JP3170052B2 - Temperature compensated safety valve - Google Patents
Temperature compensated safety valveInfo
- Publication number
- JP3170052B2 JP3170052B2 JP19528492A JP19528492A JP3170052B2 JP 3170052 B2 JP3170052 B2 JP 3170052B2 JP 19528492 A JP19528492 A JP 19528492A JP 19528492 A JP19528492 A JP 19528492A JP 3170052 B2 JP3170052 B2 JP 3170052B2
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- spring
- valve body
- safety valve
- casing
- 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.)
- Expired - Fee Related
Links
Landscapes
- Temperature-Responsive Valves (AREA)
- Safety Valves (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明はロケットのタンク等に用
いられる温度の異る２点でのリリーフ圧力が同じである
温度補償型安全弁に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a temperature-compensated safety valve used in a rocket tank or the like, which has the same relief pressure at two different temperatures.
【０００２】[0002]
【従来の技術】従来の安全弁は、図５に示すように、シ
ール（弁本体）３の一方側に気体を封入したベロー４と
スプリング１を設けている。2. Description of the Related Art As shown in FIG. 5, a conventional safety valve is provided with a bellows 4 filled with gas and a spring 1 on one side of a seal (valve body) 3.
【０００３】以上において、温度変化によるスプリング
（ばね）１の反力変化をベロー４内部の気体の圧力変化
で打ち消し、シール３部の反力を一定に保つようになっ
ている。[0003] In the above, the change in the reaction force of the spring (spring) 1 due to the temperature change is canceled by the change in the pressure of the gas inside the bellows 4, and the reaction force of the seal 3 is kept constant.
【０００４】すなわち、例えば安全弁の温度が低下した
場合、スプリング１の弾性係数が大きくなりスプリング
１の反力（Ｆ1 ）は上るが、一方ベロー４に封入された
気体の圧力（Ｐb ）は温度低下により下がり、これらが
打ち消しあってリリーフ圧力（Ｐc ）は一定に保たれ
る。つまり式（１）が常に維持される。That is, for example, when the temperature of the safety valve decreases, the elastic coefficient of the spring 1 increases and the reaction force (F 1 ) of the spring 1 increases, but the pressure (P b ) of the gas sealed in the bellows 4 increases. The temperature is lowered by the temperature drop, and these are canceled each other, so that the relief pressure (P c ) is kept constant. That is, equation (1) is always maintained.
【０００５】 Ｆ1 ＋Ｐb Ｂ＝Ｐc Ａ …………………………（１） ただし、Ｆ1 ：スプリング１の反力 Ｐc ：リリーフ圧力（クラッキング圧力） Ｐb ：ベロー内封入気体圧力 Ａ ：シール有効面積 Ｂ ：ベロー有効面積F 1 + P b B = P c A (1) where F 1 : reaction force of spring 1 P c : relief pressure (cracking pressure) P b : enclosed in bellows Gas pressure A: Seal effective area B: Bellow effective area
【０００６】[0006]
【発明が解決しようとする課題】上記従来の安全弁をリ
リーフ圧力が外気圧力に対して設定されるゲージ圧タイ
プにする必要がある場合、従来のガス封入による温度補
償は採用できない（ガス封入タイプは、封入圧力が外気
圧力によらず一定である絶対圧タイプであるため）。When the above-mentioned conventional safety valve needs to be a gauge pressure type in which the relief pressure is set with respect to the outside air pressure, the conventional temperature compensation by gas filling cannot be adopted (the gas filling type is not available). , Because the pressure is constant regardless of the outside air pressure).
【０００７】しかし、飛しよう体用の安全弁等では、ゲ
ージ圧タイプでかつ温度補償型が要望されていた。However, for a safety valve or the like for a flying object, a gauge pressure type and a temperature compensation type have been demanded.
【０００８】[0008]
【課題を解決するための手段】本発明は上記課題を解決
するため次の手段を講ずる。The present invention employs the following means to solve the above-mentioned problems.
【０００９】すなわち、温度補償型安全弁として、入口
および出口を有するボックス型のケーシングと、上記ケ
ーシング内に上記入口に同軸に配置され、軸方向移動可
能に設けられた弁本体と、同弁本体および上記ケーシン
グ間に配置されそれぞれ所定の第１および第２の温度変
化率の弾性係数を有する第１および第２のばね手段とを
備え、上記第２の弾性係数の温度変化率と第１の弾性係
数の温度変化率の比を、所定温度における上記第１のば
ね手段の反力と第２のばね手段の反力の比に等しくし
た。 That is, as a temperature-compensated safety valve, a box-shaped casing having an inlet and an outlet, a valve body disposed coaxially with the inlet in the casing and provided so as to be movable in the axial direction, First and second spring means disposed between the casings and having elastic coefficients of predetermined first and second temperature change rates, respectively.
A temperature change rate of the second elastic coefficient and a first elastic relation.
The ratio of the temperature change rates of the numbers
Equal to the ratio of the reaction force of the spring means to the reaction force of the second spring means
Was.
【００１０】[0010]
【作用】上記手段により、上記第１および第２の温度変
化率の弾性係数を有する第１および第２のばね手段は、
第２と第１の弾性係数の温度変化率の比を、所定温度に
おける第１と第２のばね手段の反力の比に等しくし、例
えば第１および第２の温度で、同一の合成力で弁本体を
押すように組合されている。従って、通常は、例えば第
１の温度で、弁本体が第１および第２のばね手段により
押されケーシングの入口に当接し、閉止状態になってい
る。According to the above- mentioned means, the first and second temperature changes are performed.
The first and second spring means having the elastic modulus of the conversion rate
The ratio of the rate of temperature change of the second and first elastic coefficients to a predetermined temperature
The first and second spring means are combined to press the valve body with the same resultant force at the first and second temperatures , for example, at the first and second temperatures. Therefore, normally, for example, at a first temperature, the valve body is pushed by the first and second spring means and abuts on the inlet of the casing to be in a closed state.
【００１１】所定のリリーフ圧力（ゲージ圧力）になる
と弁本体が軸方向に移動し、弁開となる。また上記と異
なる第２の温度でも同様に作用し、上記と同一のリリー
フ圧力で弁開となる。When a predetermined relief pressure (gauge pressure) is reached, the valve body moves in the axial direction, and the valve is opened. Further, the same operation is performed at a second temperature different from the above, and the valve is opened at the same relief pressure as above.
【００１２】このようにして、第１および第２の温度範
囲を含む広い温度範囲で同一のリリーフ圧力（ゲージ圧
力）が得られる。In this manner, the same relief pressure (gauge pressure) can be obtained in a wide temperature range including the first and second temperature ranges.
【００１３】[0013]
【実施例】（１） 本発明の第１実施例を図１，図２に
より説明する。図１にて、ボックス型のケーシング４に
は同軸に入口ａと出口ｂが設けられる。入口ａの内面に
は同軸に筒型のバネホルダ５が取付けられている。また
バネホルダ５の接続端部には周囲に孔ｃがあけられてい
る。さらに孔ｃの出口ｂ側には閉塞板６が設けられてい
る。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (1) A first embodiment of the present invention will be described with reference to FIGS. In FIG. 1, a box-shaped casing 4 is provided with an inlet a and an outlet b coaxially. A cylindrical spring holder 5 is mounted coaxially on the inner surface of the inlet a. A hole c is formed around the connection end of the spring holder 5. Further, a closing plate 6 is provided on the outlet b side of the hole c.
【００１４】バネホルダ５に、同軸に孔部が摺動挿入さ
れる一端閉の筒形の弁本体（シール）３が設けられる。
弁本体３の開端部の近くにはつばｄが設けられている。
ケーシング４の出口ｂ側の内面とつばｄ間に第１のばね
（スプリング）１が同軸に設けられる。またバネホルダ
５の閉塞板６と弁本体３の閉端面間には第２のばね２が
同軸に設けられる。The spring holder 5 is provided with a cylindrical valve body (seal) 3 having a closed end into which a hole is slidably inserted coaxially.
A collar d is provided near the open end of the valve body 3.
A first spring (spring) 1 is provided coaxially between the inner surface of the casing 4 on the outlet b side and the collar d. The second spring 2 is provided coaxially between the closing plate 6 of the spring holder 5 and the closed end face of the valve body 3.
【００１５】以上の構成の作動原理図を図２に示す。ば
ね１とばね２とは、通常の金属製で第１および第２の弾
性係数の温度変化率がα1 ，α2 で、値は異るが、同符
号のものとする。また次の式（２），（３）を満すもの
とする。式（２）は第１の温度でのバランス式、式
（３）は第２の温度でのバランス式である。FIG. 2 shows the principle of operation of the above configuration. The spring 1 and the spring 2 are made of ordinary metal, and have the first and second elastic coefficients having temperature change rates of α 1 and α 2 and different values, but have the same sign. Further, it is assumed that the following expressions (2) and (3) are satisfied. Equation (2) is a balance equation at the first temperature, and Equation (3) is a balance equation at the second temperature.
【００１６】 Ｆ1 −Ｆ2 ＝Ｐc Ａ ……………………………（２） （１＋α1 ΔＴ）Ｆ1 −（１＋α2 ΔＴ）Ｆ2 ＝Ｐc Ａ ………（３） ここで、Ｆ1 ：第１の温度でのばね１の反力 Ｆ2 ：第１の温度でのばね２の反力 Ｐc ：リリーフ圧力 Ａ ：シール有効面積 ΔＴ：第２の温度─第１の温度 以上において、第１の温度で、入口ａ側のガス圧がＰc
を越えると弁本体６は出口側に、ばね１，２の合成反力
に逆らって移動する。したがってガスは孔ｃを通って出
口ｂへ逃げる。F 1 −F 2 = P c A (2) (1 + α 1 ΔT) F 1 − (1 + α 2 ΔT) F 2 = P c A (3) Here, F 1 : reaction force of the spring 1 at the first temperature F 2 : reaction force of the spring 2 at the first temperature P c : relief pressure A: effective seal area ΔT: second temperature─second In the above, at the first temperature, the gas pressure on the inlet a side becomes P c
, The valve body 6 moves to the outlet side against the combined reaction force of the springs 1 and 2. Thus, gas escapes through port c to outlet b.
【００１７】第２温度でもばね１，２の弾性係数が変化
し、式（３）が成立して、同様に作用する。Even at the second temperature, the elastic coefficients of the springs 1 and 2 change, and the equation (3) is established, and the same effect is obtained.
【００１８】このようにして、第１，第２温度を含む広
い温度範囲にわたって、リリーフ圧力（ゲージ用）Ｐc
の安全弁として作動する。 （２） 本発明の第２実施例を図３，図４により説明す
る。なお上記で説明した部分は省略する。In this manner, the relief pressure (for the gauge) P c over a wide temperature range including the first and second temperatures.
Operates as a safety valve. (2) A second embodiment of the present invention will be described with reference to FIGS. Note that the parts described above are omitted.
【００１９】図３にて、ケーシング４ａ内に、入口ａに
同軸に弁本体３ａが配置される。弁本体３ａは入口ａ側
の端部が円錐型で、出口ｂ側が段付で径の小さい円柱形
である。またケーシング４ａの出口ｂの内面と弁本体３
ａの段付部間に同軸に、２重に第１と第２のばね１ａ，
１ｂが設けられる。In FIG. 3, a valve body 3a is disposed coaxially with an inlet a in a casing 4a. The end of the valve body 3a on the inlet a side is conical, and the outlet b side is stepped and cylindrical with a small diameter. Also, the inner surface of the outlet b of the casing 4a and the valve body 3
a, the first and second springs 1a,
1b is provided.
【００２０】ばね１ａ，１ｂの弾性係数の温度変化をα
1 ，α2 とする。ばね１ａ，１ｂは一方を通常の金属材
料とし、他方をＩＮＶＡＲ材等として、α1 ，α2 を異
符号とする。さらに式（２），式（３）に相当するバラ
ンス式が成立するものとする。The temperature change of the elastic coefficients of the springs 1a and 1b is represented by α
1, and α 2. One of the springs 1a and 1b is made of a normal metal material, the other is made of an INVAR material or the like, and α 1 and α 2 have different signs. Further, it is assumed that a balance equation corresponding to the equations (2) and (3) is established.
【００２１】以上の構成の作動原理図を図４に示す。FIG. 4 shows the principle of operation of the above configuration.
【００２２】作用効果は上記とほぼ同様である。The functions and effects are almost the same as above.
【００２３】[0023]
【発明の効果】以上に説明したように、本発明によれ
ば、弾性係数の温度変化率の異る第１と第２のばね手段
により、温度変化が生じても弁本体のリリーフ圧力（ゲ
ージ圧力）が一定に維持され、信頼性の高い安全弁がえ
られる。As described above, according to the present invention, even when a temperature change occurs, the relief pressure (gauge) of the valve body can be increased by the first and second spring means having different temperature changes in the elastic modulus. Pressure) is maintained constant, and a highly reliable safety valve is obtained.
【図面の簡単な説明】[Brief description of the drawings]
【図１】本発明の第１実施例の構成断面図である。FIG. 1 is a configuration sectional view of a first embodiment of the present invention.
【図２】同実施例の作用説明図である。FIG. 2 is an operation explanatory view of the embodiment.
【図３】本発明の第２実施例の構成断面図である。FIG. 3 is a sectional view showing the configuration of a second embodiment of the present invention.
【図４】同実施例の作用説明図である。FIG. 4 is an operation explanatory view of the embodiment.
【図５】従来例の説明図である。FIG. 5 is an explanatory diagram of a conventional example.
１，１ａ 第１のばね ２，２ａ 第２のばね ３，３ａ 弁本体 ４，４ａ ケーシング 1, 1a First spring 2, 2a Second spring 3, 3a Valve body 4, 4a Casing
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16K 17/00 - 17/168 F16K 31/64 - 31/70 G05D 16/06 ──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. 7 , DB name) F16K 17/00-17/168 F16K 31/64-31/70 G05D 16/06
Claims (1)
ーシングと、上記ケーシング内に上記入口に同軸に配置
され、軸方向移動可能に設けられた弁本体と、同弁本体
および上記ケーシング間に配置されそれぞれ所定の第１
および第２の弾性係数の温度変化率を有する第１および
第２のばね手段とを備え、上記第２の弾性係数の温度変
化率と第１の弾性係数の温度変化率の比を、所定温度に
おける上記第１のばね手段の反力と第２のばね手段の反
力の比に等しくしてなることを特徴とする温度補償型安
全弁。1. A box-shaped casing having an inlet and an outlet, a valve body disposed coaxially with the inlet in the casing and provided so as to be movable in an axial direction, and disposed between the valve body and the casing. The respective first
And first and second spring means having a temperature change rate of the second elastic coefficient, and a temperature change of the second elastic coefficient.
The ratio between the conversion rate and the rate of temperature change of the first elastic modulus to a predetermined temperature.
The reaction force of the first spring means and the reaction force of the second spring means
A temperature-compensated safety valve characterized by being equal to the force ratio .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19528492A JP3170052B2 (en) | 1992-07-22 | 1992-07-22 | Temperature compensated safety valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19528492A JP3170052B2 (en) | 1992-07-22 | 1992-07-22 | Temperature compensated safety valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0642658A JPH0642658A (en) | 1994-02-18 |
| JP3170052B2 true JP3170052B2 (en) | 2001-05-28 |
Family
ID=16338600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19528492A Expired - Fee Related JP3170052B2 (en) | 1992-07-22 | 1992-07-22 | Temperature compensated safety valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3170052B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CZ296793B6 (en) * | 2005-06-03 | 2006-06-14 | Regulus Spol. S R. O. | Safety device arrangement of water heating system |
-
1992
- 1992-07-22 JP JP19528492A patent/JP3170052B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0642658A (en) | 1994-02-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20010213 |
|
| LAPS | Cancellation because of no payment of annual fees |