Anti-seize plug valve

Abstract

This application relates to the field of plug valve technology and provides an anti-seize plug valve. The anti-seize plug valve includes: a vibration-damping weld-breaking section disposed within the mounting cavity, having an inner friction cone surface and a hammering surface, wherein the inner friction cone surface and the outer friction cone surface are tightly fitted to form a differential friction cone surface pair, and the hammering surface is fitted to the valve core; and an actuation integration section disposed within the mounting cavity, wherein the input end of the actuation integration section is connected to the valve stem, and the output end is drively connected to the vibration-damping weld-breaking section, the actuation integration section being used to realize the separable transmission between the valve stem and the vibration-damping weld-breaking section. The anti-seize plug valve provided by this application can improve the technical problem in related technologies where the microscopic cold weld is difficult to break at the moment of startup in plug valves.

Description

Technical Field

[0001] This application relates to the field of plug valve technology, and more particularly to an anti-seize plug valve. Background Technology

[0002] A plug valve is a type of valve that controls the flow of media by rotating a conical or cylindrical valve core with a through hole, which then engages with the sealing surface of the valve body. Plug valves are widely used in core processes such as delayed coking, coal gasification lock hoppers, and high-pressure hydrocracking due to their simple structure, strong flow capacity, and rapid opening and closing.

[0003] However, after prolonged standing in high temperature (>200℃), high pressure, solid or coking media, the valve core and valve seat sealing surfaces are prone to "seizing up", which makes the valve unable to open. In the existing technology, plug valves usually reduce the affinity of the sealing surface through special alloys or surface coatings. However, the coating is easy to fall off during repeated opening and closing, which causes coking material to embed into the sealing surface and form micro cold welds. Summary of the Invention

[0004] This application provides an anti-seize plug valve, which can improve the technical problem in the related art where the microscopic cold weld is difficult to break at the moment of startup of the plug valve.

[0005] In a first aspect, embodiments of this application provide an anti-seize plug valve, comprising a valve body, a valve seat, a valve cover, a valve core, a valve stem, a mounting cavity, and a driving component. The valve body has a medium flow cavity, the valve seat is disposed within the medium flow cavity, the valve core is disposed on the valve seat, and the outer sealing cone surface of the valve core is in contact with and seals the inner sealing cone surface of the valve seat. The valve cover is disposed on the valve body and has a mounting cavity communicating with the medium flow cavity. The valve stem is located within the mounting cavity and rotatably disposed on the valve cover. The driving component is drively connected to the valve stem and is used to drive the valve stem to move, thereby actuating the valve core and realizing the opening and closing of the valve. The valve stem has an outer friction cone surface. The anti-seize plug valve further includes: A vibration-damping weld-breaking section, disposed within the mounting cavity, has an inner friction cone surface and a hammering surface. The inner friction cone surface and the outer friction cone surface are tightly fitted together to form a differential friction cone surface pair. The hammering surface is fitted with the valve core. An action integration unit is disposed in the mounting cavity. The input end of the action integration unit is connected to the valve stem, and the output end is connected to the vibration-damping welding part. The action integration unit is used to realize the separable transmission between the valve stem and the vibration-damping welding part. The motion integration unit is used to transmit the rotational torque of the valve stem to the vibration-breaking welding unit when it is connected to the vibration-breaking welding unit, so that the vibration-breaking welding unit breaks the microscopic cold weld between the outer sealing cone surface and the inner sealing cone surface through the hammering surface.

[0006] The technical solutions described in this application embodiment have at least the following technical effects: The anti-seize plug valve provided in this application embodiment has a valve stem rotation angle of 0° when the valve is in the fully closed state. The outer sealing cone surface of the valve core is in contact with the inner sealing cone surface of the valve seat to seal and block the flow of media. The action integration part meshes with the vibration and welding breaking part. The input end is connected to the valve stem, and the output end is connected to the vibration and welding breaking part for transmission. The inner friction cone surface of the vibration and welding breaking part is in close contact with the outer friction cone surface of the valve stem, and the hammering surface is in contact with the upper end surface of the valve core, preparing for the welding breaking action of the next valve opening.

[0007] When the driving component drives the valve stem to rotate forward in the opening direction, within the preset action range of 0° to 4.5°: the action integration unit maintains the meshing transmission state, transmitting the rotational torque of the valve stem to the vibration-damping section; the vibration-damping section converts the rotational torque of the valve stem into axial vibration force, which is transmitted to the valve core through the hammering surface, breaking the microscopic cold welds and coking adhesions between the valve core and the valve seat sealing surface through axial impact; at this stage, the valve stem only rotates a very small angle, and the valve core does not undergo circumferential rotation sufficient to conduct the medium, only producing a micro axial displacement to complete the weld breaking, realizing the control logic of breaking the weld first and then opening, reducing the possibility of seizing and damage to the sealing surface caused by forcibly twisting the valve core.

[0008] When the valve stem rotates more than 4.5°, after the vibration-damping section completes the vibration-damping process: the action integration section separates from the vibration-damping section, interrupting the power transmission between the valve stem and the vibration-damping section, and the vibration-damping section stops operating; the valve stem continues to drive the valve core to rotate from 4.5° to the 90° fully open position, or adjust the opening at any angle, throughout the entire process the vibration-damping section does not operate or interfere, and does not affect the normal on / off control and flow regulation functions of the valve; during the valve closing process, when the valve stem rotates in the reverse direction from 90° to the 0.5° range, the action integration section always remains in a separated state, does not trigger the vibration action, and ensures that the valve closing process is smooth and uninterrupted.

[0009] When the valve is closed to the fully closed position and the valve stem rotates in the reverse direction to the range of 0.5° to 0°: the action integration unit automatically resets and re-engages with the vibration-damping welding unit. Attached Figure Description

[0010] To more clearly illustrate the technical solutions in the embodiments of this application, 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.

[0011] Figure 1 Schematic diagram of the anti-seize plug valve provided in the embodiments of this application Figure 1 ; Figure 2 A cross-sectional view of the anti-seize plug valve provided in an embodiment of this application; Figure 3 for Figure 2 Enlarged view of point A in the middle; Figure 4 This is a schematic diagram of the structure of the vibration-damping weld breakage part and the action integration part provided in the embodiments of this application; Figure 5 A cross-sectional structural schematic diagram of the vibration-damped weld breakage part and the motion integration part provided in the embodiments of this application; Figure 6 This is a schematic diagram of the structure of the motion integration unit provided in an embodiment of this application.

[0012] The following are the labeling elements in the figure: 100. Anti-seize plug valve; 101. Valve body; 102. Valve seat; 103. Valve cover; 1031. Constraint groove; 1032. Annular cam track; 104. Valve core; 105. Valve stem; 106. Drive component; 10. Vibration-induced weld breaking part; 11. Trigger vibration mechanism; 111. Axial vibration hammer; 1111. Hammering surface; 112. Gasket; 113. Energy storage spring; 12. Hammering nut; 121. Protruding structure; 13. Pad triggering mechanism; 131. Pad; 132. Reset component; 20. Action integration part; 21. Insertion device; 211. Active toothed insert; 2111. Meshing structure; 212. Driven toothed insert; 2121. Groove structure; 213. Return spring; 22. Separation device; 221. Separation rod; 222. Cam. Detailed Implementation

[0013] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0014] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs; the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the application. The terms “comprising” and “having”, and any variations thereof, in the specification, claims, and foregoing description of the drawings are intended to cover non-exclusive inclusion.

[0015] It should be noted that when a component is referred to as being "fixed to" or "set on" another component, it can be directly on or indirectly on that other component. When a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to that other component.

[0016] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0017] It should be noted that in this application, the words "in some embodiments," "exemplarily," and "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described in this application as "in some embodiments," "exemplarily," or "for example" should not be construed as being more preferred or advantageous than other embodiments or design solutions. Specifically, the use of words such as "in some embodiments," "exemplarily," and "for example" is intended to present related concepts in a specific manner, meaning that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of this application. The appearance of the above words in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments. Those skilled in the art will explicitly and implicitly understand that the embodiments described herein can be combined with other embodiments.

[0018] A plug valve is a type of valve that controls the flow of media by rotating a conical or cylindrical valve core with a through hole, which then engages with the sealing surface of the valve body. Plug valves are widely used in core processes such as delayed coking, coal gasification lock hoppers, and high-pressure hydrocracking due to their simple structure, strong flow capacity, and rapid opening and closing.

[0019] However, after prolonged standing in high temperature (>200℃), high pressure, solid or coking media, the valve core and valve seat sealing surfaces are prone to "seizing up", making the valve unable to open. In the existing technology, plug valves usually reduce the affinity of the sealing surface through special alloys or surface coatings. However, the coating is easy to fall off during repeated opening and closing, and coking material is easy to embed, resulting in cold welding.

[0020] Based on this, in order to improve the problem that the microscopic cold welds of the plug valve are difficult to remove at the moment of startup in the related technology, the embodiments of this application provide the following solution.

[0021] Please refer to the following: Figure 1 and Figure 2This application provides an anti-seize plug valve 100, which includes a valve body 101, a valve seat 102, a valve cover 103, a valve core 104, a valve stem 105, a mounting cavity, and a drive component 106. The valve body 101 has a medium flow cavity, the valve seat 102 is disposed in the medium flow cavity, the valve core 104 is disposed on the valve seat 102, and the outer sealing cone surface of the valve core 104 is in contact with and seals the inner sealing cone surface of the valve seat 102. The valve cover 103 is disposed on the valve body 101. The valve cover 103 has a mounting cavity that communicates with the medium flow cavity. The valve stem 105 is located in the mounting cavity and is rotatably mounted on the valve cover 103. The driving member 106 is connected to the valve stem 105 for driving the valve stem 105 to move and drive the valve core 104 to move, thereby realizing the opening and closing of the valve. The valve stem 105 has an external friction cone surface. The anti-seize plug valve 100 also includes a vibration-damping weld breakage part 10 and an action integration part 20.

[0022] The vibration-damping weld break part 10 is set in the mounting cavity and has an inner friction cone surface and a hammering surface 1111. The inner friction cone surface and the outer friction cone surface are closely fitted to form a differential friction cone surface pair, and the hammering surface 1111 is fitted with the valve core 104.

[0023] The motion integration unit 20 is disposed in the mounting cavity. The input end of the motion integration unit 20 is connected to the valve stem 105, and the output end is connected to the vibration-damping welding unit 10 for transmission. The motion integration unit 20 is used to realize the separable transmission between the valve stem 105 and the vibration-damping welding unit.

[0024] The action integration unit 20 is used to transmit the rotational torque of the valve stem 105 to the vibration breaking weld unit 10 when it is connected to the vibration breaking weld unit 10, so that the vibration breaking weld unit 10 breaks the micro cold weld between the outer sealing cone surface and the inner sealing cone surface through the hammering surface 1111.

[0025] It is understandable that the valve body 101 is the core load-bearing base of the valve. It can be integrally cast from high temperature, high pressure and corrosion resistant cast steel / stainless steel. It has a medium flow cavity formed through the inside, which is the main flow path of the pipeline medium. At the same time, it provides the installation reference and radial limit for the valve seat 102.

[0026] The valve seat 102 is the sealing reference component of the valve. It is fixedly assembled in the medium flow cavity of the valve body 101. The inner wall is machined with an inner sealing cone surface, which matches the taper of the outer sealing cone surface of the valve core 104. The valve seat 102 can be made of hardened wear-resistant / anti-coking alloy material.

[0027] The valve core 104 is the actuator for valve on / off control. It can be a conical plug structure, housed within the medium flow cavity, and coaxially assembled with the valve seat 102. Its outer wall is machined with an outer sealing conical surface that fits against the inner sealing conical surface of the valve seat 102, and a medium through-hole matching the medium flow cavity is opened in the center. When the valve is fully closed, the outer sealing conical surface of the valve core 104 is completely fitted with the inner sealing conical surface of the valve seat 102, blocking the flow of medium. When the valve is fully open, the medium through-hole of the valve core 104 is perfectly aligned with the medium flow cavity, enabling medium transport.

[0028] The valve cover 103 is fixedly and sealed on the top of the valve body 101 and can be rigidly connected to the valve body 101 by bolts and flanges. A high-temperature and high-pressure resistant metal gasket 112 can be set at the joint. The interior is enclosed to form an installation cavity that communicates with the medium flow cavity, providing a closed and protected installation environment for the valve stem 105, the vibration-damped weld part 10, and the actuation integration part 20.

[0029] The valve stem 105 is a power transmission rod, vertically arranged in the mounting cavity of the valve cover 103. Its lower end is rigidly connected to the valve core 104, and its upper end is connected to the drive component 106. It can rotate around its axis under the drive of the drive component 106, transmitting the rotational torque of the drive component 106 to the valve core 104, causing the valve core 104 to rotate synchronously, thus realizing the opening and closing of the valve. The outer wall of the valve stem 105 is machined with an external friction cone surface, which matches the taper of the internal friction cone surface of the vibratory weld section 10. The two fit tightly together to form a differential friction cone surface pair.

[0030] The drive unit 106 is the power source for opening and closing the valve. It is fixedly mounted on the top of the valve cover 103 and its output end is rigidly connected to the upper end of the valve stem 105. It can be equipped with manual turbine, pneumatic actuator, electric actuator, hydraulic actuator, etc., to adapt to the control requirements of different working conditions. Its core function is to output a stable rotational torque to drive the valve stem 105 to rotate the valve core 104 and realize the switching of the valve.

[0031] The vibration-damping weld-breaking section 10 is an actuator for breaking the microscopic cold weld between the valve core 104 and the valve seat 102 sealing surfaces. It is housed within the mounting cavity of the valve cover 103 and coaxially mounted on the valve stem 105. The inner friction cone surface is tightly fitted with the outer friction cone surface of the valve stem 105, forming a differential friction cone surface pair. The hammering surface 1111 is located at the lower end of the vibration-damping weld-breaking section 10, tightly fitted with the upper end face of the valve core 104 (or tightly fitted with the upper end face of the valve seat 102). It can directly transmit axial vibration force to the valve core 104, breaking the microscopic cold weld and coking adhesion between the outer and inner sealing cone surfaces through axial impact. For example, the vibration-damping weld-breaking section 10 can be an electrically controlled hammer (a servo motor mounted on the valve seat 102 with a hammer connected to its output end), or a starter hammer (a double-acting cylinder mounted on the valve seat 102 with a hammer connected to its output end), etc.

[0032] The motion integration unit 20 is a clutch-type transmission control mechanism that controls the power supply between the vibration-damping welding unit 10 and the valve stem 105. It is housed within the mounting cavity of the valve cover 103 and coaxially mounted on the valve stem 105. The input end is rigidly connected to the valve stem 105 via a key, pin, or thread, and rotates synchronously with the valve stem 105. The output end forms a separable transmission engagement with the vibration-damping welding unit 10. The motion integration unit 20 automatically connects and disconnects from the vibration-damping welding unit 10 based on the rotation angle of the valve stem 105, controlling the triggering and stopping of the vibration-damping welding action without affecting the normal opening and closing of the valve. For example, the motion integration unit 20 can be a centrifugal pawl 131 clutch, a roller wedge clutch, or a differential planetary gear clutch.

[0033] As can be seen from the above, in the anti-seize plug valve 100 provided in this application embodiment, when the valve is in the fully closed state, the valve stem 105 rotates at an angle of 0°, the outer sealing cone surface of the valve core 104 is in contact with the inner sealing cone surface of the valve seat 102 to seal and block the flow of the medium; the action integration part 20 meshes with the vibration and welding breaking part 10, the input end is connected to the valve stem 105, and the output end is connected to the vibration and welding breaking part 10 for transmission; the inner friction cone surface of the vibration and welding breaking part 10 is in close contact with the outer friction cone surface of the valve stem 105, and the hammering surface 1111 is in contact with the upper end surface of the valve core 104, preparing for the welding breaking action of the next valve opening.

[0034] When the drive unit 106 drives the valve stem 105 to rotate in the forward direction of opening, within the preset action range of 0° to 4.5° (which can be 3°~6°, preferably 4.5°): the action integration unit 20 maintains the meshing transmission state and transmits the rotational torque of the valve stem 105 to the vibration and welding breaking unit 10; the vibration and welding breaking unit 10 converts the rotational torque of the valve stem 105 into axial vibration force, which is transmitted to the valve core 104 through the hammering surface 1111, and breaks the micro-cold weld and coking adhesion between the valve core 104 and the sealing surface of the valve seat 102 through axial impact; at this stage, the valve stem 105 only rotates a very small angle, and the valve core 104 does not undergo circumferential rotation sufficient to conduct the medium, and only produces axial micro-displacement to complete the welding breaking, realizing the control logic of welding breaking first and opening later, reducing the possibility of seizing and sealing surface damage caused by forcibly twisting the valve core 104.

[0035] When the valve stem 105 rotates more than 4.5°, after the vibration-damping section 10 completes the vibration-damping: the action integration section 20 separates from the vibration-damping section 10, interrupting the power transmission between the valve stem 105 and the vibration-damping section 10, and the vibration-damping section 10 stops operating; the valve stem 105 continues to drive the valve core 104 to rotate from 4.5° to the 90° fully open position, or adjust the opening at any angle, and the vibration-damping section 10 does not operate or interfere throughout the entire process, and does not affect the normal on / off control and flow regulation function of the valve; during the valve closing process, when the valve stem 105 rotates in the opposite direction from 90° to the 0.5° range, the action integration section 20 always remains in a separated state and does not trigger the vibration action, ensuring that the valve closing process is smooth and uninterrupted.

[0036] When the valve is closed to the fully closed position, and the valve stem 105 rotates in the reverse direction to the range of 0.5° to 0°: the action integration unit 20 automatically resets and re-engages with the vibration and welding unit 10.

[0037] Optionally, a stuffing box may be provided on the upper part of the valve cover 103. The stuffing box is coaxially connected with the mounting cavity. The stuffing box is filled with high-temperature resistant sealing packing. The valve stem 105 passes through the sealing packing to achieve dynamic sealing between the valve stem 105 and the valve cover 103, preventing the medium from leaking out from where the valve stem 105 passes through the valve cover 103.

[0038] In some embodiments, the action integration unit 20 is used to drive the valve stem 105 to the vibration and welding section 10 when the valve stem 105 performs a preset action, and not to drive the valve stem 105 to the vibration and welding section 10 when the valve stem 105 does not perform a preset action. The preset action is that the valve stem 105 rotates from 0° to 4.5° in the forward direction. The forward rotation is rotation along the valve opening direction. When the valve stem 105 is at 0°, the valve is in the fully closed state.

[0039] It can be understood that the rotation direction of the preset action is forward rotation, that is, rotation along the valve opening direction, and the corresponding reverse rotation is the valve closing direction. The transmission connection logic of the preset action is not triggered during the entire reverse rotation stroke. During the forward rotation of the valve stem 105 from 0° to 4.5° (including the 0° fully closed and stationary standby state and the 4.5° critical position), it is determined that the preset action is executed, and the action integration unit 20 maintains the transmission connection with the vibration and welding breaking unit 10.

[0040] With this setting, the preset rotation angle of 4.5° ensures that the cold weld removal action is completed before the valve core 104 generates effective medium conduction circumferential rotation. Furthermore, the transmission is immediately separated after exceeding 4.5°, without affecting the normal opening and closing and flow regulation functions of the valve throughout its 90° stroke, thus retaining the advantages of the plug valve in terms of strong flow capacity and rapid opening and closing.

[0041] In some embodiments, please refer to the following: Figures 2 to 5At least one constraint groove 1031 is provided on the inner wall of the valve cover 103, and the vibration-damping weld break part 10 includes a trigger vibration mechanism 11, a hammer nut 12 and at least one ratchet trigger mechanism 13.

[0042] The triggering vibration mechanism 11 is sleeved on the valve stem 105 and has a hammering surface 1111.

[0043] The hammer nut 12 is sleeved on the valve stem 105. The upper end of the hammer nut 12 is connected to the action integration part 20 for transmission. The inner hole of the hammer nut 12 has an internal friction cone surface. The lower end of the hammer nut 12 abuts against the trigger vibration mechanism 11.

[0044] One end of the pawl trigger mechanism 13 is hinged to the outer peripheral wall of the hammer nut 12, and the other end is in contact with the bottom of the constraint groove 1031. The pawl trigger mechanism 13 and the constraint groove 1031 correspond one-to-one. The pawl trigger mechanism 13 is used to prevent the hammer nut 12 from circumferentially moving forward when it rotates. It is also used to unlock the hammer nut 12 when it rotates to a preset angle, and to limit the axial height of the hammer nut 12 by cooperating with the constraint groove 1031, so that the hammer nut 12 moves closer to the valve core 104 during the process of rotating to the preset angle.

[0045] The triggering vibration mechanism 11 is axially located below the hammer nut 12 and above the valve core 104. The action integration part 20 is used to transmit the rotational torque of the valve stem 105 to the hammer nut 12 when it is connected to the hammer nut 12 to drive the hammer nut 12 to rotate, and not to be connected to the hammer nut 12 when the hammer nut 12 rotates to a preset angle, so that the triggering vibration mechanism 11 breaks the micro-cold weld between the outer sealing cone surface and the inner sealing cone surface through the hammering surface 1111.

[0046] It can be understood that the constraint groove 1031 is a sunken trajectory groove integrally machined into the inner wall of the valve cover 103, having a first end (low starting point) and a second end (high ending point). The second end is flush with the inner wall of the valve cover 103, and the downward slope of the bottom curved surface of the groove matches the axial energy storage stroke of the hammer nut 12.

[0047] The hammer nut 12 is sleeved on the valve stem 105 and can rotate and slide axially relative to the valve stem 105. The rotation angle and axial position of the hammer nut 12 are limited by the cooperation between the pawl trigger mechanism 13 and the constraint groove 1031: when the hammer nut 12 rotates, the pawl trigger mechanism 13 slides along the bottom of the constraint groove 1031. The change in height and slope of the bottom of the groove causes the pawl trigger mechanism 13 to generate radial displacement, which in turn causes the hammer nut 12 to generate synchronous axial movement. For example, the hammer nut 12 can be a cylindrical cam driven axial sliding sleeve, an end face ratchet stepping nut, etc. The preset angle corresponds to the angle when the valve stem 105 performs a preset action, that is, when the valve stem 105 performs a preset action, it drives the hammer nut 12 to rotate to 4.5°, at which time 4.5° is the preset angle corresponding to the hammer nut 12.

[0048] The pawl trigger mechanism 13 is a mechanism that, with its own elasticity (such as a torsion spring) or hydraulic / pneumatic assistance, closely adheres to the bottom of the constraint groove 1031. The bottom of the constraint groove 1031 has a unidirectional inclined characteristic (a ramp from the first end to the second end). During the rotation of the hammer nut 12, the end of the pawl trigger mechanism 13 slides from the first end to the second end of the constraint groove 1031. For example, the pawl trigger mechanism 13 can be a spring pin-ramp trigger mechanism, a steel ball-spiral ramp clutch, etc.

[0049] The triggering vibration mechanism 11 is a device that accumulates potential energy through the movement of the hammer nut 12, and releases this potential energy when the hammer nut 12 is unlocked, thereby breaking the microscopic cold weld between the outer and inner sealing cone surfaces through the hammering surface 1111. The triggering vibration mechanism 11 can adopt an integral rigid hammer head structure, or it can integrate an energy storage spring 113 (i.e., the spring pressing against the lower end of the hammer nut 12 is located here; in this case, when the hammer nut 12 resets, there is no independent spring, but the energy is released through the spring built into the triggering vibration mechanism 11). For example, the triggering vibration mechanism 11 can be a hydraulic tappet-type rigid force transmission column, a pendulum-type heavy hammer impactor, etc.

[0050] With this configuration, when the hammer nut 12 rotates, the contact surface between the pawl trigger mechanism 13 and the constraint groove 1031 moves from the first end along the bottom of the groove to the second end. The hammer nut 12, constrained by the sidewall of the pawl trigger mechanism 13 and the constraint groove 1031, approaches the valve core 104. The trigger vibration mechanism 11 stores elastic potential energy under the pressure of the hammer nut 12. When the contact surface between the pawl trigger mechanism and the constraint groove 1031 moves to the second end, the pawl trigger mechanism 13 loses the constraint of the sidewall of the constraint groove 1031, unlocking the hammer nut 12. As the hammer nut 12 moves away from the valve core 104, it drives the pawl trigger mechanism 13 to approach and fall into the adjacent groove on the circumferential direction of the valve sleeve. At the first end of the constraint groove 1031, the pawl trigger mechanism 13 is again restricted by the constraint groove 1031, thereby fixing the position of the hammer nut 12 to complete the reset of the hammer nut 12. During the process of the hammer nut 12 from unlocking to reset, the trigger vibration mechanism 11 loses the pressure of the hammer nut 12 and releases elastic potential energy. Under the action of elastic potential energy, the hammering surface 1111 breaks the microscopic cold weld between the outer sealing cone surface and the inner sealing cone surface. After the hammer nut 12 is reset, it is no longer connected to the action integration part 20 for transmission. Therefore, the subsequent rotation of the valve stem 105 will not drive the hammer nut 12 to rotate, so that the hammer nut 12 does not affect the subsequent opening and closing process of the valve.

[0051] During the upward reset of the hammer nut 12, the actuation integration unit 20 is separated from the hammer nut 12, and the upward impact force is not directly transmitted to the top cover. Optionally, an elastic buffer pad or shock-absorbing structure (such as a buffer spring, rubber pad, etc.) can be provided at the end of the reset stroke above the hammer nut 12 to absorb the residual impact energy during its reset.

[0052] The constraint groove 1031 is a spatial curved groove that extends circumferentially along the inner wall of the valve cover 103 and gradually sinks axially at the bottom. When the pawl 131 rotates with the hammer nut 12, it slides tightly against the bottom of the groove under the elastic force of the reset member 132, and is forced to produce a radially inward swinging contraction action. This action is converted into the axial downward displacement of the hammer nut 12 through the hinge structure, thereby realizing the conversion from rotation to axial displacement.

[0053] Optionally, a guide groove (parallel to the axial direction of the valve stem 105) connecting the second end of the constraint groove 1031 and the first end of the adjacent constraint groove 1031 can be provided to guide the movement of the pawl trigger mechanism 13 to ensure the reset of the hammer nut 12.

[0054] In some embodiments, please refer to the following: Figures 2 to 5The upper end of the hammer nut 12 has at least one protrusion structure 121, and the action integration part 20 has at least one groove structure 2121. The protrusion structure 121 and the groove structure 2121 correspond one-to-one. The hammer nut 12 is connected to the action integration part 20 through the engagement of the protrusion structure 121 and the groove structure 2121.

[0055] It is understood that the protruding structure 121 is set on the upper end face or the upper outer periphery of the hammer nut 12, and is a rigid protrusion extending upward along the axial direction. It is integrally formed with the hammer nut 12 or fixedly connected by welding, pinning or other processes.

[0056] The groove structure 2121 is formed on the lower end face or lower end inner hole of the output component of the motion integration part 20. The number and circumferential position of the groove structure 2121 correspond one-to-one with the protrusion structure 121 of the hammer nut 12, forming a complete embedded fit relationship. The groove opening of the groove structure 2121 can be provided with an inlet guide structure such as a chamfer, a conical surface or a flared mouth, so that the protrusion structure 121 can be automatically guided into the groove when it approaches axially, compensating for errors such as valve stem 105 deflection and assembly eccentricity, and ensuring reliable engagement.

[0057] With this configuration, when the valve stem 105 starts to rotate forward from 0°, the actuation integration unit 20 transmits the rotational torque of the valve stem 105 to the hammer nut 12 through the groove structure 2121 that meshes with the protrusion structure 121, so that the hammer nut 12 rotates synchronously with the valve stem 105. When the valve stem 105 rotates forward to 4.5°, the hammer nut 12 and the actuation integration unit 20 move away from each other, and the protrusion structure 121 does not mesh with the groove structure 2121, so that the actuation integration unit 20 separates from the hammer nut 12. The actuation integration unit 20 no longer transmits the rotational torque of the screw to the hammer nut 12, so as to avoid the hammer nut 12 affecting the subsequent valve opening and closing process.

[0058] In some embodiments, the constraint groove 1031 has a first end and a second end, the second end being flush with the inner wall of the valve cover 103; on the same radial plane of the valve stem 105, the straight-line distance between the first end and the axis of the valve stem 105 is greater than the straight-line distance between the second end and the axis of the valve stem 105; the bottom of the constraint groove 1031 is a curved surface that gradually sinks axially towards the valve core 104, with the first end as the starting point and the second end as the ending point; during the process of the hammer nut 12 rotating to a preset angle, the contact surface between the pawl trigger mechanism 13 and the bottom of the constraint groove 1031 moves from the first end to the second end; the first end of the constraint groove 1031 and the second end of another constraint groove 1031 adjacent in the circumferential direction are collinear on the same axis of the valve cover 103.

[0059] It is understandable that the bottom of the constraint groove 1031 is not an arc surface equidistant from the axis of the valve stem 105, but a curved surface with a radially varying depth. That is, the bottom of the groove at the first end is farther from the axis and the groove is relatively deep; the bottom of the groove at the second end is closer to the axis and the groove is relatively shallow. Moving circumferentially from the first end to the second end, the bottom of the groove gradually approaches the axis and the depth of the groove gradually decreases. Finally, at the second end, the bottom of the groove is flush with the inner wall of the valve cover 103, and the constraint groove 1031 disappears at this point, with no step transition between the bottom of the groove and the inner wall.

[0060] The bottom surface of the constraint groove 1031 is defined as follows: starting from the first end and ending at the second end, it gradually sinks axially towards the valve core 104. It can be understood that the bottom surface of the groove is relatively high at the first end, close to the top side of the valve cover 103 and the hammer nut 12. As you walk along the bottom of the groove to the second end, the bottom of the groove gradually descends towards the valve core 104, and the hammer nut 12 is guided to approach the valve core 104. The spatial surface of the bottom of the constraint groove 1031 is converted into the axial displacement of the hammer nut 12.

[0061] The first end is the starting point of the constraint groove 1031 and the initial seating position of the pawl trigger mechanism 13. The bottom of the groove is far from the axis of the valve stem 105, and the groove is relatively deep. The end of the pawl trigger mechanism 13 away from the valve stem 105 can be embedded to provide reliable axial limiting and prevent the hammer nut 12 from sliding axially without control.

[0062] The second end is the end point of the constraint groove 1031, which is also the position where the hammer nut 12 reaches the preset angle. Here, the bottom of the constraint groove 1031 is flush with the reference surface of the inner wall of the valve cover 103. The constraint groove 1031 disappears naturally here, the end of the pawl trigger mechanism 13 loses radial support, the constraint is released, the hammer nut 12 is axially reset, and the hammering weld breaking is completed.

[0063] The first end of the constraint groove 1031 and the second end of another constraint groove 1031 adjacent in the circumferential direction are collinear on the same axis of the valve cover 103, that is, in the same position along the axial direction of the valve cover 103. The first constraint groove 1031 ends at the second end (flush with the inner wall), and the first end of the second constraint groove 1031 (the starting point of the deeper groove) is also on the same axial straight line. With this configuration, when the pawl trigger mechanism 13 is disengaged and unlocked at the second end and the hammer nut 12 is axially reset, the pawl trigger mechanism 13 can be aligned and enter the first end of the adjacent constraint groove 1031.

[0064] In some embodiments, please refer to the following: Figures 2 to 5 The triggering vibration mechanism 11 includes an axial vibration hammer 111, a washer 112, and an energy storage spring 113.

[0065] An axial vibratory hammer 111 is sleeved on the valve stem 105 and has a hammering surface 1111.

[0066] Gasket 112 is fitted onto valve stem 105, and the lower end of hammer nut 12 abuts against gasket 112.

[0067] The energy storage spring 113 is sleeved on the valve stem 105. One end of the energy storage spring 113 abuts against the gasket 112, and the other end abuts against the axial vibration hammer 111.

[0068] As the hammer nut 12 approaches the valve core 104, it compresses the energy storage spring 113 through the gasket 112. When the hammer nut 12 rotates to a preset angle, the pawl trigger mechanism 13 unlocks the hammer nut 12, causing the hammer nut 12 to reset and the energy storage spring 113 to release. This allows the axial vibration hammer 111 to break the microscopic cold weld between the outer sealing cone surface and the inner sealing cone surface through the hammering surface 1111.

[0069] It is understood that the axial vibratory hammer 111 is sleeved on the valve stem 105 and can slide freely along the axial direction. Located below the energy storage spring 113, it is the output component of the hammering force. The lower end face of the axial vibratory hammer 111 has a hammering surface 1111 that directly contacts the impact surface of the valve core 104, and the upper end face receives the elastic thrust of the energy storage spring 113. For example, the axial vibratory hammer 111 can be a rubber hammer, an alloy hammer, etc.

[0070] The gasket 112 is sleeved on the valve stem 105 and is axially located between the lower end face of the hammer nut 12 and the upper end of the energy storage spring 113. It serves as the transmission medium for the axial approach displacement of the hammer nut 12 to be transmitted to the energy storage spring 113. For example, the gasket 112 can be a metal washer, a rubber washer, etc.

[0071] The energy storage spring 113 is sleeved on the valve stem 105 and is axially located between the gasket 112 and the axial vibrating hammer 111. It is the core of energy storage and release. For example, the energy storage spring 113 can be a disc spring, a spiral spring, etc.

[0072] With this configuration, when the valve stem 105 is at 0°, the hammer nut 12 is at its initial high position, the energy storage spring 113 only bears the preload, and the force is transmitted to the first end of the constraint groove 1031 through the gasket 112, the hammer nut 12 and the pawl triggering mechanism 13. The axial vibration hammer 111 is in close contact with the impact surface of the valve core 104 under the preload.

[0073] During the process of the valve stem 105 rotating from 0° to 4.5°, the action integration unit 20 drives the hammer nut 12 to rotate, and the pawl 131 slides along the bottom of the constraint groove 1031 from the first end to the second end. The hammer nut 12 is axially forced close to the valve core 104. The lower end of the hammer nut 12 gradually compresses the energy storage spring 113 through the washer 112. The spring force increases linearly, and the elastic potential energy continues to accumulate. During this process, the hammering surface 1111 remains in contact with the valve core 104. The increased force of the energy storage spring 113 is limited by the side wall of the constraint groove 1031 and the pawl triggering mechanism 13, and does not act on the valve core 104.

[0074] When the valve stem 105 rotates from the forward direction to 4.5°, the hammer nut 12 rotates to the preset angle, and the pawl 131 reaches the second end of the constraint groove 1031 (flush with the inner wall of the valve cover 103). The constraint groove 1031 loses its support for the pawl 131, the axial constraint of the hammer nut 12 is released, the energy storage spring 113 extends rapidly, pushing the gasket 112 and the hammer nut 12 to return to their original axial position at high speed. At the same time, a high-frequency alternating vibration is formed at both ends of the energy storage spring 113 through transient impact, which is synchronously transmitted to the axial impact hammer 111. The hammering surface 1111 impacts the bearing surface of the valve core 104, thereby breaking the microscopic cold weld between the outer sealing cone surface and the inner sealing cone surface.

[0075] In some embodiments, please refer to the following: Figures 2 to 5 The pawl triggering mechanism 13 includes a pawl 131 and a reset member 132.

[0076] The pawl 131 is hinged to the outer peripheral wall of the hammer nut 12.

[0077] One end of the reset member 132 is connected to the hammer nut 12, and the other end is connected to the pawl 131. The pawl 131 is used to drive the pawl 131 to engage with the constraint groove 1031 to prevent the hammer nut 12 from circumferentially moving forward when rotating, and to limit the axial height of the hammer nut 12 by engaging with the constraint groove 1031, so that the hammer nut 12 moves closer to the valve core 104 when rotating to a preset angle.

[0078] When the hammer nut 12 rotates to a preset angle, the reset member 132 is compressed, and the pawl 131 is not located in the constraint groove 1031, thereby unlocking the hammer nut 12.

[0079] It can be understood that the pawl 131 is a rigid swinging component, which is swingably mounted on the outer peripheral wall of the hammer nut 12 via a hinge pin. The hinge axis is parallel to the rotation axis of the hammer nut 12, allowing the pawl 131 to swing freely around the hinge point in the radial plane of the hammer nut 12. For example, the pawl 131 can be a straight rod pawl 131, a bent arm pawl 131, a flat plate pawl 131, etc.

[0080] The reset element 132 is an elastic force-applying element that drives the pawl 131 to always maintain a tight fit with the constraint groove 1031, and continuously applies elastic force to the pawl 131 in the direction of the bottom of the constraint groove 1031. For example, the reset element 132 can be a helical compression spring, a spiral spring, an elastic compression plunger, etc.

[0081] With this configuration, the end of the pawl 131 away from the valve stem 105 is always in contact with the bottom surface of the constraint groove 1031 under the drive of the reset member 132. When the hammer nut 12 rotates, the pawl 131 slides along the bottom of the groove. The change in the radial depth of the groove bottom forces the pawl 131 to swing around the hinge point. Then, the axial displacement of the groove bottom is forcibly transmitted to the hammer nut 12 as a whole through the hinge pin, so that the hammer nut 12 is gradually pushed towards the valve core 104 during the rotation. During this process, the reset member 132 is continuously compressed, and its elastic force ensures that the pawl 131 does not detach from the bottom of the groove.

[0082] When the hammer nut 12 rotates to the preset angle and the pawl 131 reaches the second end of the constraint groove 1031, the bottom of the constraint groove 1031 is flush with the inner wall of the valve cover 103, and the radial depth of the groove bottom reaches its shallowest point. The support of the constraint groove 1031 for the pawl 131 disappears. At this time, pushed by the elastic force of the reset member 132, the end of the pawl 131 away from the valve stem 105 will naturally swing outward. However, since there is no support surface at the bottom of the groove, the pawl 131 is no longer geometrically constrained by the bottom of the groove, and the entire pawl 131 completely leaves the range of the constraint groove 1031. The axial limit of the hammer nut 12 disappears here. Here, the reset member 132 is compressed to the limit of its stroke. After unlocking, it returns to its original position with the hammer nut 12, and the pawl 131 re-fits the first end of the adjacent constraint groove 1031 in the new circumferential position.

[0083] Optionally, the hammer nut 12 may be provided with receiving grooves corresponding to the pawl 131. When the hammer nut 12 is rotated to a preset angle, the pawl 131 reaches the second end of the constraint groove 1031, and the reset member 132 is compressed to the stroke limit, the pawl 131 is completely located in the corresponding receiving groove.

[0084] In some embodiments, please refer to the following: Figures 2 to 6 The valve cover 103 has an annular cam track 1032 on its inner wall, and the action integration part 20 includes a disc device 21 and a separation device 22.

[0085] The insert device 21 is movably mounted on the valve stem 105 for transmission connection with the vibratory weld break part 10 and for rotating synchronously with the valve stem 105.

[0086] The separation device 22 has one end connected to the disc device 21, and the other end is in rolling engagement with the annular cam track 1032.

[0087] The disc insert device 21 is used to transmit the rotational torque of the valve stem 105 to the vibration-damping welding section 10 when it is connected to the vibration-damping welding section 10. The separation device 22 is used to change the axial height of the disc insert device 21 by rolling cooperation with the annular cam track 1032 when the disc insert device 21 rotates, so that the disc insert device 21 is connected to or not connected to the vibration-damping welding section 10.

[0088] It can be understood that the annular cam track 1032 serves as the spatial guide reference for the motion integration unit 20, and is located on the inner wall of the valve cover 103. Its function is to provide continuous circumferential rolling guidance for the separating device 22, and to convert the rotational motion of the separating device 22 along with the disc-mount device 21 into the axial displacement of the disc-mount device 21. The cross-section of the annular cam track 1032 can be machined into an arc-shaped groove, a V-shaped groove, or a rectangular groove, etc., to achieve stable engagement with the rolling elements of the separating device 22 and prevent the rolling elements from derailing.

[0089] The disc device 21 is an axially movable output element of the action integration unit 20. It is sleeved on the valve stem 105 and rotates synchronously with the valve stem 105 through a key, spline or similar circumferential fixing structure. At the same time, it can slide along the axial direction of the valve stem 105. The disc device 21 has a groove structure 2121 on the side near the vibration-damping weld section 10 for transmission connection with the vibration-damping weld section 10.

[0090] The separating device 22 is a motion transmission element connecting the disc device 21 and the annular cam track 1032. One end of it is connected to the disc device 21, and the other end is provided with a rolling element that rolls with the annular cam track 1032. The function of the separating device 22 is to transmit its own axial undulating motion along the annular cam track 1032 to the disc device 21, forcing the disc device 21 to produce synchronous axial displacement as the rotation angle changes.

[0091] With this configuration, when the valve core 104 engages and the valve stem 105 initially rotates (from 0° forward to 4.5°), the valve stem 105 rotates synchronously with the disc-mount device 21. However, due to the high resistance of engagement, the overall rotational speed is extremely low, or even in an intermittent micro-motion state. At this time, the rolling element of the separating device 22 is located in the trough section of the annular cam track 1032 or is in the initial stage of its lift. The disc-mount device 21 is in a low axial position and tightly engages with the protruding structure 121 of the vibratory weld-breaking part 10 through the groove structure 2121. The rotational torque of the valve stem 105 is transmitted to the vibratory weld-breaking part 10 via the disc-mount device 21, driving the hammer nut 12 to rotate.

[0092] When the valve stem 105 rotates to 4.5°, the vibratory weld-breaking part 10 performs the weld-breaking action. When the seizure is released and the valve core 104 begins to rotate with the valve stem 105 (rotating from 4.5° to 90° in the forward direction), the overall rotational resistance decreases, and the rotational speed of the valve stem 105 increases to the normal opening and closing speed. At this time, the disc-embedded device 21 rotates with the valve stem 105, and the rolling element of the separating device 22 rolls rapidly along the annular cam track 1032. Under the guidance of the track crest, the rolling element is pushed up by the axial undulation of the track. The separating device 22 drives the disc-embedded device 21 to rise axially along the valve stem 105, and the disc-embedded device 21 separates from the vibratory weld-breaking part 10, and the transmission is disconnected.

[0093] After the valve is closed, the valve stem 105 stops rotating, the separation device 22 slides from the crest of the annular cam track 1032 back to the trough, and the disc device 21 is axially reset and reconnected to the vibration-damped weld section 10.

[0094] In some embodiments, please refer to the following: Figures 2 to 6 The tooth insert device 21 includes an active tooth insert 211, a driven tooth insert 212, and at least one return spring 213.

[0095] The active toothed disc 211 is mounted on the valve stem 105.

[0096] The driven tooth insert 212 is sleeved on the active tooth insert 211 and has a groove structure 2121 for transmission connection with the vibration-damping weld section 10 through the groove structure 2121.

[0097] At least one return spring 213, with its two ends abutting against the active toothed disc 211 and the driven toothed disc 212 respectively, is used to continuously provide a preload force toward the valve core 104 to the driven toothed disc 212.

[0098] The active toothed disc 211 and the driven toothed disc 212 each have a corresponding meshing structure 2111 so that the active toothed disc 211 and the driven toothed disc 212 mesh with each other. One end of the separating device 22 is connected to the driven toothed disc 212. The separating device 22 is used to change the axial height of the driven toothed disc 212 by rolling cooperation with the annular cam track 1032 when the driven toothed disc 212 rotates, so that the driven toothed disc 212 is either connected to or not connected to the vibrating and breaking weld section 10.

[0099] It is understood that the active toothed disc 211 is fixedly mounted on the valve stem 105 and rotates synchronously with the valve stem 105. It is the rotational power input element of the disc device 21. The end face of the active toothed disc 212 is machined with a meshing structure 2111, which is used to achieve circumferential torque transmission and axial separable engagement with the corresponding meshing structure 2111 of the active toothed disc 212.

[0100] The driven toothed insert 212 is sleeved on the active toothed insert 211 and can slide freely along the axial direction of the active toothed insert 211. It is a movable element in the insert device 21 that realizes axial engagement and disengagement. Its lower end face facing the active toothed insert 211 has a meshing structure 2111 that matches the active toothed insert 211, and a groove structure 2121 for meshing and transmission connection with the protrusion structure 121 of the vibratory weld breaking part 10. At the same time, its outer periphery is connected to the separation device 22. For example, the active toothed insert 211 and the driven toothed insert 212 can be a sawtooth-shaped fixed disc, a pin-hole transmission disc, a double-sided elastic toothed insert sleeve, etc.

[0101] The return spring 213 is sleeved on the valve stem 105, axially located between the driving jaw disc 211 and the driven jaw disc 212. Its two ends abut against the lower end face of the driving jaw disc 211 and the upper end face of the driven jaw disc 212, respectively, continuously providing the driven jaw disc 212 with an axial preload force pointing towards the valve core 104 (i.e. towards the vibrating weld breakage part 10). For example, the return spring 213 can be a disc spring, a helical compression spring, etc.

[0102] With this configuration, when the valve stem 105 rotates from 0° to 4.5° in the forward direction, the valve core 104 engages, and the valve stem 105 rotates at extremely low speeds or intermittently with slight movements. The rolling element of the separating device 22 is located in the trough area of ​​the annular cam track 1032. The driven toothed disc 212 is held in a low axial position under the thrust of the return spring 213. Its lower end groove structure 2121 engages with the protruding structure 121 of the vibratory weld-breaking part 10, and simultaneously engages with the active toothed disc 211. The active toothed disc 211 rotates with the valve stem 105, and through engagement, drives the driven toothed disc 212 to rotate synchronously. The torque is then transmitted to the vibratory weld-breaking part 10 through the groove structure 2121, driving the vibratory weld-breaking part 10 to perform the weld-breaking action.

[0103] When the valve stem 105 rotates from 4.5° to 90° in the forward direction, the valve core 104 is released from seizure, and the valve stem 105 speed resumes. The separation device 22 rotates with the driven toothed disc 212, and its rolling element rolls along the annular cam track 1032 and is pushed up by the track crest, generating an axial lifting force. This force overcomes the preload of the return spring 213 and lifts the driven toothed disc 212 upward along the valve stem 105. The groove structure 2121 at the lower end of the driven toothed disc 212 disengages from the protruding structure 121 of the vibrating weld-breaking part 10, the transmission is disconnected, and the vibrating weld-breaking part 10 stops moving. At the same time, the meshing structure 2111 between the active toothed disc 211 and the driven toothed disc 212 disengages with axial separation. The rotation of the valve stem 105 is no longer transmitted to the driven toothed disc 212, and the normal opening and closing torque of the valve is not interfered with.

[0104] After the valve is closed, the valve stem 105 stops rotating, the rolling element of the separation device 22 slides from the crest area of ​​the annular cam track 1032 back to the trough area, the driven toothed disc 212 is pushed down by the preload of the return spring 213 and re-engages with the active toothed disc 211, and the groove structure 2121 re-engages with the protrusion structure 121 of the vibration-damped weld section 10.

[0105] In some embodiments, please refer to the following: Figure 2 , Figure 3 and Figure 6 The separation device 22 includes a separation rod 221 and a cam 222.

[0106] One end of the separating rod 221 is connected to the disc insert device 21.

[0107] Cam 222 is rotatably mounted on the other end of separator rod 221 and rolls with an annular cam track 1032.

[0108] The separating rod 221 is used to change the axial height of the disc device 21 by the rolling engagement of the cam 222 and the annular cam track 1032 when the disc device 21 rotates.

[0109] It can be understood that the separating rod 221 is a rigid force-transmitting component of the separating device 22. One end of it is connected to the insert device 21, and the other end provides mounting support for the cam 222. The separating rod 221 transmits the axial displacement obtained by the cam 222 from the annular cam track 1032 to the driven toothed insert 212, driving the driven toothed insert 212 to slide axially along the valve stem 105. For example, the separating rod 221 can be a rocker arm type driven lever, a straight rod, etc.

[0110] Cam 222 is rotatably mounted on the other end of separator rod 221 and rolls with an annular cam track 1032. Cam 222 transmits its axial position change as it rolls along the track to separator rod 221. For example, cam 222 can be a ball-end plunger roller, tapered roller, etc.

[0111] With this configuration, when the driven toothed disc 212 rotates, it drives the separating rod 221 to rotate synchronously. The cam 222 rolls along the annular cam track 1032. The ups and downs of the track are transmitted to the driven toothed disc 212 through the cam 222 and the separating rod 221, which is converted into the axial displacement of the driven toothed disc 212, thereby realizing the separation or engagement transmission between the driven toothed disc 212 and the hammer nut 12.

[0112] In some embodiments, the annular cam track 1032 has a low-position engagement section, a high-position holding section, and a descending reset section. When the cam 222 is in rolling engagement with the low-position engagement section, the disc device 21 is connected to the vibration-damping weld section 10. When the cam 222 is in rolling engagement with the high-position holding section, the disc device 21 is not connected to the vibration-damping weld section 10.

[0113] The low-position engagement section corresponds to a forward opening angle of 0°~4.5° for the valve stem 105, used to drive the disc insert 21 and the vibratory weld break part 10; the high-position holding section corresponds to a forward opening angle of 4.5°~90° and a reverse closing angle of 90°~0.5° for the valve stem 105, used to keep the disc insert 21 and the vibratory weld break part 10 separated during the entire opening and closing stroke of the valve; the descending reset section corresponds to a reverse closing angle of 0.5°~0° for the valve stem 105, used to drive the disc insert 21 to automatically reset and engage after the valve is fully closed.

[0114] It is understood that the axial position of the low-position engagement section is at the lowest plane of the entire annular cam track 1032, and the track maintains a stable low height within this section without significant fluctuations. When the cam 222 of the separating device 22 rolls in the low-position engagement section, the axial lifting force of the separating rod 221 on the driven toothed disc 212 is zero, and the driven toothed disc 212 is in the lowest axial position under the push of the return spring 213, engaging with the vibrating weld section 10.

[0115] The axial position of the high-position holding section is at the highest plane of the entire annular cam track 1032. The track maintains a stable high position within this section without significant fluctuations. The low-position engagement section and the high-position holding section are connected by a smooth rising transition surface, which smoothly guides the cam 222 from the low position to the high position. When the cam 222 enters the high-position holding section, the release rod 221 is pushed up to the highest axial position, lifting the driven toothed disc 212 upwards. The driven toothed disc 212 separates from the vibration-damped weld section 10, and the transmission link is disconnected.

[0116] The descending reset section is a smooth downward curved surface, starting from the high end of the high-position holding section, with the axial height gradually decreasing, eventually transitioning to the low beginning of the low-position engagement section. The descending curve of the descending reset section can be designed with various contours, such as uniform descent or a gradual-then-rapid profile, to control the reset speed and engagement impact. When the valve stem 105 is closed in the reverse direction to the remaining 0.5° rotation angle, the cam 222 begins to enter the descending reset section. As the valve stem 105 continues to rotate towards the fully closed position (0°), the cam 222 descends along the track, and the axial lifting force of the release rod 221 on the driven toothed disc 212 gradually decreases. The driven toothed disc 212 moves downward gradually under the push of the reset spring 213. When the valve stem 105 reaches the fully closed position, the cam 222 returns to the starting point of the low-position engagement section, the driven toothed disc 212 resets, and re-engages with the vibrating weld breakage part 10.

[0117] In some embodiments, the valve cover 103 may further include a one-way passage member, rotatably disposed on the valve cover 103 and located within the annular cam track 1032, for enabling the cam 222 to move from the low engagement section to the high holding section when the valve stem 105 rotates in the forward direction and the cam 222 moves along the annular cam track 1032, and for preventing the cam 222 from directly moving from the high holding section to the low engagement section when the valve stem 105 rotates in the reverse direction, instead enabling the cam 222 to move from the high holding section and the descending reset section to the starting point of the low engagement section. For example, a one-way passage component may include a limiting spring (a spiral spring, a disc spring, etc.) and a limiting plate (a circular plate, a rectangular plate, etc.). The limiting plate is rotatably mounted on the valve cover 103 and located within the annular cam track 1032. One end of the limiting spring is connected to the limiting plate, and the other end is connected to the valve cover 103. When the valve stem 105 rotates in the forward direction and the cam 222 moves along the annular cam track 1032, the cam 222 can abut against the limiting plate and drive the limiting plate to rotate, compressing the limiting spring, thereby opening the connection channel between the low-position engagement section and the high-position holding section (closing the connection between the high-position holding section and the descending reset section). (The cam 222 can move from the low engagement section to the high holding section. After the cam 222 moves from the low engagement section to the high holding section, the limiting plate is reset under the action of the limiting spring, closing the connection channel between the low engagement section and the high holding section (opening the connection between the high holding section and the descending reset section), thereby causing the valve stem 105 to rotate in the reverse direction. When the cam 222 moves in the reverse direction along the annular cam track 1032, it cannot enter the low engagement section through the high holding section, but enters the descending reset section through the high holding section, and then enters the inlet end of the low engagement section through the outlet end of the descending reset section to complete the reset.

[0118] Optionally, when the valve stem 105 can drive the valve core 104 to rotate 360° in the same direction (the valve core 104 is fully closed when it is at 0°, fully open when it is at 90°, fully closed when it is at 180°, and fully closed when it is at 360° (0°)), the annular cam track 1032 includes at least four sets of mating sections. Each set of mating sections corresponds to a 90° rotation angle range that does not overlap with the valve stem 105. Each set of mating sections has a low-position engagement section, a high-position holding section, and a descending reset section. The outlet end of the descending reset section of the mating section is connected to the inlet end of the low-position engagement section of another adjacent mating section. The cam 222 can move to the low-position engagement section of another adjacent mating section through the outlet end of the descending reset section of the mating section.

[0119] The above are merely preferred embodiments of this application and are not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. An anti-seize plug valve, comprising a valve body, a valve seat, a valve cover, a valve core, a valve stem, and a driving component, wherein the valve body has a medium flow cavity, the valve seat is disposed within the medium flow cavity, the valve core is disposed on the valve seat, and the outer sealing cone surface of the valve core is in contact with and seals the inner sealing cone surface of the valve seat, the valve cover is disposed on the valve body and has a mounting cavity communicating with the medium flow cavity, the valve stem is located within the mounting cavity and rotatably disposed on the valve cover, and the driving component is pulsatorically connected to the valve stem for driving the valve stem to move, thereby actuating the valve core, thereby realizing the opening and closing of the valve, characterized in that... The valve stem has an external friction cone surface, and the anti-seize plug valve further includes: A vibration-damping weld-breaking section, disposed within the mounting cavity, has an inner friction cone surface and a hammering surface. The inner friction cone surface and the outer friction cone surface are tightly fitted together to form a differential friction cone surface pair. The hammering surface is fitted with the valve core. An action integration unit is disposed in the mounting cavity. The input end of the action integration unit is connected to the valve stem, and the output end is connected to the vibration-damping welding part. The action integration unit is used to realize the separable transmission between the valve stem and the vibration-damping welding part. The motion integration unit is used to transmit the rotational torque of the valve stem to the vibration-breaking welding unit when it is connected to the vibration-breaking welding unit, so that the vibration-breaking welding unit breaks the microscopic cold weld between the outer sealing cone surface and the inner sealing cone surface through the hammering surface.

2. The anti-seize plug valve as described in claim 1, characterized in that, The motion integration unit is used to drive the vibration and welding breaking unit when the valve stem performs the preset action, and not to drive the vibration and welding breaking unit when the valve stem does not perform the preset action. The preset action is that the valve stem rotates from 0° to 4.5° in the forward direction. The forward rotation is rotation along the valve opening direction. When the valve stem is at 0°, the valve is in the fully closed state.

3. The anti-seize plug valve as described in claim 1, characterized in that, At least one constraint groove is provided on the inner wall of the valve cover, and the vibration-damped weld section includes: A trigger vibration mechanism is sleeved on the valve stem and has the hammering surface; A hammer nut, fitted onto the valve stem, has its upper end connected to the actuation integration part, its inner bore having the internal friction cone surface, and its lower end abutting against the triggering vibration mechanism; and At least one pawl trigger mechanism is provided, one end of which is hinged to the outer peripheral wall of the hammer nut, and the other end is in contact with the bottom of the constraint groove. The pawl trigger mechanism corresponds to the constraint groove one by one. The pawl trigger mechanism is used to prevent the hammer nut from circumferentially moving forward when it rotates, and is also used to unlock the hammer nut when it rotates to a preset angle, and to limit the axial height of the hammer nut by cooperating with the constraint groove, so that the hammer nut moves closer to the valve core during the process of rotating to the preset angle. The triggering vibration mechanism is axially located below the hammer nut and above the valve core. The actuation integration part is used to transmit the rotational torque of the valve stem to the hammer nut when it is connected to the hammer nut to drive the hammer nut to rotate, and not to be connected to the hammer nut when the hammer nut rotates to the preset angle, so that the triggering vibration mechanism breaks the microscopic cold weld between the outer sealing cone and the inner sealing cone through the hammering surface.

4. The anti-seize plug valve as described in claim 3, characterized in that, The upper end of the hammering nut has at least one protrusion structure, and the action integration part has at least one groove structure. The protrusion structure and the groove structure correspond one-to-one. The hammering nut is connected to the action integration part through the engagement of the protrusion structure and the groove structure.

5. The anti-seize plug valve as described in claim 3, characterized in that: The constraint groove has a first end and a second end, the second end being flush with the inner wall of the valve cover; on the same radial plane of the valve stem, the straight-line distance between the first end and the valve stem axis is greater than the straight-line distance between the second end and the valve stem axis; the bottom of the constraint groove is a curved surface that gradually sinks axially towards the valve core, starting from the first end and ending at the second end; during the process of the hammer nut rotating to the preset angle, the contact surface between the pawl trigger mechanism and the bottom of the constraint groove moves from the first end to the second end; the first end of the constraint groove and the second end of another constraint groove adjacent in the circumferential direction are collinear on the same axis of the valve cover.

6. The anti-seize plug valve as described in claim 3, characterized in that, The triggering vibration mechanism includes: An axial vibratory hammer is sleeved on the valve stem and has the hammering surface; A gasket, fitted onto the valve stem, with the lower end of the hammer nut abutting against the gasket; and An energy storage spring is sleeved on the valve stem, with one end of the energy storage spring abutting against the gasket and the other end abutting against the axial vibration hammer; As the hammer nut approaches the valve core, it compresses the energy storage spring through the gasket. When the hammer nut rotates to the preset angle, the pawl trigger mechanism unlocks the hammer nut, causing it to reset. The energy storage spring is then released, allowing the axial vibration hammer to break the microscopic cold weld between the outer sealing cone and the inner sealing cone through the hammering surface.

7. The anti-seize plug valve as described in claim 3, characterized in that, The pawl triggering mechanism includes: A pawl, hinged to the outer peripheral wall of the hammer nut; and A reset component, one end of which is connected to the hammer nut and the other end of which is connected to the pawl, is used to drive the pawl to engage with the constraint groove to prevent circumferential forward movement when the hammer nut rotates, and to limit the axial height of the hammer nut by cooperating with the constraint groove, so that the hammer nut moves closer to the valve core when rotating to the preset angle; Specifically, when the hammer nut rotates to the preset angle, the reset member is compressed, and the pawl is no longer located in the constraint groove, thereby unlocking the hammer nut.

8. The anti-seize plug valve as described in claim 1, characterized in that, The valve cover has an annular cam track on its inner wall, and the motion integration part includes: A disc-mounted device, movably mounted on the valve stem, is for transmission connection with the vibratory weld-breaking part and for rotating synchronously with the valve stem; and The separation device has one end connected to the disc device and the other end rollingly engaged with the annular cam track. The disc insert device is used to transmit the rotational torque of the valve stem to the vibratory weld breaking part when it is in drive connection with the vibratory weld breaking part. The separation device is used to change the axial height of the disc insert device by rolling cooperation with the annular cam track when the disc insert device rotates, so that the disc insert device is either in drive connection or not in drive connection with the vibratory weld breaking part.

9. The anti-seize plug valve as described in claim 8, characterized in that, The disc insertion device includes: An active toothed disc is mounted on the valve stem; A driven toothed insert, fitted onto the active toothed insert, has a groove structure for transmission connection with the vibratory weld-breaking part via the groove structure; and At least one return spring, the two ends of which abut against the active toothed disc and the driven toothed disc respectively, the return spring being used to continuously provide a preload force toward the valve core to the driven toothed disc; The active toothed disc and the driven toothed disc each have corresponding meshing structures to allow the active toothed disc and the driven toothed disc to mesh with each other. One end of the separating device is connected to the driven toothed disc. The separating device is used to change the axial height of the driven toothed disc by rolling cooperation with the annular cam track when the driven toothed disc rotates, so that the driven toothed disc is either connected to or not connected to the vibration-damped weld section.

10. The anti-seize plug valve as described in claim 8, characterized in that, The separation device includes: A separating rod, one end of which is connected to the disc-mounting device; and A cam is rotatably mounted on the other end of the separating rod and rolls in engagement with the annular cam track; The separating rod is used to change the axial height of the disc device by means of the rolling engagement between the cam and the annular cam track when the disc device rotates.

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