JPH04506853A - Butterfly method and device - Google Patents

Butterfly method and device

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Publication number
JPH04506853A
JPH04506853A JP2510566A JP51056690A JPH04506853A JP H04506853 A JPH04506853 A JP H04506853A JP 2510566 A JP2510566 A JP 2510566A JP 51056690 A JP51056690 A JP 51056690A JP H04506853 A JPH04506853 A JP H04506853A
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JP
Japan
Prior art keywords
valve plate
shaft
torque
valve
fluid
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.)
Pending
Application number
JP2510566A
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Japanese (ja)
Inventor
ターボ，ジヨン　エヌ．
バル，ラリイー　ケイ．
ハインズ，マーシヤル　ユー．
Original Assignee
アライド・シグナル・インコーポレーテツド
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Publication date
Priority claimed from US07/395,234 external-priority patent/US4964422A/en
Priority claimed from US07/422,354 external-priority patent/US4967778A/en
Priority claimed from US07/426,921 external-priority patent/US4967997A/en
Priority claimed from US07/533,965 external-priority patent/US5000213A/en
Application filed by アライド・シグナル・インコーポレーテツド filed Critical アライド・シグナル・インコーポレーテツド
Publication of JPH04506853A publication Critical patent/JPH04506853A/en
Pending 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member
    • F16K15/031—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member the hinge being flexible
    • 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
    • F16K1/16—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
    • F16K1/221—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 specially adapted operating means 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
    • 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
    • F16K1/2261—Shaping or arrangements of the sealing the sealing being arranged on 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member
    • F16K15/035—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member with a plurality of valve 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
    • 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
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/528—Mechanical actuating means with crank, eccentric, or cam with pin and slot
    • F16K31/5282—Mechanical actuating means with crank, eccentric, or cam with pin and slot comprising a pivoted disc or flap

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Lift Valve (AREA)

Abstract

(57)【要約】本公報は電子出願前の出願データであるため要約のデータは記録されません。 (57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

【発明の詳細な説明】 螺形弁法及び装置 （技術分野） 以下の未決定で通常に所有された、平衡トルク弁を開示する米国特許出願、１９ ８９年６月３０日出願の第３７４．８９７号、１９８９年８月１７日出願の第３ ９５．２３４号、１９８９年１０月１６日出願の第４２２゜３５４号並びに１９ ８９年ＩＯ月２４日出願の第４２６．９２１号を参照する。[Detailed description of the invention] Spiral valve method and device (Technical field) The following pending and commonly owned U.S. Patent Application Discloses a Balanced Torque Valve, No. 19 No. 374.897 filed on June 30, 1989, No. 3 filed on August 17, 1989 No. 95.234, No. 422゜354 filed on October 16, 1989, and No. 19 No. 426.921, filed IO/24/89.

本発明は螺形弁（制御Ｉ）法及び装置、特に旋回機構に対する弁プレートの変位 が可能な構造の螺形弁法及び装置に関する５゜ （背景技術） 螺形弁では、旋回機構に対する弁プレートの変位を利用して流体によるトルクの 動的平衡をとりこのトルクをを用いて簡単に弁プレートを回転駆動する。この原 理は本願出願人による１９８９年６月３０日付けの特許出願第３７４．８９７号 に示される。The present invention relates to a spiral valve (control I) method and apparatus, in particular the displacement of a valve plate relative to a pivoting mechanism. 5° regarding the spiral valve method and device with a structure capable of (Background technology) Spiral valves utilize the displacement of the valve plate relative to the pivot mechanism to reduce the torque caused by the fluid. Dynamic balance is achieved and this torque is used to simply rotate the valve plate. this field Patent Application No. 374.897 dated June 30, 1989 by the applicant is shown.

この場合は第１２Ａ図〜第１２Ｃ図には、弁プレート２０、旋回シャフト２２、 ダクト２４、ブラツケト２６及び流れ方向２８が簡略に示されている。矢印３０ は流体の流れの方向を示し、旋回線３２は流体により弁プレート２０に加わる力 に基づく中央圧力を示し、弁プレート２０は旋回線３２を中心に旋回可能である 。In this case, FIGS. 12A to 12C show the valve plate 20, the pivot shaft 22, The duct 24, bracket 26 and flow direction 28 are shown schematically. arrow 30 indicates the direction of fluid flow, and the swirl line 32 represents the force exerted on the valve plate 20 by the fluid. , and the valve plate 20 is pivotable about a pivot line 32 .

第１２Ａ図では、旋回シャフト２２は弁プレート２０の長手寸法に対し中心に配 置され、弁プレート２０が閉鎖位置にある。圧力３０の中心は旋回線３２と整合 されるので、流体による弁プレート２０に加わる実質トルクは零である。弁プレ ート２０が第１２Ｂ図に示すような開放位置に回転され旋回シャフト２２に対し 変位移動され圧力３０が第１２Ｃ図に示すように旋回線３２と整合されると、弁 プレート２０は効果的にトルク平衡が得られ、回転角３４に基づく流量は作動器 ３６から要求される最小入力で維持可能である。変位移動の範囲があまり制限さ れ弁プレート２０の総ての回転位置でのトルク平衡が得られない場合でも、流体 による実質トルクを最小にするために好適に使用出来るので、作動器３６からの 要求される入力が最小にされ得る。In FIG. 12A, the pivot shaft 22 is centered relative to the longitudinal dimension of the valve plate 20. and the valve plate 20 is in the closed position. The center of pressure 30 is aligned with the swirl line 32 Therefore, the effective torque exerted on the valve plate 20 by the fluid is zero. Benpre The shaft 20 is rotated to the open position as shown in FIG. 12B relative to the pivot shaft 22. Once the pressure 30 is displaced and aligned with the swirl line 32 as shown in FIG. 12C, the valve The plate 20 is effectively torque balanced and the flow rate based on the rotation angle 34 is controlled by the actuator. can be maintained with the minimum input required from 36. The range of displacement movement is less limited Even if torque balance cannot be obtained at all rotational positions of the valve plate 20, the fluid The output from actuator 36 can be advantageously used to minimize the effective torque due to Required input may be minimized.

回転角３４を変更することが望ましいときには、弁プレート２０は好適な方向に 旋回シャフト２２に対し変位され圧力３０の中心と旋回線３２とを整合出来、従 って実質流体動的トルクが増加され変更するに必要な力はダクト２４内を移動す る流体により全部あるいは一部与えられる。When it is desired to change the angle of rotation 34, the valve plate 20 is moved in a suitable direction. The center of the pressure 30 displaced relative to the rotation shaft 22 and the rotation line 32 can be aligned, and the Therefore, the actual fluid dynamic torque is increased and the force required to change it is transferred within the duct 24. It is provided in whole or in part by the fluid that is present.

上述した目的の一方あるいは両方のため旋回シャフト２２に対し弁プレート２０ を変位するよう構成される螺形弁は以下平衡トルク蝶形弁と呼ぶ。A valve plate 20 is attached to the pivot shaft 22 for one or both of the above-mentioned purposes. A helical valve configured to displace is hereinafter referred to as a balanced torque butterfly valve.

すなわち、平衡トルク蝶形弁を閉鎖位置に相当する回転角３４を要求する場合に 使用すると、変位が生じまた弁プレート２０を最初に開放することは理解されよ う。弁プレート２０を最初に開放するためい（つかの構成が提案された。１）旋 回シャフト２２をダクト２４内に可動に装着し、旋回シャフト２２はそれ自身の 長手軸に対し垂直な方向に変位可能にし、圧力３０の中心と旋回線３２とを零角 度に整合する：２）パイロット弁を弁プレートを介し設はパイロット弁を零角度 で開放作動し圧力中心の位置を変更する；３）弁プレート上に作動器を装着し作 動器の出力シャフトは旋回シャフト２２に対し回転可能に保持され、作動器を用 いて最初の開放のための回転と次のトルク平衡のための変位を行う。That is, when requiring a rotation angle 34 corresponding to the closed position of the balanced torque butterfly valve, It will be appreciated that in use, a displacement occurs and the valve plate 20 is initially opened. cormorant. Several configurations have been proposed for initially opening the valve plate 20. A rotating shaft 22 is movably mounted within the duct 24, and the pivoting shaft 22 has its own Displacement is possible in a direction perpendicular to the longitudinal axis, and the center of pressure 30 and rotation line 32 are at zero angle. 2) Install the pilot valve through the valve plate so that the pilot valve is at zero angle. 3) Attach the actuator to the valve plate and operate. The output shaft of the actuator is rotatably held relative to the pivot shaft 22, and the output shaft of the actuator is Then perform the rotation for the first opening and the displacement for the next torque balance.

上記構成は自在に作動可能であることが要求される。多くの場合、弁を作動する とき外部に配置された単一の作動器３６のみを用いて周知の作動原理に従い最初 の開放及びこれに続（変位を与えることが望ましい。また、一般に作動器３６の トルク条件を最小にして小さな作動器を使用可能にすることが望ましい。The above configuration is required to be freely operable. often actuates valves Initially, according to well-known actuation principles using only a single externally arranged actuator 36, It is desirable to open the actuator 36 and to provide a subsequent displacement. It is desirable to minimize torque requirements to allow the use of small actuators.

（発明の開示） 本発明によれば、平衡トルク蝶形弁法及び装置が提供される。用語［平衡トルク ］とは、方法上は螺形弁構造を用いて、弁プレートを流路内で旋回させる旋回機 構に対し弁プレートを変位させる方法を意味し、装置上はこの構成を含む装置を 意味する。この動作に関連する利点は［背景技術］において説明しである。(Disclosure of invention) In accordance with the present invention, a balanced torque butterfly valve method and apparatus is provided. Terminology [equilibrium torque ] is a turning machine that uses a spiral valve structure to turn a valve plate in a flow path. means a method of displacing the valve plate relative to the structure, and the device that includes this structure is means. The advantages associated with this operation are explained in the Background section.

以下に説明し請求の範囲に掲げたように実質トルクを最大限に利用し螺形弁を容 易に制御する方法によれば、弁プレートは第１の回転位ｌから第２の回転位置へ 移動され、一方流路に沿って流動される流体により実質トルクを受ける。実質ト ルクにより上述した（直線的）変位が阻止され、弁プレートが再び第１の回転位 置へ回転される傾向になる。弁プレートの変位は連続する回転移動と変位を特徴 とし、変位により実質トルクが減少されて回転移動が容易にされる。全体の移動 は実質的に連続であるが、回転移動成分及び変位成分を特徴とすることは以下の 説明から理解されよう。As explained and claimed below, the helical valve can be accommodated by making full use of the effective torque. According to a method of easy control, the valve plate is moved from a first rotational position l to a second rotational position. while being moved and subjected to a substantial torque by the fluid flowing along the flow path. Actual The above-mentioned (linear) displacement is prevented by the torque and the valve plate returns to the first rotational position. It tends to be rotated towards the position. The displacement of the valve plate is characterized by continuous rotational movement and displacement The displacement reduces the net torque and facilitates rotational movement. whole movement is substantially continuous, but it is characterized by a rotational movement component and a displacement component as follows. It will be understood from the explanation.

以下に説明し請求の範囲に掲げる装置では、回転移動と（直線的）変位の両方が 、流体を流動させる流路の一部を区画する取付胴部と、流路内にこれを横断する ように支承された弁プレートと、取付胴部内に枢支され弁プレートを支承する旋 回装置と、旋回装置に動作可能に接続されトルクを旋回装置に伝達する差動ギア と、差動ギアに対し動作可能に接続され入力トルクを差動ギアに与える入力シャ フトとを備える螺形弁により与えられる。差動ギアは入力シャフトの回転に応動 して弁プレートの回転移動あるいは変位を与える機械的な変換器として機能する 。上述の結果生じる移動量は両方の移動の一方を阻止する程度に左右される。本 装置には更に弁プレートの変位を阻止するバネあるいはこれと等価なバイアス機 構が備えられる。このような構成を使用する場合、差動ギアはバイアス機構によ り与えられる力と流体により弁プレートに加わる実質トルクとの関係により、入 力シャフトの回転移動を弁プレートの回転移動あるいは変位に変換する機械的変 換器として機能する。In the device described and claimed below, both rotational movement and (linear) displacement are possible. , a mounting body that partitions a part of the flow path through which the fluid flows, and a mounting body that traverses this into the flow path. A valve plate is supported in a manner similar to a swivel device and a differential gear operably connected to the swivel device to transmit torque to the swivel device and an input shaft operably connected to the differential gear to provide input torque to the differential gear. It is provided by a spiral valve with a foot. Differential gear responds to input shaft rotation act as a mechanical transducer to provide rotational movement or displacement of the valve plate. . The amount of movement that results from the above depends on the extent to which one of the two movements is prevented. Book The device also includes a spring or equivalent bias device to prevent displacement of the valve plate. A structure is provided. When using such a configuration, the differential gear is biased The relationship between the force applied by the fluid and the effective torque applied to the valve plate by the fluid determines the input Mechanical displacement that converts rotational movement of the force shaft into rotational movement or displacement of the valve plate. Functions as a converter.

（図面の簡単な説明） 第１図は組み立てられた螺形弁の斜視図、第２図は第１図の螺形弁の分解斜視図 、第３図は旋回装置及び差動ギアを含む第２図の各構成部材の一部を断面で示す 側面図、第４図〜第６図は第３図の各線４−４．５−５．６−６に沿って切断し た断面図、第７図は旋回装置の部分正面図、第８図は第１図及び第２図の弁プレ ートの平面図、第９図は第８図の弁プレートの一部を断面で示す側面図、第１０ 図は弁プレート及び旋回機構の両方に対し平行な方向から見た螺形弁の一部を断 面で示す正面図、第１１図は第１０図の線１１−１１に沿って切断した部分正面 図、第１２Ａ図〜第１２１１図は平衡トルク蝶形弁の原理及び本発明の方法の両 方を示すための弁プレートの各回転位置及び変位位置を示す平衡トルク蝶形弁の 簡略図、第１３図は密封機能が要求される用途において好適な密封構成を備える 螺形弁の簡略図である。(Brief explanation of the drawing) Figure 1 is a perspective view of the assembled spiral valve, and Figure 2 is an exploded perspective view of the spiral valve in Figure 1. , FIG. 3 is a cross-sectional view of a portion of each component shown in FIG. 2, including the swing device and the differential gear. Side views, Figures 4 to 6 are taken along lines 4-4.5-5.6-6 in Figure 3. 7 is a partial front view of the swing device, and FIG. 8 is a sectional view of the valve plate shown in FIGS. 1 and 2. FIG. 9 is a side view showing a part of the valve plate in FIG. 8 in cross section, and FIG. The illustration shows a partially cutaway view of a helical valve from a direction parallel to both the valve plate and the pivot mechanism. Figure 11 is a partial front view taken along line 11-11 in Figure 10. Figures 12A to 1211 illustrate both the principle of a balanced torque butterfly valve and the method of the present invention. Balance torque of the butterfly valve to indicate each rotational position and displacement position of the valve plate. The simplified diagram, FIG. 13, has a sealing configuration suitable for applications where sealing function is required. FIG. 2 is a simplified diagram of a spiral valve.

（発明を実施するための最良の形態） 第１図には、外部の作動器３６を介し作動され弁プレート４２の位置を制御する 螺形弁４０が図示される。弁プレート４２は取付胴部４６により区画された流路 ４４（第１０図参照）内において旋回可能に且つ流路４４を横断するように配置 される。(Best mode for carrying out the invention) 1 is actuated via external actuator 36 to control the position of valve plate 42. A spiral valve 40 is illustrated. The valve plate 42 has a flow path defined by the mounting body 46. 44 (see FIG. 10) and arranged so as to be able to rotate within the channel 44 (see FIG. 10) and to cross the flow path 44. be done.

使用時に、流体供給源から流体を流動させる長手の流路を形成したダクト部材（ 図示せず）が取付胴部４６に固設され、流体は更に螺形弁４０を経て１以上の使 用箇所へ送られるつ流体の流れは弁プレート４２の回転位置決めにより制御され る。In use, a duct member ( (not shown) is fixedly attached to the mounting body 46, and the fluid is further passed through a helical valve 40 to one or more uses. The flow of fluid to the point of use is controlled by the rotational positioning of the valve plate 42. Ru.

この回転位置決めは作動器３６により入力シャフト４８に与えられるトルクに応 答して得られる。このトルクは作動ギア５０（第３図参照）を介し旋回機構５２ （第７図参照）へ伝達され、旋回機構５２は取付胴部４６に枢支され弁プレート ４２が枢支されることになる。This rotational positioning is responsive to the torque applied to input shaft 48 by actuator 36. can be obtained by answering This torque is transmitted to the turning mechanism 52 through the operating gear 50 (see FIG. 3). (see Fig. 7), and the turning mechanism 52 is pivoted to the mounting body 46 and is connected to the valve plate. 42 will be supported.

第８図及び第９図には弁プレート４２の詳細図が示される。A detailed view of the valve plate 42 is shown in FIGS. 8 and 9.

円形の弁プレート４２の直径は取付胴部４６の内径より僅かに小さくされ、弁プ レート４２の変位動作が流路４４内で円滑に行われ得る。旋回機構５２（第７図 参照）に対する弁プレート４２の（直線的）変位移動は図示の弁プレート４２を 貫通して延びる好適な寸法の空洞部５４において吸収される。スロット５６．５ ８は弁プレート４２の下流の対向面６０と空洞部５４との間に形成される１、弁 プレート４２内には小さなネジ穴（図示せず）が形成され、円弧フェンス６２と 弁プレート４２を弁プレート４２の先端部の近傍で固定するプレート受はネジ６ １がこのネジ穴内に挿入される。また１対のラックギア６４．６６（第２図参照 ）を弁プレート４２に取り付けるためのスロット５６．５８が具備される。The diameter of the circular valve plate 42 is made slightly smaller than the inner diameter of the mounting body 46, so that the valve plate 42 has a diameter slightly smaller than the inner diameter of the mounting body 46. A displacement operation of rate 42 can be performed smoothly within flow path 44 . Rotating mechanism 52 (Fig. 7 The (linear) displacement movement of the valve plate 42 with respect to It is absorbed in a suitably sized cavity 54 extending therethrough. slot 56.5 8 is a valve 1 formed between the downstream facing surface 60 of the valve plate 42 and the cavity 54; A small screw hole (not shown) is formed in the plate 42 and connects it to the arc fence 62. The plate holder that fixes the valve plate 42 near the tip of the valve plate 42 has screws 6. 1 is inserted into this screw hole. Also, a pair of rack gears 64 and 66 (see Figure 2) ) are provided with slots 56,58 for attaching them to the valve plate 42.

第２図、第３図及び第７図には旋回機構５２及び作動ギア５０が詳しく示される 。旋回機構５２には中央シャフト７０とシャフト支承体７２が包有される。シャ フト支承体７２は中央部の長方形部材７６と２個の円筒状端部７８．８０を有す る。円筒状端部７８にはナツト８２が螺合されており、円筒状端部８０にはこれ に対し横断方向に貫通して延びる開口部８４が形成される。長手方向に延びる段 付き開口部８６がシャフト支承体７２内に形成され、段付き開口部８６には中央 シャフト７０が挿入され且つ段付き開口部８６は作動ギア５０を収納するハウジ ングとしても機能する。FIGS. 2, 3, and 7 show the pivot mechanism 52 and operating gear 50 in detail. . The pivot mechanism 52 includes a central shaft 70 and a shaft support 72. Sha The foot support 72 has a central rectangular member 76 and two cylindrical ends 78,80. Ru. A nut 82 is threaded onto the cylindrical end 78 , and a nut 82 is threaded onto the cylindrical end 80 . An opening 84 is formed that extends transversely therethrough. longitudinally extending steps A stepped opening 86 is formed in the shaft bearing 72, with the stepped opening 86 having a central The stepped opening 86 into which the shaft 70 is inserted is a housing that houses the actuating gear 50. It also functions as a tool.

段付き開口部８６の直径は十分に大にされており、中央シャフト７０が段付き開 口部８６内において回転可能に設けられている。The diameter of the stepped opening 86 is sufficiently large so that the central shaft 70 It is rotatably provided within the mouth portion 86.

スロット９０．９２は長方形部材７６にこれを横断する方向に形成されており、 貫通スロット９４．９６は横断スロット９０．９２からシャフト支承体７２の上 流の対向面９８へ向かって延設される。Slots 90,92 are formed in rectangular member 76 in a direction transverse thereto; Through slots 94.96 extend from transverse slots 90.92 onto shaft bearing 72. It extends toward the opposite surface 98 of the flow.

貫通スロット９４．９６は図示のように長平に延びる段付き開口部８６に対しこ れを横断するように設けられる。深溝１００及びこれに対応するクロススロット １０２が５個のローラ１０４を取り付けるためシャフト支承体７２に形成される 。各ローラ１０４はニードルベアリング１０７（第６図参照）を介し小シャフト １０６に対し回転可能に取り付けられる。小シャフト１０６はクロススロット１ ０２内に圧力嵌めされる。ローラ１０４は弁プレート４２の変位１０９（第１θ 図参照）の動作中シャフト支承体７２と弁プレート４２との間の摩擦を最小限に 押さえるベアリングとして機能する。長手に延びる段付き開口部８６は２カ所で 大にされこの拡大部にベアリング１０８．１１Ｇが配設される。ベアリング８８ も図示のように円筒状端部８０に付設される。板バネ１１２はネジ穴内に延びる ネジを介しシャフト支承体７２の縁部に固定される（注：図示のものには板バネ １１２が内蔵されているが、多くの場合にはより堅牢なバイアス機構を用いるこ とが好ましいと考えられる。従って板バネ１１２は好適に配置され装着された２ 個のコイルバネあるいは用途に応じ機能的に等価な他のバイアス機構と置換可能 である）。The through slots 94 and 96 are arranged in parallel to the elongated stepped opening 86 as shown. It is installed so as to cross the road. Deep groove 100 and corresponding cross slot 102 are formed on the shaft bearing 72 for mounting five rollers 104. . Each roller 104 is connected to a small shaft via a needle bearing 107 (see Fig. 6). 106 so as to be rotatable. Small shaft 106 is cross slot 1 Press fit into 02. The roller 104 corresponds to the displacement 109 (1st θ) of the valve plate 42. (see figure) to minimize friction between the shaft support 72 and the valve plate 42 during operation. Functions as a holding bearing. There are two longitudinally extending stepped openings 86. The bearing 108.11G is arranged in this enlarged portion. bearing 88 is also attached to the cylindrical end 80 as shown. The leaf spring 112 extends into the screw hole. It is fixed to the edge of the shaft support 72 via a screw (note: the one shown has a leaf spring). 112, but in many cases a more robust biasing mechanism can be used. is considered preferable. Therefore, the leaf spring 112 is suitably arranged and attached to the 2 Can be replaced with individual coil springs or other functionally equivalent biasing mechanisms depending on the application ).

差動ギア５０の第１のベベルギア１１４は差動ハウジング内に延びる端部の近傍 で中央シャフト７０に装着される。中央シャフト７０は図示のように、長手方向 に延びる段付き開口部８６内に収容され、ベアリング１０８．１１０及び貫通ス ロット９４．９６内に２個のビニオンギア１１６．１１８が貫通して延設されて いる。The first bevel gear 114 of the differential gear 50 is located near the end that extends into the differential housing. and is attached to the central shaft 70. The central shaft 70 is longitudinally oriented as shown. The bearings 108, 110 and the through shaft are Two pinion gears 116.118 extend through the lot 94.96. There is.

クロスシャフト１２Ｇはクロス開口部８４及びニードルベアリング（図示せず） を貫通し互いに嵌め固定して延び、第２及び第３のベベルギア１２２．１２４の 軸方向の開口部（図示せず）内に収納される。差動ギア５０の第４のベベルギア １２６は入力シャフト４８に対し嵌め装着される。入力シャフト４８はエンドキ ャップ７４の軸方向に延びる段付き開口部を貫通して延び、エンドキャップ７４ に着座されたベアリングを貫通し嵌め固定される。次にエンドキャップ７４は図 示のようにシャフト支承体７２の端部に固定され、第４のベベルギア１２６は第 ２及び第３のベベルギア１２２，１２４と係合され、第２及び第３のベベルギア １２２．１２４自体は第１のベベルギア１１４と係合されて差動ギア５０が形成 されている。The cross shaft 12G has a cross opening 84 and a needle bearing (not shown). The second and third bevel gears 122 and 124 extend through and are fitted and fixed to each other. It is housed within an axial opening (not shown). Fourth bevel gear of differential gear 50 126 is fitted onto the input shaft 48. The input shaft 48 is an end key The end cap 74 extends through an axially extending stepped opening in the end cap 74 . It passes through the bearing seated on and is fixed in place. Next, the end cap 74 is The fourth bevel gear 126 is fixed to the end of the shaft support 72 as shown. The second and third bevel gears 122 and 124 are engaged with the second and third bevel gears. 122, 124 itself is engaged with the first bevel gear 114 to form the differential gear 50. has been done.

第１及び第４のベベルギア１１４．１２６はそれぞれ中央シャフト７０及び入力 シャフト４８に固定され、一方策２及び第３のベベルギア１２２．１２４はクロ スシャフト１２Ｇに対し回転可能に装着されることは理解されよう。回転トルク が入カシ・ヤフト４８に与えられると、このトルクは差動ギア５ｏを経て中央シ ャフト７０へ伝達される。中央シャフト７０が自在に回転する場合、入力シャフ ト４８の回転に応答して中央シャフト７ｏが自在に回転する。一方、中央シャフ ト７０の回転が制限される場合、トルクはクロスシャフト１２０を介しシャフト 支承体７２へ伝達される。The first and fourth bevel gears 114, 126 respectively connect the central shaft 70 and the input The second and third bevel gears 122 and 124 are fixed to the shaft 48, and the second and third bevel gears 122 and 124 are It will be appreciated that the shaft 12G is rotatably mounted to the shaft 12G. Rotation torque is applied to the input shaft 48, this torque is transferred to the central shaft via the differential gear 5o. It is transmitted to the shaft 70. When the central shaft 70 rotates freely, the input shaft In response to the rotation of the shaft 48, the central shaft 7o freely rotates. On the other hand, the central shaft When the rotation of the shaft 70 is limited, the torque is transferred to the shaft through the cross shaft 120. It is transmitted to the support body 72.

ラックギア６４．６６は横断スロット９０．９２内においてピニオンギア１１６ ．１１８と係合される。弁プレート４２は取付胴部４６内に保持され、旋回機構 ５２がアクセスポートエ２８及び空洞部５４（第９図参照）を貫通して延び、板 バネ１１２が押圧されており、ネジ山付きの円筒状端部７８は取付胴部を貫通し て形成された対向するボート１３０に突出する。Rack gears 64,66 are connected to pinion gears 116 within transverse slots 90,92. ．． 118. The valve plate 42 is retained within the mounting body 46 and has a pivot mechanism. 52 extends through the access port 28 and the cavity 54 (see FIG. 9), and The spring 112 is compressed and the threaded cylindrical end 78 passes through the mounting body. protrudes into an opposing boat 130 formed by

そらせ板１３２．１３４はベアリング８８と長方形部材７６との間のシャフト支 承体７２の周囲において取付胴部４６の環形リム１３８あるいはボスに対して配 置される。そらせ板１３２．１３４の内側面（第２図では表されてない面）の輪 郭は取付胴部４６の内面６８と合致され、そらせ板１３２，１３４の内側面は上 述のように配置されるとき面一にされる。The baffles 132 and 134 support the shaft between the bearing 88 and the rectangular member 76. disposed about the annular rim 138 or boss of the mounting body 46 around the receptacle 72; be placed. Rings on the inner surfaces of the deflectors 132 and 134 (surfaces not shown in Figure 2) The shell is matched with the inner surface 68 of the mounting body 46, and the inner surface of the baffle plates 132, 134 is When placed as described, they are flush.

旋回機構５２は更に空洞部５４内に延び、ベアリング８８はそらせ板１３２．１ ３４に形成された環形ランド部１４０に当接する。カバープレート１４２はベア リング８８の対向する側部に当接し、例えば開口部１４６内に延び、段付き開口 部１４８内に延びたネジ１４４を介し取付胴部４６に固定される。カバープレー ト１４２の中央開口部１５０に円筒状端部８０が挿入され、円筒状端部８０及び 入力シャフト４８はカバープレート１４２の中央開口部１５０から突出される。The pivoting mechanism 52 further extends into the cavity 54 and the bearing 88 is connected to the baffle plate 132.1. It abuts on an annular land portion 140 formed at 34. The cover plate 142 is bare. abutting opposite sides of ring 88 and extending, for example, into opening 146 and forming a stepped opening; It is secured to the mounting body 46 via a screw 144 extending into a portion 148 . cover play The cylindrical end 80 is inserted into the central opening 150 of the cylindrical end 80 and Input shaft 48 projects from a central opening 150 in cover plate 142 .

ラックギア６４．６６はスロット５６．５８　（第８図参照）を経てラックギア ６４．６６に形成されたネジ穴１５２内に延びるネジ１５１により弁プレート４ ２に対し装着される。ベアリング１３６は円筒状端部７８と取付胴部４ｄとの間 の対向するポート１３０内に嵌め装着され、旋回機構５２はナツト８２を円筒状 端部７８に締め付けることにより最終的に固定される。The rack gears 64 and 66 are connected to the rack gears through the slots 56 and 58 (see Figure 8). The valve plate 4 is secured to the valve plate 4 by screws 151 extending into screw holes 152 formed at 64 and 66. It is attached to 2. The bearing 136 is located between the cylindrical end 78 and the mounting body 4d. The pivoting mechanism 52 rotates the nut 82 into a cylindrical shape. It is finally secured by tightening to the end 78.

螺形弁４０が組み立てられると、中央シャフト７０は弁プレート４２に対し中央 に配置され、使用時に弁プレート４２が閉鎖位置にあるとき流体動的トルクは実 質的に零となる。板バネ１１２には予荷重が与えられ、弁プレート４２の一方の 横断方向に延びる内面１５４（第９図参照）に当接し、一方シャフト支承体７２ の他端部のローラ１０４は逆の横断方向に延びる内面１５６と当接する。常時、 ローラ１０４は全体として対向する内面及び長手に延びる弁プレート４２の内面 （第９図及び第１０図において弁プレート４２とほぼ平行な面であるが参照番号 を付してない）の両方に当接される、７従って旋回機構５２及びローラ１０４は 協働して流体により弁プレート４２に加わる圧力を支承し、ラックギア６４．６ ６及びピニオンギア１１６．１１８による荷重の支承によって動力伝達と関連す る荷重の支承が制限される。When the helical valve 40 is assembled, the central shaft 70 is centered relative to the valve plate 42. , and in use, when the valve plate 42 is in the closed position, the fluid dynamic torque is Qualitatively becomes zero. The leaf spring 112 is preloaded so that one of the valve plates 42 abuts a transversely extending inner surface 154 (see FIG. 9) while shaft bearing 72 The other end roller 104 abuts an opposite transversely extending inner surface 156. Always, Rollers 104 generally have opposing inner surfaces and an inner surface of longitudinally extending valve plate 42. (In Figures 9 and 10, the surface is approximately parallel to the valve plate 42, but the reference number 7) Therefore, the turning mechanism 52 and the roller 104 are The rack gear 64.6 cooperates to support the pressure exerted by the fluid on the valve plate 42. 6 and pinion gears 116 and 118 to support power transmission. The load bearing capacity is limited.

入力シャフト４８が回転されると、回転トルクは中央シャフト７０に伝達され、 板バネ１１２が存在しない場合通常の応答は中央シャフト７０の回転である。中 央シャフト７０の回転はラックギア６４．６６及びピニオンギア１１６．１１８ の協働により弁プレート４２をシャフト支承体７２に対し変位することにより達 成される。変位が阻止されて中央シャフト７０の回転が防止されると、入力シャ フト４８の回転に対する応答はシャフト支承体７２の回転になるため、弁プレー ト４２が回転される。シャフト支承体７２の長方形部材７６は全体的に空洞部５ ４に合致される（変位が許容されローラ１０４が設けられる）と、弁プレート４ ２及びシャフト支承体は一方が回転されシャフト支承体の円筒状端部８０は流路 ４４から外側へ取付胴部４６を貫通して延び、弁プレート４２の回転位置がシャ フト支承体の回転位置に対する基準により取付胴部の外部から容易に確かめられ 得る。When input shaft 48 is rotated, rotational torque is transmitted to central shaft 70; In the absence of leaf spring 112, the normal response is rotation of central shaft 70. During ~ The rotation of the central shaft 70 is controlled by rack gears 64, 66 and pinion gears 116, 118. This is achieved by displacing the valve plate 42 relative to the shaft support 72 in cooperation with the will be accomplished. Once the displacement is blocked and rotation of the central shaft 70 is prevented, the input shaft Since the response to the rotation of the foot 48 is the rotation of the shaft support 72, the valve plate 42 is rotated. The rectangular member 76 of the shaft support 72 is generally connected to the hollow portion 5. 4 (displacement is allowed and roller 104 is provided), the valve plate 4 2 and the shaft bearing are rotated on one side and the cylindrical end 80 of the shaft bearing forms a flow path. 44 and extends outwardly through the mounting body 46 so that the rotational position of the valve plate 42 is The reference for the rotational position of the foot support allows for easy confirmation from the outside of the mounting body. obtain.

弁プレート４２が閉鎖位置にあるとき、弁プレート４２は取付胴部４６の内面６ ８に対し縁部方向に押されるので変位が板バネ１１２を使用する事なく阻止され る。一方このような構成では、阻止が取付胴部４６と弁プレート４２との間の摩 擦力により得られるので、相当に高い初期開放トルクが必要である。従って、好 ましい実施例においてはバイアス機構が包有され、弁プレート４２が閉鎖位置か ら移動されると回転移動が正常に遂行される。回転開放位置では、回転移動に対 する阻止力、即ち実質流体動的トルクからの阻止力が小さく阻止力がバネ力によ る変位より小さいとき、弁プレート４２は入力シャフト４８の回転に応動して回 転する。回転移動に対する阻止力が十分に高くなる（即ち、圧力３０の中心が第 １２図に示すように旋回線３２と整合されなくなり好ましい実施例の旋回線がシ ャフト支承体７２の長手軸になる）と、弁プレート４２は変位され実質トルクが 減少され阻止力が再び小さくなり実質流体動的トルクからの阻止力が小さくなり 、阻止力がバネ力による変位より小さくなる。When the valve plate 42 is in the closed position, the valve plate 42 contacts the inner surface 6 of the mounting body 46. 8, the displacement is prevented without using the leaf spring 112. Ru. On the other hand, in such a configuration, the blocking is due to the friction between the mounting body 46 and the valve plate 42. Since it is achieved by frictional forces, a fairly high initial opening torque is required. Therefore, good In a preferred embodiment, a biasing mechanism is included to ensure that valve plate 42 is in the closed position. When the rotational movement is performed, the rotational movement is normally performed. In the rotation open position, rotational movement is not supported. The stopping force from the actual fluid dynamic torque is small and the stopping force is due to the spring force. valve plate 42 rotates in response to rotation of input shaft 48. Turn around. The blocking force against rotational movement becomes sufficiently high (i.e. the center of pressure 30 12, the pivot line of the preferred embodiment is no longer aligned with the pivot line 32. (which becomes the longitudinal axis of the shaft support 72), the valve plate 42 is displaced and a substantial torque is applied. The blocking force is reduced again and the blocking force from the actual fluid dynamic torque becomes smaller. , the blocking force becomes smaller than the displacement due to the spring force.

閉鎖回転位置で密封を要求するような用途に用いる場合、弁プレート４２の円周 部に周知のリム密封部が設けられる。これにより過度の変位が制限され、このた め取付胴部４６の内面６８の形状を好適になして所定の移動を吸収する。また好 適に成形された内面４６及び面密封部は共に協働動作可能である。When used in applications requiring sealing in the closed rotational position, the circumference of the valve plate 42 The section is provided with a well-known rim seal. This limits excessive displacement; The inner surface 68 of the mounting body 46 is suitably shaped to absorb the predetermined movement. Good again The suitably shaped inner surface 46 and face seal are capable of cooperating together.

第１３図には流体の連通は回転角がほぼ零のとき弁プレート４２により密封閉鎖 される構成が示される。取付胴部４６には好適な止め部１５８が設けられ、この ため弁プレート４２の不都合な回転移動が防止される。且つ変位を吸収するため 、取付胴部４６の内面６８は弁プレート４２の円周縁部に形成される環形溝１６ ０の直ぐ下流で範囲１５９に亙り半径方向に延びる。環形溝１６０はシャフト支 承体７２から偏位されており、円周に沿い連続的に密封される。密封部１６２は 環形溝１６０内に着座され、内面６８に当接する。高圧比を必要とする用途でリ ム密封部を使用する螺形弁の問題点はずｒプレート４２の上流側の高圧流体が環 形溝１６０と密封部１６２との間にあることにある１、流体により半径方向外側 の力が密封部１６２に与えられて密封部１６２が内面６８に対しより強（接触さ れる。この効果は密封のためには望ましいが、同時に最初に弁を開放するに必要 なトルクを増加するので望ましくない。従って第１３図の構成では、弁プレート ４２により環形溝１６０から弁プレート４２の下流側への一方向の流体連通が与 えられ、密封部１６２に加わる外側への圧力が解放される。これは環形溝１６０ と流路１６６とを連通させる環状体１６４を形成することにより達成される。流 路１６６は環状体１６４から弁プレート４２の下流の対向面へ延び、逆止め弁１ ６８によりブロックされる。押し棒１７Ｇはシャフト支承体７２に固定され、逆 止め弁１６８と接触されるので、弁プレート４２の極めて僅かな変位により逆止 め弁が開放される。図示の閉鎖位置では、弁プレート４２の回転移動の密封部１ ６２による阻止力は板バネ１１２（第２図参照）による変位の阻止力より大きい 。従って、弁プレート４２が図示のように密封閉鎖されると、入力シャフト４８ （第２図参照）の回転により中央シャフト７０が回転され、弁プレート４２はシ ャフト支承体７２に対し極めて僅かに変位される。この極めて僅かな変位により 逆止め弁１６８が開放され、密封部１６２に加わる半径方向外側への圧力が除去 され、弁プレート４２の回転移動に対する阻止力が減少される。In FIG. 13, fluid communication is sealed and closed by the valve plate 42 when the rotation angle is approximately zero. The configuration to be used is shown. Mounting body 46 is provided with a suitable stop 158, which Therefore, an undesirable rotational movement of the valve plate 42 is prevented. And to absorb displacement , the inner surface 68 of the mounting body 46 has an annular groove 16 formed in the circumferential edge of the valve plate 42. 0 and extends radially over an area 159 immediately downstream of 0. The annular groove 160 supports the shaft. It is offset from the receiving body 72 and is continuously sealed along the circumference. The sealing part 162 is It is seated within annular groove 160 and abuts inner surface 68 . For applications requiring high pressure ratios. The problem with a spiral valve that uses a sealing part is that the high pressure fluid on the upstream side of the plate 42 is 1 between the shaped groove 160 and the sealing part 162; A force of It will be done. This effect is desirable for sealing, but is also necessary to initially open the valve. This is undesirable because it increases the torque. Therefore, in the configuration shown in Fig. 13, the valve plate 42 provides one-way fluid communication from the annular groove 160 to the downstream side of the valve plate 42. The outward pressure applied to the sealing portion 162 is released. This is the annular groove 160 This is achieved by forming an annular body 164 that communicates with the flow path 166. style A passage 166 extends from the annular body 164 to the downstream opposing surface of the valve plate 42 and is connected to the check valve 1 . Blocked by 68. The push rod 17G is fixed to the shaft support 72 and is Since it is in contact with the stop valve 168, a very slight displacement of the valve plate 42 causes a non-return check. The valve is opened. In the illustrated closed position, the seal 1 of the rotational movement of the valve plate 42 62 is larger than the displacement preventing force caused by the leaf spring 112 (see Fig. 2). . Thus, when the valve plate 42 is hermetically closed as shown, the input shaft 48 (see FIG. 2) rotates the central shaft 70, and the valve plate 42 It is displaced very slightly relative to the shaft bearing 72. Due to this extremely small displacement The check valve 168 is opened and the radially outward pressure on the seal 162 is removed. This reduces the blocking force against rotational movement of the valve plate 42.

バイアス（即ち、第２図の板バネ１１２の等個物として）するため並びに密封す るため逆止め弁１６８が使用されるが、これは現在まで十分に開発されていない １゜円形の弁プレート４２が図示されたが、本発明は矩形の弁プレート４２ある いは矩形のダクトを用いる場合にも同様に使用出来、ここに使用する用語［螺形 弁コはこのよううな構造を包有することは理解されよう。For biasing (i.e., as an individual piece like leaf spring 112 in FIG. 2) and for sealing. A check valve 168 is used for this purpose, but this has not been fully developed to date. Although a 1° circular valve plate 42 is illustrated, the present invention also includes a rectangular valve plate 42. It can also be used in the same way when using a rectangular duct, and the term used here [spiral It will be understood that Benco encompasses such a structure.

第１２Ａ図〜第１２Ｆ図を参照するに、本発明の方法によれば、弁プレート２Ｇ は最初第１の回転位置（第１２Ａ図参照）にあり流路４４に沿った流体の流動を 最大限に抑止しており、第１の位置から第２の回転位置（第１２Ｆ図参照）へ回 転移動されて流体を最大限通過させることは理解されよう。弁プレート２０は流 路４４に沿って流動する流体による実質トルクを受け、実質トルクは圧力３０の 中心が旋回線３２の下部に移動し、回転移動と共に増加する。この状態は第１２ Ｂ図に示される。弁プレー１２０が旋回シャフト２２に対し変位される、圧力３ ０の中心が旋回線３２とより正確に整合されると、実質トルクが減少される（第 １２Ｃ図参照）。変位により容易に第２の位置（第１２Ｆ図参照）への連続回転 移動は、圧力３０の加わる位置が再び旋回線３２に対し移動し実質トルクが増加 することにより実行される（第１２Ｄ図参照）。連続して変位すると圧力３０の 中心がより正確に旋回線３２と整合され第２の位ｆｌ（第１２Ｆ図参照）へ容易 に且つ更に回転移動される（第１２Ｅ図参照）。Referring to FIGS. 12A to 12F, according to the method of the present invention, the valve plate 2G is initially in a first rotational position (see FIG. 12A) and directs the flow of fluid along channel 44. The rotation from the first position to the second rotation position (see Figure 12F) is maximized. It will be appreciated that it is rotated to maximize fluid passage. The valve plate 20 Subject to a substantial torque due to fluid flowing along path 44, the substantial torque is at pressure 30. The center moves to the bottom of the turning line 32 and increases with rotational movement. This state is the 12th Shown in Figure B. Valve plate 120 is displaced relative to pivot shaft 22, pressure 3 0 center is more accurately aligned with the swirl line 32, the net torque is reduced (the (See Figure 12C). Easy continuous rotation to the second position (see Figure 12F) by displacement The movement is such that the position where the pressure 30 is applied moves again with respect to the turning line 32, and the actual torque increases. (See Figure 12D). When continuously displaced, the pressure of 30 The center is more accurately aligned with the turning line 32 and it is easier to move to the second position fl (see Figure 12F). and further rotated (see FIG. 12E).

弁プレート２０の回転移動は、弁プレートが所望の流量に相当する所望の回転位 置（例えば第１２Ｅ図の位置）に達するまで連続する。変位により回転移動が容 易にされ、また流体による弁プレートに加わる実質トルクは変位により最小限に されるので、所望の回転位置での作動器３６の負荷が最小限にされる。The rotational movement of the valve plate 20 causes the valve plate to reach a desired rotational position corresponding to the desired flow rate. This continues until a position (eg, the position of FIG. 12E) is reached. Rotational movement is possible due to displacement. The actual torque exerted on the valve plate by the fluid is minimized by the displacement. so that the load on the actuator 36 at the desired rotational position is minimized.

弁プレートの全体の移動は、回転位置と他の位置との間を実質的に連続的に行わ れるが、回転移動成分と変位成分との両方を特徴とする。従って、全体の移動の 理解を容易にするため、第１２Ａ図〜第１２Ｅ図は連続する変位成分及び回転移 動成分が誇張して別個に図示されている。The entire movement of the valve plate is substantially continuous between the rotational position and the other position. However, it is characterized by both a rotational movement component and a displacement component. Therefore, the total movement For ease of understanding, Figures 12A to 12E show continuous displacement components and rotational transitions. The dynamic components are exaggerated and shown separately.

第１２Ｇ図及び第１２１１図には本発明の方法が逆に実施される場合が示される 。更に詳述するに、弁プレート２０が実質的にトルク平衡される第１２Ｅ図のよ うな回転位置から始動し、弁プレート２０が第１の位置（第１２Ａ図参照）へ回 転移動されるので、圧力３０の中心と旋回線３２とが第１２Ｇ図に示すように大 きく不整合になる。弁プレート２０はまた第１２１１図に示すように変位され不 整合の程度が小さくなるため、第１の位置への更に回転移動が容易となる。FIGS. 12G and 1211 show the case where the method of the invention is carried out in reverse. . More specifically, as shown in FIG. 12E, the valve plate 20 is substantially torque balanced. Starting from this rotational position, the valve plate 20 rotates to the first position (see Figure 12A). Since the center of the pressure 30 and the turning line 32 are rotated, the center of the pressure 30 and the turning line 32 are greatly changed as shown in Fig. 12G. The sound becomes inconsistent. The valve plate 20 is also displaced as shown in FIG. The reduced degree of alignment facilitates further rotational movement to the first position.

本発明は図面の好ましい実施例に沿った詳細な説明に限定されないことは以上の 説明から理解されよう。本発明は添付の請求の範囲に含まれる広範な方法を包有 する。It should be understood that the present invention is not limited to the detailed description of the preferred embodiments shown in the drawings. It will be understood from the explanation. The invention encompasses a wide variety of methods falling within the scope of the appended claims. do.

Ｆｘｒ、、、、８ Ｆｘｒ５．１ＥＥ　Ｆｘｒ＝−ＩＥＦ Ｆｘｒ、、１３ 補正書の写しく翻訳文）提出書 （特許法第１８４条の８） 平成４年１月４日Fxr,,,,8 Fxr5.1EE Fxr=-IEF Fxr,,13 Copy and translation of written amendment) Submission form (Article 184-8 of the Patent Act) January 4, 1992

Claims (9)

【特許請求の範囲】[Claims] １．流体を移動させる流路（４４）の一部を区画する取付胴部（４６）と、流路 内に横断するように支承される弁プレート（４２）と、取付胴部内に枢支され弁 プレートを支承するシヤフト（７２）と、シヤフトに動作可能に接続されトルク をシヤフトに伝達する差動ギアと、差動ギアに対し動作可能に接続され入力トル クを差動ギアに与える入力シヤフトとを備え、弁プレートがシヤフトに対し旋回 移動可能及び変位可能である蝶形弁。1. A mounting body (46) that partitions a part of the flow path (44) for moving fluid, and a flow path. a valve plate (42) transversely supported within the mounting body; a shaft (72) supporting the plate; and a torque bearing member operably connected to the shaft. a differential gear that transmits an input torque to the shaft, and a differential gear that transmits an input torque to the shaft; and an input shaft that provides torque to the differential gear, and the valve plate pivots relative to the shaft. Butterfly valve that is movable and displaceable. ２．回転移動が不十分に阻止されたとき入力トルクに応動して弁プレートが回転 移動され、回転移動が十分に阻止されるときにはシヤフトに対し弁プレートが変 位されてなる特許請求の範囲第１項記載の蝶形弁。2. Valve plate rotates in response to input torque when rotational movement is insufficiently blocked. When the valve plate is moved and rotational movement is sufficiently prevented, the valve plate changes relative to the shaft. The butterfly valve according to claim 1, wherein the butterfly valve is ３．更にシヤフトに対し弁プレートの変位を阻止するバネを備えてなる特許請求 の範囲第２項記載の蝶形弁。3. The patent claim further comprises a spring that prevents displacement of the valve plate with respect to the shaft. A butterfly valve according to item 2 of the scope of the invention. ４．シヤフトが取付胴部に枢支される支承シヤフトであり、更に支承シヤフトに 枢支される中央シヤフトを備え、中央シヤフト及び支承シヤフトは差動ギアに連 結され、入力シヤフトが回転されると差動ギアが動作されてトルクが中央シヤフ トに伝達され中央シヤフトの回転が阻止されたとき支承シヤフトが回転されてな る特許請求の範囲第１項記載の蝶形弁。4. A support shaft in which the shaft is pivotally supported on the mounting body; It has a central shaft that is pivotally supported, and the central shaft and the support shaft are connected to a differential gear. When the input shaft is rotated, the differential gear is operated and the torque is transferred to the center shaft. When the rotation of the central shaft is prevented, the bearing shaft is not rotated. A butterfly valve according to claim 1. ５．弁プレートは弁プレートと実質的に同空間の方向に旋回装置に対し変位可能 であり、流体により弁プレートにかかる実質流体動的トルクが変更されてなる特 許請求の範囲第１項記載の蝶形弁。5. The valve plate can be displaced relative to the swivel device in substantially the same spatial direction as the valve plate. is a characteristic in which the actual fluid dynamic torque applied to the valve plate is changed by the fluid. A butterfly valve according to claim 1. ６．ダクト２４により区画される長手の流路４４内に旋回可能に配置される弁プ レート（２０）を備え、弁プレートは流路に沿っての流体を最大限に閉鎖する第 １の回転位置から流路に沿っての流体を最大限に通過させる第２の回転位置へと 旋回可能であり、旋回可能に配置される弁プレートは流路に沿っての流体による 実質トルクを受ける蝶形弁において、第１の位置から第２の位置へと弁プレート を回転移動して実質トルクを増加させる工程と、弁プレートを変位して実質トル クを減少し第２の位置へ弁プレートを更に容易に回転移動させる工程と、弁プレ ートを更に第２の位置へと回転移動して実質トルクを再び増加させる工程と、弁 プレートを変位し再び増加された実質トルクを減少させて第２の位置へ弁プレー トを更に容易に回転移動させる工程とを包有することを特徴とする実質トルクを 利用して蝶形弁を容易に制御する方法。6. A valve valve pivotably disposed within a longitudinal flow path 44 defined by a duct 24. rate (20), the valve plate is configured to provide maximum closure of fluid along the flow path. from one rotational position to a second rotational position that maximizes the passage of fluid along the flow path. The valve plate is pivotable and the pivotably arranged valve plate allows fluid to flow along the flow path. In a butterfly valve that is subjected to a substantial torque, the valve plate is moved from a first position to a second position. The process of rotationally moving the valve plate to increase the actual torque and displacing the valve plate to increase the actual torque the process of rotating the valve plate more easily to the second position with reduced friction; further rotationally moving the seat to a second position to again increase the effective torque; and Displace the plate and reduce the increased net torque again to move the valve to the second position. and the process of further easily rotating and moving the actual torque. How to easily control butterfly valves using ７．弁プレートは第１及び第２の位置の間の位置であり所望の流量に相当する所 望の回転位置へ回転移動され、所望の位置に変位移動されると実質トルクは最小 にされ所望回転位置での弁プレートの維持が容易にされてなる特許請求の範囲第 １項記載の方法。7. The valve plate is positioned between the first and second positions corresponding to the desired flow rate. When the rotation is moved to the desired rotational position and the displacement is moved to the desired position, the actual torque is minimum. Claim No. 1, wherein the valve plate is easily maintained in a desired rotational position. The method described in Section 1. ８．回転移動及び変位とが合成されて第１の位置から第２の位置へ弁プレートが 実質的に連続して移動されてなる特許請求の範囲第１項記載の方法。8. The combination of rotational movement and displacement moves the valve plate from the first position to the second position. 2. A method as claimed in claim 1, wherein the movement is substantially continuous. ９．更に第２の回転位置から第１の位置へ弁プレートを回転移動して実質トルク を増加させる工程と、弁プレートを変位移動させ再び実質トルクを減少して第１ の位置へのさらなる回転移動を容易にする工程とを包有してなる特許請求の範囲 第１項記載の方法。9. The valve plate is further rotated from the second rotational position to the first position to generate the actual torque. and the step of displacing the valve plate to decrease the actual torque again to obtain the first and facilitating further rotational movement to the position of The method described in paragraph 1.
JP2510566A 1989-06-30 1990-06-20 Butterfly method and device Pending JPH04506853A (en)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
US37489789A 1989-06-30 1989-06-30
US374,897 1989-06-30
US07/395,234 US4964422A (en) 1989-08-17 1989-08-17 Butterfly-type check valve
US395,234 1989-08-17
US07/422,354 US4967778A (en) 1989-10-16 1989-10-16 Butterfly valve apparatus and method
US422,354 1989-10-16
US426,921 1989-10-24
US07/426,921 US4967997A (en) 1989-10-24 1989-10-24 Butterfly valve with intra-shaft actuator means
US07/533,965 US5000213A (en) 1989-06-30 1990-06-06 Butterfly valve method and apparatus
US533,965 1990-06-06

Publications (1)

Publication Number Publication Date
JPH04506853A true JPH04506853A (en) 1992-11-26

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JP2510566A Pending JPH04506853A (en) 1989-06-30 1990-06-20 Butterfly method and device

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CN108374899B (en) * 2018-03-12 2020-02-14 天工阀门集团有限公司 High-flexibility strong-erosion-resistant butterfly valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3498583A (en) * 1966-10-07 1970-03-03 Martin Marietta Corp Compound movement butterfly valve
JPS4921235B1 (en) * 1970-12-22 1974-05-30

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2641485A (en) * 1949-07-26 1953-06-09 Guillaume M Dupuy Valved pipe fitting
EP0320491A3 (en) * 1985-05-30 1991-12-27 SCHMIDT, Fritz Closure element for pipelines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3498583A (en) * 1966-10-07 1970-03-03 Martin Marietta Corp Compound movement butterfly valve
JPS4921235B1 (en) * 1970-12-22 1974-05-30

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WO1991000455A1 (en) 1991-01-10
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EP0479917A1 (en) 1992-04-15

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