WO2021200180A1 - 二重偏心型バタフライ弁とその製造方法 - Google Patents

二重偏心型バタフライ弁とその製造方法 Download PDF

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Publication number
WO2021200180A1
WO2021200180A1 PCT/JP2021/010967 JP2021010967W WO2021200180A1 WO 2021200180 A1 WO2021200180 A1 WO 2021200180A1 JP 2021010967 W JP2021010967 W JP 2021010967W WO 2021200180 A1 WO2021200180 A1 WO 2021200180A1
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WO
WIPO (PCT)
Prior art keywords
seat ring
tapered surface
seat
disc
butterfly valve
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/JP2021/010967
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
幸博 宮下
直角 横澤
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.)
Kitz Corp
Original Assignee
Kitz Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kitz Corp filed Critical Kitz Corp
Priority to KR1020227033518A priority Critical patent/KR20220158728A/ko
Priority to CN202180026448.9A priority patent/CN115298464A/zh
Priority to US17/915,003 priority patent/US11982360B2/en
Publication of WO2021200180A1 publication Critical patent/WO2021200180A1/ja
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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/222—Shaping of the valve member
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/46—Attachment of sealing rings
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/226—Shaping or arrangements of the sealing
    • F16K1/2263—Shaping or arrangements of the sealing the sealing being arranged on the valve seat
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/226—Shaping or arrangements of the sealing
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • 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
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves
    • F16K27/0218—Butterfly valves

Definitions

  • the present invention particularly relates to a double eccentric butterfly valve suitable for high-pressure fluids and a method for manufacturing the same.
  • an eccentric butterfly valve is generally known as a valve particularly suitable for high-pressure fluids.
  • the rotation shaft (valve shaft) of the valve body is eccentric from the center line of the flow path, and the rotation shaft is further eccentric from the sealing surface of the valve body in the flow path direction.
  • the seat ring is often made of fluororesin to improve high temperature resistance, and the seat ring is sandwiched between the seat retainer and the body and has the above double eccentricity. It is placed in the designated position.
  • This double eccentric structure makes it possible to prevent seal leakage when the valve is closed with high accuracy in both positive pressure and reverse pressure flow directions in various sizes from small diameter to large diameter.
  • back leakage refers to a phenomenon in which leakage occurs through the back side of the seat ring due to a gap between the body and the seat ring.
  • the seat ring has a seat ring main body and a gasket portion integrally extended through an edge cutting portion on the outer peripheral side of the seat ring main body, and the edge cutting portion includes a body and a gasket portion.
  • An engaging portion is provided to prevent back leakage of the gasket portion in the engaged state.
  • the engaging portion is a portion where the tapered step surface formed on the gasket portion and the tapered surface formed on the body are engaged, and both the tapered step surface and the tapered surface have the same inclination angle. Formed by slopes.
  • an annular clearance is usually provided between the outer peripheral side of the seat retainer and the inner peripheral side of the body facing the outer peripheral side of the seat retainer.
  • the valve body when assembling the valve body or the valve shaft to the body, a dimensional error occurs between the shaft hole of each of the valve body and the body and the center line of the flow path.
  • the valve body is arranged with respect to the body with a dimensional error deviated from the normal position.
  • the seat ring when the seat ring is aligned with the valve body, the seat retainer with respect to the body due to this dimensional error also shifts.
  • Patent Document 1 When a dimensional error occurs in the parts in this way, in Patent Document 1, the tapered stepped surface of the seat ring and the tapered surface of the body cannot be engaged with each other in a predetermined surface contact state, and the tapered stepped surface and the tapered surface cannot be engaged with each other.
  • the tapered step surface rides on the tapered surface and a place where a gap is generated between the tapered step surface and the tapered surface.
  • the surface pressure between the tapered step surface and the tapered surface is partially interrupted, and when a high-pressure fluid flows, back leakage may occur from the portion where the surface pressure is interrupted.
  • the sealing surface pressure is higher than in the place where a gap is created between them, and the annular sealing part of the seat ring by the seat retainer and the body is made uniform. Is difficult to form. These phenomena occur, for example, when a material that is unlikely to be crushed or deformed (such as PTFE containing a filler) is used for the seat ring, or when the seat cannot be sufficiently tightened by the seat retainer.
  • a material that is unlikely to be crushed or deformed such as PTFE containing a filler
  • the seat ring can be deformed appropriately to fill the gap, and even if the seat ring is tightened with an excessive force, even if the seat ring is tightened with an excessive force, Since the gap between the seat rings can be completely crushed, the above-mentioned problems are unlikely to occur.
  • PTFE PTFE without a filler, etc.
  • Patent Document 1 in order to bring the tapered stepped surface and the tapered surface into surface contact in a predetermined state, a level of dimensional accuracy that does not cause a dimensional error in each part is required, and a sheet is required at the time of assembly. It will also be necessary to integrate the seat retainer with the ring in a state where it is accurately aligned with the body. Moreover, it is difficult to satisfy both the high-precision dimensional accuracy and the alignment between the seat ring and the valve body, and in the actual alignment, the positions of the tapered step surface and the tapered surface deviate from each other. It may cause the above problems.
  • the present invention has been developed to solve conventional problems, and its purpose is particularly suitable for high-pressure fluids, even when the dimensional error of parts is large, the seat ring and the body.
  • the seat ring is centered on the disc while ensuring the sealing performance with the disc, and the sealing surface pressure between the disc and the seat ring is secured and the sealing performance is exhibited in either case of positive pressure or reverse pressure. It is an object of the present invention to provide an eccentric butterfly valve and a method for manufacturing the same, which reliably prevents fluid leakage by ensuring a continuous sealing portion between the seat ring and the seat ring.
  • the disc is rotatably supported at the center of the flow path and at a position eccentric from the sealing surface through the stem in the tubular body, and the disc is rotatably supported.
  • a double eccentric butterfly valve provided in a body that can be sealed in a sealed state by a seat ring made of an elastic material fixed by a seat retainer, a tapered surface formed on the seat ring and a step portion formed on the body.
  • a double eccentric butterfly valve in which an annular seal portion is formed on the opposite surface between the body and the seat ring by biting the corner portion on the tapered surface side of the step portion into the tapered surface.
  • the seat retainer is formed with a protruding portion that protrudes near the facing portion between the tapered surface and the stepped portion, and a part or all of the protruding portion overlaps the stepped portion in the flow path direction. It is a double eccentric type butterfly valve provided in.
  • the seat ring comprises a seat ring main body and a gasket portion integrally extended on the outer peripheral side of the seat ring main body, and a seat is provided near a boundary portion between the seat ring main body and the gasket portion.
  • This is a double eccentric butterfly valve in which the tapered surface of the ring and the stepped portion of the body face each other.
  • the volume of the region where the stepped portion bites into the tapered surface and is crushed is substantially the same as the volume of the space region where the stepped portion does not bite into the tapered surface. It is a double eccentric butterfly valve that is the size of.
  • the disc is rotatably supported in the center of the flow path and at a position eccentric from the sealing surface through the stem in the tubular body, and the disc is fixed in the body by a sheet retainer.
  • This is a method for manufacturing a double eccentric butterfly valve that is provided so that it can be sealed in a sealed state by a seat ring made of an elastic material.
  • the seat ring is aligned with the position of the disc within the range of the clearance formed between the mounting recess and the outer circumference of the seat retainer, and the tapered surface formed on the seat ring and the step formed on the body.
  • annular sealing portion is formed on the opposing surface between the body and the seat ring, and the sealing surface on the tip side of the seat ring.
  • the seat ring comprises a seat ring main body and a gasket portion integrally extended on the outer peripheral side of the seat ring main body, and a seat is provided near a boundary portion between the seat ring main body and the gasket portion.
  • the invention according to claim 7 is a method for manufacturing a double eccentric butterfly valve in which the radial length of the clearance is shorter than the radial width of the tapered surface.
  • the invention of claim 1 since it is a double eccentric type, it is particularly suitable for high-pressure fluid, and is an annular structure composed of a tapered surface formed on the seat ring side and a stepped portion formed on the body side.
  • a reliable local pressure portion is formed by pressing the tapered surface toward the step portion side with the protruding portion, and the seat ring and the body are increased by increasing the surface pressure of the seal portion provided with the local pressure portion. Make sure to prevent leakage from between.
  • the seat ring is provided by the seat ring main body and the gasket portion, the seat ring is formed when the valve is closed regardless of whether the fluid flows in either the positive pressure or the reverse pressure direction.
  • the main body can be flexed to ensure the sealing property with the disc, and the gasket portion can prevent back leakage.
  • the gasket portion is functionally separated from the seat ring main body, and this gasket portion is the seat ring main body. Since it is less susceptible to deformation, the sealing performance of the gasket portion is enhanced and the leakage prevention performance is further improved.
  • the volume of the region where the tapered surface is crushed and the volume of the other space region are substantially the same size.
  • the seat ring can be attached while setting the filling rate of the seat ring extruded from the crushed area to the area to almost 100% or more, preventing overfilling and leaving an unfilled area, and sealing.
  • the surface pressure of the portion can be secured substantially uniformly in the circumferential direction to improve the sealing property.
  • the sealing surface of the seat ring and the disc are sealed while ensuring uniform sealing property between the seat ring and the body by the annular sealing portion.
  • the retaining surface can be sealed in an annular shape, and the seat retainer and body can be assembled while satisfying the sealing properties of both the seat ring and the body and the seat ring and the disc.
  • the tapered surface and the stepped portion are surely brought into contact with each other in at least line contact in the circumferential direction, and from this state, the seat ring and the body are integrated.
  • An annular seal portion is formed, and the seal portion can continuously secure the sealing force in the circumferential direction to prevent fluid leakage.
  • the seat ring main body when the fluid flows in either the positive pressure or the reverse pressure direction, the seat ring main body is flexed when the valve is closed to ensure the sealing property with the disc, and the gasket portion is used. Back leakage can be prevented, and the tapered surface and the stepped portion face each other near the boundary between the seat ring main body and the gasket portion, so that the gasket portion is functionally separated from the seat ring main body, and this gasket portion is formed.
  • the sealing performance of the gasket portion is enhanced and the leakage prevention performance is further improved.
  • the stepped portion does not come off from the tapered surface, the stepped portion is surely opposed to the tapered surface, and at least these are in line contact with each other. Sufficient sealing performance can be ensured by forming an annular sealing portion.
  • FIG. 1 It is a vertical sectional view which shows the embodiment of the double eccentric type butterfly valve of this invention. It is a front view of the double eccentric type butterfly valve of FIG. It is an enlarged schematic view of a main part of FIG. It is an enlarged schematic view of part A of FIG.
  • FIG. 1 and 2 show an embodiment of the double eccentric butterfly valve of the present invention
  • FIG. 3 shows an enlarged schematic view of a main part of FIG.
  • valve body 1 The double eccentric butterfly valve (hereinafter referred to as valve body 1) shown in FIG. 1 includes a body 2, a stem 3, a disc 4, a seat retainer 5, and a seat ring 6. Of these, the body 2, the stem 3, the disc 4, and the seat retainer 5 are molded from a metal material such as stainless steel.
  • the body 2 is formed in a tubular shape, and a shaft mounting portion 10 for mounting the stem 3 is provided on the upper and lower parts of the body 2.
  • An annular mounting recess 11 is formed on one side of the body 2, and the mounting recess 11 is provided with an inner diameter capable of accommodating the seat retainer 5 on which the seat ring 6 is mounted.
  • the bottom surface 11a of the mounting recess 11 is provided so as to be parallel to the rotation axis of the stem 3.
  • the disc 4 is formed in a substantially disk shape, a sealing surface 12 is provided on the outer peripheral surface of the disc 4, and a boss portion 13 is formed so as to project from one surface side, and a stem is formed on the boss portion 13. 3
  • the mounting hole 14 is formed at a position eccentric from the sealing surface 12, which is the sealing position.
  • a flow path 15 is provided in the valve body 1 of FIG. 1, and in the case of a forward flow, the right side of the valve body 1 is the primary side of the flow path 15 and the left side is the secondary side of the flow path 15. A fluid flows through the main body 1 from the right side to the left side.
  • the disc 4 is integrally fixed to the stem 3 with a taper pin 16, and is rotatably supported at an eccentric position from the center of the flow path 15 and the sealing surface 12 through the stem 3.
  • the seat ring 6 is formed into a ring shape by an elastic material, and in the present embodiment, it is formed of a resin material such as PTFE (polytetrafluoroethylene) containing a filler such as carbon. ..
  • the seat ring 6 has a seat ring main body 20 and a gasket portion 21 integrally extending on the outer peripheral side of the seat ring main body 20.
  • the seat ring main body 20 is provided so that the vicinity of the outer diameter is fixed between the body 2 and the seat retainer 5, while the vicinity of the inner circumference is flexible, and the end surface on the inner circumference side (the tip side of the inner circumference) is sealed. It becomes a surface and is provided so as to be in contact with the sealing surface 12 of the disc 3 when the valve is closed so that an annular seal can be performed.
  • a flexible portion 22 is provided on the inner diameter side thereof, and a fixed portion 23 is provided on the outer diameter side of the flexible portion 22, and a space portion is provided between the flexible portion 22 and the fixed portion 23. 24 is provided.
  • the flexible portion 22 has a seal surface 25 and an inclined surface 26, and the seal surface 25 has a C-plane shape on the inner diameter end side of the flexible portion 22 or a predetermined seal width according to the R-plane shape of the cross section. It is provided in an annular shape, and the inclined surface 26 is provided in a gently inclined shape following the seal contact portion 25.
  • FIG. 4A is an enlarged schematic view of part A in FIG. 3, and FIG. 4B shows a state before the body 2 and the seat ring 6 are attached.
  • a stepped surface 30 having a step in the radial direction is formed between the body 2 and the seat ring 6 as a facing surface in the circumferential direction.
  • the tapered surface 31 formed on the seat ring 6 side and the stepped portion 32 formed on the body 2 side face each other.
  • the tapered surface 31 is provided with a width W1 in the radial direction by a gentle rounded surface connecting the seat ring main body 20 and the gasket portion 21 in the cross-sectional direction, and the body increases from the inner diameter side to the outer diameter side. It is inclined toward the 2nd side.
  • the step portion 32 is provided at a position facing the tapered surface 31 so as to have a surface (inclined surface 36) inclined at an angle of about 45 ° in cross section from the bottom surface 11a of the mounting recess 11, and the step portion 32 is provided.
  • the inner diameter side protrudes toward the seat ring 6 with the inclined surface 36 as a boundary, and the cross-sectional uneven shape is formed.
  • the corner portion 35 protruding toward the seat ring 6 side is located within the radial width W1 of the tapered surface 31.
  • the inclined surface 36 of the stepped portion 31 has a width W2 that can be arranged within the radial width W1 of the tapered surface 31, and is formed so that the inclined surface 36 has a steeper radial inclination than the tapered surface 31. Will be done. In this way, the inclined surface 36 and the tapered surface 31 of the stepped portion 32 face each other so as to intersect each other. Further, since the height of the step portion 32 of the body 2 (width in the flow path direction) and the height of the step sandwiching the tapered surface 31 of the seat ring 6 are substantially the same, the seat ring 6 other than the step surface 30 The facing surfaces of the body 2 and the body 2 can be brought into contact with each other.
  • the corner portion 35 on the tapered surface 31 side of the stepped portion 32 bites into the tapered surface 31, and the seat is formed so that the tapered surface 31 side follows the shape of the stepped portion 32.
  • the ring 6 is elastically deformed, and an annular sealing portion 33 is formed on the stepped surface 30 by the tapered surface 31 and the corner portion 35, and the sealing portion 33 enables the seat ring 6 and the body 2 to be uniformly sealed.
  • the region R1 (hatched region shown by the solid line) crushed by the stepped portion 32 on the tapered surface 31 and the seat ring 6 in this region R1 are extruded and accommodated.
  • the stepped portion 32 to be formed is provided so as to have substantially the same size as the space region R2 (hatching region shown by the broken line) that does not bite into the tapered surface 31, and is crushed by the stepped portion 32 due to the deformation of the seat ring 6.
  • the formed region R1 is deformably provided in the space region R2.
  • the sealing surface pressure of the sealing portion 33 is extremely lowered, while if the filling rate is too high, the tightening force becomes excessive, so that the filling rate surely exceeds 100%. It is desirable to configure the tapered surface 31 and the stepped portion 32 so that the region R1 and the space region R2 are substantially the same so as not to be excessive.
  • the fixing portion 23 is sandwiched between the body 2 and the seat retainer 5 in a state where the flexible portion 22 is flexible, and the seat ring main body 20 is fixed in this state.
  • the space portion 24 is formed by notching in a groove shape along the circumferential direction, and the flexible portion 22 bends in the positive pressure direction or the reverse pressure direction due to the surface pressure or fluid pressure from the disc 4 through the space portion 24 to seal.
  • the surface 25 is provided on the sealing surface 12 of the disc 4 so as to be abutted and sealed.
  • the solid line showing the seat ring main body 20 in FIG. 3 shows the shape in which the sealing surface 25 receives positive pressure and comes into contact with the disc 4 when the valve is closed, and the broken line indicates that the disc 4 receives reverse pressure when the valve is closed and is deformed. It shows the shape when it is used.
  • the alternate long and short dash line represents the cross-sectional shape of the seat ring main body 20 before being attached to the seat retainer 5.
  • the gasket portion 21 is integrally extended by a thin-walled portion 34 on the outer peripheral side of the fixing portion 23, and the thin-walled portion 34 is formed to a thickness capable of suppressing the outflow of excess portions due to thermal expansion, together with the gasket portion 21. Sufficient thickness is secured.
  • the seat retainer 5 is provided in a substantially annular shape, and a projecting portion 40, a concave groove 41, a protruding portion 42, and a mounting concave groove 43 are formed on the side facing the body 2.
  • the projecting portion 40 is formed at a position facing the space portion 24 of the seat ring main body 20 in a length shorter than the depth of the space portion 24 in the direction perpendicular to the stem 3.
  • the concave groove 41 is formed on the outer diameter side of the projecting portion 40, and has a width that is substantially the same as or slightly longer than the length of the fixing portion 23 in the direction perpendicular to the stem 3 and longer than the fixing portion 23 in the radial direction. It is provided in.
  • a gap portion G is provided between the outer peripheral surface of the fixing portion 23 and the inner peripheral surface of the seat retainer 5.
  • the capacity of the gap portion G is set to be larger than the volume even if the fixing portion 23 is crushed and deformed to the outer diameter side by tightening with the retainer bolt 50 for fixing the seat retainer 5.
  • the fixing portion 23 is fixed in the concave groove 41. Further, the fixing portion 23 hardly crushes the concave groove 41, so that the protruding portion 42 of the thin-walled portion 34 is likely to be crushed or the gasket portion 21 is crushed by the mounting concave groove 43.
  • the protruding portion 42 is formed so as to project in the vicinity of the boundary portion 27 between the seat ring main body 20 and the gasket portion 21 in the direction perpendicular to the stem 3 by a width narrower on the outer diameter side than the concave groove 41, and the protruding portion 42 is formed.
  • a part or all of the above is provided at a position overlapping the stepped portion 32 in the flow path direction, that is, at a portion facing the tapered surface 31 and the stepped portion 32.
  • the gasket portion 21 is provided with a width shorter than the protruding portion and thinner than the thin portion 34 in the radial direction, and a gap D is provided between the outer peripheral side of the fixing portion 23 and the inner peripheral side of the protruding portion 42.
  • the protruding portion 42 is charged from a narrow charging space 51 provided between the fixing portion 23 of the seat ring main body 20 and the gasket portion 21, and the thin portion 34 is moved to the body 2 side at the tip of the protruding portion 42. Pressed with high surface pressure.
  • the surplus portion due to the thermal expansion is absorbed by the gap D so as not to affect the sealing surface 25 and the gasket portion 21.
  • the mounting concave groove 43 is formed on the outer diameter side of the protruding portion 42 in the direction perpendicular to the stem 3 and longer than the tip side of the gasket portion 21 and in the radial direction.
  • the seat retainer 5 is provided so that its outer diameter is slightly smaller than the mounting recess 11, and an annular clearance C is formed between the mounting recess 11 and the outer circumference of the seat retainer 5. Within this clearance C, the seat retainer 5 can move with respect to the body 2, and within this range, the seat ring 6 can be aligned with the position of the disc 4. As a result, the seat retainer 5 and the body 2 can be assembled in a state where the sealing surface 25 of the seat ring 6 and the sealing surface 12 of the disc 4 are sealed in an annular shape.
  • the seat retainer 5 is formed with an outer diameter such that the radial length L of the clearance C is shorter than the radial width W1 of the tapered surface 31. For this reason, when the seat retainer 5 is housed in the mounting recess 11, even if the seat retainer 5 is maximally offset in the mounting recess 11, the seat retainer 5 is tapered to the step portion 32 (particularly near the corner portion). The seat retainer 5 and the body 2 can be fixed while maintaining the state in which the surfaces 31 are overlapped.
  • the seat retainer 5 is formed with stepped tightening holes 52 at eight locations at equal intervals, and the retainer bolts are formed on the body 2 side to which the tightening holes 52 correspond.
  • a male screw 53 of 50 and a female screw 54 that can be screwed are provided.
  • the body 2 and the seat retainer 5 are provided so as to be tightenable by the retainer bolt 50 with the seat ring main body 20 mounted between them, and the gasket portion is provided between the body 2 and the seat retainer 5 by the tightening force. 21 is sandwiched.
  • valve body 1 After tightening the retainer bolt 50, the valve body 1 is sandwiched between piping flanges (not shown), and the outer peripheral side is joined by the piping bolt 56 shown in FIG. 2, so that the seat ring body 20 is more firmly attached. Become.
  • a space S1 is provided between the body 2 and the flexible portion 22, and a space S2 is provided between the seat retainer 5 and the flexible portion 22, and these spaces are provided. Due to S1 and S2, the flexible portion 22 is flexibly deformed in the direction of the seat retainer 5 and the body 2.
  • the tapered surface 31 is formed by a gentle rounded surface, but the tapered surface may be formed by a linear inclined surface, or may be a gently convex curved surface.
  • the inclined surface 36 of the step portion 32 is formed at an angle of approximately 45 °, and this angle may be an angle other than 45 °, but at least the inclined surface 36 having a steeper inclination than the tapered surface 31. It is desirable to do. As a result, it becomes easy for the corner portion 35 of the step portion 32 to bite into the tapered surface 31.
  • a tapered surface may be formed on the body 2 side and a stepped portion may be formed on the seat ring 6 side.
  • the outer diameter side is the primary side and the inner diameter side is the inner diameter side with the stepped portion as a boundary.
  • An uneven shape displaced to the secondary side may be provided near the boundary portion.
  • the stem 3 is inserted into the shaft mounting portion 10 of the body 2 and the hole portion 14 of the disc 4, the disc 4 is fixed to the stem 3 with a taper pin 16, and the disc 4 can be rotated by the stem 3 with respect to the body 2. Attach to the state.
  • the stem 3 is rotated in the closing direction to close the disc 4.
  • the seat retainer 5 equipped with the seat ring 6 is housed in the mounting recess 11 of the body 2.
  • an annular clearance C is formed between the outer circumference of the seat ring 6 and the inner circumference of the mounting recess 11, and the seat ring 6 can move in the mounting recess 11 in the radial direction by the amount of this clearance C. ..
  • the retainer bolt 50 is inserted into the tightening hole 52 and tightened, and the seat retainer 5 and the body 2 are fixed with the retainer bolt 50.
  • a clearance is also provided between the retainer bolt 50 and the tightening hole 52 (including the head 55 and the periphery) to enable alignment described later.
  • the sealing surface 25 is guided along the inclination of the sealing surface 12 with the tightening of the retainer bolt 50, and the seat ring 6 (seat retainer 5) has a diameter of the mounting recess 11 within the range of the clearance C by this guidance.
  • the contact between the sealing surface 25 and the sealing surface 12 is appropriately adjusted so that the contact sealing can be performed in an annular shape. In this way, by tightening the retainer bolt 50, the seat retainer 5 is subjected to a centering action for aligning the seat ring 6 with the position of the disc 4.
  • the tapered surface 31 and the stepped portion 32 face each other, the tapered surface 31 abuts on the stepped portion 32, and the tapered surface 31 is guided so as to slide near the corner portion of the stepped portion 32. It is smoothly aligned.
  • the corner portion 35 of the step portion 32 bites into the tapered surface 31, and the tapered surface 31 is elastically deformed along the step portion 32.
  • the tapered surface 31 is gradually deformed along the uneven shape of the stepped portion 32 while maintaining the state in which the tapered surface 31 is in contact with the corner portion of the stepped portion 32, so that the body 2 and the seat ring 6 are formed.
  • the seat retainer 5 is in a state where the sealing surface 25 and the sealing surface 12 can be annularly sealed while forming an annular sealing portion 33 on the facing surface by line contact between the corner portion 35 of the step portion 32 and the tapered surface 31. And body 2 are fixed. Therefore, it is possible to form the seal portion 33 by surface contact while gradually increasing the contact area from at least the state where the line contact is maintained.
  • the tapered surface 31 is formed by a gentle rounded surface with a width W1
  • the stepped portion 32 is formed so as to have an inclined surface 36 at approximately 45 ° from the mounting recess bottom surface 11a.
  • the width W2 is provided to a size that can be arranged within the width W1 of the tapered surface 31, and the step portion 32 is provided with a radial inclination of the step portion 32 more steeply than the tapered surface 31.
  • the seat retainer 5 is accommodated in the mounting recess 11 when the seat retainer 5 is accommodated in the mounting recess 11. Even when it moves to the maximum within the clearance C, it is possible to maintain a state in which a part of the tapered surface 31 overlaps the stepped portion 32 in the direction of the flow path 15, so that the tapered surface 31 and the corner portion 35 of the stepped portion 32
  • the annular seal portion 33 can be reliably formed from the state where the seal portions 33 are in line contact with each other.
  • the width W1 is 4 to 6 times the clearance length L, the annular seal portion 33 can be reliably formed, and a higher seal surface pressure can be obtained.
  • the flexible portion 22 tilts to the left due to the fluid pressure, secures a contact state with the disc 4, and maintains a sealed state. Even when a higher pressure is applied from this state, the flexible portion 22 elastically deforms to the disc 4 side and collapses, so that the seal surface 25 is strongly pressed against the disc 4. Moreover, since the so-called self-sealing function in which the fluid enters the space from the space S2 and presses it to the downstream side works, the sealing surface pressure in the sealing portion increases in proportion to the increase in pressure.
  • the flexible portion 22 tilts to the right due to the fluid pressure, so that the sealing surface pressure is improved while ensuring the contact state with the disc 4.
  • the flexible portion 22 comes into contact with the seat retainer 5 to prevent an increase in the internal stress of the seat ring main body 20, and the elasticity of the material can be maintained to ensure the sealing property.
  • a force F in the direction shown by the arrow in FIG. 3 acts on the flexible portion 22, and this force F increases as the diameter of the valve body 1 becomes larger, such as 250A or 300A. Since the movement of the disc 4 becomes large, it becomes larger.
  • the force F increases, the tensile force F1 in the inner diameter direction due to the tilting of the flexible portion 22 also increases with the increase, and a great pulling force is applied in the vicinity of the gasket portion 21.
  • the seal portion 33 exerts a sealing force in the circumferential direction to ensure back leakage. It also prevents the effect of tilting of the seat ring main body 20 due to the flow of fluid from affecting the gasket portion 21.
  • the space region R2 between the region R1 crushed by the stepped portion 32 and the stepped portion 32 in which this region R1 is housed has substantially the same size
  • the stepped portion A seal portion 33 is provided in the vicinity of the stepped surface 30 while the region R1 crushed by 32 is deformed so as to escape to the space region R2, and the surface pressure between the tapered surface 31 and the stepped portion 32 is applied in the circumferential direction by this seal portion 33. Seals while continuously exerting almost evenly without interruption. Therefore, it is possible to prevent an excessive pressure from being applied to a part of the tapered surface 31 from the stepped portion 32 or a gap between the tapered surface 31 and the stepped portion 32, and the sealing portion 33 has excellent sealing performance. Can be demonstrated.
  • the seat retainer 5 is formed with a protruding portion 42 projecting near the boundary portion 27, and a part or all of the protruding portion 42 is provided at a position overlapping the step portion 32 in the flow path 15 direction, the seat retainer 5 is provided.
  • the tapered surface 31 is pressed against the stepped portion 32 through the thin portion 34 by the protruding portion 42, and by pressing these strongly, the tapered surface 31 is deformed along the shape of the stepped portion 32 and is uniform.
  • the seal portion 33 that exerts surface pressure can be configured.
  • the body 2 and the seat retainer 5 are tightened with the retainer bolt 50, and the gasket portion 21 is sandwiched by the tightening force of the retainer bolt 50.
  • the tightening force on the 21 can be increased, and the sealing force by the gasket portion 21 can be increased to improve the back leakage prevention function.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
PCT/JP2021/010967 2020-03-31 2021-03-18 二重偏心型バタフライ弁とその製造方法 Ceased WO2021200180A1 (ja)

Priority Applications (3)

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KR1020227033518A KR20220158728A (ko) 2020-03-31 2021-03-18 이중 편심형 버터플라이 밸브와 그 제조 방법
CN202180026448.9A CN115298464A (zh) 2020-03-31 2021-03-18 双偏心型蝶阀和其制造方法
US17/915,003 US11982360B2 (en) 2020-03-31 2021-03-18 Double eccentric butterfly valve and manufacturing method therefor

Applications Claiming Priority (2)

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JP2020063931A JP7500249B2 (ja) 2020-03-31 2020-03-31 二重偏心型バタフライ弁とその製造方法
JP2020-063931 2020-03-31

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CN119412507A (zh) * 2024-11-08 2025-02-11 苏州纽威阀门股份有限公司 一种双偏心蝶阀
CN119435732B (zh) * 2025-01-08 2025-04-11 福建省真特阀门科技有限公司 一种快速启闭的零摩擦球面密封蝶阀

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016056535A1 (ja) * 2014-10-07 2016-04-14 株式会社キッツ バタフライ弁用シートリングとその固定構造並びに偏心型バタフライ弁
JP2017180742A (ja) * 2016-03-31 2017-10-05 株式会社キッツ バタフライ弁用シートリングの固定構造と偏心型バタフライ弁

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Publication number Priority date Publication date Assignee Title
NO148902C (no) * 1981-10-14 1984-01-04 Westad Armaturfab Anordning ved dreiespjeldventil.
JPS646564A (en) * 1987-06-29 1989-01-11 Akira Oshima Sealing device for butterfly valve
US6224064B1 (en) * 1997-01-21 2001-05-01 Stephen V. St. Germain Cantering spring loaded fixed base butterfly valve seal
JPH10288262A (ja) * 1997-04-14 1998-10-27 Asahi Organic Chem Ind Co Ltd プラスチック製バタフライ弁
DE19918128A1 (de) * 1999-04-21 2000-10-26 Dieter Moellmann Absperrklappe für Rohrleitungen und Verfahren zur Herstellung derselben

Patent Citations (2)

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WO2016056535A1 (ja) * 2014-10-07 2016-04-14 株式会社キッツ バタフライ弁用シートリングとその固定構造並びに偏心型バタフライ弁
JP2017180742A (ja) * 2016-03-31 2017-10-05 株式会社キッツ バタフライ弁用シートリングの固定構造と偏心型バタフライ弁

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JP2021162082A (ja) 2021-10-11
CN115298464A (zh) 2022-11-04
KR20220158728A (ko) 2022-12-01
US20230151888A1 (en) 2023-05-18
US11982360B2 (en) 2024-05-14

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