JP2008232260A - Valve - Google Patents

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Publication number
JP2008232260A
JP2008232260A JP2007072537A JP2007072537A JP2008232260A JP 2008232260 A JP2008232260 A JP 2008232260A JP 2007072537 A JP2007072537 A JP 2007072537A JP 2007072537 A JP2007072537 A JP 2007072537A JP 2008232260 A JP2008232260 A JP 2008232260A
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Japan
Prior art keywords
holding member
plug
seat ring
valve
flow path
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JP2007072537A
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Japanese (ja)
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Yasumasa Honma
康正 本間
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Azbil Corp
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Azbil Corp
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Priority to JP2007072537A priority Critical patent/JP2008232260A/en
Priority to TW097106631A priority patent/TW200905111A/en
Priority to KR1020080021842A priority patent/KR20080085699A/en
Priority to CN2008100846503A priority patent/CN101270822B/en
Publication of JP2008232260A publication Critical patent/JP2008232260A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/06—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having spherical surfaces; Packings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/06—Construction of housing; Use of materials therefor of taps or cocks
    • F16K27/067—Construction of housing; Use of materials therefor of taps or cocks with spherical plugs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
    • F16K5/08—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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Lift Valve (AREA)
  • Taps Or Cocks (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve superior in durability, by reducing abrasion of a seat ring, by reducing operation torque, by reducing an increase in pressing force to a plug of the seat ring by a variation in fluid differential pressure. <P>SOLUTION: Assuming a distance up to a contact part A between the plug 35 and the seat ring 50 from the flow passage axis 34 of a valve body 33 as (a), a distance b<SB>1</SB>up to an outer peripheral surface of a thin part 51A of a first holding part 51 from the flow passage axis 34 is set substantially equal to the distance (a). Here, the pressure receiving surface S<SB>1</SB>when pressing the seat ring 50 to the plug 35 by the fluid differential pressure P, is expressed by (b<SB>1</SB><SP>2</SP>- a<SB>1</SB><SP>2</SP>) × π, but since the b<SB>1</SB>is substantially equal to (a), the S<SB>1</SB>becomes substantially zero. Thus, the force F of pressing the seat ring 50 to the plug 35 by a variation in the fluid differential pressure, is reduced, compared with a conventional valve of setting the distance b1 up to a contact part B between the first holding member 51 and an O ring 54 from the flow passage axis 34, to be larger than the distance (a), and the valve of small operation torque is provided. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、弁本体内を流れる流体の流量を制御するバルブに関し、特に球状のプラグを備えたトラニオン形のバルブに関するものである。   The present invention relates to a valve for controlling the flow rate of fluid flowing in a valve body, and more particularly to a trunnion type valve having a spherical plug.

各種流体の制御、例えば空調用の冷温媒体を制御するために使用されるバルブとしては、二方ボールバルブが従来から知られている。この種の二方ボールバルブは、ボールプラグの支持方式によって大別すると、上流側と下流側に配置された一対のシートリングによってボールプラグを回動自在に支持するようにしたフローティングタイプと、弁軸によってボールプラグを回動自在に支持するようにしたトラニオンタイプの二種類がある。フローティングタイプは、全閉時にボールプラグが一次側流体圧によって二次側シートリングに押し付けられることにより、主としてボールプラグと二次側シートリングとの接触によってシールを図っている（例えば、特許文献１参照）。一方、トラニオンタイプは、弁軸の両端を弁本体に設けた軸受孔によって回転自在に枢支する構造を採っているため、全閉時にボールプラグが一次側流体圧によって二次側シートリングに強く押し付けられることがなく、このため通常ボールプラグと一次側シートリングとの接触のみによってシールし、二次側のシートリングを省略した構造を採っている（例えば、特許文献２参照）。このうち、特に本発明は後者のトラニオンタイプのボールバルブに関する。   As a valve used to control various fluids, for example, a cooling medium for air conditioning, a two-way ball valve is conventionally known. This type of two-way ball valve can be broadly classified according to the ball plug support system. A floating type in which a ball plug is rotatably supported by a pair of seat rings arranged on the upstream side and the downstream side, and a valve There are two types of trunnion types that support the ball plug in a rotatable manner by a shaft. In the floating type, when the ball plug is pressed against the secondary side seat ring by the primary side fluid pressure when fully closed, sealing is mainly achieved by contact between the ball plug and the secondary side seat ring (for example, Patent Document 1). reference). On the other hand, the trunnion type has a structure in which both ends of the valve shaft are rotatably supported by bearing holes provided in the valve body, so that the ball plug is strong against the secondary seat ring by the primary fluid pressure when fully closed. For this reason, a structure is employed in which sealing is performed only by contact between the ball plug and the primary side seat ring, and the secondary side seat ring is omitted (see, for example, Patent Document 2). Of these, the present invention particularly relates to the latter trunnion type ball valve.

図５に従来のトラニオン形ボールバルブのシール構造を示す。
同図において、トラニオン形ボールバルブ１（以下、単にバルブ１と称する）は、第１の保持部材３を一次側からばね等の弾性部材４による付勢力で付勢し、これによりシートリング５をプラグ２の外周面の着座部に押し付けることにより、プラグ２とシートリング５との隙間７からの流体８の漏洩を防止するようにしている。 FIG. 5 shows a seal structure of a conventional trunnion type ball valve.
In the figure, a trunnion-type ball valve 1 (hereinafter simply referred to as valve 1) urges a first holding member 3 from the primary side by an urging force of an elastic member 4 such as a spring, whereby the seat ring 5 is By pressing against the seating portion on the outer peripheral surface of the plug 2, the fluid 8 is prevented from leaking from the gap 7 between the plug 2 and the seat ring 5.

プラグ２とシートリング５とが接触している部分Ａ（以下、単に接触部Ａという）の位置と、第１の保持部材３のＯリング（シール部材）１２が接触する外周面の部分Ｂ（以下、単に接触部Ｂという）の位置は、弁本体６内の流路９の径方向において異なり、接触部Ｂが流路中心軸線１０から接触部Ａよりも遠くに位置している。すなわち、流路９の中心軸線１０から接触部Ａまでの長さをａとし、流路中心軸線１０から接触部Ｂまでの長さをｂとすると、ａ＜ｂであり、一次側と二次側の流体差圧Ｐ（＝Ｐ1 −Ｐ2 ）が発生した場合、シートリング５は前述の弾性部材４の付勢力に加えて、受圧面積Ｓ（＝（ｂ2 −ａ2 ）×π）にＰを乗じた力Ｆ（＝（ｂ2 −ａ2 ）×πＰ）の分だけプラグ２に押し付けられるようになる。なお、１１は第１の保持部材３を軸線方向に移動可能に保持する第２の保持部材で、この第２の保持部材１１は、外周面に形成された雄螺子１４が弁本体６の内壁面に形成された雌螺子１５に螺合することにより、弁本体６の内壁に固定されている。なお、第２の保持部材１１は弁本体６と一体構造としてもよい。１３はプラグ２を回動させる弁軸である。 The position of the portion A where the plug 2 and the seat ring 5 are in contact (hereinafter simply referred to as the contact portion A) and the outer peripheral surface portion B where the O-ring (seal member) 12 of the first holding member 3 is in contact ( Hereinafter, the position of the contact part B) is different in the radial direction of the flow path 9 in the valve body 6, and the contact part B is located farther than the contact part A from the flow path center axis 10. That is, if the length from the center axis 10 of the flow path 9 to the contact portion A is a and the length from the flow path center axis 10 to the contact portion B is b, a <b, and the primary side and the secondary side Side fluid differential pressure P (= P 1 −P 2 ) Occurs, the seat ring 5 has a force F (= (b 2 −−) obtained by multiplying the pressure receiving area S (= (b 2 −a 2 ) × π) by P in addition to the urging force of the elastic member 4 described above. A 2 ) × πP) is pressed against the plug 2. Reference numeral 11 denotes a second holding member that holds the first holding member 3 so as to be movable in the axial direction. The second holding member 11 has a male screw 14 formed on the outer peripheral surface thereof within the valve body 6. It is fixed to the inner wall of the valve body 6 by being screwed into a female screw 15 formed on the wall surface. The second holding member 11 may be integrated with the valve body 6. Reference numeral 13 denotes a valve shaft for rotating the plug 2.

特開平１１−１４８５６５号公報Japanese Patent Laid-Open No. 11-148565 特開２００４−２０４９４６号公報JP 2004-204946 A

しかしながら、図５に示したような従来のバルブ１の構造においては、前述した通り弾性部材による付勢力に加えて、受圧面積差Ｓと流体差圧Ｐとの積（Ｓ×Ｐ）によるシートリング５のプラグ２に対する押圧力Ｆが生じるため、流体差圧Ｐの影響を受けて押圧力Ｆも大きくなり、バルブの操作トルクが増大するという問題があった。また、プラグとシートリング間の面圧が増大するとシートリングの摩耗量が増加し易くなり、シートリーク性能が低下するという問題もあった。   However, in the structure of the conventional valve 1 as shown in FIG. 5, in addition to the biasing force by the elastic member as described above, the seat ring is based on the product (S × P) of the pressure receiving area difference S and the fluid pressure difference P. Therefore, there is a problem in that the pressing force F increases due to the influence of the fluid differential pressure P and the operating torque of the valve increases. Further, when the surface pressure between the plug and the seat ring is increased, the amount of wear of the seat ring is liable to increase, and the seat leak performance is lowered.

このため、弁が開いている状態は流体差圧Ｐが小さく、小さな操作トルクで十分であるにもかかわらず、弁が全閉で最大差圧状態となった場合では、大きな操作トルクが必要になるという問題があった。   For this reason, when the valve is open, the fluid differential pressure P is small and a small operating torque is sufficient, but when the valve is fully closed and the maximum differential pressure state is reached, a large operating torque is required. There was a problem of becoming.

本発明は上記したような従来の問題を解決するためになされたもので、その目的とするところは、流体差圧の変動によるプラグへの押圧力の増大を防ぐことで、最大操作トルクが小さく、シートリングの摩耗量を低減させ、シートリーク性能を向上させたバルブを提供することにある。   The present invention has been made in order to solve the above-described conventional problems. The object of the present invention is to prevent the maximum operating torque from being reduced by preventing an increase in the pressing force to the plug due to a change in fluid differential pressure. An object of the present invention is to provide a valve with reduced seat ring wear and improved seat leak performance.

上記目的を達成するために本発明は、弁本体の流路内に回動自在に配設され前記流路を通過する流体の流量を調節するプラグと、前記プラグの着座部が接触するシートリングと、前記シートリングを保持する第１の保持部材と、前記弁本体の内壁に取付けられ前記第１の保持部材を軸線方向に移動可能に保持する第２の保持部材と、前記第１の保持部材と前記第２の保持部材との間に軸線方向に圧縮された状態で介装され前記第１の保持部材を介して前記シートリングを前記プラグに押し付ける弾性部材と、前記第１の保持部材と前記第２の保持部材との間に径方向に圧縮された状態で介装され、前記第１の保持部材と第２の保持部材との隙間をシールするシール部材とを備え、前記弁本体の流路中心軸線から前記プラグと前記シートリングとの接触部までの距離と、前記流路中心軸線から前記第１の保持部材と前記シール部材との接触部までの距離とを略等しくしたものである。   In order to achieve the above object, the present invention provides a seat ring that is rotatably disposed in a flow path of a valve body and that adjusts the flow rate of a fluid passing through the flow path, and a seating portion of the plug is in contact with the plug. A first holding member that holds the seat ring, a second holding member that is attached to an inner wall of the valve body and holds the first holding member movably in the axial direction, and the first holding member An elastic member interposed between a member and the second holding member in a compressed state in an axial direction, and pressing the seat ring against the plug via the first holding member; and the first holding member A seal member interposed between the first holding member and the second holding member in a radially compressed state, and sealing a gap between the first holding member and the second holding member. The plug and the seat ring from the flow path center axis And distance to the contact portion, is obtained by substantially equal to the distance from the flow path center axis to the contact portion between the sealing member and the first holding member.

また、本発明は、弁本体の流路内に回動自在に配設され前記流路を通過する流体の流量を調節するプラグと、前記プラグの着座部が接触するシートリングと、前記シートリングを保持する第１の保持部材と、前記弁本体の内壁に取付けられ前記第１の保持部材を軸線方向に移動可能に保持する第２の保持部材と、前記第１の保持部材と前記第２の保持部材との間に軸線方向に圧縮された状態で介装され前記第１の保持部材を介して前記シートリングを前記プラグに押し付ける弾性部材と、前記第１の保持部材と前記第２の保持部材との間に径方向に圧縮された状態で介装され、前記第１の保持部材と第２の保持部材との隙間をシールするシール部材とを備え、前記弁本体の流路中心軸線から前記プラグと前記シートリングとの接触部までの距離と、前記流路中心軸線から前記第２の保持部材と前記シール部材との接触部までの距離とを略等しくしたものである。   The present invention also provides a plug that is rotatably disposed in the flow path of the valve body and adjusts the flow rate of the fluid passing through the flow path, a seat ring that contacts a seating portion of the plug, and the seat ring A first holding member that holds the first holding member movably in the axial direction, attached to the inner wall of the valve body, the first holding member, and the second holding member. An elastic member that is interposed between the first holding member and the first ring and the second holding member, the elastic member pressing the seat ring against the plug via the first holding member, A seal member that is interposed between the holding member and being compressed in the radial direction, and that seals a gap between the first holding member and the second holding member. To the contact portion between the plug and the seat ring When it is obtained by substantially equal to the distance from the flow path center axis to the contact portion between the sealing member and the second holding member.

本発明においては、流路中心軸線からプラグとシートリングとの接触部までの距離と、流路中心軸線から第１の保持部材とシール部材との接触部までの距離とを略等しくしたので、第１の保持部材への一次側流体圧が加わる受圧面積を小さくすることができる。このため、流体差圧が大きくなっても、シートリングのプラグに対する押圧力が増大しない。その結果、操作トルクも増大せず、シートリングの摩耗も少なく、バルブのシートリーク性能を向上させることができる。   In the present invention, the distance from the flow path center axis to the contact portion between the plug and the seat ring and the distance from the flow path center axis to the contact portion between the first holding member and the seal member are substantially equal. The pressure receiving area to which the primary fluid pressure is applied to the first holding member can be reduced. For this reason, even if the fluid differential pressure increases, the pressing force against the plug of the seat ring does not increase. As a result, the operating torque is not increased, the seat ring is less worn, and the seat leak performance of the valve can be improved.

また、本発明においては、流路中心軸線からプラグとシートリングとの接触部までの距離と、流路中心軸線から第２の保持部材とシール部材との接触部までの距離とを略等しくし、同じく第１の保持部材への一次側流体圧が加わる受圧面積を小さくすることができる。このため、流体差圧が大きくなっても、シートリングのプラグに対する押圧力が増大しない。その結果、操作トルクも増大せず、シートリングの摩耗も少なく、バルブのシートリーク性能を向上させることができる。   In the present invention, the distance from the flow path center axis to the contact portion between the plug and the seat ring is made substantially equal to the distance from the flow path center axis to the contact portion between the second holding member and the seal member. Similarly, the pressure receiving area where the primary fluid pressure is applied to the first holding member can be reduced. For this reason, even if the fluid differential pressure increases, the pressing force against the plug of the seat ring does not increase. As a result, the operating torque is not increased, the seat ring is less worn, and the seat leak performance of the valve can be improved.

以下、本発明を図面に示す実施の形態に基づいて詳細に説明する。
図１は本発明に係るバルブの一実施の形態を示す全閉時の断面図、図２は図１の要部の拡大断面図である。これらの図において、全体を参照符号３０で示すトラニオン形のバルブは、内部が流体３１の流路３２を形成する弁本体３３と、この弁本体３３の内部中央に弁本体３３の軸線（流路中心軸線）３４と直交する面内において回動するように配設され前記流路３２を開閉するボール状のプラグ３５と、このプラグ３５を弁本体３３の外部から回転操作する弁軸３６等で構成されている。 Hereinafter, the present invention will be described in detail based on embodiments shown in the drawings.
FIG. 1 is a cross-sectional view of a valve according to an embodiment of the present invention when fully closed, and FIG. 2 is an enlarged cross-sectional view of the main part of FIG. In these drawings, a trunnion type valve generally indicated by reference numeral 30 has a valve main body 33 that internally forms a flow path 32 of a fluid 31, and an axis (flow path) of the valve main body 33 in the center of the valve main body 33. A ball-shaped plug 35 that is arranged to rotate in a plane orthogonal to the central axis 34, and opens and closes the flow path 32, and a valve shaft 36 that rotates the plug 35 from the outside of the valve body 33. It is configured.

前記弁本体３３は、両端部に配管との接続部を構成するフランジ部３７ａ，３７ｂが一体に突設され、上面中央には前記弁軸３６が貫通する貫通孔３８が形成されている。弁本体３３内の流路３２は、前記プラグ３５によって一次側流路３２Ａと二次側流路３２Ｂに仕切られている。   The valve body 33 is integrally provided with flanges 37a and 37b constituting connecting portions with pipes at both ends, and a through hole 38 through which the valve shaft 36 passes is formed at the center of the upper surface. The flow path 32 in the valve body 33 is partitioned by the plug 35 into a primary flow path 32A and a secondary flow path 32B.

前記プラグ３５は、略球状の中空体からなり、内部が貫通流路４０を形成し、流入孔側開口部４１と流出口側開口部（図示せず）を有している。貫通流路４０の流入孔側開口部４１と流出口側開口部は、プラグ３５の周壁に回転方向に１８０°離間して設けられている。プラグ３５の外周面は、球面状の着座部４４を形成しており、上面中央には前記弁軸３６の下端部が挿入される凹陥部４５が形成されている。一方、プラグ３５の下面中央には、軸部材４６が軸線を弁軸３６の軸線と一致するように挿入される凹陥部４５が形成されている。この軸部材４６は、弁本体３３の下面中央に設けた軸受部材４７に圧入されている。   The plug 35 is formed of a substantially spherical hollow body, and the inside forms a through channel 40 and has an inlet hole side opening 41 and an outlet side opening (not shown). The inflow hole side opening 41 and the outflow port side opening of the through channel 40 are provided on the peripheral wall of the plug 35 so as to be 180 ° apart in the rotational direction. A spherical seating portion 44 is formed on the outer peripheral surface of the plug 35, and a recessed portion 45 into which the lower end portion of the valve shaft 36 is inserted is formed at the center of the upper surface. On the other hand, in the center of the lower surface of the plug 35, a recessed portion 45 is formed in which the shaft member 46 is inserted so that the axis line coincides with the axis line of the valve shaft 36. The shaft member 46 is press-fitted into a bearing member 47 provided at the center of the lower surface of the valve body 33.

前記弁本体３３の貫通孔３８には、筒状の蓋部材４８が嵌合されている。前記弁軸３６は、前記蓋部材４８にシール部材４９を介して回転自在に貫通され、弁本体３３の上方に突出する外端部が図示を省略したアクチュエータによって駆動されることにより、前記プラグ３５を矢印θ方向に略９０°の角度範囲内で回動させるように構成されている。   A cylindrical lid member 48 is fitted in the through hole 38 of the valve body 33. The valve shaft 36 is rotatably passed through the lid member 48 via a seal member 49, and an outer end protruding above the valve main body 33 is driven by an actuator (not shown), whereby the plug 35 is driven. Is rotated within the angle range of approximately 90 ° in the direction of the arrow θ.

前記弁本体３３の内部で一次側流路３２Ａには、前記プラグ３５の着座部４４に密接するシートリング５０と、このシートリング５０を保持する第１の保持部材５１と、この第１の保持部材５１を軸線方向に移動可能に保持する第２の保持部材５２と、第１の保持部材５１を下流側に付勢しシートリング５０をプラグ３５に押し付ける弾性部材としてのばね５３と、第１、第２の保持部材５１，５２間をシールするＯリング（シール部材）５４が配設されており、これらによってシートリング部のシール構造を構成している。   Inside the valve body 33, the primary flow path 32A has a seat ring 50 in close contact with the seating portion 44 of the plug 35, a first holding member 51 for holding the seat ring 50, and the first holding. A second holding member 52 that holds the member 51 movably in the axial direction; a spring 53 as an elastic member that urges the first holding member 51 downstream and presses the seat ring 50 against the plug 35; An O-ring (seal member) 54 that seals between the second holding members 51 and 52 is provided, and these constitute a seat ring seal structure.

前記シートリング５０は、前記プラグ３５の流入孔側開口部４１の高さ寸法より大きな内径（もしくは略等しい内径）を有し、第１の保持部材５１の下流側端面に密接されている。   The seat ring 50 has an inner diameter (or substantially the same inner diameter) larger than the height dimension of the inflow hole side opening 41 of the plug 35, and is in close contact with the downstream end surface of the first holding member 51.

前記第１の保持部材５１は、穴径が全長にわたって略同一の径からなる両端開放の筒状体に形成され、前半部が薄肉部５１Ａを形成し、後半部が厚肉部５１Ｂを形成している。薄肉部５１Ａの外径は、前記シートリング５０と前記プラグ３５の接触径と略等しく設定されている。厚肉部５１Ｂの上流側端面には、環状の溝からなり前記ばね５３を収納する第１の収納部５５が形成されている。また、厚肉部５１Ｂの外周面には、下流側に延在し前記シートリング５０の外周を覆う薄肉の円筒体５６が取付けられている。この円筒体５６の下流側端部には、内側に折り曲げられた折曲部５６Ａが一体に設けられている。このため、筒状体５６と厚肉部５１Ｂの下流側端面との間には、シートリング５０を収納する環状溝が形成されており、これによりシートリング５０の径方向および軸線方向の移動を規制している。   The first holding member 51 is formed in a cylindrical body having both ends opened to have substantially the same diameter over the entire length, the first half part forms a thin part 51A, and the second half part forms a thick part 51B. ing. The outer diameter of the thin portion 51 </ b> A is set substantially equal to the contact diameter of the seat ring 50 and the plug 35. On the upstream end face of the thick portion 51B, a first storage portion 55 that is formed of an annular groove and stores the spring 53 is formed. A thin cylindrical body 56 that extends downstream and covers the outer periphery of the seat ring 50 is attached to the outer peripheral surface of the thick portion 51B. A bent portion 56 </ b> A bent inward is integrally provided at the downstream end portion of the cylindrical body 56. For this reason, an annular groove for accommodating the seat ring 50 is formed between the cylindrical body 56 and the downstream end face of the thick portion 51B, thereby allowing the radial movement and axial movement of the seat ring 50 to be performed. It is regulated.

前記第２の保持部材５２は、筒状体に形成されて中央部が厚肉部５２Ａを形成し、その外周面には弁本体３３の内壁に形成された雌螺子６０に螺合する雄螺子６１が形成されている。第２の保持部材５２の厚肉部５２Ａの前半部内周面には、第１の保持部材５１の薄肉部５１Ａの上流側端面５１ａに対向する突起部５２Ｂが一体に突設されている。また、厚肉部５２Ａは、前記第１の保持部材５１の薄肉部５１Ａの外径と略等しい内径を有し、その内周面に前記Ｏリング５４を径方向に圧縮させた状態で収納する環状の溝からなる第２の収納部６３が形成されている。また、厚肉部５２Ａの外周面には、下流側に延在する薄肉の環状体５２Ｃが一体に突設されており、この環状体５２Ｃに前記第１の保持部材５１の厚肉部５１Ｂが摺動自在に嵌挿されている。そして厚肉部５２Ａの下流側端面は、前記ばね５３を軸線方向に押圧する押圧面６４を形成している。なお、保持部材５２は弁本体３３と一体構造としてもよい。   The second holding member 52 is formed in a cylindrical body, the central part forms a thick part 52A, and the outer peripheral surface of the second holding member 52 is a male screw that is screwed into a female screw 60 formed on the inner wall of the valve body 33. 61 is formed. On the inner peripheral surface of the front half of the thick portion 52A of the second holding member 52, a protruding portion 52B that faces the upstream end surface 51a of the thin portion 51A of the first holding member 51 is integrally projected. The thick portion 52A has an inner diameter that is substantially equal to the outer diameter of the thin portion 51A of the first holding member 51, and stores the O-ring 54 in a radially compressed state on the inner peripheral surface thereof. A second storage portion 63 formed of an annular groove is formed. Further, a thin annular body 52C extending downstream is integrally projected on the outer peripheral surface of the thick part 52A, and the thick part 51B of the first holding member 51 is formed on the annular body 52C. It is slidably inserted. The downstream end surface of the thick portion 52A forms a pressing surface 64 that presses the spring 53 in the axial direction. The holding member 52 may be integrated with the valve body 33.

前記Ｏリング５４は、前記第２の収納部６３内に第１、第２の保持部材５１，５２により径方向に圧縮された状態で収納されることにより、前記第１の保持部材５１の薄肉部５１Ａの外周面に押し付けられており、これにより第１の保持部材５１の薄肉部５１Ａの外周面と第２の保持部材５２の厚肉部５２Ａの内周面との間の隙間をシールしている。薄肉部５１Ａは、Ｏリング５４の流路中心軸線３４に対して直角内向き方向の移動を規制している。第２の収納部６３は、Ｏリング５４の流路中心軸線３４に対して直角外向き方向の移動および流路中心軸線３４と平行な方向の移動を規制している。   The O-ring 54 is stored in the second storage portion 63 in a state compressed in the radial direction by the first and second holding members 51, 52, so that the thin wall of the first holding member 51 is stored. Is pressed against the outer peripheral surface of the portion 51A, thereby sealing the gap between the outer peripheral surface of the thin portion 51A of the first holding member 51 and the inner peripheral surface of the thick portion 52A of the second holding member 52. ing. The thin-walled portion 51 </ b> A restricts the movement of the O-ring 54 in the inward direction perpendicular to the flow path center axis 34. The second storage part 63 restricts the movement of the O-ring 54 in the direction perpendicular to the flow path center axis 34 and the movement in the direction parallel to the flow path center axis 34.

このような構造からなるバルブ３０において、図１はバルブ３０の全閉状態を示す。この状態から弁軸３６によってプラグ３５を図１において反時計方向に徐々に回動させていくと、流入側開口部４１が一次側流路３２Ａに徐々に連通し、流出側開口部が二次側流路３２Ｂに徐々に連通していくため、流体３１が一次側流路３２Ａからプラグ３５の貫通流路４０を通って二次側流路３２Ｂに流れはじめる。そして、プラグ３５を最大角度（略９０°）回動させると、バルブ３０は全開状態になる。   In the valve 30 having such a structure, FIG. 1 shows a fully closed state of the valve 30. When the plug 35 is gradually rotated counterclockwise in FIG. 1 by the valve shaft 36 from this state, the inflow side opening 41 gradually communicates with the primary side flow path 32A, and the outflow side opening is secondary. Since the fluid gradually communicates with the side channel 32B, the fluid 31 starts to flow from the primary channel 32A through the through channel 40 of the plug 35 to the secondary channel 32B. When the plug 35 is rotated by the maximum angle (approximately 90 °), the valve 30 is fully opened.

ここで、本実施の形態においては、シートリング５０をばね５３によってプラグ３５に押し付け、Ｏリング５４を第２の収納部６３内に圧縮状態で収納しているので、バルブ全閉時における流体３１の二次側流路３２Ｂ側への漏洩を確実に防止することができる。   Here, in the present embodiment, the seat ring 50 is pressed against the plug 35 by the spring 53, and the O-ring 54 is stored in the second storage portion 63 in a compressed state, so that the fluid 31 when the valve is fully closed. Leakage to the secondary side flow path 32B side can be reliably prevented.

また、本実施の形態においては、弁本体３３の流路中心軸線３４からプラグ３５とシートリング５０との接触部Ａまでの距離ａと、前記流路中心軸線３４から第１の保持部材５１とＯリング５４との接触部Ｂまでの距離、言い換えれば流路中心軸線３４から第１の保持部材５１の薄肉部５１Ａの外周面までの距離ｂ1 とを略等しくしているので（ａ＝ｂ1 ）、流体差圧Ｐ（＝Ｐ2 −Ｐ1 ）によるシートリング５０のプラグ３５に対する押圧力Ｆを小さくすることができる。 In the present embodiment, the distance a from the flow path center axis 34 of the valve body 33 to the contact portion A between the plug 35 and the seat ring 50, and the first holding member 51 from the flow path center axis 34. The distance to the contact portion B with the O-ring 54, in other words, the distance b 1 from the flow path center axis 34 to the outer peripheral surface of the thin portion 51A of the first holding member 51 is substantially equal (a = b 1 ) The pressing force F against the plug 35 of the seat ring 50 due to the fluid differential pressure P (= P 2 −P 1 ) can be reduced.

本発明の上記実施の形態におけるバルブ３０は、弁本体３３の流路中心軸線３４からプラグ３５とシートリング５０との接触部Ａまでの距離ａを変えずに従来と同じ値とする一方、流路中心軸線３４から第１の保持部材５１の薄肉部５１Ａの外周面までの距離ｂ1 を前記距離ａと略等しくしたので、円筒部５６によって一体となった第１の保持部材５１およびシートリング５０の一次側流体圧Ｐ1 が加わる受圧面積Ｓ1 は、（ｂ1 2−ａ1 2）×πとなる。そして、前述のようにｂ1 とａは略等しくしているので、この受圧面積Ｓ1 は略ゼロとなり、流体３１の一次側と二次側の流体差圧Ｐ（＝Ｐ1 −Ｐ2 ）の変動により操作トルクが増大するのを防止することができる。したがって、操作トルクの小さいアクチュエータを使用することができ、特に、口径が大きいバルブや差圧仕様の大きなバルブになればなるほど、その効果は顕著である。 In the above-described embodiment of the present invention, the valve 30 has the same value as the conventional one without changing the distance a from the flow path center axis 34 of the valve body 33 to the contact portion A between the plug 35 and the seat ring 50. Since the distance b 1 from the road center axis 34 to the outer peripheral surface of the thin portion 51A of the first holding member 51 is substantially equal to the distance a, the first holding member 51 and the seat ring integrated by the cylindrical portion 56 are used. receiving area S 1 of the primary side fluid pressure P 1 of the 50 added becomes (b 1 2 -a 1 2) × π. Since b 1 and a are substantially equal as described above, the pressure receiving area S 1 is substantially zero, and the fluid differential pressure P (= P 1 −P 2) between the primary side and the secondary side of the fluid 31. ) Fluctuations in operating torque can be prevented. Therefore, an actuator having a small operating torque can be used. In particular, the effect becomes more remarkable as the valve has a large diameter or a valve having a large differential pressure specification.

また、シートリング５０のプラグ３５に対する押圧力Ｆは、流体３１の一次側と二次側の流体差圧Ｐ（＝Ｐ1 −Ｐ2 ）の変動によって増大しないため、プラグ３５の着座部４４やシートリング５０の摩耗が少なく、バルブ３０の耐久性を向上させることができる。 The pressing force F of the seat ring 50 against the plug 35 is a fluid differential pressure P (= P 1 −P 2) between the primary side and the secondary side of the fluid 31. ), The wear of the seating portion 44 of the plug 35 and the seat ring 50 is small, and the durability of the valve 30 can be improved.

図３は本実施の形態によるバルブ３０と図５に示した従来のバルブ１による操作トルクの実験データを示す図である。横軸は流体の一次側と二次側の差圧（ＭＰａ）を示し、縦軸は操作トルク（Ｎｍ）を示す。図中、実線Ｉは本実施の形態によるバルブ３０の操作トルク、点線IIは従来バルブ１の操作トルクである。この図からも明らかなように、本実施の形態によるバルブ３０によれば、従来のバルブ１に比べて操作トルクを最大で５割程度削減することができる。これはとりもなおさず、弁本体３３の流路中心軸線３４からプラグ３５とシートリング５０との接触部Ａまでの距離ａと、前記流路中心軸線３４から第１の保持部材５１とＯリング５４との接触部Ｂまでの距離ｂ1 とを略
等しくし、流体差圧Ｐによってシートリング５０がプラグに押し付けられる際の受圧面積Ｓ1 を小さくしたことによるものである。 FIG. 3 is a diagram showing experimental data of operating torque by the valve 30 according to the present embodiment and the conventional valve 1 shown in FIG. The horizontal axis indicates the differential pressure (MPa) between the primary side and the secondary side of the fluid, and the vertical axis indicates the operating torque (Nm). In the figure, the solid line I is the operating torque of the valve 30 according to the present embodiment, and the dotted line II is the operating torque of the conventional valve 1. As is apparent from this figure, according to the valve 30 of the present embodiment, the operating torque can be reduced by up to about 50% compared to the conventional valve 1. Of course, the distance a from the flow path center axis 34 of the valve body 33 to the contact portion A between the plug 35 and the seat ring 50, and the first holding member 51 and the O-ring from the flow path center axis 34. This is because the distance b 1 to the contact portion B with 54 is made substantially equal, and the pressure receiving area S 1 when the seat ring 50 is pressed against the plug by the fluid differential pressure P is reduced.

図４は本発明の他の実施の形態を示すバルブの要部の断面図である。
なお、図１および図２と同一構成部材のものについては同一符号をもって示し、その説明を適宜省略する。この実施の形態は請求項２に記載のバルブを示すものであり、第１の保持部材５１の薄肉部５１Ａの外周面と第２の保持部材５２の厚肉部５２Ａの内周面に凹部７１，７２をそれぞれ形成してこれら凹部によりＯリング５４を収納する環状の第２の収納部７０を形成した点と、弁本体３３の流路中心軸線３４からプラグ３５とシートリング５０との接触部までの距離ａと、流路中心軸線３４から第２の保持部材５２とＯリング５４との接触部Ｂまでの距離ｂ2とを等しく（ａ＝ｂ2 ）した点が図１および図２に示したバルブ３０と異なっている。 FIG. 4 is a cross-sectional view of a main part of a valve showing another embodiment of the present invention.
1 and 2 are denoted by the same reference numerals, and description thereof will be omitted as appropriate. This embodiment shows a valve according to claim 2, and a recess 71 is formed on the outer peripheral surface of the thin portion 51 </ b> A of the first holding member 51 and the inner peripheral surface of the thick portion 52 </ b> A of the second holding member 52. , 72 are formed, and the annular second storage part 70 for storing the O-ring 54 is formed by these recesses, and the contact part between the plug 35 and the seat ring 50 from the flow path center axis 34 of the valve body 33. 1 and FIG. 2 is that the distance a between the flow path center axis 34 and the distance b 2 from the flow path center axis 34 to the contact portion B between the second holding member 52 and the O-ring 54 is equal (a = b 2 ). It differs from the valve 30 shown.

前記凹部７１は、第１の保持部材５１の薄肉部５１Ａの外周面に形成された上流側および弁本体３３の径方向外側の２方向に開放する環状凹部で構成されている。前記凹部７１は、第２の保持部材５２の厚肉部５２Ａの内周面に形成された下流側および弁本体３３の径方向内側の２方向に開放する環状凹部で構成されている。このような凹部７１、７２で構成された第２の収納部７０は、流路中心軸線３４と平行な方向において対抗する前壁７０ａと後壁７０ｂとでＯリング５４の流路中心軸線３４に平行な方向の移動を規制し、第２の収納部７０の流路中心軸線３４と直交する方向において対向する上壁７０ｃと下壁７０ｄとでＯリング５４の流路中心軸線３４と直交する方向の移動を規制している。   The recess 71 is an annular recess that is formed in the outer peripheral surface of the thin portion 51 </ b> A of the first holding member 51 and opens in two directions, ie, radially outward of the valve body 33. The recess 71 is an annular recess that is formed on the inner peripheral surface of the thick portion 52 </ b> A of the second holding member 52 and opens in two directions on the radially inner side of the valve body 33. The second storage part 70 constituted by the recesses 71 and 72 is formed on the flow path center axis 34 of the O-ring 54 with the front wall 70a and the rear wall 70b facing each other in the direction parallel to the flow path center axis 34. Direction in which the movement in the parallel direction is restricted and the upper wall 70c and the lower wall 70d facing each other in the direction orthogonal to the flow path center axis 34 of the second storage unit 70 are orthogonal to the flow path center axis 34 of the O-ring 54 Is restricted from moving.

このような構造においても、弁本体３３の流路中心軸線３４からプラグ３５とシートリング５０との接触部Ａまでの距離ａと、流路中心軸線３４から第１の保持部材５１とＯリング５４との接触部Ｂまでの距離ｂ2 を略等しく設定して一次側流体圧Ｐ1 を受ける第１の保持部材５１の受圧面積を小さくしたので、上記した実施の形態と同様な効果が得られる。 Even in such a structure, the distance a from the flow path center axis 34 of the valve body 33 to the contact portion A between the plug 35 and the seat ring 50, and the first holding member 51 and the O ring 54 from the flow path center axis 34. Since the pressure receiving area of the first holding member 51 that receives the primary fluid pressure P 1 is reduced by setting the distance b 2 to the contact portion B to be substantially equal, the same effect as in the above-described embodiment can be obtained. .

本発明に係るバルブの一実施の形態を示す全閉時における断面図である。It is sectional drawing in the time of a full closure which shows one Embodiment of the valve | bulb which concerns on this invention. 図１の要部の拡大断面図である。It is an expanded sectional view of the principal part of FIG. 操作トルクを示す図である。It is a figure which shows the operation torque. 本発明の他の実施の形態を示すバルブの要部の断面図である。It is sectional drawing of the principal part of the valve | bulb which shows other embodiment of this invention. 従来のバルブの要部の断面図である。It is sectional drawing of the principal part of the conventional valve | bulb.

符号の説明Explanation of symbols

１…二方ボールバルブ、２…プラグ、３…第１の保持部材、４…ばね、５…シートリング、６…弁本体、９…流路、１０…流路中心軸線、１１…第２の保持部材、１２…Ｏリング、１３…弁軸、３０…バルブ、３３…弁本体、３４…流路中心軸線、３５…プラグ、３６…弁軸、５０…シートリング、５１…第１の保持部材、５２…第２の保持部材、５３…ばね、５４…Ｏリング、５５…第１の収納部、６３，７０…第２の収納部。   DESCRIPTION OF SYMBOLS 1 ... Two-way ball valve, 2 ... Plug, 3 ... 1st holding member, 4 ... Spring, 5 ... Seat ring, 6 ... Valve body, 9 ... Flow path, 10 ... Flow path center axis, 11 ... 2nd Holding member, 12 ... O-ring, 13 ... Valve shaft, 30 ... Valve, 33 ... Valve body, 34 ... Flow path center axis, 35 ... Plug, 36 ... Valve shaft, 50 ... Seat ring, 51 ... First holding member 52 ... 2nd holding member, 53 ... Spring, 54 ... O-ring, 55 ... 1st accommodating part, 63, 70 ... 2nd accommodating part.

Claims (2)

弁本体の流路内に回動自在に配設され前記流路を通過する流体の流量を調節するプラグと、
前記プラグの着座部が接触するシートリングと、
前記シートリングを保持する第１の保持部材と、
前記弁本体の内壁に取付けられ前記第１の保持部材を軸線方向に移動可能に保持する第２の保持部材と、
前記第１の保持部材と前記第２の保持部材との間に軸線方向に圧縮された状態で介装され前記第１の保持部材を介して前記シートリングを前記プラグに押し付ける弾性部材と、
前記第１の保持部材と前記第２の保持部材との間に径方向に圧縮された状態で介装され、前記第１の保持部材と第２の保持部材との隙間をシールするシール部材とを備え、
前記弁本体の流路中心軸線から前記プラグと前記シートリングとの接触部までの距離と、前記流路中心軸線から前記第１の保持部材と前記シール部材との接触部までの距離とを略等しくしたことを特徴とするバルブ。 A plug that is rotatably disposed in the flow path of the valve body and adjusts the flow rate of the fluid passing through the flow path;
A seat ring with which the seat of the plug contacts;
A first holding member for holding the seat ring;
A second holding member attached to the inner wall of the valve body and holding the first holding member movably in the axial direction;
An elastic member interposed between the first holding member and the second holding member in an axially compressed state and pressing the seat ring against the plug via the first holding member;
A seal member interposed between the first holding member and the second holding member in a radially compressed state and sealing a gap between the first holding member and the second holding member; With
The distance from the flow path center axis of the valve body to the contact portion between the plug and the seat ring and the distance from the flow path center axis to the contact portion between the first holding member and the seal member are approximately Valve characterized by equality. 弁本体の流路内に回動自在に配設され前記流路を通過する流体の流量を調節するプラグと、
前記プラグの着座部が接触するシートリングと、
前記シートリングを保持する第１の保持部材と、
前記弁本体の内壁に取付けられ前記第１の保持部材を軸線方向に移動可能に保持する第２の保持部材と、
前記第１の保持部材と前記第２の保持部材との間に軸線方向に圧縮された状態で介装され前記第１の保持部材を介して前記シートリングを前記プラグに押し付ける弾性部材と、
前記第１の保持部材と前記第２の保持部材との間に径方向に圧縮された状態で介装され、前記第１の保持部材と第２の保持部材との隙間をシールするシール部材とを備え、
前記弁本体の流路中心軸線から前記プラグと前記シートリングとの接触部までの距離と、前記流路中心軸線から前記第２の保持部材と前記シール部材との接触部までの距離とを略等しくしたことを特徴とするバルブ。 A plug that is rotatably disposed in the flow path of the valve body and adjusts the flow rate of the fluid passing through the flow path;
A seat ring with which the seat of the plug contacts;
A first holding member for holding the seat ring;
A second holding member attached to the inner wall of the valve body and holding the first holding member movably in the axial direction;
An elastic member interposed between the first holding member and the second holding member in an axially compressed state and pressing the seat ring against the plug via the first holding member;
A seal member interposed between the first holding member and the second holding member in a radially compressed state and sealing a gap between the first holding member and the second holding member; With
The distance from the flow path center axis of the valve body to the contact portion between the plug and the seat ring and the distance from the flow path center axis to the contact portion between the second holding member and the seal member are approximately Valve characterized by equality.
JP2007072537A 2007-03-20 2007-03-20 Valve Pending JP2008232260A (en)

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CN103234059A (en) * 2013-05-15 2013-08-07 岳阳东方自控工程设备有限公司 Ball valve with elastic membrane type hard-sealing valve seat
CN105909818A (en) * 2016-06-16 2016-08-31 五洲阀门股份有限公司 Anti-corrosion ball valve and manufacturing method thereof
EP3232099A4 (en) * 2014-12-12 2017-11-22 Aisin Seiki Kabushiki Kaisha Refrigerant control valve device
KR101872683B1 (en) * 2017-12-05 2018-06-29 (주)비티엑스 Self-adjustment type ball-valve
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JP2011241943A (en) * 2010-05-20 2011-12-01 Tyco Flow Control Japan Kk Ball valve
CN102900865A (en) * 2011-07-27 2013-01-30 株式会社京滨 Valve device
US8820706B2 (en) 2011-07-27 2014-09-02 Keihin Corporation Valve device
CN102900865B (en) * 2011-07-27 2015-04-22 株式会社京滨 Valve device
CN103234059A (en) * 2013-05-15 2013-08-07 岳阳东方自控工程设备有限公司 Ball valve with elastic membrane type hard-sealing valve seat
US11608903B2 (en) 2014-07-07 2023-03-21 Denso Corporation Valve device
US10808848B2 (en) 2014-07-07 2020-10-20 Denso Corporation Valve device
EP3366960A1 (en) 2014-07-07 2018-08-29 Denso Corporation Valve device
US10066751B2 (en) 2014-07-07 2018-09-04 Denso Corporation Valve device
EP3428491A1 (en) 2014-07-07 2019-01-16 Denso Corporation Valve device
US11067180B2 (en) 2014-07-07 2021-07-20 Denso Corporation Valve device
EP3232099A4 (en) * 2014-12-12 2017-11-22 Aisin Seiki Kabushiki Kaisha Refrigerant control valve device
US20170335750A1 (en) * 2014-12-12 2017-11-23 Aisin Seiki Kabushiki Kaisha Refrigerant control valve apparatus
US10513968B2 (en) * 2014-12-12 2019-12-24 Aisin Seiki Kabushiki Kaisha Refrigerant control valve apparatus
DE112016006319T5 (en) 2016-01-28 2018-10-18 Denso Corporation valve device
US10539100B2 (en) 2016-03-03 2020-01-21 Denso Corporation Valve device
CN105909818A (en) * 2016-06-16 2016-08-31 五洲阀门股份有限公司 Anti-corrosion ball valve and manufacturing method thereof
KR101872683B1 (en) * 2017-12-05 2018-06-29 (주)비티엑스 Self-adjustment type ball-valve
JP2020143736A (en) * 2019-03-06 2020-09-10 株式会社デンソー Valve device
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KR20080085699A (en) 2008-09-24

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