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WO1999058884A1 - Vanne a boisseau spherique - Google Patents

Vanne a boisseau spherique Download PDF

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Publication number
WO1999058884A1
WO1999058884A1 PCT/KR1999/000014 KR9900014W WO9958884A1 WO 1999058884 A1 WO1999058884 A1 WO 1999058884A1 KR 9900014 W KR9900014 W KR 9900014W WO 9958884 A1 WO9958884 A1 WO 9958884A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressurizing
ball
diameter portion
inlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR1999/000014
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English (en)
Inventor
Jang Hong Ahn
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO1999058884A1 publication Critical patent/WO1999058884A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16K5/0673—Composite packings
    • F16K5/0678—Composite packings in which only one of the components of the composite packing is contacting the plug

Definitions

  • the present invention relates to a ball valve, and in particular to an improved ball valve which is capable of effectively implementing a sealing effect between a ball and a seat without using a sealant and which requires only a small amount of force for effectively opening and closing a ball valve.
  • the conventional ball valve includes a valve body having a ball operating space formed therewithin and an inlet and outlet formed at both sides of the ball operating space, with a valve ball being rotatable within the ball operating space and having a valve hole communicating with the inlet and outlet, respectively.
  • the valve hole is opened to communicate with the inlet and outlet.
  • the center axis of the valve hole is perpendicular with respect to the center axis of the inlet and outlet, the inlet and outlet are blocked.
  • the above-described ball valve is classified into a side entry type ball valve and a top entry type ball valve.
  • the valve ball is inserted from one side of the valve body for thereby assembling the ball valve.
  • the valve ball is inserted from the top portion of the valve body.
  • FIGS 1 through 3 illustrate the conventional side entry type ball valve.
  • a valve body 10 includes a cylindrical body 11 and flange tubes 12 and 13.
  • a ball operating space is defined between the body 11 and the flange tubes 12 and 13, and an inlet P1 and an outlet P2 are formed respectively in the flange tubes 12 and 13.
  • the valve ball 20 is inserted into the ball operating space in the direction that the flange tube 13 is assembled.
  • a ball rotation member is assembled from the top of the body 11.
  • Big diameter portions 12a and 13a and small diameter portions 12b and 13b are formed in the respective inner circumferential surfaces of the flange tubes 12 and 13, and respective spring engaging surfaces 12c and 13c are 2 formed therebetween.
  • Inner flange portions 12d and 13d fixedly engaged with the respective ends of the body 11 by fixing screws 14a and 15a are formed in the inner end portions of the flange tubes 12 and 13.
  • outer flange portions 12e and 13e having screw holes 14b and 15b are formed in the respective outer end portions of the same for connecting a pipe line (not shown).
  • the valve ball 20 includes an outer circumferential surface portion 21 for blocking the inlet P1 and the outlet P2, and a valve hole 22 for communicating the inlet P1 with the outlet P2.
  • a ball shaft 21 for blocking the inlet P1 and the outlet P2
  • a valve hole 22 for communicating the inlet P1 with the outlet P2.
  • each bearing plate 25 is in turn fixing protrusions 24 formed in an inner circumferential surface in the ball operating space by fixing pins 24a.
  • the bearing plates 25 are constructed such that the circular support hole
  • the bushing 26 is made of a material such as copper and is disposed at a friction point.
  • the ball rotation unit includes a decelerating member 28 for decelerating the rotation of an operating handle 27 and a stem 29 connecting the output shaft of the decelerating member 28 and the ball shaft 23.
  • Seat assemblies 30 and 40 are respectively inserted into the flange tubes
  • the seat assemblies 30 and 40 respectively include seat rings 31 and 41 inserted into the flange tubes 12 and 13 and seats 32 and 42 engaged with the seat rings 31 and 41 and being closely contacted with the outer circumferential surface portion 21 of the valve ball 20.
  • Big diameter portions 31a and 41 a and small diameter portions 31 b and 41 b respectively corresponding with the big diameter portions 12a and 13a and the small diameter portions 12b and 13b formed in the inner circumferential 3 surfaces of the flange tubes 12 and 13 are formed in the outer circumferential surfaces of the seat rings 31 and 41.
  • Spring engaging surfaces 31c and 41c to which respective pressurizing springs 34 and 44 are engaged are respectively formed between the big diameter portions 31a and 41a and the small diameter portions 31 b and 41b.
  • Pressurizing surfaces 31 d and 41 d against which the fluid pressure from the inlet P1 and outlet P2 is applied are formed in the respective outer end portions of the seat rings 31 , 41.
  • Slanted surfaces 31 e and 41 e to which a predetermined fluid pressure of a fluid flowing in the interior of the valve hole 22 is applied are formed in the respective inner end portions of the seat rings 31 , 41.
  • O-rings 33 and 43 are respectively inserted into respective grooves formed in the outer circumferential surface of the small diameter portions 31 b and 41 b of the seat rings 31 and 41 and respectively closely contact with the small diameter portions 12b and 13b of the flange tubes 12 and 13 for thereby implementing a sealing effect.
  • Pressurizing springs 34 and 44 are respectively disposed between the spring engaging surfaces 31c and 41c of the seat rings 31 and 41 and the spring engaging surfaces 12c and 13c of the flange tubes 12 and 13.
  • the thickness A(and hence the area) of the pressurizing surfaces 31a and 41a is greater than the thickness B(and hence the area) of the slanted surfaces 31 b and 41 b, Poau>Pobu, Poad>Pobd.
  • the contacting force between the seat 32 engaged to the seat ring 31 in the side of the inlet P1 and the outer circumferential surface portion 21 of the valve ball 20 is (Poau + Posu) - Pobu
  • the contacting force between the seat 42 engaged to the seat ring 41 in the side of the outlet P2 and the outer circumferential surface portion 21 of the valve ball 20 is (Poad + Posd) - Pobd.
  • the pressure Pcbd(Pcd x B) applied to the pressurizing surface 41 e of the seat ring 41 at the outlet P2 side is smaller than the pressure Pcad applied to the pressurizing surface 41 d of the seat ring 41 at the outlet P2 side, so that the 5 contacting force (Pcau + Pcsu) - Pcbu between the seat 32 at the inlet P1 side and the outer circumferential surface portion 21
  • the internal leakage is a leakage between the up stream inlet P1 and the down stream outlet P2 in a state that the ball valve is closed. Namely, even in the state that the ball valve is closed, the fluid should be prevented from flowing to the outlet P2 side through the ball operating space.
  • the seats 32 and 42 are damaged, a sufficient contacting state between the seats 32 and 42 and the valve ball 20 may not be implemented due to the pressure applied to the pressurizing surfaces 31 d and 41 d and the elastic forces of the pressurizing springs 34 and 44, so that an internal leakage occurs.
  • a sealant such as grease is packed between the seats 32 and 42 and the valve ball 20.
  • sealant injection portions 16a and 17a are respectively formed in the outer circumferential walls of the flange tubes 1 and 13, and one end portion of each of the seat rings 31 and 41 is respectively connected with the corresponding sealant inlets 16a and 17a, and in the other end portions of the same, sealant injection paths 16b and 17b are formed, which are opened at the slanted surfaces 31e and 41e, so that the sealant is provided between the slanted surfaces 31 e and 41 e and the seats 32 and 42 and the valve ball 20.
  • check valves 16c and 17c are installed for preventing the sealant provided through the sealant injection portions 16a and 17a from flowing 6 reversely.
  • the ball valve includes a ball operating space formed in the interior when the inlet and outlet are engaged, a pair of flange type bodies having an opening portion through which the ball is provided on the upper portion of the ball operating space and a cover for covering the opening.
  • the flange body in order to disassemble the valve ball rotatably installed in the ball operating space, the flange body must be disengaged from the pipe and then the flange body must be disengaged for thereby disassembling the valve ball and the seat, so that the assembling and disassembling operation of the valve is complicated.
  • a ball valve which includes a valve body including a cylindrical body portion and a pair of flange tubes engaged at both sides of the body, said flange tubes respectively forming an inlet and an outlet and each having a big diameter portion and a small diameter portion formed in an inner circumferential surface of the same and a spring engaging surface formed between the big diameter portion and the small diameter portion; a valve ball rotatably installed within a ball operating space defined within the valve body and having a valve hole for communicating the inlet and outlet and an outer circumferential surface for blocking the inlet and the outlet; a pair of seat assemblies including a big diameter portion and a small diameter portion corresponding with the big and small diameter portions of a corresponding flange tube; a spring engaging surface formed between the big diameter portion and the small diameter portion; a pressurizing surface formed in an outer end portion; a seat ring having a slanted surface formed at an inner end portion for contacting with the valve ball and a de
  • a ball valve which includes a valve body including a ball operating space formed interiorly therein; an opening portion formed in an upper portion of the valve body; a pair of flange-shaped body portions extending laterally therefrom and respectively defining an inlet and an outlet; and a cover for covering the opening in the body; a valve ball rotatably installed within the ball operating space and having a valve hole for communicating the inlet and outlet and an outer circumferential surface for blocking the inlet and the outlet; a seat assembly including a big diameter portion and a small diameter portion corresponding with a big diameter portion and a small diameter portion of a corresponding flange tube; a spring engaging surface formed between the big diameter portion and the small diameter portion; a pressurizing surface formed in an outer end portion; a seat ring having a slanted surface formed in an inner end portion for contacting with the valve ball and a depressurizing surface formed in an inner end portion and contacting with a space formed
  • a ball valve which includes a valve body including a cylindrical body portion and a pair of flange tubes engaged at respective sides of the body, said flange tubes respectively forming an inlet and an outlet and each having a big diameter portion and a small diameter portion formed in an inner circumferential surface of the same with a spring engaging surface formed between the big diameter portion and the small diameter portion; a valve ball rotatably installed within a ball operating space defined within the valve body and having a valve hole for communicating with an outer circumferential surface partitioning the inlet and the outlet and the inlet and the outlet, respectively; a seat assembly including a big diameter portion and a small diameter portion corresponding with the big and small diameter portions of the flange tube; a spring engaging surface formed between the big diameter portion and the small diameter portion; a pressurizing surface formed in an outer end portion; a seat ring having a slanted surface formed at an inner end portion for contacting with the valve ball and a depress
  • Figure 1 is a cross-sectional view illustrating a conventional ball valve
  • Figure 2 is an enlarged cross-sectional view illustrating the portion "A" of Figure 1 ;
  • Figure 3 is an enlarged cross-sectional view illustrating the portion "B" of Figure 2;
  • FIGS. 4 through 8 are views illustrating a ball valve according to a first embodiment of the present invention, of which:
  • Figure 4 is a cross-sectional view illustrating an open state of a ball valve according to the present invention.
  • Figure 5 is a cross-sectional view illustrating a closed state of a ball valve according to the present invention.
  • Figure 6 is an enlarged cross-sectional view illustrating the portion 11
  • Figure 7 is an enlarged cross-sectional view illustrating the portion "D" of Figure 6;
  • Figure 8 is an enlarged cross-sectional view taken along line VIII- VIII of Figure 5;
  • FIGS 9 through 11 are views illustrating a ball valve according to a second embodiment of the present invention, of which:
  • Figure 9 is a cross-sectional view illustrating an open state of a ball valve according to the present invention
  • Figure 10 is an enlarged cross-sectional view illustrating the portion "E" of Figure 9;
  • Figure 11 is an enlarged cross-sectional view illustrating the portion "F" of Figure 10;
  • FIGS 12 through 15 are views illustrating a ball valve according to a third embodiment of the present invention, of which:
  • Figure 12 is a cross-sectional view illustrating an open state of a ball valve according to the present invention.
  • Figures 13 through 15 are partial enlarged cross-sectional views illustrating a disassembling procedure of a ball valve according to the present invention.
  • the ball valve according to the first embodiment of the present invention includes a valve body 110 having a ball operating space and an inlet P1 with outlet P2, a valve ball 120 rotatably installed in the ball operating space and having a valve hole 122 communicating the inlet P1 and the outlet P2 and an outer circumferential surface portion 121 blocking the inlet P1 and the outlet P2, seat assemblies 130 and 140 respectively installed in the inner circumferential surface portions of the inlet P1 and outlet P2 of the valve body 110, and a seat pressure control unit for pressing the seat assemblies 130 and 140 against the outer circumferential surface portion 121 of the valve ball 120. 12
  • the valve body 110 includes flange tubes 112 and 113 engaged to both sides of a cylindrical body 111.
  • the ball operating space is formed by the cylindrical body 111 and the inner end portions of the flange tubes 112 and 113, and the inlet P1 and the outlet P2 are formed in the flange tubes 112 and 113, respectively.
  • Big diameter portions 112a and 113a and small diameter portions 112b and 113b are formed in the respective inner circumferential surfaces of the flange tubes 112 and 113 with a step(shouldered) therebetween.
  • Spring engaging surfaces 112c and 113c against which pressurizing springs 134 and 144 of a seat pressurizing control unit are engaged are respectively formed by the steps(shoulders) between the big diameter portions 112a and 113a and the small diameter portions 112b and 113b.
  • Inner flange portions 112d and 113d fixedly engaged with both sides of the body 111 by fixing screws 114a and 115a or bolts are respectively formed in the inner end portions of the flange tubes 112 and 113, and outer flange portions 112e and 113e having screw holes 114b and 115b are respectively formed in the outer end portions of the same for connecting a pipe line (not shown).
  • the valve ball 120 includes an outer circumferential surface portion 121 blocking the inlet P1 and the outlet P2 valve ball 120 is rotated to its closed position and a valve hole 122 communicating the inlet P1 with the outlet P2 when the valve ball 120 is in its open position.
  • the valve ball 120 has at each of its top and bottom portions a protruded ball axis 123 by which the valve ball 120 is rotatably supported in a circular support hole 125a of a bearing plate 125 and a bushing 126 formed between the inner circumferential surface of the circular support hole 125a of the bearing plate 125 and the outer circumferential surface of the ball shaft 123.
  • the plate 125 is fixed to fixing protrusions 124 formed in an inner circumferential surface of the ball operating space by fixing pins 124a.
  • each bearing plate is configured with the circular support hole 125a formed at a center portion of a square plate, and the inner diameter of the circular support hole 125a is smaller than the outer diameter of the ball shaft 123 by the thickness of the bushing 126.
  • the bushing 126 is 13 made of a material such as copper and is friction fitted.
  • a space S1 is formed between an end portion of the ball shaft 123 and an inner surface of the body 111 , and spaces S2 and S3 formed by the outer circumferential surface 121 of the valve ball 120 are blocked by the bearing plate 125.
  • the bearing plate 125 is square-shaped, the space S1 and the spaces S2 and S3 communicate with each other through paths "a".
  • the ball rotation unit includes an operating control handle 127, a decelerating unit 128 decelerating the rotation of the operating control handle 127 and a stem 129 connecting an output shaft of the decelerating unit 128 with the upper ball shaft 123a.
  • the seat assemblies 130 and 140 include seat rings 131 and 141 respectively inserted into the inner circumferential surfaces of the flange tubes
  • the seat rings 131 and 141 include respective big diameter portions 131a and 141a and respective small diameter portions 131 b and 141 b respectively formed on an outer circumferential surface thereof and corresponding respectively with the big diameter portions 112a and
  • Depressurizing surfaces 131f and 141f respectively contacting with the spaces S2 and S3 between the inner circumferential surface of the body 111 and the outer circumferential surface of the valve ball 120 are formed at respective inner end 14 portions of the seat rings 131 , 141.
  • the slanted surfaces 131e and 141e are formed to face with the inlet P1 and the outlet P2.
  • O-rings 133a, 143a and 133b, 143b are installed in ring grooves formed respectively in the outer circumferential surfaces of the big diameter portions
  • Pressurizing springs 134 and 144 are installed between the spring engaging surfaces 112c and 113c of the flange tubes 112 and 113 and the spring engaging surfaces 131 c and 141c of the seat rings 131 and 141 for elastically urging the seat rings 131 and 141 toward the valve ball 120.
  • the seat pressure control unit includes a pressurizing fluid supply source 151 , a main supply tube 152 connected with the pressurizing fluid supply source
  • pressurizing supply tubes 153 and 154 having respective pressurizing valves 153a and 154a, one end of each of which tubes 153, 154 is connected with the main supply tube 152 and the other end of each of which is communicated with a respective space formed between the spring engaging surfaces 112c and
  • a depressurizing connection tube 155 having a depressurizing valve 155a, one end of which tube 155 is connected with the main supply tube 152 and the other end of which tube 155 is connected with the space S1 formed between the inner circumferential surface of the body 111 and the outer circumferential surface of the valve ball 120.
  • the pressurizing fluid supply source 151 pressurizes a fluid which does not react with the fluid flowing in the pipe in which the ball valve is connected.
  • a fluid which does not react with the fluid flowing in the pipe in which the ball valve is connected.
  • the fluid flowing within the pipe is chlorine gas, N 2 gas or an inert gas such as Ar may be used as the pressurizing fluid.
  • the depressurizing connection tube 155 passes through the wall of the body 111 and communicates with the space S1.
  • the valves 152a, 153a, 154a and 155a may be selected from a manual operating valve or a solenoid valve. 15
  • the seat rings 131 and 141 in which the seats 132 and 142 are engaged are pressurized by the seat pressure control unit, so that the contacting force between the seats 132 and 142 and the valve ball 120 is increased for thereby preventing an internal leakage.
  • the entire pressure Ptu applied to the seat ring 131 at the inlet P1 side is obtained by summing the pressure Pcau applied to the pressurizing surface 131d by the pressure Pcu of the fluid and the pressure Pfu applied to the spring engaging surface 131 c by the pressurizing fluid, namely, "Pcau + Pfu".
  • the entire pressure applied to the seat ring 141 at the outlet P2 side is obtained by summing the pressure Pcad applied to the pressurizing surface 141d by the pressure Pcd of the fluid at the outlet P2 side and the pressure Pfd applied to the spring engaging surface 141 c by the pressurizing fluid, namely, "Pcad + Pfd".
  • the pressure applied to the depressurizing surfaces 131f and 141f of the seat rings 131 and 141 is increased more than the pressure which is obtained by summing the pressure applied to the pressurizing surfaces 131d and 141d and the elastic force of the spring rings 134 and 144, so that the valve ball 120 is able to be easily rotated by backwardly moving the seat rings 131 and 141.
  • the depressurizing valve 155a is opened, and the 17 pressurizing fluid of the pressurizing fluid supply source 151 is supplied to the depressurizing surfaces 131f and 141f through the main supply tube 152, the depressurizing connection tube 155, the space S1 and the spaces S2 and S3, so that the pressure applied to the depressurizing surfaces 131f and 141f becomes a difference pressure ⁇ t, and the depressurizing valve 155a is then closed.
  • the depressurizing force (Pb+Pd) applied to the seat ring 131 is larger than the pressurizing force (Pc+Pa+Ps), so that the seat ring 131 moves backwardly, and the seat 132 is separated from the outer circumferential surface portion 121 of the valve ball 120, so that the inlet P1 and the spaces S2 and S3 communicate with each other.
  • the difference pressure ⁇ Pt between the entire pressure Ptu applied to the seat ring 131 at the inlet side and the entire pressure Ptd applied to the seat ring 141 at the outlet side is decreased, so that it is possible to rotate the valve ball 120 using a small amount of force, whereby it is possible to prevent friction and damage of the seats 132 and 142 and the ball 120 which are the disadvantages of the conventional ball valve.
  • valve ball 120 is rotated and closed, when the main valve 152a is closed and the depressurizing valve 155a is opened, the pressure in the spaces S1 , S2 and S3 and the pressure applied to the spring engaging surfaces 131 c and 141c become equalized, so that the seat rings 131 and 141 move forwardly by the elastic force of the pressurizing springs 134 and 144, and the seats 132 and 142 contact with the outer circumferential surface portion
  • FIGS 9 through 11 illustrate a ball valve according to another embodiment of the present invention.
  • the thickness(and hence the area) of the slanted surfaces 231 e and 241 e is greater than the thickness A ( and hence the area) of the pressurizing surfaces 231 d and 241 d of the seat rings 231 and 241 , and the pressurizing supply tube 253 at the inlet side and the pressurizing supply tube 254 at the outlet side are extended, and bypass tubes 256 and 257 19 communicate respectively with the pressurizing surfaces 231 d and 241 d, and bypass valves 256a and 257a are respectively installed in the bypass tubes 256 and 257.
  • Parts and assemblies which are similar to those in the earlier embodiment of the present invention are assigned identical reference numerals and their repeated detailed description will be omitted.
  • the main valve 252a, the depressurizing valve 255a, and the bypass valve 257a at the outlet side are opened, and the pressurizing valves 253a and 254a and the bypass valve 256a at the inlet side are closed.
  • the pressure at the inlet side is applied to the spring engaging surface 241c of the seat ring 241 at the outlet side through the bypass tube 256 at the inlet side, the pressurizing supply tube 253 at the inlet side and the pressurizing supply tube 254 at the outlet side.
  • the seat 242 closely contacts with the outer circumferential surface of the valve ball 220, so that it is possible to prevent an internal leakage between the inlet and outlet.
  • the pressure applied to the spring engaging surface 241c of the seat ring 241 at the outlet side is removed through the pressurizing supply tube 254 at the outlet side and the bypass tube 257.
  • the pressure Pcd at the outlet P2 is applied only to the pressurizing surface 241 d and the slanted surface 241 e.
  • the pressure Pcbd applied to the slanted surface 241 e is larger than the pressure Pcad applied to the pressurizing surface 241 d, so that the seat ring 241 moves backwardly. Therefore, the seats 232 and 242 are separated from the outer circumferential surface portion 221 of the valve ball 220, and the inlet P1 and the outlet P2 communicate with each other 20 through the spaces S2 and S3. Therefore, the fluid in the side of the inlet P1 flows toward the outlet P2, and the difference pressure ⁇ P between the inlet and the outlet is decreased.
  • the inlet P1 and the outlet P2 can be communicated via the bypass tubes 256 and 257 and the pressurizing supply tubes 253 and 254, in a state that the ball valve is closed, it is possible to control the bypass valves 256a and 257a without rotating the valve ball 220, whereby a predetermined amount of fluid can be made to flow from the inlet P1 to the outlet P2. Therefore, a large amount of fluid is able to flow by the rotation of the valve ball 220, and a small amount of fluid is able to flow by operating the bypass valves 256a and 257a, so that the ball valve is applicable as a control valve.
  • Figures 12 through 15 illustrate a ball valve according to another embodiment of the present invention which is adapted to a top entry type ball valve.
  • a valve body 310 is configured to have an inlet P1 and an outlet P2, and a ball operating space is formed therein.
  • the ball valve includes a valve body 310 formed as a single unit with a pair of flange-shaped bodies 312, 313 extending outwardly at the respective sides thereof.
  • An opening 311 is formed in the top of the valve body 310 for permitting the insertion of a valve ball 320 and seat rings 331 , 341 into the valve body 310. The opening 311 is closed by a cover
  • the cover 319 is engaged to the valve body 310 by fixing screws or bolts.
  • Seat ring fixing screws 361 and 362 are threadedly engaged in the 2 1 bodies 312 and 313 for fixing the seat rings 331 and 341 in respective rearwardly moved positions.
  • Fixing portions 361a and 362a are formed in the respective lower end portions of the seat ring fixing screws 361 and 362, and fixing grooves 335 and 345 corresponding with the fixing portions 361a and 362a are respectively formed in the seat rings 331 and 341.
  • the seat ring fixing screws 361 and 362 have respective square head portions 361 b and 362b, and corresponding wrench shafts 363 and 364 are rotatably engaged in the cover 319 for respectively rotating the seat ring fixing screws 361 and 362.
  • the fixing portions 361a and 362a and the fixing grooves 335 and 345 are conically shaped.
  • Square groove portions 363a and 364a are respectively formed in the lower end portions of the wrench shafts 363 and 364 to be engaged with the square head portions 361 b and 362b of the seat ring fixing screws 361 and 362 , and corresponding square head portions 363b and 364b are respectively formed on the upper end portions of the same for implementing an easier rotation of the screws 361 , 362.
  • reference numerals 365 and 366 represent O-rings for sealing the portion between the cover 319 and the wrench shafts 363 and 364.
  • the seat ring fixing screws 361 and 362 and the wrench shafts 363 and 364 are shown in Figure 13.
  • the fixing portions 361a and 362a of the seat ring fixing screws 361 and 362 are not inserted into the fixing grooves 335 and 345 of the seat rings 331 and 341. Namely, the fixing portions 361a and 362a are separated from the big diameter portions 331a and 341a of the seat rings 331 and 341 , so that the seat rings 331 and 341 move forwardly and rearwardly by the pressurizing and depressurizing operation. Since the opening/closing operation and the pressurizing and depressurizing operations are the same as the embodiments of Figures 4 through 8, the detailed description thereof will be omitted.
  • the valve ball and the seats may be disassembled without disengaging the valve body 310 from the pipe line.
  • the seat rings 331 and 341 are rearwardly moved in the manner 22 of the embodiments of Figures 4 through 8 from the state shown in Figure 13 to the state shown in Figure 14. Therefore, the fixing portions 335 and 345 of the seat rings 331 and 341 are positioned below the corresponding fixing portions 361 a and 362a of the seat ring fixing screws 361 and 362. In this state, the square head portions 363d and 364d of the wrench shafts 363 and 364 which are rotatably engaged in the cover 319 are rotated using a tool such as a wrench, etc.
  • the seat ring fixing screws 361 and 362 are rotated in the screw disengaging direction using a tool such as a wrench for thereby separating the fixing portions 361a and 362a from the fixing grooves 335 and 345 of the seat rings 331 and 341. Thereafter, the seat rings 331 and 341 are moved to the ball operating space and then are removed through the opening 311 for thereby disassembling the seat rings 331 and 341.
  • the assembling procedure of the same is performed in the reverse sequence of the disassembling operation. In the present invention, it is possible to disassemble the valve ball 320 and the seat rings 331 and 341 without removing the valve body 310 from the pipe line. Therefore, it is possible to easily implement an exchange operation of the valve ball 320 and the seat rings 331 and 341.
  • the embodiment of Figures 4 through 8 is adapted to the top entry type ball valve. More preferably, the embodiment of Figures 9 through 11 may be adapted to the top entry type ball valve.
  • the ball valve according to the present invention may be used as a control valve.
  • the ball valve according to the present invention is adapted to a top entry type ball valve, it is possible externally to fix the seat rings in a state that the seat rings are rearwardly moved. Therefore, the valve ball and seats are easily removed without disassembling the valve body from the pipe line.

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

Abstract

Une vanne à boisseau sphérique possède des ressorts de mise en pression qui poussent élastiquement des sièges vers une surface circonférentielle extérieure d'une vanne à boisseau sphérique, des joints toriques insérés dans une partie à grand diamètre et une partie à petit diamètre desdits sièges, et qui viennent en contact étroit avec des parties à grand diamètre et des parties à petit diamètre de tubes à bride; une unité de commande de la pression sur les sièges, constituée d'une source d'alimentation en fluide de pressurisation, d'un tube d'alimentation principale relié à ladite source d'alimentation en fluide de pressurisation et dans lequel une soupape principale est prévue, de tubes d'alimentation en fluide de pressurisation côté entrée et côté sortie, dont une extrémité est reliée au tube d'alimentation principal et l'autre extrémité est reliée à un espace formé entre les surface venant en contact avec les ressorts. Chaque tube d'alimentation en fluide de pressurisation côté entrée et côté sortie possède une soupape de mise en pression, et un tube de raccord de dépressurisation dont une extrémité est reliée au tube d'alimentation principale et l'autre extrémité est reliée à un espace formé entre une surface circonférentielle du corps de robinet et une partie d'extrémité d'un axe de boisseau, le tube de raccord de dépressurisation comprenant une soupape de mise hors pression.
PCT/KR1999/000014 1998-05-12 1999-01-12 Vanne a boisseau spherique Ceased WO1999058884A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1019980017003A KR100274656B1 (ko) 1998-05-12 1998-05-12 볼 밸브
KR1998/17003 1998-05-12

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Publication Number Publication Date
WO1999058884A1 true WO1999058884A1 (fr) 1999-11-18

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PCT/KR1999/000014 Ceased WO1999058884A1 (fr) 1998-05-12 1999-01-12 Vanne a boisseau spherique

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WO (1) WO1999058884A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002029294A3 (fr) * 2000-10-03 2002-06-20 Fisher Controls Int Robinet de regulation de debit fluidique a basculement de joint d'etancheite limite
CN102374308A (zh) * 2011-09-14 2012-03-14 克里特集团有限公司 一种全焊接阀体管线球阀
CN105202216A (zh) * 2015-10-26 2015-12-30 无锡阳工机械制造有限公司 一种双溢流口安全球阀
CN105202217A (zh) * 2015-10-26 2015-12-30 无锡阳工机械制造有限公司 一种具有泄压功能的安全球阀
CN108119688A (zh) * 2017-12-26 2018-06-05 福斯流体控制（苏州）有限公司 煤气化严苛工况硬密封固定球阀
CN108547974A (zh) * 2018-07-17 2018-09-18 江苏应流机械制造有限责任公司 一种锻造球阀的枢轴支撑板及其锻造球阀

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Publication number Priority date Publication date Assignee Title
US10774937B2 (en) * 2018-03-29 2020-09-15 Victaulic Company Combination control and check valve assembly for a wet piping system
KR102666490B1 (ko) * 2021-11-01 2024-05-20 영도산업 주식회사 소방설비용 유체 제어 선택밸브

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US3856261A (en) * 1973-08-02 1974-12-24 Acf Ind Inc Pressure relief means for valve body chamber
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US5533738A (en) * 1994-07-01 1996-07-09 Borsig Kugelhahn Gmbh Pressure controlled apparatus for sealing shutoff devices located in pipelines
DE19510709A1 (de) * 1995-03-15 1996-09-26 Rautenkranz Int Hermann Absperrarmatur für Rohrleitungen mit zum Schalten druckentlastbaren Sitzringen
DE19639070A1 (de) * 1995-03-15 1998-04-02 Rautenkranz Int Hermann Absperrarmatur für Rohrleitungen mit zum Schalten druckentlastbaren Sitzringen

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US3776506A (en) * 1971-12-15 1973-12-04 Acf Ind Inc Valve structure having fluid pressure actuated sealing members
US3856261A (en) * 1973-08-02 1974-12-24 Acf Ind Inc Pressure relief means for valve body chamber
US5322261A (en) * 1990-05-16 1994-06-21 Rag Aarnes Arrangement in closing valves
US5533738A (en) * 1994-07-01 1996-07-09 Borsig Kugelhahn Gmbh Pressure controlled apparatus for sealing shutoff devices located in pipelines
DE19510709A1 (de) * 1995-03-15 1996-09-26 Rautenkranz Int Hermann Absperrarmatur für Rohrleitungen mit zum Schalten druckentlastbaren Sitzringen
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002029294A3 (fr) * 2000-10-03 2002-06-20 Fisher Controls Int Robinet de regulation de debit fluidique a basculement de joint d'etancheite limite
CN102374308A (zh) * 2011-09-14 2012-03-14 克里特集团有限公司 一种全焊接阀体管线球阀
CN105202216A (zh) * 2015-10-26 2015-12-30 无锡阳工机械制造有限公司 一种双溢流口安全球阀
CN105202217A (zh) * 2015-10-26 2015-12-30 无锡阳工机械制造有限公司 一种具有泄压功能的安全球阀
CN108119688A (zh) * 2017-12-26 2018-06-05 福斯流体控制（苏州）有限公司 煤气化严苛工况硬密封固定球阀
CN108119688B (zh) * 2017-12-26 2024-01-02 福斯流体控制（苏州）有限公司 煤气化严苛工况硬密封固定球阀
CN108547974A (zh) * 2018-07-17 2018-09-18 江苏应流机械制造有限责任公司 一种锻造球阀的枢轴支撑板及其锻造球阀

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