JPH0972430A - Main steam control valve - Google Patents
Main steam control valveInfo
- Publication number
- JPH0972430A JPH0972430A JP25016595A JP25016595A JPH0972430A JP H0972430 A JPH0972430 A JP H0972430A JP 25016595 A JP25016595 A JP 25016595A JP 25016595 A JP25016595 A JP 25016595A JP H0972430 A JPH0972430 A JP H0972430A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- steam
- main valve
- valve seat
- annular gap
- 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
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、蒸気加減弁（蒸気
流量調整弁）に関し、特に発電プラントに好適な蒸気加
減弁に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a steam control valve (steam flow control valve), and more particularly to a steam control valve suitable for a power plant.
【０００２】[0002]
【従来の技術】一般に、発電プラントにおける蒸気加減
弁は、図３，４に示すように、蒸気室チャンバ１内の蒸
気が主弁２と弁座３とによって形成される環状隙間４を
通過して、図示していない高圧タービンに流れ込むよう
になっている。ここで蒸気の通過流量はアクチュエータ
９の操作で弁棒５を上下に作動させることにより、環状
隙間４の面積を変えて制御される。従来の蒸気加減弁で
は蒸気流路の最小面積位置は環状隙間４の途中部分に位
置する構成となっている。符号６は蒸気流の方向を、符
号７は弁本体を、符号８は閉鎖バネをそれぞれ示してい
る。2. Description of the Related Art Generally, in a steam control valve in a power plant, as shown in FIGS. 3 and 4, steam in a steam chamber chamber 1 passes through an annular gap 4 formed by a main valve 2 and a valve seat 3. And flows into a high pressure turbine (not shown). Here, the flow rate of steam is controlled by operating the actuator 9 to move the valve rod 5 up and down to change the area of the annular gap 4. In the conventional steam control valve, the minimum area position of the steam flow path is located in the middle of the annular gap 4. Reference numeral 6 indicates the direction of the steam flow, reference numeral 7 indicates the valve body, and reference numeral 8 indicates the closing spring.
【０００３】すなわち図５(a)〜(d)における円形10が主
弁２と弁座３とで構成される環状隙間４（蒸気流路）の
最小断面積位置を示している。すなわち図５(a)に示し
た最大開度，つまり〔Ｌ（弁リフト量）／Ｄ（主弁シー
ト径）〕が0.34状態から図５(b)に示した中間開度
〔（Ｌ／Ｄ）が0.2〕，および図５(c)に示した小開度
〔（Ｌ／Ｄ）が0.1〕を経て、弁閉状態〔図５(d)〕に至
るまで、環状隙間４の最小断面位置が、円形10の位置、
すなわち蒸気流路の途中に位置するようになっている。That is, the circle 10 in FIGS. 5A to 5D shows the minimum cross-sectional area position of the annular gap 4 (steam flow path) formed by the main valve 2 and the valve seat 3. That is, the maximum opening shown in FIG. 5 (a), that is, [L (valve lift amount) / D (main valve seat diameter)] is 0.34, and the intermediate opening [(L / D ) Is 0.2] and the small opening [(L / D) is 0.1] shown in Fig. 5 (c) until the valve closed state [Fig. 5 (d)] is reached. But the position of the circle 10,
That is, it is located in the middle of the steam flow path.
【０００４】また、弁座３は円弧半径Ｒ2の円弧形状に
形成され、一方主弁２の弁頭部は半径Ｒ1の球面に形成
されて、主弁２と弁座３とは基本的に線接触となるよう
に形成されている。なお通常Ｒ1＝0.75Ｄ，Ｒ2＝0.25
Ｄ，Ｒ2＝0.3Ｒ1に設計されている。Further, the valve seat 3 is formed in an arc shape having an arc radius R 2 , while the valve head of the main valve 2 is formed in a spherical surface having a radius R 1 , so that the main valve 2 and the valve seat 3 are basically formed. It is formed so as to be in line contact with. Normally R 1 = 0.75D, R 2 = 0.25
It is designed so that D, R 2 = 0.3R 1 .
【０００５】[0005]
【発明が解決しようとする課題】ところで、上述の従来
の蒸気加減弁においては、環状隙間４（蒸気流路）の最
小断面積位置が環状隙間の途中部分にあるため、蒸気流
路が途中で絞られ、これにより蒸気流路の途中に流れの
スロートが存在し、特に流れが遷音速流れ状態となる時
に衝撃波の発生に伴う流れの乱れが大きくなり、弁の振
動を引起こすという問題点がある。また遷音速流れ条件
以外の場合にも、弁座の曲率半径が小さいことから流れ
の剥離が発生し易く、ひいてはフローパタンが不安定と
なりこれが弁の振動を引起こすという問題点もある。本
発明は、このような問題点を解決しようとするものであ
る。By the way, in the above-described conventional steam control valve, since the minimum cross-sectional area position of the annular gap 4 (steam flow path) is in the middle of the annular clearance, the steam flow path is in the middle. There is a problem in that there is a flow throat in the middle of the steam flow path due to the throttling, and when the flow becomes a transonic flow state, the turbulence of the flow increases due to the generation of shock waves, causing valve vibration. is there. Further, even under conditions other than the transonic flow condition, there is a problem that flow separation easily occurs due to the small radius of curvature of the valve seat, and the flow pattern becomes unstable, which causes vibration of the valve. The present invention is intended to solve such a problem.
【０００６】[0006]
【課題を解決するための手段】本発明は、蒸気加減弁に
おいて、主弁と弁座とで形成される環状隙間（蒸気流
路）の最小断面積となる位置を、同環状隙間の出口に位
置させて課題解決の手段としている。また、主弁の弁頭
部および弁座の曲率半径Ｒ1，Ｒ2を、それぞれ主弁シー
ト径Ｄに対して Ｒ1＝（0.6 〜0.85）Ｄ Ｒ2＝（0.45〜0.60）Ｄ と設定して課題解決の手段としている。なお弁座の曲率
半径およびこれに関連して決定される主弁の弁頭部の曲
率半径の最適値は、実験によって決定される。According to the present invention, in a steam control valve, a position where the annular cross section (steam flow path) formed by a main valve and a valve seat has a minimum cross-sectional area is set at an outlet of the annular clearance. It is positioned and used as a means to solve the problem. In addition, the curvature radii R 1 and R 2 of the valve head and valve seat of the main valve are set to R 1 = (0.6 to 0.85) D R 2 = (0.45 to 0.60) D with respect to the main valve seat diameter D, respectively. And is used as a means for solving the problem. The optimum value of the radius of curvature of the valve seat and the radius of curvature of the valve head of the main valve, which is determined in relation to this, is determined by experiment.
【０００７】そして本発明によれば、主弁と弁座とで形
成される環状隙間（蒸気流路）の最小断面積部を蒸気流
路の出口に位置させる、つまり環状隙間を先細り型とす
ることによって、（衝撃波は流れのスロートの下流で発
生するから）衝撃波の発生位置を環状隙間の出口より下
流側とし衝撃波の発生に伴う流れの乱れを主弁から遠ざ
けることができる。また主弁弁頭部および弁座の各曲率
半径を従来のものよりも大きくすることによって、蒸気
流れの転向を緩やかとし、これにより通路表面からの流
れの剥離を従来のものよりも起き難くすることができ、
これらの相乗作用により弁の振動を低減することができ
る。According to the present invention, the minimum cross-sectional area portion of the annular gap (steam passage) formed by the main valve and the valve seat is located at the outlet of the steam passage, that is, the annular gap is tapered. As a result, the shock wave is generated downstream from the outlet of the annular gap (since the shock wave is generated downstream of the throat of the flow), and the turbulence of the flow due to the generation of the shock wave can be kept away from the main valve. In addition, by making the radii of curvature of the main valve valve head and valve seat larger than in the conventional case, the diversion of the steam flow is made slower, which makes the separation of the flow from the passage surface more difficult than in the conventional case. It is possible,
The vibration of the valve can be reduced by these synergistic effects.
【０００８】[0008]
【発明の実施の形態】以下、図面により本発明の一実施
形態としての蒸気加減弁について説明すると、図１その
断面図、図２(a)〜(d)いずれもその流路形状図である。
なお、図１，図２(a)〜(d)中図３，図４，図５(a)〜(d)
と同じ符号はほぼ同一の部材を示している。BEST MODE FOR CARRYING OUT THE INVENTION A steam control valve as an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view thereof and FIGS. 2 (a) to 2 (d) are flow path shape diagrams thereof. .
In addition, in FIG. 1, FIG. 2 (a)-(d), FIG. 3, FIG. 4, FIG. 5 (a)-(d)
The same reference numerals as in FIG.
【０００９】図１に示すように、この実施形態の蒸気加
減弁も、蒸気室チャンバ１内の蒸気が主弁２と弁座３と
によって形成される環状隙間（蒸気流路）４を通過し
て、図示していない高圧タービンに流れ込むようになっ
ており、その蒸気量は、弁棒５を上下し環状隙間４を変
化させることで調節できるようになっている。さらに、
この実施形態の蒸気加減弁では、図２(a)〜(d)に示すご
とく、環状隙間４（蒸気流路）が、出口部で最小断面積
となるように、設計してある。つまり環状隙間４が先細
り形状となるように、主弁２の球面状弁頭部の曲率半径
Ｒ1および弁座３の円弧半径（主弁２との当接部付近の
曲率半径）Ｒ2が選定されている。As shown in FIG. 1, also in the steam control valve of this embodiment, the steam in the steam chamber chamber 1 passes through an annular gap (steam flow path) 4 formed by the main valve 2 and the valve seat 3. Then, it flows into a high-pressure turbine (not shown), and the amount of steam can be adjusted by moving the valve rod 5 up and down and changing the annular gap 4. further,
In the steam control valve of this embodiment, as shown in FIGS. 2 (a) to 2 (d), the annular gap 4 (steam flow path) is designed to have a minimum cross-sectional area at the outlet. That is, the radius of curvature R 1 of the spherical valve head of the main valve 2 and the arc radius of the valve seat 3 (the radius of curvature in the vicinity of the contact portion with the main valve 2) R 2 are set so that the annular gap 4 is tapered. It has been selected.
【００１０】すなわち最大開度状態を示す図２(a)にお
ける円形10Ａがこの状態における環状隙間４の最小断面
積位置を示している。また、中間開度状態および小開度
状態をそれぞれ示す図２(b)および図２(c)における円形
10Ｂ，10Ｃが、それぞれそれらの状態における環状隙間
４の最小断面積位置を示している。さらに、主弁２の弁
頭部の曲率半径Ｒ1および弁座３の主弁２との当接部付
近の曲率半径Ｒ2を実験に基づいて、Ｒ1＝（（0.6 〜0.
85）Ｄ，Ｒ2＝(0.45〜0.60）Ｄ（最適値としては、Ｒ1
＝0.81Ｄ，Ｒ2＝0.48Ｄである）としている。That is, the circle 10A in FIG. 2 (a) showing the maximum opening state shows the minimum sectional area position of the annular gap 4 in this state. 2 (b) and 2 (c) showing the intermediate opening state and the small opening state, respectively.
10B and 10C respectively indicate the minimum cross-sectional area positions of the annular gap 4 in those states. Further, based on experiments, the radius of curvature R 1 of the valve head of the main valve 2 and the radius of curvature R 2 of the valve seat 3 in the vicinity of the contact portion with the main valve 2 are R 1 = ((0.6 to 0.
85) D, R 2 = (0.45 to 0.60) D (The optimum value is R 1
= 0.81D and R 2 = 0.48D).
【００１１】上述の構成により、すなわち主弁２と弁座
３とで形成される環状隙間４の最小断面部を、環状隙間
４（蒸気流路）出口に位置させることにより、衝撃波の
発生位置を環状隙間の出口よりも下流側に位置させるこ
とができる。さらに、主弁２の弁頭部および弁座３の円
弧部の各曲率半径を従来のものより大きく設定したた
め、蒸気流れの転向が緩やかとなり、これにより流路表
面から流れ（蒸気流）が剥離するのを抑制でき、これら
が相乗的に作用して、弁の振動を低減することができ
る。With the above-described structure, that is, by locating the minimum cross-section of the annular gap 4 formed by the main valve 2 and the valve seat 3 at the outlet of the annular gap 4 (steam flow path), the shock wave generation position is determined. It can be located downstream of the outlet of the annular gap. Further, since the radius of curvature of each of the valve head portion of the main valve 2 and the arc portion of the valve seat 3 is set to be larger than that of the conventional one, the turning of the steam flow becomes gradual, and the flow (steam flow) is separated from the flow path surface. Can be suppressed, and these can act synergistically to reduce the vibration of the valve.
【００１２】図６は実験結果を示すグラフである。図６
において点ａ0，ｂ0，ｃ0，ｄ0がこの実施形態の蒸気加
減弁の代表的作動点における横方向の主弁変動力（ΔＦ
／Ａ・Ｐ0）（縦軸）を示しており、各作動点をプロッ
トした折線Ｘがこの実施形態の蒸気加減弁の特性を示し
ている。図６における各作動点ａ0〜ｄ0は、図７に点ａ
〜ｄで示した開弁状態（作動状態）にそれぞれ対応して
いる。また、図６における点ａ1〜ｄ1は従来の蒸気加減
弁における各代表的作動点（図７の点ａ〜ｄに対応す
る）での横方向の主弁変動力（縦軸）を示しており、各
作動点ａ1〜ｄ1等をプロットした折線Ｙが従来の蒸気加
減弁の特性を示している。FIG. 6 is a graph showing the experimental results. Figure 6
At points a 0 , b 0 , c 0 , and d 0 are lateral main valve fluctuation forces (ΔF) at typical operating points of the steam control valve of this embodiment.
/ A · P 0 ) (vertical axis), and the broken line X plotting each operating point shows the characteristic of the steam control valve of this embodiment. The operating points a 0 to d 0 in FIG. 6 are the points a in FIG.
Each corresponds to the valve open state (operating state) indicated by d. Further, points a 1 to d 1 in FIG. 6 represent lateral main valve fluctuation forces (vertical axis) at typical operating points (corresponding to points a to d in FIG. 7) in the conventional steam control valve. The polygonal line Y plotting the operating points a 1 to d 1 shows the characteristics of the conventional steam control valve.
【００１３】ここで、 ΔＦ ： 弁に加わる流体力（励振力）：実験にて計測 Ａ ： 弁のスロート面積（図２参照） Ｐ0： 弁入口圧力 であり、また図７において ＰE： 弁出口圧力 ＰE／Ｐ0： 弁前後圧力比 Ｌ ： 弁開度 Ｄ ： 主弁シート径 Ｌ／Ｄ ： 無次元弁開度 である。Here, ΔF: fluid force (excitation force) applied to the valve: measured in an experiment A: throat area of the valve (see FIG. 2) P 0 : valve inlet pressure, and in FIG. 7, P E : valve Outlet pressure P E / P 0 : Valve front-rear pressure ratio L: Valve opening D: Main valve seat diameter L / D: Dimensionless valve opening.
【００１４】この実験結果は、この実施形態の蒸気加減
弁が、主弁の低開度状態（ａ0）から高開度状態（d0）
にいたるすべての開度において、主弁の横方向変動力を
従来のものよりも低減できることを示している。The results of this experiment show that the steam control valve of this embodiment is operated from a low opening state (a 0 ) to a high opening state (d 0 ) of the main valve.
It is shown that the lateral fluctuation force of the main valve can be reduced as compared with the conventional one at all opening degrees.
【００１５】[0015]
【発明の効果】以上詳述したように、本発明の蒸気加減
弁によれば、主弁および弁座の形状を改善することによ
り、蒸気加減弁の主弁に作用する流体励振力を低減し、
これにより弁の振動を低減することができ、弁の信頼性
を向上できる利点が得られる。As described in detail above, according to the steam control valve of the present invention, by improving the shapes of the main valve and the valve seat, the fluid excitation force acting on the main valve of the steam control valve is reduced. ,
This has the advantage of reducing valve vibration and improving valve reliability.
【図１】本発明の一実施形態としての蒸気加減弁の断面
図。FIG. 1 is a sectional view of a steam control valve as an embodiment of the present invention.
【図２】(a) 同弁全開（最大開度）時における流路形状
の模式図。 (b) 同弁中開時における流路形状の模式図。 (c) 同弁小開時における流路形状の模式図。 (d) 同弁全閉時における流路形状の模式図。FIG. 2 (a) is a schematic view of a flow path shape when the valve is fully opened (maximum opening). (b) A schematic view of the flow path shape when the valve is open. (c) A schematic view of the flow path shape when the valve is opened slightly. (d) A schematic view of the flow path shape when the valve is fully closed.
【図３】従来の蒸気加減弁の断面図。FIG. 3 is a cross-sectional view of a conventional steam control valve.
【図４】同要部拡大断面図。FIG. 4 is an enlarged sectional view of the main part.
【図５】(a) 従来の蒸気加減弁における弁全開（最大開
度）時における流路形状の模式図。 (b) 同弁中開時における流路形状の模式図。 (c) 同弁小開時における流路形状の模式図。 (d) 同弁全閉時における流路形状の模式図。FIG. 5 (a) is a schematic diagram of the flow path shape when the valve is fully opened (maximum opening) in the conventional steam control valve. (b) A schematic view of the flow path shape when the valve is open. (c) A schematic view of the flow path shape when the valve is opened slightly. (d) A schematic view of the flow path shape when the valve is fully closed.
【図６】図１の蒸気加減弁の実験結果を示すグラフ。FIG. 6 is a graph showing an experimental result of the steam control valve of FIG.
【図７】図６における代表的作動点ａ0．ｂ0，ｃ0，ｄ0
の内容を示すグラフ。FIG. 7 shows a representative operating point a 0 . b 0 , c 0 , d 0
A graph showing the contents of.
１ 蒸気室チャンバ ２ 主弁 ３ 弁座 ４ （蒸気）流路としての環状隙間 ５ 弁棒 ６ 蒸気流の方向 Ｒ1 主弁の球状弁頭部の曲率半径 Ｒ2 弁座の曲率半径 Ｄ 主弁シート径1 steam chamber chamber 2 main valve 3 valve seat 4 annular gap as a (steam) flow path 5 valve rod 6 direction of steam flow R 1 radius of curvature of spherical valve head of main valve R 2 radius of curvature of valve seat D main valve Seat diameter
Claims (2)
て、主弁および弁座と、同主弁と弁座とにて形成される
流路とをそなえ、同流路の最小断面積位置を上記流路の
出口に位置させたことを特徴とする、蒸気加減弁。1. A steam control valve for adjusting the amount of supplied steam, comprising a main valve and a valve seat, and a flow path formed by the main valve and the valve seat, and determining a minimum cross-sectional area position of the flow path. A steam control valve, which is located at the outlet of the flow path.
上記弁座の曲率半径Ｒ2を、同弁座の主弁シート径Ｄに
対して、Ｒ1＝（0.6〜0.85）Ｄ，Ｒ2＝（0.45〜0.60）
Ｄとしたことを特徴とする、請求項１に記載の蒸気加減
弁。2. The curvature radius R 1 of the valve head of the main valve and the curvature radius R 2 of the valve seat are R 1 = (0.6 to 0.85) D with respect to the main valve seat diameter D of the valve seat. , R 2 = (0.45 to 0.60)
The steam control valve according to claim 1, wherein the steam control valve is D.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25016595A JPH0972430A (en) | 1995-09-04 | 1995-09-04 | Main steam control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25016595A JPH0972430A (en) | 1995-09-04 | 1995-09-04 | Main steam control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0972430A true JPH0972430A (en) | 1997-03-18 |
Family
ID=17203795
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25016595A Pending JPH0972430A (en) | 1995-09-04 | 1995-09-04 | Main steam control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0972430A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006063957A (en) * | 2004-08-30 | 2006-03-09 | Toshiba Corp | Steam valve device |
| US7926745B2 (en) | 2006-11-27 | 2011-04-19 | Mitsubishi Electric Corporation | Fuel injection valve |
| CN103939623A (en) * | 2014-05-05 | 2014-07-23 | 无锡卓尔阀业有限公司 | Ultrahigh pressure steam emptying valve |
| CN113700878A (en) * | 2021-09-01 | 2021-11-26 | 致微(厦门)仪器有限公司 | Air escape valve and application thereof |
| CN113700878B (en) * | 2021-09-01 | 2024-05-03 | 致微(厦门)仪器有限公司 | Air escape valve and application thereof |
-
1995
- 1995-09-04 JP JP25016595A patent/JPH0972430A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006063957A (en) * | 2004-08-30 | 2006-03-09 | Toshiba Corp | Steam valve device |
| US7931252B2 (en) | 2004-08-30 | 2011-04-26 | Kabushiki Kaisha Toshiba | Steam valve |
| US7926745B2 (en) | 2006-11-27 | 2011-04-19 | Mitsubishi Electric Corporation | Fuel injection valve |
| CN103939623A (en) * | 2014-05-05 | 2014-07-23 | 无锡卓尔阀业有限公司 | Ultrahigh pressure steam emptying valve |
| CN113700878A (en) * | 2021-09-01 | 2021-11-26 | 致微(厦门)仪器有限公司 | Air escape valve and application thereof |
| CN113700878B (en) * | 2021-09-01 | 2024-05-03 | 致微(厦门)仪器有限公司 | Air escape valve and application thereof |
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