of the second valve seat ring abuts against the outer wall of the O-shaped sphere.

[0014] By adopting the above technical solution, the problem of potential media leakage under different pressure conditions is solved. When the system pressure changes, the elastic characteristics of the second support ring allow it to adapt to different pressure conditions and maintain tight contact with the second valve seat gland, while providing the necessary preload. The second valve seat ring forms a seal with the O-ring when the valve is closed, effectively preventing media leakage. The elastic connection of the second support ring allows it to be flexibly adjusted under high pressure changes to adapt to different working environments. The combination design of the O-ring and the second valve seat ring provides additional safety protection when the valve is closed, ensuring that the media will not leak unexpectedly and enhancing the safety of the system.

[0015] Preferably, the safety locking mechanism includes a first slider fixed to the top of the O-shaped ball, and the end of the upper valve stem is provided with a first groove, in which the first slider is slidably connected.

[0016] Preferably, the upper pressure cover has a second sliding groove in the middle, and the upper valve stem is slidably connected to the inner wall of the second sliding groove via a second slider.

[0017] Preferably, the second slider and the first slider are axially aligned, and the lengths of the first groove and the second groove are equal.

[0018] By adopting the above technical solution, the problem of avoiding deviation or reversal of the operation sequence during the movement of the upper and lower valve stems is solved. The precise cooperation of the first and second sliders in their respective grooves ensures the safe, stable and smooth operation of the valve during operation. The docking and axial alignment design between the slider and the groove enhances the sealing performance and response speed, and reduces friction and wear, thereby improving the working efficiency and service life of the valve. This design enables the valve to maintain high performance even under high pressure and long-term operation, and reduces the maintenance frequency.

[0019] Preferably, an L-shaped indicator rod is fixedly connected to the lower end of the lower valve stem, and a pointer is vertically provided in the middle of the L-shaped indicator rod.

[0020] Preferably, the outer wall of the L-shaped indicator rod is slidably fitted with an arc-shaped groove plate, and the side wall of the arc-shaped groove plate is fixed to the outer wall of the lower bushing.

[0021] By adopting the above technical solution, the problem of not being able to intuitively see the rotation position of the lower valve stem is solved. An L-shaped indicator rod is fixedly connected to the lower end of the lower valve stem. The L-shaped indicator rod serves to connect the lower valve stem to the indicating device. Through this connection method, the lower valve stem can drive the L-shaped indicator rod to make corresponding displacements during the movement, thereby achieving the purpose of indicating the valve position or status. The arc-shaped groove plate is fixedly connected to the outer wall of the lower bushing. This fixed design effectively prevents the arc-shaped groove plate from shifting or moving asymmetrically during use.

[0022] In summary, this application includes at least one of the following beneficial technical effects:

[0023] 1. The large differential pressure operation hemispherical valve described in this application significantly reduces actuator load, extends valve service life, and reduces manufacturing costs through a staged pressure reduction and step-by-step opening and closing design. Specifically, it achieves staged pressure reduction by first opening channel two to balance upstream and downstream pressures, and then opening channel one, which greatly reduces the medium force that the actuator needs to overcome. At the same time, it uses dual actuators instead of a single actuator, with two low-torque actuators controlling two valve cores respectively. Its total cost is much lower than that of a single high-torque actuator. Furthermore, the two valve seat rings are set independently, and with the corresponding hemispherical and O-type small ball valve cores, bidirectional sealing is achieved, effectively improving sealing reliability.

[0024] 2. The hemispherical valve for high differential pressure operation described in this application solves the problem of the O-shaped ball and the hemispherical valve needing to open sequentially by setting an L-shaped indicator rod and two sliders. The L-shaped indicator rod is located at the opening position of the O-shaped ball and can accurately indicate whether the second channel is open or not. At the same time, the two sliders can play a limiting and locking role. If the lower actuator malfunctions and the second channel fails to open as expected, the upper valve stem cannot be directly rotated to open the first channel by the limiting and locking of the first slider. This avoids excessive load on the upper valve stem, which would affect the service life of the valve. It achieves the dual effect of direct external observation and internal locking, improving the efficiency of fault diagnosis and the safety of valve use. Attached Figure Description

[0025] Figure 1 This is a cross-sectional structural diagram of this application;

[0026] Figure 2 yes Figure 1 A magnified view of part A in the middle;

[0027] Figure 3 yes Figure 1 A magnified view of part B in the middle section;

[0028] Figure 4 This is a three-dimensional structural diagram of this application;

[0029] Figure 5 This is a schematic diagram of the valve stem and O-ring in this application;

[0030] Figure 6 This is a structural schematic diagram of the valve stem and O-ring in this application;

[0031] Figure 7 This is a schematic diagram of the exploded structure of this application;

[0032] Figure 8 This is a schematic diagram of the structure of the second slider and the second slide groove of this application.

[0033] Explanation of reference numerals in the attached drawings: 1. Flange; 2. Valve body; 3. Upper gland; 4. Lower bushing; 5. Upper actuator; 6. Lower actuator; 7. Staged pressure reduction mechanism; 71. Hemisphere; 72. First valve seat ring; 73. First support ring; 74. First O-ring; 75. First valve seat gland; 76. Small O-ring; 77. Second valve seat ring; 78. Second support ring; 79. Second O-ring; 710. Second valve seat gland; 711. Channel 1; 712. Channel 2; 713. Upper valve stem; 714. Lower valve stem; 8. Safety locking mechanism; 81. L-shaped indicator bar; 82. Arc-shaped groove plate; 83. First slide groove; 84. First slider; 85. Second slider; 86. Second slide groove. Detailed Implementation

[0034] The following is in conjunction with the appendix Figure 1 To be continued Figure 8 This application will be described in further detail below.

[0035] Example 1

[0036] Please refer to the following carefully. Figure 1 , Figure 4 , Figure 5 , Figure 6 A ball valve for large differential pressure operation includes a valve body 2, flanges 1 are fixedly connected to both ends of the valve body 2, an upper pressure cover 3 is fixedly connected to the top of the valve body 2, an upper actuator 5 is fixedly connected to the top of the upper pressure cover 3, a lower shaft sleeve 4 is fixedly connected to the bottom of the valve body 2, and a lower actuator 6 is fixedly connected to the bottom of the lower shaft sleeve 4.

[0037] It also includes a graded pressure reduction mechanism 7 and a safety locking mechanism 8. The graded pressure reduction mechanism 7 includes a hemisphere 71, an O-shaped ball 76, a channel one 711, a channel two 712, an upper valve stem 713, and a lower valve stem 714.

[0038] The top of the hemisphere 71 is fixed to the middle of the upper valve stem 713, and the bottom of the hemisphere 71 is rotatably sleeved on the middle of the lower valve stem 714. The top of the O-shaped ball 76 is rotatably connected to the end of the upper valve stem 713, and the bottom of the O-shaped ball 76 is fixed to the end of the lower valve stem 714. The outer ends of the upper valve stem 713 and the lower valve stem 714 are respectively fixed to the upper actuator 5 and the lower actuator 6. A channel 1 711 is opened in the middle of the valve body 2, and a channel 2 712 is opened in the middle of the hemisphere 71.

[0039] Specifically, in the initial state, the valve is closed, with channels 1 (711) and 2 (712) completely sealed. The upper valve stem (713) and lower valve stem (714) are driven by the upper actuator (5) and lower actuator (6), respectively. When the valve begins to open, the upper actuator (5) first drives the upper valve stem (713), causing the hemisphere (71) to open channel 1 (711). Simultaneously, the lower actuator (6) drives the lower valve stem (714), causing the O-ring (76) to rotate, gradually opening channel 2 (712). During this process, the pressure across the valve gradually equalizes. Since channel 2 (712) is partially open, the pressure difference is alleviated, preventing the impact of a sudden, excessive pressure difference on the valve and system. After pressure equalization, the upper valve stem (713) continues to rotate the hemisphere (71) until channel 1 (711) is fully opened. At this point, the upstream and downstream channels are completely connected, the valve is fully open, and the medium can flow freely. When it is necessary to close the valve, the lower actuator (6) first drives the lower valve stem (714) to close the O-ring (76) and gradually close channel 2 (712). As the O-shaped ball 76 closes, the valve begins to slow the flow. Finally, the upper valve stem 713 drives the hemispherical body 71 to close the channel 711, thus completely closing the valve and stopping the flow of the medium. Through staged operation, the energy consumption and pressure loss of the valve are reduced, while the shock wave of liquid or gas is also reduced, thereby reducing the energy loss of the system and improving the overall system efficiency. The upper actuator 5 and the lower actuator 6 can be driven by electric or pneumatic means according to the working conditions, making them more adaptable. Compared with traditional single actuators, this application can reduce the torque specification of the actuator, save costs, reduce the impact and wear during valve opening and closing, improve the sealing life, and has a compact structure and high reliability. It is suitable for harsh high pressure differential environments and can be achieved through existing valve manufacturing processes, making it easy to promote.

[0040] Please refer to this carefully. Figure 1 , Figure 2 The graded pressure reduction mechanism 7 also includes a first valve seat cover 75 fixed to the edge of the valve body 2. The end of the first valve seat cover 75 is elastically connected to a first support ring 73. The first support ring 73 abuts against the inner cavity of the valve body 2 through a plurality of first O-rings 74, and the end of the first support ring 73 abuts against the outer wall of the hemisphere 71 through a first valve seat ring 72.

[0041] Specifically, the first valve seat gland 75 is fixedly connected to the edge of the valve body 2, serving to compress and stabilize the pressure-reducing structure. Its end is connected to the first support ring 73 via an elastic connection, forming a structure that can be flexibly adjusted under pressure changes. The first support ring 73 is in close contact with the inner cavity of the valve body 2 through several first O-rings 74, ensuring the valve's sealing performance. These O-rings provide good sealing performance, preventing media leakage and ensuring the normal operation of the system. The end of the first support ring 73 contacts the outer wall of the hemisphere 71 through the first valve seat ring 72. This structural design ensures that the hemisphere 71 can maintain a stable position under pressure, while controlling the pressure drop process through the elastic connection and the sealing performance of the O-rings. As the valve gradually opens, the pressure is gradually relieved, avoiding the impact of a sudden large pressure difference on the system.

[0042] Please refer to this carefully. Figure 1 , Figure 3 A second valve seat cover 710 is fixedly connected to the inner edge of the hemisphere 71. A second support ring 78 is elastically connected to the middle of the second valve seat cover 710. The outer wall of the second support ring 78 abuts against the second valve seat cover 710 through a second O-ring 79. A second valve seat ring 77 is fixedly connected to the end of the second support ring 78. The end of the second valve seat ring 77 abuts against the outer wall of the O-ring sphere 76.

[0043] Specifically, when system pressure changes, the elastic properties of the second support ring 78 allow it to adapt to different pressure conditions while maintaining tight contact with the second valve seat gland 710, providing necessary support. The second valve seat ring 77 forms a seal with the O-ring 76 when the valve is closed, effectively preventing media leakage. The elastic connection of the second support ring 78 allows for flexible adjustment under high pressure changes, adapting to different working environments. This design reduces shocks caused by instantaneous pressure changes, improving valve reliability. The combination of the O-ring 76 and the second valve seat ring 77 provides additional safety when the valve is closed, ensuring that the media will not leak unexpectedly, enhancing system safety. The overall structure ensures good sealing and adaptability, while improving valve safety and service life.

[0044] The working principle of this embodiment is as follows:

[0045] Initially, the valve is closed. During valve opening, when there is pressure upstream and no medium downstream, the pressure difference between upstream and downstream is large. The lower actuator 6 needs to be opened first, rotating the lower valve stem 714 to open channel two 712 via the O-ring 76. At this point, the upstream medium enters the downstream through channel two 712, balancing the pressure difference. Next, the upper actuator 5 is opened, driving the upper valve stem 713 to open the hemispherical body 71, connecting channel one 711 to the upstream. This links the upstream and downstream, completing the valve opening operation. During this process, because the lower actuator 6 operates the O-ring 76 to connect the upstream and downstream and balance the pressure difference, the lower actuator 6 only needs to overcome the medium force in channel one 711, the spring preload, the friction of the first O-ring 74, and the friction of the lower valve stem 714, while the upper valve stem 713 needs to overcome friction, the friction of the first valve seat ring 72, and the spring preload. Therefore, the upper actuator 5 and lower actuator 6 can be reduced in size by several levels, saving costs and significantly extending the valve's service life.

[0046] During valve closure, the upper actuator 5 is closed first, driving the upper valve stem 713 to close the hemispherical body 71. At this time, because channel two 712 is still in the open position, the upstream and downstream are connected, so there is no pressure difference, and closing is effortless. Next, the lower actuator 6 is closed. The lower actuator 6 overcomes the medium force at channel two 712, the spring preload force, the friction force of the second O-ring 79, and the friction force of the lower valve stem 714 to close the valve, effectively adapting to operating environments with large pressure differences.

[0047] Example 2

[0048] Compared with Embodiment 1, another implementation of this application is as follows:

[0049] Please refer to this carefully. Figure 6 , Figure 7 , Figure 8 The safety locking mechanism 8 includes a first slider 84 fixed to the top of the O-shaped ball 76, a first groove 83 opened at the end of the upper valve stem 713, and the first slider 84 slidably connected in the first groove 83; a second groove 86 opened in the middle of the upper pressure cover 3, and the middle of the upper valve stem 713 slidably connected to the inner wall of the second groove 86 through the second slider 85; the positions of the second slider 85 and the first slider 84 are axially aligned, and the lengths of the first groove 83 and the second groove 86 are equal.

[0050] Specifically, the upper valve stem 713 has a first groove 83 at its end, and the first slider 84 is slidably connected within the first groove 83. This design allows the upper valve stem 713 to slide along the groove direction during operation, while ensuring that the first slider 84 maintains its correct position, thereby ensuring the safety of valve regulation. The upper pressure cap 3 has a second groove 86 in its middle, and the middle part of the upper valve stem 713 is slidably connected to the inner wall of the second groove 86 via a second slider 85. The second slider 85 can move smoothly within the second groove 86, ensuring that the upper valve stem 713 maintains stable and smooth sliding during movement. The positions of the first slider 84 and the second slider 85 are axially aligned, ensuring their movements are coordinated. This axial alignment design helps to prevent deviation during valve operation and maintain system stability. The safety locking mechanism 8, through the precise cooperation of the first slider 84 and the second slider 85 within their respective grooves, ensures the safe, stable, and smooth operation of the valve during operation. The mating and axial alignment design of the slider and groove enhances sealing and response speed, while reducing friction and wear, thus improving valve efficiency and service life. This design allows the valve to maintain high performance even under high pressure and long-term operation, reducing maintenance frequency and ensuring system safety and reliability.

[0051] Please refer to this carefully. Figure 4 , Figure 6 , Figure 7 The lower end of the lower valve stem 714 is fixedly connected to an L-shaped indicator rod 81, and a pointer is vertically opened in the middle of the L-shaped indicator rod 81; an arc-shaped groove plate 82 is slidably sleeved on the outer wall of the L-shaped indicator rod 81, and the side wall of the arc-shaped groove plate 82 is fixedly connected to the outer wall of the lower bushing 4.

[0052] Specifically, an L-shaped indicator rod 81 is fixedly connected to the lower end of the lower valve stem 714. The L-shaped indicator rod 81 connects the lower valve stem 714 to the indicating device. Through this connection, the lower valve stem 714 can move the L-shaped indicator rod 81 accordingly during operation, thereby indicating the valve position or status. The arc-shaped groove plate 82 is fixed to the outer wall of the lower bushing 4. This fixing design effectively prevents the arc-shaped groove plate 82 from shifting or moving asymmetrically during use. The lower bushing 4, as a support component, ensures the stability of the entire indicating system during operation, thereby enhancing the reliability and accuracy of the valve control system.

[0053] The working principle of this embodiment is as follows:

[0054] When the valve is opened, each time the lower valve stem 714 rotates the O-shaped ball 76, it simultaneously drives the first slider 84 to slide and limit its position within the first groove 83. At the same time, the lower valve stem 714 also drives the L-shaped indicator rod 81 to slide within the arc-shaped groove plate 82. Since the L-shaped indicator rod 81 is oriented towards the opening of the O-shaped ball 76, the operator can directly observe the position of the L-shaped indicator rod 81 to determine whether the O-shaped ball 76 has rotated to the correct position. When the first slider 84 slides from one end of the first groove 83 to the other, the second slider 85 on the upper valve stem 713 is stationary within the second groove 86. Then, the upper actuator 5 drives the upper valve stem 713 to rotate, causing the second slider 85 to slide from one end of the second groove 86 to the other. At this time, the first groove 83 moves, and the first slider 84 resets within it, allowing the upper valve stem 713 to drive the hemisphere 71 to rotate stably.

[0055] If the lower actuator 6 malfunctions, causing the O-shaped ball 76 to not rotate to its proper position and connect channel two 712, then the upper valve stem 713 will be locked in position by the limiting action of the first slider 84. Channel one 711 cannot be opened directly by rotating the hemisphere 71 through the upper valve stem 713. To fully open the valve, the lower valve stem 714 and the upper valve stem 713 must be rotated sequentially to balance the pressure difference before connecting the upstream and downstream, thus enhancing valve safety. Furthermore, when the upper valve stem 713 cannot rotate, the L-shaped indicator bar 81 can be observed to determine if the failure is due to the lower valve stem 714 not rotating to its proper position, improving troubleshooting efficiency.

[0056] The embodiments described in this specific implementation are preferred embodiments of this application and are not intended to limit the scope of protection of this application. Identical components are represented by the same reference numerals. Therefore, all equivalent changes made to the structure, shape, and principle of this application should be covered within the scope of protection of this application.

Claims

1. A ball valve for high differential pressure operation, comprising: The valve body (2) has flanges (1) fixedly connected to both ends. The top of the valve body (2) is fixedly connected to an upper pressure cover (3). The top of the upper pressure cover (3) is fixedly connected to an upper actuator (5). The bottom of the valve body (2) is fixedly connected to a lower bushing (4). The bottom of the lower bushing (4) is fixedly connected to a lower actuator (6). The valve body (2) is characterized by further including a graded pressure reducing mechanism (7) and a safety locking mechanism (8). The graded pressure reducing mechanism (7) includes a hemisphere (71), an O-shaped small ball (76), a channel one (711), a channel two (712), an upper valve stem (713), and a lower valve stem (714). The top of the hemisphere (71) is fixed to the end of the upper valve stem (713), and the bottom of the hemisphere (71) is rotatably sleeved to the end of the lower valve stem (714). The top of the O-shaped ball (76) is rotatably connected to the end of the upper valve stem (713), and the bottom of the O-shaped ball (76) is fixed to the end of the lower valve stem (714). The outer ends of the upper valve stem (713) and the lower valve stem (714) are respectively fixed to the upper actuator (5) and the lower actuator (6). The valve body (2) has a channel one (711) in the middle, and the hemisphere (71) has a channel two (712) in the middle.

2. The ball valve for high differential pressure operation according to claim 1, characterized in that, The graded pressure reduction mechanism (7) further includes a first valve seat cover (75) fixed to the edge of the valve body (2), and the end of the first valve seat cover (75) is elastically connected to a first support ring (73).

3. A ball valve for high differential pressure operation according to claim 2, characterized in that, The first support ring (73) abuts against the inner cavity of the valve body (2) through a plurality of first O-rings (74), and the end of the first support ring (73) abuts against the outer wall of the hemisphere (71) through the first valve seat ring (72).

4. A ball valve for high differential pressure operation according to claim 1, characterized in that, The inner edge of the hemisphere (71) is fixed with a second valve seat cover (710), and the middle of the second valve seat cover (710) is elastically connected with a second support ring (78). The outer wall of the second support ring (78) abuts against the second valve seat cover (710) through a second O-ring (79).

5. A ball valve for high differential pressure operation according to claim 4, characterized in that, The second support ring (78) is fixed to the end of the second valve seat ring (77), and the end of the second valve seat ring (77) abuts against the outer wall of the O-shaped ball (76).

6. A ball valve for high differential pressure operation according to claim 1, characterized in that, The safety locking mechanism (8) includes a first slider (84) fixed to the top of the O-shaped ball (76), and a first groove (83) is provided at the end of the upper valve stem (713). The first slider (84) is slidably connected in the first groove (83).

7. A ball valve for high differential pressure operation according to claim 1, characterized in that, The upper pressure cover (3) has a second sliding groove (86) in the middle, and the upper valve stem (713) is slidably connected to the inner wall of the second sliding groove (86) through the second slider (85).

8. A ball valve for high differential pressure operation according to claim 7, characterized in that, The second slider (85) and the first slider (84) are axially aligned, and the second groove (86) and the first groove (83) are of equal length.

9. A ball valve for high differential pressure operation according to claim 1, characterized in that, The lower end of the lower valve stem (714) is fixedly connected to an L-shaped indicator rod (81), and a pointer is vertically opened in the middle of the L-shaped indicator rod (81).

10. A ball valve for high differential pressure operation according to claim 9, characterized in that, The outer wall of the L-shaped indicator rod (81) is slidably fitted with an arc-shaped groove plate (82), and the side wall of the arc-shaped groove plate (82) is fixed to the outer wall of the lower bushing (4).

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