WO2015188452A1 - 阀座环及具有该阀座环的多路阀 - Google Patents

阀座环及具有该阀座环的多路阀 Download PDF

Info

Publication number
WO2015188452A1
WO2015188452A1 PCT/CN2014/084929 CN2014084929W WO2015188452A1 WO 2015188452 A1 WO2015188452 A1 WO 2015188452A1 CN 2014084929 W CN2014084929 W CN 2014084929W WO 2015188452 A1 WO2015188452 A1 WO 2015188452A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
seat ring
annular boss
sealing
valve seat
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/CN2014/084929
Other languages
English (en)
French (fr)
Inventor
万明敏
姚建设
高智
陈云召
朱立云
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.)
KELAMAYI KING-BULL INFORTEC PETROLEUM EQUIPMENT Co Ltd
Original Assignee
KELAMAYI KING-BULL INFORTEC PETROLEUM EQUIPMENT Co Ltd
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 KELAMAYI KING-BULL INFORTEC PETROLEUM EQUIPMENT Co Ltd filed Critical KELAMAYI KING-BULL INFORTEC PETROLEUM EQUIPMENT Co Ltd
Priority to RU2016150707A priority Critical patent/RU2635746C1/ru
Priority to CA2951584A priority patent/CA2951584C/en
Priority to US15/317,769 priority patent/US9958074B2/en
Priority to EP14894802.9A priority patent/EP3156702B1/en
Publication of WO2015188452A1 publication Critical patent/WO2015188452A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B34/00—Valve arrangements for boreholes or wells
    • 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
    • F16K25/00—Details relating to contact between valve members and 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
    • F16K25/00—Details relating to contact between valve members and seats
    • F16K25/02—Arrangements using fluid issuing from valve members or 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/12—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with wedge-shaped arrangements of sealing faces
    • F16K3/14—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with wedge-shaped arrangements of sealing faces with special arrangements for separating the sealing faces or for pressing them together
    • 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
    • F16K1/465—Attachment of sealing rings to the 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • F16K11/0743—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces with both the supply and the discharge passages being on one side of the closure plates
    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
    • F16K11/0856—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug having all the connecting conduits situated in more than one plane perpendicular to the axis of the 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
    • F16K5/08—Details
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/16—Special arrangements for separating the sealing faces or for pressing them together for plugs with conical surfaces
    • F16K5/168—Sealing effected by the flowing medium
    • 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
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/18—Special arrangements for separating the sealing faces or for pressing them together for plugs with cylindrical surfaces
    • F16K5/188—Sealing effected by the flowing medium
    • 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
    • F16K5/14—Special arrangements for separating the sealing faces or for pressing them together
    • F16K5/20—Special arrangements for separating the sealing faces or for pressing them together for plugs with spherical surfaces
    • F16K5/205—Sealing effected by the flowing medium
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86863—Rotary valve unit

Definitions

  • This invention generally relates to a valve seat ring, and more particularly to a seat ring on a multi-way valve of a petroleum, chemical, and natural gas metering station and having the seat ring Multi-way valve.
  • BACKGROUND OF THE INVENTION Multi-way valves are typically used to measure the production of a single well in an oil well to obtain dynamic well production data.
  • the valve spool of the multi-way valve is provided with a seat ring, and the sealing surface of the seat ring is closely fitted to the outer cover of the upper valve body.
  • the sealing surface of the existing valve seat ring is spray-welded/surfacing hard alloy or cermet, such as the Chinese patent application patent No. ZL200420006528. 1 , the patent number ZL200620167076. 4 Chinese patent application and patent number is ZL200920291629 . 0 Chinese patent application.
  • the seat ring rotates around the axial core of the valve core on the sealing surface of the upper valve body, and the sealing surface of the sealing surface of the valve seat ring and the sealing surface of the upper valve body is mainly driven by the disc.
  • the spring is provided by the spring force of the disc spring.
  • the existing multi-way valve can only meet the requirements of the inner seal test under low pressure difference (DP).
  • DP test pressure difference
  • the sealing pressure is only limited by the disc spring to reach the leak level ANSI FCI-70. 2 Class VI leakage requirements.
  • the structure of the original seat ring has a wide sealing ring on the sealing surface, so that the force receiving area of the sealing is too large, and the sealing pressure required for the VI-level sealing is large, so that it is required to provide
  • the technical problem to be solved by the present invention is to provide a valve seat ring capable of achieving an adaptive sealing by hydraulic pressure, thereby improving the inner sealing specific pressure of the multi-way valve and achieving a high differential pressure seal. Level requirements.
  • a seat ring which is applied to a multi-way valve, the multi-way valve includes an upper valve body, a lower valve body and a rotary valve core, and the lower valve body is opened a plurality of oil passages penetrating into the chamber, wherein the valve seat ring is disposed in the rotary valve core and is in contact with a sealing surface of the upper valve body;
  • the valve seat ring includes a cylindrical body for fitting in the rotary valve core, the body having a through hole extending in an axial direction thereof and capable of communicating with the oil passage, the outer wall of the body a first annular boss is disposed, the inner wall of the body is provided with a second annular boss; the upper surface of the first annular boss and the upper surface of the second annular boss are both flat with the upper surface of the body Forming a sealing surface for sealingly sealing with the sealing surface of the upper valve body; forming an annular gap between the lower surface of the first annular boss and the rotating valve core to cause liquid action in the chamber Forming a sealing load on a lower surface of the first annular boss; a liquid in the oil passage acts on a lower surface of the second annular boss to form a sealing load.
  • the cross-sectional shape of the oil passage is a circular multi-way valve, and the first annular boss and the second annular boss are shaped to fit the shape of the oil passage. shape.
  • the horizontal section of the oil passage is circular in cross section
  • the cross section of the vertical section is a fan-shaped multi-way valve
  • the shape of the first annular boss and the second annular boss is The vertical section of the oil passage has a fan shape in which the cross-sectional shape is adapted.
  • the upper surface of the first annular boss is provided with at least one annular groove.
  • the annular groove is 1 to 2 tracks.
  • the annular groove having a cross-sectional shape of a U-shaped, the depth of the annular groove is 0. 05mm-0. 2mm.
  • the first annular boss and the second annular boss are integrally formed with the body.
  • the invention also discloses a multi-way valve, which comprises an upper valve body, a lower valve body and a rotary valve core, wherein the lower valve body is provided with a chamber, and the upper valve body is provided with a plurality of penetrating bodies to the chamber.
  • the oil passage, the multi-way valve further includes the above-mentioned valve seat ring, the body of the valve seat ring is disposed in the rotary valve core, and the sealing surface of the valve seat ring is opposite to the sealing surface of the upper valve body Fit the seal.
  • the valve seat ring of the present invention has a first annular boss and a second annular boss, so that the multi-way valve is pressed into the cavity by the collecting port for the inner seal leakage test, or is pressed by the metering port.
  • the oil passage is subjected to an inner seal leakage test, and the liquid in the chamber generates a force acting on the lower surface of the first annular boss, or the liquid in the oil passage generates a force acting on the lower surface of the second annular boss, thereby forming a force
  • the upward load of the hydraulically acting seat ring realizes the hydraulic adaptive sealing of the seat ring and increases the sealing specific pressure of the seat ring.
  • the annular seat groove is formed on the sealing surface of the seat ring of the valve seat ring of the invention, the contact sealing area of the upper valve body and the seat ring is reduced, the sealing specific pressure is increased, and the multi-way valve core is improved. Torque reduction, the seat ring reaches the ANSI FCI-70. 2VI level of leakage at a seal differential pressure (DP) of 6. 9 MPa / 1000 psi (or higher).
  • DP seal differential pressure
  • the depth of the annular groove on the cover of the valve seat ring is controlled at 0. 05 ⁇ 0. 2mm, so that it does not participate in the sealing area, and the high sand content of the crude oil does not affect the rotary motion of the seat ring.
  • FIG. 1 is a plan view of a valve seat ring according to a first embodiment of the present invention.
  • Figure 2 is a cross-sectional view taken along the line A-A of Figure 1.
  • Fig. 3 is a longitudinal sectional view showing a multi-way valve having a valve seat ring according to a first embodiment of the present invention.
  • Figure 4 is a plan view of a valve seat ring of a second embodiment of the present invention.
  • Fig. 5 is a cross-sectional view taken along line BB of Fig. 4;
  • Figure 6 is a longitudinal sectional view of a multi-way valve having a valve seat ring of a second embodiment of the present invention.
  • the seat ring of an embodiment of the present invention is used in a multi-way valve.
  • the cross-sectional shape at any position of the oil passage of the multi-way valve in this embodiment is circular.
  • the multi-way valve includes an upper valve body 1, a lower valve body 2, and a rotary valve core 3.
  • the lower valve body 2 is provided with a chamber 4, and the upper valve body 1 is opened with a plurality of openings to the chamber 4.
  • the oil channel 5 is coming.
  • the lower valve body 2 is provided with a metering port 6 and a collecting port 7, and the metering port 6 is connected to the oil passage 5 through the chamber in the rotary valve body 3, and the collecting port 7 is in communication with the chamber 4.
  • the valve seat ring 8 of the present embodiment is disposed in the rotary valve body 3 and is in contact with the sealing surface of the upper valve body 1, and the sealing surface of the upper valve body 1 is now defined as the first sealing surface 9.
  • the valve seat ring 8 of the embodiment of the present invention includes a cylindrical body 10 for fitting in a rotary valve body 3, and the body 10 has a through hole 18 penetrating therethrough in the axial direction thereof.
  • the outer wall 11 of the 10 is provided with a first annular boss 13 on the inner wall 12 of the body 10.
  • a second annular boss 14 is provided; the upper surface of the first annular boss 13 and the upper surface of the second annular boss 14 are flush with the upper surface of the body 10 to form a first sealing surface with the upper valve body 1.
  • the 9-phase sealing seals the second sealing surface 15; an annular gap 16 is formed between the lower surface of the first annular boss 13 and the rotary valve core.
  • the high pressure liquid in the chamber 4 acts on the lower surface of the first annular boss 13, for the seat ring.
  • 8-upward force, which forms the sealing load of the seat ring 8 realizes the hydraulic adaptive sealing of the seat ring 8, thereby increasing the contact sealing pressure of the seat ring 8, and achieving the multi-way valve
  • the inner seal is required to seal level VI leakage level under high pressure difference.
  • the metering port 6 to the oil channel 5 form an adaptive seal of the valve seat ring 8 in both directions, and the pressure difference (DP) of the collecting port 7 and the metering port 6 is more The larger the seal, the larger the seal specific pressure and the smaller the seal leakage.
  • the cross-sectional shape of the oil passage 5 of the multi-way valve in the present embodiment is circular, as shown in FIGS. 1 and 2, the shapes of the first annular boss 13 and the second annular boss 14 are The shape of the oil passage 5 is adapted to a circular shape.
  • the sealing contact area between the first sealing surface 9 and the second sealing surface 15 is correspondingly increased, i.e., the sealing band is wider. This will result in a larger rotational torque for driving the rotary spool 3. Therefore, as shown in Figs. 1 and 2, at least one annular groove 17 is formed on the upper surface of the first annular boss 13 so as not to participate in the sealing area to reduce the sealing contact area.
  • the number and opening width of the annular groove 17 should be determined according to the area of the upper surface of the first annular boss 13, and if the area of the upper surface is larger, the number of the annular grooves 17 is increased correspondingly, and vice versa.
  • the sealing contact area of the first sealing surface 9 and the second sealing surface 15 is equivalent to the sealing contact area of the ordinary low-pressure multi-way valve, so as to control the driving torque of the rotary spool 3 to be not too large.
  • two annular grooves 17 are opened.
  • the cross-sectional shape of the annular groove 17 is U-shaped, and the depth of the annular groove 17 is 0. 05mm-0.
  • the sand in the crude oil of the sand does not remain in the annular groove 17, so that it does not affect the rotational movement of the seat ring 8.
  • the principle of this embodiment is exactly the same as that of the first embodiment, except that the horizontal section of the oil passage 5 of the multi-way valve of the present embodiment (for a section connected with a single well) is horizontally different due to the application of the multi-way valve.
  • the cross-sectional shape is a circle, and the cross-sectional shape of the vertical section (for a portion that is butted against the rotary valve body 3) is a fan shape.
  • the shapes of the first annular boss 13 and the second annular boss 14 are different from those of the first embodiment. As shown in FIG. 4 and FIG.
  • the body 10 of the valve seat ring 8 of the present embodiment is the same as that of the first embodiment, and is also cylindrical, and has a through hole 18 for cooperating with the rotary valve core 3.
  • the first annular boss 13 and the second annular boss 14 are each a fan shape adapted to the cross-sectional shape of the vertical section of the oil passage 5, for example, a fan shape similar to that of the fan fan shown in Fig. 4.
  • the invention also discloses a multi-way valve as shown in FIG. 3 and FIG. 6, which comprises an upper valve body 1, a lower valve body 2, a rotary valve core 3 and the above-mentioned valve seat ring 8, and a cavity is opened in the lower valve body 2
  • the upper valve body 1 is provided with a plurality of oil passages 5 extending into the chamber 4, and the body 10 of the seat ring 8 is disposed in the rotary valve core 3, and the second sealing surface 15 of the valve seat ring 8 is upper
  • the first sealing surface 9 of the valve body 1 is fitted and sealed.
  • the seal of the seat ring 8 and the upper valve body 1 is sufficient to press against the disc spring 19 below the seat ring.
  • the internal seal pressure difference (DP) reaches 6.9 MPa/1000 psi (or higher)
  • the sealing pressure of the seat ring 8 and the upper valve body 1 is only by the seat ring 8
  • the disc spring 19 below provides a level of leakage that is far below the VI level.
  • the invention forms the sealing load of the hydraulically acting valve seat ring 8 by changing the structure of the valve seat ring 8 through the hydraulic force in the cavity 4 or the oil passage 5, thereby realizing the hydraulic adaptive sealing of the valve seat ring 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Multiple-Way Valves (AREA)
  • Sliding Valves (AREA)
  • Lift Valve (AREA)
  • Taps Or Cocks (AREA)

Abstract

阀座环（8）及具有该阀座环（8）的多路阀。多路阀包括上阀体（1）、下阀体（2）和旋转阀芯（3），阀座环（8）设于旋转阀芯（3）内，阀座环（8）包括本体（10），本体（10）具有贯通的通孔（18），本体（10）的外壁（11）上设有第一环形凸台（13），内壁（12）上设有第二环形凸台（14）；第一环形凸台（13）和第二环形凸台（14）的上表面均与本体（10）的上表面平齐形成与上阀体（1）的密封面（9）相贴合密封的密封面（15）；第一环形凸台（13）的下表面与旋转阀芯（3）之间形成环形间隙，使腔室（4）和来油通道（5）内的液体分别作用于第一环形凸台（13）或第二环形凸台（14）的下表面形成密封载荷。无论是从腔室（4）还是计量口（6）打压，通过腔室（4）或计量口（6）液压作用力，形成液压作用阀座环（8）的密封载荷，实现阀座环（8）液压自适应性密封，达到多路阀内密封在高压差下密封等级Ⅵ级泄漏水平的要求。

Description

阀座环及具有该阀座环的多路阀 技术领域 本发明涉及一种阀座环， 尤其涉及一种石油、 化工及天然气计量 站的多路阀上的阀座环及具有该阀座环的多路阀。 背景技术 多路阀一般用于对油井单井产量轮番计量， 以获得动态油井生产 数据。 多路阀的阀芯上设置有阀座环， 阀座环的密封面与上阀体的密 封面紧密贴合。 目前， 现有的阀座环的密封面喷焊 /堆焊硬质合金或金 属陶瓷， 如专利号为 ZL200420006528. 1 的中国专利申请， 专利号为 ZL200620167076. 4的中国专利申请和专利号为 ZL200920291629. 0的中 国专利申请。
在多路阀正常工作时， 阀座环围绕着阀芯的轴芯在上阀体的密封 面上做圆周运动， 阀座环的密封面与上阀体的密封面的密封比压主要 靠碟形弹簧提供， 受碟形弹簧弹力的限制， 现有的多路阀只能满足低 压差 （DP ) 下的内密封试验的要求。 当多路阀的集输口和计量口的试 验压差 （DP) 达 6. 9MPa即 lOOOpsi甚至更高时，仅仅依靠碟形弹簧提 供密封比压远远达不到泄漏等级 ANSI FCI-70. 2 VI级泄漏的要求。 况 且， 原有阀座环的结构， 其密封面上密封环带较宽， 使密封的受力面 积太大， 达到 VI级密封所需提供的密封比压的力量很大， 这样一来需 要提供的驱动阀芯转动的力矩越大， 尤其在高压工作条件下， 驱动力 矩越大， 需要传递力矩阀芯的轴芯的轴径变大， 不利于多路阀的阀体 的结构设计， 而且需要选装更大功率的驱动电装。 发明内容 鉴于现有技术中存在的上述问题， 本发明所要解决的技术问题是 提供一种能够通过液压实现自适应性密封的阀座环， 从而提高多路阀 的内密封比压， 达到高差压密封等级的要求。
为了解决上述技术问题， 本发明采用了如下技术方案： 阀座环， 应用于多路阀中， 所述多路阀包括上阀体、 下阀体和旋转阀芯， 所述 下阀体内开设有腔室， 所述上阀体内开设有多条贯通至所述腔室的来 油通道， 所述阀座环设置于所述旋转阀芯内并与所述上阀体的密封面 相贴合；
所述阀座环包括用于装配于所述旋转阀芯内的圆柱状的本体， 所 述本体具有沿其轴向贯通并且能够与所述来油通道连通的通孔， 所述 本体的外壁上设有第一环形凸台， 所述本体的内壁上设有第二环形凸 台； 所述第一环形凸台的上表面和第二环形凸台的上表面均与所述本 体的上表面平齐形成用于与所述上阀体的密封面相贴合密封的密封 面； 所述第一环形凸台的下表面与所述旋转阀芯之间形成环形间隙， 使所述腔室内的液体作用于所述第一环形凸台的下表面形成密封载 荷； 所述来油通道内的液体作用于所述第二环形凸台的下表面形成密 封载荷。
作为优选， 所述来油通道的横截面形状为圆形的多路阀， 所述第 一环形凸台和第二环形凸台的形状为与所述来油通道的形状相适配的 圆环形。
作为优选， 所述来油通道的水平段的横截面形状为圆形， 竖直段 的横截面形状为扇形的多路阀， 所述第一环形凸台和第二环形凸台的 形状为与所述来油通道的竖直段横截面形状相适配的扇形。
作为优选， 所述第一环形凸台的上表面上开设有至少 1道环形凹 槽。
作为优选， 所述环形凹槽为 1〜2道。
作为优选， 所述环形凹槽的横截面形状为 U型， 所述环形凹槽的 深度为 0. 05mm-0. 2mm。
作为优选， 所述第一环形凸台、 第二环形凸台与本体一体成型。 本发明同时公开了一种多路阀， 包括上阀体、 下阀体和旋转阀芯， 所述下阀体内开设有腔室， 所述上阀体内开设有多条贯通至所述腔室 的来油通道， 所述多路阀还包括上述的阀座环， 所述阀座环的本体设 置于所述旋转阀芯内， 所述阀座环的密封面与所述上阀体的密封面相 贴合密封。
与现有技术相比， 本发明的阀座环及具有该阀座环的多路阀的有 益效果在于：
1、 本发明的阀座环由于增设了第一环形凸台和第二环形凸台， 使 多路阀无论是通过集输口打压给腔体做内密封泄漏试验， 还是通过计 量口打压给来油通道做内密封泄漏试验， 腔体内的液体产生作用于第 一环形凸台下表面的作用力， 或来油通道内的液体产生作用于第二环 形凸台下表面的作用力， 从而形成了液压作用阀座环的向上的载荷， 实现阀座环液压自适应性密封， 增大阀座环的密封比压。
2、 由于本发明的阀座环的阀座环密封面上开设有环形凹槽， 从而 减小上阀体与阀座环的接触密封的面积， 提高了密封比压， 使多路阀 轴芯力矩减轻， 在密封压差 （DP) 6. 9MPa/1000psi (甚至更高） 的条 件下， 使阀座环达到 ANSI FCI-70. 2VI级的泄漏水平。 另外， 阀座环密 封面上的环形凹槽的深度控制在 0. 05〜0. 2mm,使其不参与密封面积， 而且原油高含沙也不会对阀座环旋转运动工作造成影响。
3、 本发明的多路阀的结构合理， 运行平稳， 驱动的力矩减轻， 并 达到了高差压密封等级的要求， 扩大了高压油井或高压气井平面硬密 封的多路阀的高压应用领域。 附图说明 图 1为本发明的实施例一的阀座环的俯视图。
图 2为图 1的 A-A向剖视图。
图 3为具有本发明的实施例一的阀座环的多路阀的纵剖视图。 图 4为本发明的实施例二的阀座环的俯视图。 图 5为图 4的 B-B向剖视图。
图 6为具有本发明的实施例二的阀座环的多路阀的纵剖视图 附图标记说明
I-上阀体 2-下阀体
3-旋转阀芯 4-腔室
5 -来油通道 6-计量口
7-集输口 8-阀座环
9-第一密封面 10-本体
I I-外壁 12-内壁
13-第一环形凸台 14-第二环形凸台
15-第二密封面 16-环形间隙
17-环形凹槽 18-通孔
19-碟形弹簧 具体实施方式 下面结合附图和具体实施例对本发明作进一歩详细描述， 但不作 为对本发明的限定。
实施例一
本发明的实施例的阀座环应用于多路阀中。 本实施例中的多路阀 的来油通道任何位置处的横截面形状均为圆形。 如图 3所示， 多路阀 包括上阀体 1、 下阀体 2和旋转阀芯 3， 下阀体 2内开设有腔室 4， 上 阀体 1内开设有多条贯通至腔室 4的来油通道 5。下阀体 2上开设有计 量口 6和集输口 7，计量口 6通过旋转阀芯 3内的腔室能够与来油通道 5连通，集输口 7与腔室 4连通。本实施例的阀座环 8设置于旋转阀芯 3内并与上阀体 1的密封面相贴合，现将上阀体 1的密封面定义为第一 密封面 9。
如图 1和图 2所示， 本发明的实施例的阀座环 8包括用于装配于 旋转阀芯 3 内的圆柱状的本体 10， 本体 10具有沿其轴向贯通的通孔 18， 本体 10的外壁 11上设有第一环形凸台 13， 本体 10的内壁 12上 设有第二环形凸台 14; 第一环形凸台 13的上表面和第二环形凸台 14 的上表面均与本体 10的上表面平齐形成用于与上阀体 1的第一密封面 9相贴合密封的第二密封面 15; 第一环形凸台 13的下表面与旋转阀芯 之间形成环形间隙 16。
继续结合图 1，当由集输口 7向腔室 4内通入高压液体做内密封泄 漏试验时， 腔室 4内的高压液体作用于第一环形凸台 13的下表面， 给 阀座环 8—个向上的力， 该作用力形成了阀座环 8的密封载荷， 实现 阀座环 8的液压自适应性密封， 从而增大阀座环 8的接触密封比压， 达到了多路阀内密封在高压差下密封等级 VI级泄漏水平的要求。 当由 计量口 6向来油通道 5内通入高压液体做内密封泄漏试验时， 来油通 道 5内的高压液体作用于第二环形凸台 14的下表面， 给阀座环 8—个 向上的力， 该作用力形成了阀座环 8的密封载荷， 实现阀座环 8的液 压自适应性密封， 从而增大阀座环 8 的接触密封比压， 达到了多路阀 内密封在高压差下密封等级 VI级泄漏水平的要求。 这样从集输口 7至 腔室 4，计量口 6至来油通道 5两个方向均形成了阀座环 8的自适应性 密封， 当集输口 7和计量口 6压差 （DP )越来越大时， 密封比压越大， 密封泄漏量越来越小。
由于本实施例中的多路阀的来油通道 5 的横截面形状为圆形， 因 此， 如图 1和图 2所示， 第一环形凸台 13和第二环形凸台 14的形状 为与来油通道 5的形状相适配的圆环形。
继续结合图 1和图 2， 由于第一环形凸台 13的设置， 相应增大了 第一密封面 9和第二密封面 15之间的密封接触面积，即密封环带较宽。 这将导致用于驱动旋转阀芯 3的转动力矩较大。 因此， 如图 1和图 2， 在第一环形凸台 13的上表面上开设有至少 1道环形凹槽 17，使其不参 与密封面积， 以减小密封接触面积。 环形凹槽 17的开设数量和开设宽 度应根据第一环形凸台 13的上表面的面积确定， 若上表面的面积较大 则环形凹槽 17的开设数量相应增加， 反之亦然。 通常情况下应保证第 一密封面 9和第二密封面 15的密封接触面积与普通低压的多路阀的密 封接触面积相当， 以控制驱动旋转阀芯 3 的转动力矩不会太大。 本实 施例中开设了 2道环形凹槽 17。
作为本实施例的进一歩优选方案， 环形凹槽 17的横截面形状为 U 型， 环形凹槽 17的深度为 0. 05mm-0. 2mm 0 由于环形凹槽 17的深度较 小， 使高含沙的原油中的沙粒不会存留到环形凹槽 17中， 从而不会对 阀座环 8的旋转运动工作造成影响。
实施例二
本实施例的原理与实施例一完全相同， 区别仅在于由于所应用的 多路阀不同， 本实施例的多路阀的来油通道 5 的水平段 （用于与单井 连接的一段） 横截面形状为圆形， 而竖直段 （用于与旋转阀芯 3对接 的一段） 的横截面形状为扇形。 为了与多路阀的来油通道 5 的竖直段 相适配， 第一环形凸台 13和第二环形凸台 14的形状与实施例一有所 不同。 如图 4和图 5所示， 本实施例的阀座环 8的本体 10与实施例一 相同， 也为圆柱状， 并具有贯通的通孔 18， 本体 10用于与旋转阀芯 3 相配合。 第一环形凸台 13和第二环形凸台 14均为与来油通道 5的竖 直段的横截面形状相适配的扇形， 例如呈如图 4所示近似于蒲扇的一 种扇形。
本发明同时公开了如图 3和图 6所示的多路阀， 其包括上阀体 1、 下阀体 2、 旋转阀芯 3和上述的阀座环 8， 下阀体 2内开设有腔室 4， 上阀体 1 内开设有多条贯通至腔室 4的来油通道 5， 阀座环 8的本体 10设置于旋转阀芯 3内，阀座环 8的第二密封面 15与上阀体 1的第一 密封面 9相贴合密封。
由于普通低压的多路阀需要的内密封压差 （DP ) 较低， 所以阀座 环 8与上阀体 1的密封比压靠阀座环下面的碟形弹簧 19提供足够了。 对于高端高压的多路阀的内密封， 内密封压差（DP)达 6. 9MPa/1000psi (甚至更高） 时， 阀座环 8与上阀体 1的密封比压仅靠阀座环 8下面 的碟形弹簧 19提供远远达不到 VI级泄漏水平。 本发明通过改变阀座环 8的结构，通过腔体 4或来油通道 5内的液压作用力， 形成了液压作用 阀座环 8的密封载荷， 实现阀座环 8的液压自适应性密封， 增大阀座 环 8 的接触密封比压， 达到了高压多路阀内密封在高压差 （DP ) 下密 封等级 VI级泄漏水平的要求。 因此， 本发明的阀座环 8 的设计结构合 理， 提高了高压差 （DP) 下的密封等级， 旋转阀芯 3的驱动力矩减轻， 选配驱动电装功率减小， 扩大了高压油井或高压气井平面硬密封多路 阀的高压应用领域。 以上实施例仅为本发明的示例性实施例， 不用于限制本发明， 本 发明的保护范围由权利要求书限定。 本领域技术人员可以在本发明的 实质和保护范围内， 对本发明做出各种修改或等同替换， 这种修改或 等同替换也应视为落在本发明的保护范围内。

Claims

权 利 要 求
1、 阀座环， 应用于多路阀中， 所述多路阀包括上阀体、 下阀体和 旋转阀芯， 所述下阀体内开设有腔室， 所述上阀体内开设有多条贯通 至所述腔室的来油通道， 所述阀座环设置于所述旋转阀芯内并与所述 上阀体的密封面相贴合， 其特征在于，
所述阀座环包括用于装配于所述旋转阀芯内的圆柱状的本体， 所 述本体具有沿其轴向贯通并且能够与所述来油通道连通的通孔， 所述 本体的外壁上设有第一环形凸台， 所述本体的内壁上设有第二环形凸 台； 所述第一环形凸台的上表面和第二环形凸台的上表面均与所述本 体的上表面平齐形成用于与所述上阀体的密封面相贴合密封的密封 面； 所述第一环形凸台的下表面与所述旋转阀芯之间形成环形间隙， 使所述腔室内的液体作用于所述第一环形凸台的下表面形成密封载 荷； 所述来油通道内的液体作用于所述第二环形凸台的下表面形成密 封载荷。
2、 根据权利要求 1所述的阀座环， 其特征在于， 所述来油通道的 横截面形状为圆形的多路阀， 所述第一环形凸台和第二环形凸台的形 状为与所述来油通道的形状相适配的圆环形。
3、 根据权利要求 1所述的阀座环， 其特征在于， 所述来油通道的 水平段的横截面形状为圆形， 竖直段的横截面形状为扇形的多路阀， 所述第一环形凸台和第二环形凸台的形状为与所述来油通道的竖直段 横截面形状相适配的扇形。
4、 根据权利要求 1至 3中任一项所述的阀座环， 其特征在于， 所 述第一环形凸台的上表面上开设有至少 1道环形凹槽。
5、 根据权利要求 4所述的阀座环， 其特征在于， 所述环形凹槽为 1〜2道。
6、 根据权利要求 4所述的阀座环， 其特征在于， 所述环形凹槽的 横截面形状为 U型， 所述环形凹槽的深度为 0. 05mm-0. 2mm 0
7、 根据权利要求 1至 3中任一项所述的阀座环， 其特征在于， 所 述第一环形凸台、 第二环形凸台与本体一体成型。
8、 多路阀， 包括上阀体、 下阀体和旋转阀芯， 所述下阀体内开设 有腔室， 所述上阀体内开设有多条贯通至所述腔室的来油通道， 其特 征在于， 还包括权利要求 1至 7中任一项所述的阀座环， 所述阀座环 的本体设置于所述旋转阀芯内， 所述阀座环的密封面与所述上阀体的 密封面相贴合密封。
PCT/CN2014/084929 2014-06-10 2014-08-21 阀座环及具有该阀座环的多路阀 Ceased WO2015188452A1 (zh)

Priority Applications (4)

Application Number Priority Date Filing Date Title
RU2016150707A RU2635746C1 (ru) 2014-06-10 2014-08-21 Кольцо седла клапана и многоходовой клапан, имеющий кольцо седла клапана
CA2951584A CA2951584C (en) 2014-06-10 2014-08-21 A valve seat ring and a multi-way valve having valve seat ring
US15/317,769 US9958074B2 (en) 2014-06-10 2014-08-21 Valve seat ring and multi-way valve having valve seat ring
EP14894802.9A EP3156702B1 (en) 2014-06-10 2014-08-21 Multi-way valve having a valve seat ring

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410256679.0 2014-06-10
CN201410256679.0A CN105202225B (zh) 2014-06-10 2014-06-10 阀座环及具有该阀座环的多路阀

Publications (1)

Publication Number Publication Date
WO2015188452A1 true WO2015188452A1 (zh) 2015-12-17

Family

ID=54832776

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/084929 Ceased WO2015188452A1 (zh) 2014-06-10 2014-08-21 阀座环及具有该阀座环的多路阀

Country Status (6)

Country Link
US (1) US9958074B2 (zh)
EP (1) EP3156702B1 (zh)
CN (1) CN105202225B (zh)
CA (1) CA2951584C (zh)
RU (1) RU2635746C1 (zh)
WO (1) WO2015188452A1 (zh)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107339465B (zh) * 2017-08-17 2023-05-26 江苏中科机械有限公司 蓄热燃烧系统旋转式换向阀的气环液力密封装置
US10871234B2 (en) * 2018-10-23 2020-12-22 Cameron International Corporation Low-torque disc for a multiple orifice valve
WO2020264298A1 (en) 2019-06-28 2020-12-30 Cameron International Corporation Adjustable erosion resistant choke valve
CN110552681B (zh) * 2019-08-31 2022-10-14 中国石油集团川庆钻探工程有限公司 一种用于试油测试的分离器液位调节系统
DE102020201190A1 (de) * 2019-10-14 2021-04-15 Vitesco Technologies GmbH Fluidventil
DE102020207925A1 (de) * 2020-06-25 2021-12-30 Vitesco Technologies GmbH Mischventil
CN117267402A (zh) * 2023-10-17 2023-12-22 中山市伟力宝电机电器有限公司 一种旋转式浓水截流阀

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2840109A (en) * 1957-02-25 1958-06-24 Win Well Mfg Company Rotary selector valve
US2996083A (en) * 1958-07-10 1961-08-15 Huska Paul Continuous flow rotary selector valve
NL7607014A (en) * 1976-06-25 1977-12-28 Metzalwarenfabriek Venlo B V Multiway stop for liquids or gases - has valve stem and sealing plunger pressure balanced to turn easily
JPH06174118A (ja) * 1992-11-30 1994-06-24 Toto Ltd 流体弁
CN201034178Y (zh) * 2006-12-11 2008-03-12 克拉玛依市金牛信泰工业控制有限公司 扇形流道密封副多通阀
CN201173313Y (zh) * 2008-04-14 2008-12-31 黄建奇 自动补偿密封的多通阀
CN201875189U (zh) * 2009-12-14 2011-06-22 克拉玛依市金牛信泰工业控制有限公司 环槽式阀座环
CN102466059A (zh) * 2010-11-19 2012-05-23 沈志刚 双密封多通阀密封调整装置
CN203036009U (zh) * 2013-01-21 2013-07-03 克拉玛依市金牛信泰石油设备有限公司 多路阀
CN204025764U (zh) * 2014-06-10 2014-12-17 克拉玛依市金牛信泰石油设备有限公司 阀座环及具有该阀座环的多路阀

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2821998A (en) * 1956-01-27 1958-02-04 Win Well Mfg Company Rotary selector valve
US3561479A (en) * 1968-08-12 1971-02-09 Lyle J Archer Noninterflow rotary valve and improved fluid seals
US3964517A (en) * 1975-01-14 1976-06-22 Dickenson Harvard G Four way diverter valve
FR2367966A1 (fr) * 1976-10-15 1978-05-12 Liautaud Jean Repartiteur antipolluant
SU879116A2 (ru) * 1978-06-19 1981-11-07 Комбинат "Таджикхладторгмонтаж" Министерства Торговли Таджикской Сср Запорное устройство
US4575048A (en) * 1984-06-15 1986-03-11 Jamesbury Corporation Insert retainer for a wafer style butterfly valve
US4989641A (en) * 1989-10-11 1991-02-05 Santa Fe Energy Co. Rotary selector valve
US5927330A (en) * 1996-02-06 1999-07-27 Oil States Industries Modular, high-volume, rotary selector valve
DE19820513A1 (de) * 1998-05-08 1999-11-11 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzdüse für eine Brennkraftmaschine
CA2314641C (en) * 2000-07-28 2003-04-01 Chung Cheng Faucet Co., Ltd. Diverting valve for mixing faucet
US6736162B2 (en) * 2002-04-05 2004-05-18 Fisher Controls International, Llc Pressure relief valve with improved repairability
US20050046114A1 (en) * 2003-08-27 2005-03-03 Bohner Stephan Ernst Rotary seal member, assembly and methods for a hydraulic rotary swivel
EP1566584B1 (en) * 2004-02-18 2009-12-23 Emech Control Limited Control valve
CN2709740Y (zh) * 2004-02-27 2005-07-13 克拉玛依金牛信泰工业控制有限公司 计量集输选通装置
US7343933B2 (en) * 2004-04-27 2008-03-18 Cameron International Corporation Multi-port flow selector manifold valve and manifold system
US9038664B2 (en) * 2007-11-20 2015-05-26 Fisher Controls International Llc Fluid flow control device having a seat ring retainer
CN201588945U (zh) * 2009-12-23 2010-09-22 丛爱国 一种压力容器阀门
US9228664B2 (en) * 2014-06-05 2016-01-05 Charles C. Partridge Rotary multi-port valve

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2840109A (en) * 1957-02-25 1958-06-24 Win Well Mfg Company Rotary selector valve
US2996083A (en) * 1958-07-10 1961-08-15 Huska Paul Continuous flow rotary selector valve
NL7607014A (en) * 1976-06-25 1977-12-28 Metzalwarenfabriek Venlo B V Multiway stop for liquids or gases - has valve stem and sealing plunger pressure balanced to turn easily
JPH06174118A (ja) * 1992-11-30 1994-06-24 Toto Ltd 流体弁
CN201034178Y (zh) * 2006-12-11 2008-03-12 克拉玛依市金牛信泰工业控制有限公司 扇形流道密封副多通阀
CN201173313Y (zh) * 2008-04-14 2008-12-31 黄建奇 自动补偿密封的多通阀
CN201875189U (zh) * 2009-12-14 2011-06-22 克拉玛依市金牛信泰工业控制有限公司 环槽式阀座环
CN102466059A (zh) * 2010-11-19 2012-05-23 沈志刚 双密封多通阀密封调整装置
CN203036009U (zh) * 2013-01-21 2013-07-03 克拉玛依市金牛信泰石油设备有限公司 多路阀
CN204025764U (zh) * 2014-06-10 2014-12-17 克拉玛依市金牛信泰石油设备有限公司 阀座环及具有该阀座环的多路阀

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3156702A4 *

Also Published As

Publication number Publication date
EP3156702A4 (en) 2017-04-26
EP3156702B1 (en) 2019-10-16
CN105202225B (zh) 2017-12-22
US20170130850A1 (en) 2017-05-11
CA2951584A1 (en) 2015-12-17
US9958074B2 (en) 2018-05-01
RU2635746C1 (ru) 2017-11-15
CA2951584C (en) 2018-11-20
CN105202225A (zh) 2015-12-30
EP3156702A1 (en) 2017-04-19

Similar Documents

Publication Publication Date Title
WO2015188452A1 (zh) 阀座环及具有该阀座环的多路阀
WO2022222284A1 (zh) 凡尔弹簧座套、阀门组件和柱塞泵
CN203516886U (zh) 调节类阀门的先导式平衡阀芯
CA2653254A1 (en) Mechanical sliding sleeve
WO2016029689A1 (zh) 新型双活塞效应阀门
CN103089733A (zh) 一种多控式可变阻尼双自由度阀芯旋转式四通换向阀
CN101737506A (zh) 单座调节阀
CN205260897U (zh) 一种微型高温高压电动转阀
CN204300410U (zh) 高压压力平衡式旋塞阀
CN105443783A (zh) 自密封截止阀
CN216742957U (zh) 防汽蚀v型球阀
CN205479445U (zh) 自密封偏心半球阀
CN203979567U (zh) 一种单体球阀
CN117145997A (zh) 一种自泄压闸阀
CN115750819A (zh) 用于175MPa超高压的平板闸阀密封结构
CN203628011U (zh) 防外漏自密封阀门
KR20230149981A (ko) 사중 편심 구조의 버터플라이 밸브
CN205260914U (zh) 一种新型三通旋塞阀
CN201764040U (zh) 截止止回阀
CN219549683U (zh) 一种多通阀
CN206738579U (zh) 低泄漏低噪音平衡笼式控制阀
CN205908790U (zh) 一种带保护结构的球阀金属阀座安装结构
CN219388116U (zh) 一种双流道抽油泵
CN110762257B (zh) 一种带有介质自驱不平衡阀芯的止回阀
CN218118679U (zh) 一种多段式套筒控速调节阀

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14894802

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2951584

Country of ref document: CA

WWE Wipo information: entry into national phase

Ref document number: 15317769

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2014894802

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2014894802

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2016150707

Country of ref document: RU

Kind code of ref document: A