CN113309871A - Valve rod guide structure of forced sealing ball valve - Google Patents

Valve rod guide structure of forced sealing ball valve Download PDF

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Publication number
CN113309871A
CN113309871A CN202110632011.1A CN202110632011A CN113309871A CN 113309871 A CN113309871 A CN 113309871A CN 202110632011 A CN202110632011 A CN 202110632011A CN 113309871 A CN113309871 A CN 113309871A
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CN
China
Prior art keywords
valve
wedge
shaft
guide
guide rail
Prior art date
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Granted
Application number
CN202110632011.1A
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Chinese (zh)
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CN113309871B (en
Inventor
兰正辉
舒维泉
唐克超
文玉龙
刘佳
张政
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Construction Project Management Branch Of China National Petroleum Pipeline Network Group Co ltd
Zigong Zigao Valve Co Ltd
Original Assignee
Zigong Zigao Valve Co ltd
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Priority to CN202110632011.1A priority Critical patent/CN113309871B/en
Publication of CN113309871A publication Critical patent/CN113309871A/en
Application granted granted Critical
Publication of CN113309871B publication Critical patent/CN113309871B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0605—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor with particular plug arrangements, e.g. particular shape or built-in means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/06—Construction of housing; Use of materials therefor of taps or cocks
    • F16K27/067—Construction of housing; Use of materials therefor of taps or cocks with spherical plugs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0647—Spindles or actuating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0657—Particular coverings or materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0663—Packings
    • F16K5/0689—Packings between housing and plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F16K5/0663—Packings
    • F16K5/0694—Spindle sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—Details
    • F16K5/22—Features relating to lubrication
    • F16K5/227—Features relating to lubrication for plugs with spherical surfaces

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Taps Or Cocks (AREA)

Abstract

The invention discloses a valve rod guide structure of a forced sealing ball valve, which comprises a drive assembly, a valve cover and a valve body which are sequentially connected, wherein a valve rod and a wedge-shaped shaft connected with the valve rod are arranged in the valve cover; the lower part of the wedge-shaped shaft is provided with a wedge-shaped surface, and the ball body is provided with a wedge-shaped pin matched with the wedge-shaped surface; according to the invention, the traditional linear contact between the guide shaft and the guide rail groove is changed into surface contact, so that the contact area between the guide shaft and the guide rail groove is effectively increased, the guide shaft is prevented from damaging the guide rail groove, and the abrasion between the guide shaft and the guide rail groove is reduced; in addition, the invention reduces the extrusion surface stress on the groove side surface of the guide rail groove and the contact surface of the guide shaft, thereby effectively improving the guide matching stress of the guide rail groove and the guide shaft, reducing the abrasion between the guide rail groove and the guide shaft, greatly prolonging the service life of the guide shaft and the guide rail groove and reducing the maintenance cost.

Description

Valve rod guide structure of forced sealing ball valve
Technical Field
The invention relates to the technical field of ball valves, in particular to a valve rod guide structure of a forced sealing ball valve.
Background
The forced sealing ball valve is also called orbit ball valve, and the orbit ball valve and the gate valve belong to a same type of valve, and the difference is that a closing member of the forced sealing ball valve is a ball body, and the ball body rotates around the central line of a valve body to achieve the opening and closing of the valve. Ball valves are used in pipelines primarily to shut off, distribute and change the direction of flow of media. The forced sealing ball valve has the advantages of compact structure, reliable sealing, long service life, rapid action and the like, and is widely applied to various fields in recent years.
The guide structure of the forced sealing ball valve comprises a guide rail groove with equal width arranged on a valve rod and a guide shaft movably connected with the guide rail groove, and the guide shaft of the traditional forced sealing ball valve is cylindrical or has a roller structure. The forced sealing ball valve completely depends on the forced external force to drive the valve rod to operate, and forced sealing is realized. At the moment the valve is opened to achieve a forced seal full closure or full closure, a very large external driving force is required. The torque generated by driving the valve rod by the external force acts on the guide shaft, and the guide shaft is contacted with the guide shaft and is extruded by the shearing force of the lifting rotating flange of the valve rod and the contact of the side of the guide rail groove and the guide shaft. It can be seen that the stress of the guide shaft is very complicated, while the contact area of the traditional cylindrical guide shaft and the guide rail groove is small on the one hand, and the internal stress received on the other hand is large, so that the guide shaft and the guide rail groove are seriously abraded, the service lives of the guide shaft and the guide rail groove are short, the guide shaft and the guide rail groove need to be disassembled and repaired after being damaged, the production progress is influenced, the disassembly process is complicated, the labor intensity is high, time and labor are wasted, the efficiency is low, and the maintenance cost is high.
Disclosure of Invention
Aiming at the technical problems of serious abrasion, short service life and high maintenance cost of the traditional guide structure of the forced sealing ball valve, the invention provides the guide structure of the valve rod of the forced sealing ball valve.
The technical scheme adopted by the invention is as follows: the valve rod guide structure of the forced sealing ball valve comprises a drive assembly, a valve cover and a valve body which are sequentially connected, wherein a valve rod and a wedge-shaped shaft connected with the valve rod are arranged in the valve cover; the lower part of wedge axle is provided with the wedge face, is provided with the wedge pin that matches with the wedge face on the spheroid, the guide rail groove is including consecutive first straight flute section, spiral section and second straight flute section, first straight flute section and second straight flute section vertical arrangement, and the width of first straight flute section is the same with the width of second straight flute section, and the width of spiral section is greater than first straight flute section, and the guide shaft stretches into the parallel two first flat positions that are provided with in position to the guide rail inslot.
Compared with the traditional guide structure, the guide rail groove structure is symmetrically provided with two parallel first flat positions on the guide shaft, the spiral section of the guide rail groove is widened, the groove widths of the first straight groove section and the second straight groove section are matched with the distance between the two flat positions, and the groove width of the spiral section is matched with the distance between the diagonals of the two cambered surfaces of the guide shaft. When the guide shaft moves in the first straight flute section and the second straight flute section, the two sides of the guide rail groove are tightly attached to the first flat position, and the traditional linear contact is changed into surface contact, so that the contact area between the guide shaft and the guide rail groove is effectively increased, the guide shaft is prevented from damaging the guide rail groove, and the abrasion between the guide shaft and the guide rail groove is reduced. In addition, the stress of the extrusion surface on the groove side surface of the improved rear guide rail groove and the contact surface of the guide shaft is smaller, so that the guide matching stress between the groove side surface and the guide shaft is effectively improved, the abrasion between the groove side surface and the guide shaft is reduced, the service lives of the guide shaft and the guide rail groove are greatly prolonged, the maintenance cost is reduced, and the production efficiency is improved.
Furthermore, the two sides of the wedge-shaped shaft on which the ball body is arranged are provided with cylindrical pins, and the part of the wedge-shaped shaft, which is contacted with the cylindrical pins, is provided with a second flat position. The relative position of wedge axle and spheroid is guaranteed to the cylindric lock, and when the wedge axle was made elevating movement, cylindric lock and wedge axle sliding friction. The position that wedge axle and cylindric lock contacted is provided with the flat position of second, that is to say the face that wedge axle and cylindric lock contacted is the plane to the area of contact of wedge axle and cylindric lock can effectively be increased, wedge axle lift process's stationarity is guaranteed.
Furthermore, an upper end hole movably connected with the wedge-shaped shaft is arranged in the center of the upper end face of the sphere, and the center of the sphere flow passage hole is horizontally spaced from the center line of the upper end hole by a certain distance. The center of a ball flow channel hole of a traditional forced sealing ball valve is overlapped with the center line of a valve rod, namely, the center of the ball flow channel hole is arranged in a centering mode, the ball body rotates 90 degrees from a closed state to an open state under the influence of a ball sealing surface, the center of the ball flow channel hole and the center of the flow channel hole of the valve body are not on the same central line, a medium cannot completely pass through the valve body, the cross section area of medium circulation is reduced, and the medium circulation efficiency is reduced. Therefore, the center of the ball flow passage hole and the central line of the upper end hole are horizontally arranged at a certain distance. Force sealed ball valve when the closure state need be opened, drive assembly drives the lifting of valve rod, the guiding axle removes for the guide rail groove, under the cooperation of wedge face and wedge pin, the spheroid breaks away from the disk seat is stirred to the wedge axle, spheroidal sealed face breaks away from with the disk seat, along with the guiding axle removes in the guide rail inslot, spheroid reverse rotation 90, the runner hole of spheroidal runner hole and valve body communicates, the guiding axle continues to remove until the valve is opened entirely in the guide rail inslot, the center in spheroid runner hole is concentric with valve body runner hole, the circulation keeps full latus rectum when realizing the valve is opened entirely. The forced sealing ball valve adopts the design principle of the cam mechanism, and before the valve is opened and closed, the ball body is separated from the valve seat at first and then is rotated, so that no friction operation exists between the ball body and the valve seat in the opening and closing process, the abrasion is reduced, and the service life of the forced sealing ball valve is effectively prolonged; in addition, by the eccentric design mode, the center of the flow passage hole of the ball body needs to horizontally deviate a small distance relative to the center line of the hole at the upper end so as to ensure that the flow passage hole of the ball body is concentric with the flow passage hole of the valve body in the full-open state of the valve, and the full-diameter operation of the valve is realized; moreover, through an eccentric design mode, when the guide shaft moves in the guide rail groove, the ball body can incline, so that a gap is formed between the sealing surface of the ball body and the valve seat, and the sealing surface can be cleaned by a medium.
Further, the upper portion of the valve rod is provided with filler, a first grease injection valve is arranged on a valve cover corresponding to the filler, a cleaning hole communicated with an inner cavity of the valve cover is formed in the valve cover between the wedge-shaped shaft and the filler, a through hole communicated with the guide rail groove is formed in the top of the wedge-shaped shaft, a groove communicated with the valve body is formed in the bottom of the guide rail groove, a sewage discharge hole is formed in the valve body, and a sewage discharge valve is arranged on the sewage discharge hole. Firstly, the cleaning hole is communicated with the inner cavity of the valve cover and then communicated with the inner cavity of the valve body through the through hole, the guide rail groove and the open groove in sequence, so that air in the inner cavity of the valve body can be discharged during a ball valve hydraulic strength test, the error of the hydraulic strength test is reduced, and the test accuracy is ensured; secondly, the ball valve equipment is accomplished the back, and the accessible injects the washing liquid toward clean hole in toward the ball valve, can wash because of the assembly just moves impurity such as small burr, tiny iron powder that interlock extrusion etc. produced, and impurity passes through the blowoff hole and discharges, guarantees the cleanliness of spheroid inner chamber, reduces the part wearing and tearing that impurity brought, improves the life of ball valve.
Further, a second grease injection valve is arranged on the cleaning hole. After the ball valve is assembled and tested, a second grease injection valve can be arranged on the cleaning hole, lubricating grease flows into the inner cavity of the valve cover through the second grease injection valve and then flows into the guide rail groove and the open groove through the through hole, so that the wedge-shaped shaft, the guide rail groove, the guide shaft and the guide sleeve are lubricated, the friction among all parts is reduced, and the service life of the ball valve is prolonged; in addition, the upper part and the lower part can be pressed flatly through the lubricating channel, so that the pressure difference cannot be generated due to the change of the upper space under the condition of ensuring normal opening and closing work, and the generation of operation vibration is prevented.
Furthermore, a valve seat is clamped in the support ring, and the support ring is clamped in the valve body. The support ring of traditional ball valve links to each other through threaded connection or welding mode between the valve body, in case the support ring breaks down, just needs pull down whole ball valve and returns the factory maintenance, and the dismantlement process is complicated, and intensity of labour is big, wastes time and energy, inefficiency, and the maintenance cost is high, can not realize the online maintenance of ball valve. The valve body and the support ring are connected in an open-loop clamping manner, and the clamping ring is connected with the support ring in a clamping manner, so that the whole dismounting process is simple and rapid, time and labor are saved, the ball valve can be maintained on line, the maintenance efficiency is greatly improved, the labor intensity is reduced, and the time and the cost for returning to a factory for maintenance are saved.
Furthermore, a groove is arranged on the valve body, a circular clamping ring is arranged on the supporting ring, and the inner side surface of the clamping ring is flush with the inner side surface of the supporting ring; the rand is formed by a fixed snap ring and at least two activity snap rings concatenation, and fixed snap ring passes through countersunk head bolt and links to each other with the lock ring, is provided with convex outer snap ring on the outer lane of activity snap ring, and outer snap ring runs through the lock ring and extends to in the recess. The method specifically comprises the following steps: the clamping ring is formed by splicing the fixed clamping ring and the movable clamping ring, so that the clamping ring can be conveniently and nondestructively mounted and dismounted; the fixed clamping ring is connected with the support ring through the countersunk head bolt, so that the falling off of other movable clamping rings can be effectively prevented, the clamping ring is prevented from withdrawing from the support ring, and the fixation of the clamping ring and the support ring can be realized. In addition, because outer snap ring runs through the lock ring and extends to the recess, consequently the recess plays limiting displacement to outer snap ring, just also plays synchronous spacing fixed action to rand and lock ring, realizes fixing between lock ring and the valve body, prevents that the lock ring from withdrawing from the recess of valve body. In addition, the countersunk head bolt is hidden in the fixed snap ring, so that the bolt is prevented from protruding out of the fixed snap ring to influence the circulation of media in the valve body.
Further, the valve seat is made of elastic materials, a barb for preventing the valve seat from sliding out of the support ring is arranged on the support ring, the barb plays a role in fixing and limiting the valve seat, and the valve seat is prevented from sliding out of the support ring.
Furthermore, a first O-shaped sealing ring is arranged at the position where the top of the supporting ring is connected with the valve body, a second O-shaped sealing ring and a third O-shaped sealing ring are sequentially arranged on the side surface, connected with the valve seat, of the supporting ring from top to bottom, a fourth O-shaped sealing ring is arranged at the top of the supporting ring where the groove is located, and a graphite fireproof strip is arranged on the side surface, connected with the valve seat, of the supporting ring. The graphite fire-proof strip also has a fire-proof function; a plurality of sealing washers play multiple seal from a plurality of faces to supporting ring, disk seat and valve body, have effectively guaranteed sealed effect.
Furthermore, the sphere is integrally formed by cast steel, and hard alloy is welded on the sealing surface of the sphere in a surfacing mode; the wedge-shaped shaft and the guide shaft are subjected to high-frequency quenching treatment, and hard alloy is deposited on the surfaces of the wedge-shaped shaft, the guide shaft and the guide rail groove in a surfacing mode. The sphere is integrally formed by cast steel, so that the strength of the sphere is ensured, the manufacturing process is simpler, and the effect is better. The hard alloy is welded on the sealing surface of the ball body in a surfacing mode, so that the wear resistance of the sealing surface of the ball body is enhanced, the service life of the ball body is prolonged, and the sealing surface of the ball body is the surface, connected with the valve seat, of the ball body when the ball valve is closed. The wedge-shaped shaft and the guide shaft are stressed greatly in the opening and closing process of the valve and continuously rub in the opening and closing process, so that the wedge-shaped shaft and the guide shaft are hardened through high-frequency quenching, and the strength of the wedge-shaped shaft and the guide shaft is improved. Meanwhile, hard alloy is deposited on the surfaces of the wedge-shaped shaft, the guide shaft and the guide rail groove in a surfacing mode, so that the wear resistance of the wedge-shaped shaft, the guide shaft and the guide rail groove is enhanced, and the service life of the wedge-shaped shaft is prolonged.
The invention has the beneficial effects that:
1. the guide shaft and the guide rail groove are changed from traditional linear contact into surface contact, so that the contact area of the guide shaft and the guide rail groove is effectively increased, the guide shaft is prevented from damaging the guide rail groove, and the abrasion of the guide shaft and the guide rail groove is reduced.
2. The invention reduces the extrusion surface stress on the groove side surface of the guide rail groove and the contact surface of the guide shaft, thereby effectively improving the guide matching stress of the groove side surface and the guide shaft, reducing the abrasion between the groove side surface and the guide shaft, greatly prolonging the service life of the guide shaft and the guide rail groove, reducing the maintenance cost and improving the production efficiency.
3. The forced sealing ball valve of the valve adopts the design principle of a cam mechanism, firstly, the ball body is separated from the valve seat before the valve is opened or closed, and then, the ball body is rotated, so that no friction operation exists between the ball body and the valve seat in the opening and closing process, the abrasion is reduced, and the service life of the forced sealing ball valve is effectively prolonged.
4. According to the invention, through an eccentric design mode, the center of the flow passage hole of the ball body needs to horizontally deviate a small distance relative to the center line of the upper end hole to ensure that the flow passage hole of the ball body is concentric with the flow passage hole of the valve body in the full-open state of the valve, so that the full-diameter operation of the valve is realized; in addition, through an eccentric design mode, when the guide shaft moves in the guide rail groove, the ball body can incline, so that a gap is generated between the sealing surface of the ball body and the valve seat, and the sealing surface can be cleaned by a medium.
5. The valve body and the support ring are connected in an open-loop clamping manner, and the clamping ring is connected with the support ring in a clamping manner, so that the whole dismounting process is simple and rapid, time and labor are saved, the ball valve can be maintained on line, the maintenance efficiency is greatly improved, the labor intensity is reduced, and the time and the cost for returning to a factory for maintenance are saved.
6. According to the invention, lubricating grease can be injected into the inner cavity of the valve cover through the second grease injection valve, and then flows into the guide rail groove and the open groove through the through holes, so that the wedge-shaped shaft, the guide rail groove, the guide shaft and the guide sleeve are lubricated, the friction among all parts is reduced, and the service life of the ball valve is prolonged; the upper part and the lower part of the ball valve can be pressed flatly through the lubricating channel, so that the pressure difference cannot be generated due to the change of the upper space under the condition of normal opening and closing work, and the generation of operation vibration is prevented.
Drawings
Fig. 1 is a schematic view of a guide mechanism of a prior art positive seal ball valve.
Fig. 2 is an exploded view of the present invention.
Fig. 3 is a cross-sectional view of the present invention.
Fig. 4 is a schematic view of the construction of the wedge shaft.
Fig. 5 is a schematic view of a sphere.
Fig. 6 is a schematic structural view of the guide shaft.
Fig. 7 is an assembly schematic of the wedge shaft and the guide shaft.
Fig. 8 is a diagram showing a moving locus of the guide shaft in the guide rail groove after the deployment.
FIG. 9 is a schematic view of the assembly of the wedge shaft and ball.
Fig. 10 is a schematic view of the rotation of a sphere.
Fig. 11 is a partially enlarged view of a in fig. 3.
Fig. 12 is a schematic structural view of the support ring.
Figure 13 is a schematic view of the collar construction.
Labeled as:
1. a power head; 2. a bevel gear box; 3. a valve cover; 4. a valve body; 5. a valve stem; 6. a wedge shaft; 7. a sphere; 8. a valve seat; 9. a guide rail groove; 10. a guide shaft; 11. a support ring; 12. a first O-ring seal; 13. a second O-ring seal; 14. a third O-shaped sealing ring; 15. a fourth O-shaped sealing ring; 16. a graphite fire-retardant strip;
101. a first flat position;
301. a first grease injection valve; 302. cleaning the hole; 303. a second grease injection valve;
401. a blowoff valve; 402. a groove; 403. a lower end hole;
501. a filler;
601. a wedge-shaped surface; 602. a second flat position; 603. a through hole;
701. a wedge-shaped pin; 702. a cylindrical pin; 703. an upper end hole; 704. a lower shaft sleeve;
901. a first straight groove section; 902. a helical section; 903. a second straight groove section; 904. grooving;
110. a collar; 111. fixing the snap ring; 112. a movable snap ring; 113. a countersunk bolt; 114. an outer snap ring.
Detailed Description
In the description of the present invention, it should be noted that the terms "front", "upper", "lower", "left", "right", "vertical", "horizontal", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or element must have a specific orientation, be configured in a specific orientation, and operate, and thus, should not be construed as limiting the present invention.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
The invention is further described below with reference to the accompanying drawings.
Example one
Referring to fig. 1 to 10, the valve rod guide structure of the forced sealing ball valve of the invention comprises a drive assembly, a valve cover 3 and a valve body 4 which are connected in sequence, wherein a valve rod 5 and a wedge-shaped shaft 6 connected with the valve rod are arranged in the valve cover 3, a ball body 7 and a valve seat 8 are arranged in the valve body, two guide rail grooves 9 are symmetrically arranged on the wedge-shaped shaft, a guide shaft 10 is fixedly connected on the valve cover, and the guide shaft extends into the guide rail grooves; the lower part of wedge axle is provided with wedge face 601, is provided with the wedge pin 701 that matches with the wedge face on the spheroid, guide rail groove 9 is including consecutive first straight flute section 901, spiral section 902 and second straight flute section 903, and first straight flute section 901 and second straight flute section 903 vertical layout, and the width of first straight flute section is the same with the width of second straight flute section, and the width of spiral section is greater than first straight flute section, and the position that the guide shaft stretched into to the guide rail inslot is parallel is provided with two first flat position 101. The driving assembly of the present embodiment employs a power head 1 and a bevel gear box 2.
Referring to fig. 1, at present, guide structures of various manufacturers in China, including international and well-known manufacturers of forced sealing valves, are cylindrical and matched with equal-width guide rail grooves. Description of the acting force of the guide rail groove and the guide shaft: the first straight groove section is a matching length of a guide shaft and a guide groove which can occur when the valve is driven by a force to open or close, the spiral section rotates for 90 degrees, and the second straight groove section is a valve friction-free operation matching section. So that a large external force is only present in the region of the first straight groove section.
And (3) analyzing the acting force: the torque generated by driving the valve rod and the wedge shaft by external force acts on the guide shafts symmetrically arranged at left and right sides, and the guide shafts are contacted with the guide shafts to extrude stress by the lifting and rotating flange shearing force of the valve rod and the side of the guide rail groove.
F＝M/(dF/2) (1)
τ＝F/nA1 (2)
σjy＝F/nA2 (3)
In formula (1): f is the stress of the guide shaft, M is the torque, dFThe diameter of the wedge shaft portion where the guide rail groove is located can be deduced from fig. 1 and 8: at dFIn the case of the same M, the guide shaft force F in fig. 1 and 8 can be determined, and the guide shaft force F in both is the same.
In formula (2): tau is the shearing force of the flange of the guide shaft which is lifted and rotated by the wedge shaft, n is the number of the guide mechanisms, A1 is the shearing force area of the circumferential part of the guide shaft, and can be seen from figures 1 and 8: the guide shaft of fig. 8 has a larger shear-receiving area due to the two first flat positions, whereas n and F of fig. 1 and 8 are the same, and thus are derived from equation (2): the value of a1 in fig. 8 is greater and therefore the calculated value of τ is smaller, i.e. the guide shaft of the invention is subjected to smaller flange shear forces.
In formula (3): sigmajyIn order to contact the guide rail groove side with the guide shaft and press stress, n is the number of the guide mechanisms, and a2 is the shearing force bearing area of the circumferential part of the guide shaft, which can be seen from fig. 1 and 8: the guide shaft of fig. 8 has a larger shear-receiving area due to the two first flat positions, and n and F of fig. 1 and 8 are the same, thus being derived from equation (3): the value of A1 in FIG. 8 is larger, so that the calculated σ isjyThe value is smaller, that is, the contact extrusion stress of the guide rail groove side and the guide shaft is smaller.
In conclusion, the guide shaft of the invention is subjected to smaller flange shearing force, and the contact extrusion stress between the guide rail groove side and the guide shaft is also smaller.
Compared with the traditional guide structure, the guide rail groove structure has the advantages that the two parallel first flat positions are symmetrically arranged on the guide shaft, the spiral section of the guide rail groove is widened, the groove widths of the first straight groove section and the second straight groove section are matched with the distance between the two flat positions, and the groove width of the spiral section is matched with the distance between the diagonals of the two cambered surfaces of the guide shaft. When the guide shaft moves in the first straight flute section and the second straight flute section, the two sides of the guide rail groove are tightly attached to the first flat position, and the traditional linear contact is changed into surface contact, so that the contact area between the guide shaft and the guide rail groove is effectively increased, the guide shaft is prevented from damaging the guide rail groove, and the abrasion between the guide shaft and the guide rail groove is reduced. In addition, the stress of the extrusion surface on the groove side surface of the improved rear guide rail groove and the contact surface of the guide shaft is smaller, so that the guide matching stress between the groove side surface and the guide shaft is effectively improved, the abrasion between the groove side surface and the guide shaft is reduced, the service lives of the guide shaft and the guide rail groove are greatly prolonged, the maintenance cost is reduced, and the production efficiency is improved.
Referring to fig. 4 and 5, in this embodiment, cylindrical pins 702 are disposed on both sides of a wedge shaft disposed on a sphere, and a second flat portion 602 is disposed at a portion where the wedge shaft contacts the cylindrical pins. The relative position of wedge axle and spheroid is guaranteed to the cylindric lock, and when the wedge axle was made elevating movement, cylindric lock and wedge axle sliding friction. The position that wedge axle and cylindric lock contacted is provided with the flat position of second, that is to say the face that wedge axle and cylindric lock contacted is the plane to the area of contact of wedge axle and cylindric lock can effectively be increased, wedge axle lift process's stationarity is guaranteed.
The sphere of the embodiment is integrally formed by cast steel, and hard alloy is welded on the sealing surface of the sphere in a surfacing mode; the wedge-shaped shaft and the guide shaft are subjected to high-frequency quenching treatment, and hard alloy is deposited on the surfaces of the wedge-shaped shaft, the guide shaft and the guide rail groove in a surfacing mode. The sphere is integrally formed by cast steel, so that the strength of the sphere is ensured, the manufacturing process is simpler, and the effect is better. The hard alloy is welded on the sealing surface of the ball body in a surfacing mode, so that the wear resistance of the sealing surface of the ball body is enhanced, the service life of the ball body is prolonged, and the sealing surface of the ball body is the surface, connected with the valve seat, of the ball body when the ball valve is closed. The wedge-shaped shaft and the guide shaft are stressed greatly in the opening and closing process of the valve and continuously rub in the opening and closing process, so that the wedge-shaped shaft and the guide shaft are hardened through high-frequency quenching, and the strength of the wedge-shaped shaft and the guide shaft is improved. Meanwhile, hard alloy is deposited on the surfaces of the wedge-shaped shaft, the guide shaft and the guide rail groove in a surfacing mode, so that the wear resistance of the wedge-shaped shaft, the guide shaft and the guide rail groove is enhanced, and the service life of the wedge-shaped shaft is prolonged.
Example two
The center of a ball flow channel hole of a traditional forced sealing ball valve is overlapped with the center line of a valve rod, namely, the center of the ball flow channel hole is arranged in a centering mode, the ball body rotates 90 degrees from a closed state to an open state under the influence of a ball sealing surface, the center of the ball flow channel hole and the center of the flow channel hole of the valve body are not on the same central line, a medium cannot completely pass through the valve body, the cross section area of medium circulation is reduced, and the medium circulation efficiency is reduced.
Referring to fig. 9 and 10, in the first embodiment, an upper end hole 703 movably connected to the wedge shaft is provided at the center of the upper end surface of the ball, and the center of the ball flow passage hole is horizontally spaced from the center line of the upper end hole by a certain distance. Force sealed ball valve when the closure state need be opened, the electric head drives the valve rod through bevel gear case and promotes, the guiding axle removes for the guide rail groove, under the cooperation of wedge face and wedge pin, the spheroid breaks away from the disk seat is stirred to the wedge axle, spheroidal sealed face breaks away from with the disk seat, along with the guiding axle removes in the guide rail groove, spheroid reverse rotation 90, the runner hole of spheroidal runner hole and the runner hole intercommunication of valve body, the guiding axle continues to remove until the valve is opened entirely in the guide rail groove, the center and the valve body runner hole in spheroid runner hole are concentric, the circulation keeps full latus rectum when realizing the valve is opened entirely. The forced sealing ball valve adopts the design principle of the cam mechanism, and before the valve is opened and closed, the ball body is separated from the valve seat at first and then is rotated, so that no friction operation exists between the ball body and the valve seat in the opening and closing process, the abrasion is reduced, and the service life of the forced sealing ball valve is effectively prolonged; in addition, by the eccentric design mode, the center of the flow passage hole of the ball body needs to horizontally deviate a small distance relative to the center line of the hole at the upper end so as to ensure that the flow passage hole of the ball body is concentric with the flow passage hole of the valve body in the full-open state of the valve, and the full-diameter operation of the valve is realized; moreover, through an eccentric design mode, when the guide shaft moves in the guide rail groove, the ball body can incline, so that a gap is formed between the sealing surface of the ball body and the valve seat, and the sealing surface can be cleaned by a medium.
The working principle is as follows: referring to fig. 3, fig. 3 shows the closed state of the ball valve, in which the ball is pressed against the valve seat by the external force applied by the wedge shaft. When the ball valve needs to be opened, the electric head drives the valve rod to lift through the bevel gear box in an anticlockwise rotating mode, the guide shaft moves relative to the guide rail groove, referring to fig. 8, the guide shaft moves in the first straight groove section, the wedge shaft pulls the ball body to be separated from the valve seat under the matching of the wedge surface and the wedge pin, and the sealing surface of the ball body is separated from the valve seat; the guide shaft continues to move in the guide rail groove, after the guide shaft moves to the spiral section, the ball rotates 90 degrees anticlockwise, the flow passage hole of the ball is communicated with the flow passage hole of the valve body, the guide shaft continues to move in the guide rail groove until the valve is fully opened, the center of the flow passage hole of the ball is concentric with the flow passage hole of the valve body, and the full-diameter circulation is kept when the valve is fully opened.
When the ball valve is closed and needs to be opened, the electric head drives the valve rod to descend through clockwise rotation of the bevel gear box, the guide shaft moves relative to the guide rail groove, the guide shaft moves in the second straight groove section at the moment, the wedge shaft pulls the ball body to separate from the valve seat under the matching of the wedge surface and the wedge pin, and the sealing surface of the ball body is separated from the valve seat; and the guide shaft continuously moves in the guide rail groove, after the guide shaft moves to the spiral section, referring to fig. 10, the ball body rotates clockwise by 90 degrees, the guide shaft continuously moves in the first straight groove section of the guide rail groove, and the wedge-shaped shaft pushes the ball body to press the valve seat until the ball body is tightly pressed on the valve seat, so that the closing of the ball valve is completed.
EXAMPLE III
Referring to fig. 2 and 3, on the basis of the first embodiment, in the first embodiment, a filler 501 is arranged on the upper portion of a valve rod, a first grease injection valve 301 is arranged on a valve cover corresponding to the filler, a cleaning hole 302 communicated with an inner cavity of the valve cover is arranged on the valve cover between a wedge-shaped shaft and the filler, a through hole 603 communicated with a guide rail groove is arranged at the top of the wedge-shaped shaft, a slotted groove 904 communicated with a valve body is arranged at the bottom of the guide rail groove, a sewage discharge hole is arranged on the valve body, and a sewage discharge valve 401 is arranged on the sewage discharge hole.
The traditional forced sealing ball valve is also provided with a first grease injection valve, and a cleaning hole is not arranged, but the first grease injection valve only has a lubricating effect on a filler and a valve rod and cannot have a lubricating effect on a wedge-shaped shaft and a guide rail groove, so that the friction between parts is overlarge, and the service life of equipment is influenced; in addition, during the initial operation of ball valve assembly, burrs and fine iron powder are generated by occlusion and extrusion of all parts, and the wear among the parts is increased by untimely discharge, so that the service life of equipment is also influenced; and the traditional ball valve can also generate pressure difference during operation, so that the ball valve vibrates and has high noise.
Firstly, the cleaning hole is communicated with the inner cavity of the valve cover and then communicated with the inner cavity of the valve body through the through hole, the guide rail groove and the open groove in sequence, so that air in the inner cavity of the valve body can be discharged during a ball valve hydraulic strength test, the error of the hydraulic strength test is reduced, and the test accuracy is ensured; secondly, the ball valve equipment is accomplished the back, and the accessible injects the washing liquid toward clean hole in toward the ball valve, can wash because of the assembly just moves impurity such as small burr, tiny iron powder that interlock extrusion etc. produced, and impurity passes through the blowoff hole and discharges, guarantees the cleanliness of spheroid inner chamber, reduces the part wearing and tearing that impurity brought, improves the life of ball valve.
Referring to fig. 2, the present embodiment is provided with a second grease injecting valve 303 on the cleaning hole. After the ball valve is assembled and tested, a second grease injection valve can be arranged on the cleaning hole, lubricating grease flows into the inner cavity of the valve cover through the second grease injection valve and then flows into the guide rail groove and the open groove through the through hole, so that the wedge-shaped shaft, the guide rail groove, the guide shaft and the guide sleeve are lubricated, the friction among all parts is reduced, and the service life of the ball valve is prolonged; in addition, the upper part and the lower part can be pressed flatly through the lubricating channel, so that the pressure difference cannot be generated due to the change of the upper space under the condition of ensuring normal opening and closing work, and the generation of operation vibration is prevented.
Example four
Referring to fig. 11 and 12, in the first embodiment, on the basis of the first embodiment, the valve seat 8 is clamped in the support ring 11 in the valve body, and the support ring 11 is clamped in the valve body 4.
The support ring of traditional ball valve links to each other through threaded connection or welding mode between the valve body, in case the support ring breaks down, just needs pull down whole ball valve and returns the factory maintenance, and the dismantlement process is complicated, and intensity of labour is big, wastes time and energy, inefficiency, and the maintenance cost is high, can not realize the online maintenance of ball valve. Therefore, the valve body is connected with the support ring in an open-loop clamping manner, and the clamping ring is connected with the support ring in a clamping manner, so that the whole dismounting process is simple and rapid, time and labor are saved, the ball valve can be maintained on line, the maintenance efficiency is greatly improved, the labor intensity is reduced, and the time and the cost for returning to a factory for maintenance are saved.
Referring to fig. 11, 12 and 13, in the present embodiment, a groove 402 is provided on the valve body, a circular collar 110 is provided on the support ring, and the inner side surface of the collar is flush with the inner side surface of the support ring; the clamping ring is formed by splicing a fixed clamping ring 111 and three movable clamping rings 112, the fixed clamping ring 111 is connected with the support ring 11 through a countersunk bolt 113, an outer circular arc-shaped clamping ring 114 is arranged on the outer ring of each movable clamping ring, and the outer clamping ring 114 penetrates through the support ring and extends into the groove 402. The method specifically comprises the following steps: the clamping ring is formed by splicing the fixed clamping ring and the movable clamping ring, so that the clamping ring can be conveniently and nondestructively mounted and dismounted; the fixed clamping ring is connected with the support ring through the countersunk head bolt, so that the falling off of other movable clamping rings can be effectively prevented, the clamping ring is prevented from withdrawing from the support ring, and the fixation of the clamping ring and the support ring can be realized. In addition, because outer snap ring runs through the lock ring and extends to the recess, consequently the recess plays limiting displacement to outer snap ring, just also plays synchronous spacing fixed action to rand and lock ring, realizes fixing between lock ring and the valve body, prevents that the lock ring from withdrawing from the recess of valve body. In addition, the countersunk head bolt is hidden in the fixed snap ring, so that the bolt is prevented from protruding out of the fixed snap ring to influence the circulation of media in the valve body.
The disk seat of this embodiment is made by elastic material, is provided with the barb (not shown in the figure) that prevents the disk seat roll-off lock ring on the lock ring, and the barb plays fixed and limiting displacement to the disk seat, avoids the disk seat roll-off lock ring.
Referring to fig. 11, in this embodiment, a first O-ring 12 is disposed at a position where the top of the support ring is connected to the valve body, a second O-ring 13 and a third O-ring 14 are sequentially disposed from top to bottom on a side surface where the support ring is connected to the valve seat, a fourth O-ring 15 is disposed at the top of the support ring where the groove is located, and a graphite fire-proof strip 16 is disposed on a side surface where the support ring is connected to the valve seat. The graphite fire-proof strip also has a fire-proof function; a plurality of sealing washers play multiple seal from a plurality of faces to supporting ring, disk seat and valve body, have effectively guaranteed sealed effect.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. The valve rod guide structure of the forced sealing ball valve comprises a drive assembly, a valve cover (3) and a valve body (4) which are sequentially connected, wherein a valve rod (5) and a wedge-shaped shaft (6) connected with the valve rod are arranged in the valve cover (3), a ball body (7) and a valve seat (8) are arranged in the valve body, two guide rail grooves (9) are symmetrically arranged on the wedge-shaped shaft, a guide shaft (10) is fixedly connected to the valve cover, and the guide shaft extends into the guide rail grooves; the wedge-shaped shaft guide rail structure is characterized in that the guide rail groove (9) comprises a first straight groove section (901), a spiral section (902) and a second straight groove section (903) which are sequentially connected, the first straight groove section (901) and the second straight groove section (903) are vertically arranged, the width of the first straight groove section is the same as that of the second straight groove section, the width of the spiral section is larger than that of the first straight groove section, and two first flat positions (101) are arranged on the guide shaft in a position extending into the guide rail groove in parallel.
2. A guide structure for a valve stem of a positive seal ball valve according to claim 1, wherein the ball is provided with cylindrical pins (702) at both sides of a wedge shaft, and a second flat portion (602) is provided at a portion of the wedge shaft contacting the cylindrical pins.
3. A valve stem guide structure of a positive seal ball valve in accordance with claim 1, wherein the center of the upper end surface of the ball body is provided with an upper end hole (703) movably connected to the wedge shaft, and the center of the ball flow passage hole is horizontally spaced from the center line of the upper end hole by a certain distance.
4. A guide structure of a valve rod of a forced sealing ball valve according to claim 1, characterized in that the upper part of the valve rod is provided with a filler (501), a first grease injection valve (301) is arranged on a valve cover corresponding to the filler, a cleaning hole (302) communicated with an inner cavity of the valve cover is arranged on the valve cover between the wedge-shaped shaft and the filler, a through hole (603) communicated with the guide rail groove is arranged at the top of the wedge-shaped shaft, a slot (904) communicated with the valve body is arranged at the bottom of the guide rail groove, a sewage discharge hole is arranged on the valve body, and a sewage discharge valve (401) is arranged on the sewage discharge hole.
5. A positive seal ball valve stem guide structure as defined in claim 4, wherein the purge hole is provided with a second grease injection valve (303).
6. A valve rod guide structure of a forced sealing ball valve according to claim 1, characterized in that a support ring (11) in the valve body, the valve seat (8) is clamped in the support ring (11), and the support ring (11) is clamped in the valve body (4).
7. A positive seal ball valve stem guide structure as claimed in claim 6, wherein the valve body is provided with a groove (402), the support ring is provided with a circular collar (110), and the inner side surface of the collar is flush with the inner side surface of the support ring; the clamping ring is formed by splicing a fixed clamping ring (111) and at least two movable clamping rings (112), the fixed clamping ring (111) is connected with the support ring (11) through a countersunk bolt (113), an outer circular arc-shaped clamping ring (114) is arranged on the outer ring of each movable clamping ring, and the outer clamping ring (114) penetrates through the support ring and extends into the groove (402).
8. A positive seal ball valve stem guide structure as defined in claim 6, wherein the valve seat is made of an elastic material, and the support ring is provided with barbs for preventing the valve seat from slipping out of the support ring.
9. The guide structure of the valve rod of the forced sealing ball valve according to claim 6, wherein a first O-shaped sealing ring (12) is arranged at the position where the top of the support ring is connected with the valve body, a second O-shaped sealing ring (13) and a third O-shaped sealing ring (14) are sequentially arranged on the side surface where the support ring is connected with the valve seat from top to bottom, a fourth O-shaped sealing ring (15) is arranged on the top of the support ring where the groove is located, and a graphite fire-proof strip (16) is arranged on the side surface where the support ring is connected with the valve seat.
10. A valve stem guide structure of a forced sealing ball valve according to claim 1, wherein the ball is integrally formed of cast steel, and the sealing surface of the ball is welded with hard alloy; the wedge-shaped shaft and the guide shaft are subjected to high-frequency quenching treatment, and hard alloy is deposited on the surfaces of the wedge-shaped shaft, the guide shaft and the guide rail groove in a surfacing mode.
CN202110632011.1A 2021-06-07 2021-06-07 Valve rod guide structure of forced sealing ball valve Active CN113309871B (en)

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2221138Y (en) * 1995-03-29 1996-02-28 裴守智 Sealing ball valve with translational rotary single seat
CN102261487A (en) * 2011-05-07 2011-11-30 浙江万龙机械有限公司 Valve rod lifting track ball valve
CN104295764A (en) * 2014-09-26 2015-01-21 宣达实业集团有限公司 Forced sealing ball valve
CN106979352A (en) * 2017-04-12 2017-07-25 圣博莱阀门有限公司 The high temperature orbit ball valve used in molecular sieve device
CN207261704U (en) * 2017-08-24 2018-04-20 成都成高阀门有限公司 A kind of bracing type forced seal ball valve
CN108825810A (en) * 2018-07-10 2018-11-16 浙江福瑞科流控机械有限公司 Adjustable three eccentricity one-way valve seat orbit ball valve and its working method
CN109780307A (en) * 2019-01-16 2019-05-21 圣博莱阀门有限公司 A kind of pneumatic rail ball valve with buffering hydraulic damping device
CN109990110A (en) * 2019-05-05 2019-07-09 凯瑞特阀业有限公司 Forced seal ball valve
CN210265990U (en) * 2019-07-18 2020-04-07 成都金陵能源装备有限公司 Valve rod guide structure of forced sealing ball valve
CN112728151A (en) * 2020-12-31 2021-04-30 五洲阀门股份有限公司 Ball valve with multiple sealing track structure

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2221138Y (en) * 1995-03-29 1996-02-28 裴守智 Sealing ball valve with translational rotary single seat
CN102261487A (en) * 2011-05-07 2011-11-30 浙江万龙机械有限公司 Valve rod lifting track ball valve
CN104295764A (en) * 2014-09-26 2015-01-21 宣达实业集团有限公司 Forced sealing ball valve
CN106979352A (en) * 2017-04-12 2017-07-25 圣博莱阀门有限公司 The high temperature orbit ball valve used in molecular sieve device
CN207261704U (en) * 2017-08-24 2018-04-20 成都成高阀门有限公司 A kind of bracing type forced seal ball valve
CN108825810A (en) * 2018-07-10 2018-11-16 浙江福瑞科流控机械有限公司 Adjustable three eccentricity one-way valve seat orbit ball valve and its working method
CN109780307A (en) * 2019-01-16 2019-05-21 圣博莱阀门有限公司 A kind of pneumatic rail ball valve with buffering hydraulic damping device
CN109990110A (en) * 2019-05-05 2019-07-09 凯瑞特阀业有限公司 Forced seal ball valve
CN210265990U (en) * 2019-07-18 2020-04-07 成都金陵能源装备有限公司 Valve rod guide structure of forced sealing ball valve
CN112728151A (en) * 2020-12-31 2021-04-30 五洲阀门股份有限公司 Ball valve with multiple sealing track structure

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Inventor after: Lan Zhenghui

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