JP2557216Y2 - Liquid helium liquefaction refrigeration system Ejector for refrigerant circulation - Google Patents
Liquid helium liquefaction refrigeration system Ejector for refrigerant circulationInfo
- Publication number
- JP2557216Y2 JP2557216Y2 JP14448189U JP14448189U JP2557216Y2 JP 2557216 Y2 JP2557216 Y2 JP 2557216Y2 JP 14448189 U JP14448189 U JP 14448189U JP 14448189 U JP14448189 U JP 14448189U JP 2557216 Y2 JP2557216 Y2 JP 2557216Y2
- Authority
- JP
- Japan
- Prior art keywords
- inner diameter
- nozzle
- mixer
- ejector
- refrigeration system
- 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 - Lifetime
Links
Landscapes
- Jet Pumps And Other Pumps (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） 本考案は、極低温域の冷媒を循環させるためのヘリウ
ム液化冷凍装置冷媒循環用エジェクターに関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION (Industrial application field) The present invention relates to a helium liquefaction refrigeration system refrigerant circulating ejector for circulating a refrigerant in a cryogenic region.
（従来の技術） 従来、ヘリウム液化冷凍装置において、特に極低温域
で冷媒を循環させるための流体機械として第１図に示す
エジェクターが公知である。(Prior Art) Conventionally, in a helium liquefaction refrigeration apparatus, an ejector shown in FIG. 1 is known as a fluid machine for circulating a refrigerant particularly in an extremely low temperature region.
このエジェクターは駆動流体である高圧の１次流体を
噴出させるノズル１と、被駆動流体である２次流体の入
口２と１次,2次流体を混合させる混合器部３と、この混
合流体をエジェクター外に出すディフェーザ４とを備え
ている。The ejector includes a nozzle 1 for ejecting a high-pressure primary fluid as a driving fluid, an inlet 2 for a secondary fluid as a driven fluid, and a mixer section 3 for mixing the primary and secondary fluids. And a dephaser 4 to be taken out of the ejector.
そして、高圧の１次流体をノズル１から噴出させて膨
張させることにより、この流体の有する熱エネルギの速
度エネルギへの変換が行われる。このため、ノズル１を
出た１次流体の圧力は低下し、この低圧部に２次流体が
導かれ、混合器部３にて高速の１次流体との混合が行わ
れる。さらに、２次流体は１次流体との間の運動量の変
換により加速され、１次流体と２次流体との高速の混合
流体はディフェーザ４にて減速され、速度エネルギの圧
力への変換が行われ、ここから送り出される。Then, a high-pressure primary fluid is ejected from the nozzle 1 and expanded, thereby converting thermal energy of the fluid into velocity energy. For this reason, the pressure of the primary fluid that has exited from the nozzle 1 decreases, and the secondary fluid is guided to the low-pressure portion, where the mixing with the high-speed primary fluid is performed in the mixer section 3. Further, the secondary fluid is accelerated by the conversion of momentum between the primary fluid and the primary fluid, and the high-speed mixed fluid of the primary fluid and the secondary fluid is decelerated by the dephaser 4 to convert velocity energy into pressure. We are sent from here.
このように、エジェクターは高速で１次流体をノズル
１より噴出し、その噴流によって２次流体を吸引し、混
合器部３内で両者を混合してからディフェーザ４で昇圧
して、外部へ出すもので、２次流体の圧縮或は輸送に用
いられ、機械式循環ポンプや排気ポンプに比べて稼動部
がないので、長期運転において信頼性が高いことが特長
である。As described above, the ejector ejects the primary fluid from the nozzle 1 at a high speed, sucks the secondary fluid by the jet, mixes the two in the mixer unit 3, raises the pressure by the dephaser 4, and outputs the mixture to the outside. It is used for compressing or transporting a secondary fluid and has no moving parts compared to a mechanical circulating pump or an exhaust pump, and thus has a feature of high reliability in long-term operation.
（考案が解決しようとする課題） 一般的に、上記エジェクターの性能は１次流体の流量
Ｇ1と２次流体の流量Ｇ2との比、即ち循環比Ｇ2/G1の大
小により判断され、この循環比Ｇ2/G1が大きい程良いと
されている。In (devised Problems to be Solved) generally, the performance of the ejector is determined by the primary fluid ratio of the flow rate G 1 and flow G 2 of the secondary fluid, i.e. the magnitude of the circulation ratio G 2 / G 1 , there is a good larger the circulation ratio G 2 / G 1.
例えば、CRYOGENICS,8月号（1978）第494頁に、最適
なエジェクター寸法として、混合器部の漏斗形状の入口
部角度θ1:60°〜90°，ディフェーザ出口部角度θ2:8
°〜10°，混合器部の上記入口部に続く一定内径部の長
さＬ1：（６〜10）×ｄ2（ｄ2：混合器部内径），ディ
フェーザ長さＬ2：（６〜７）（ｄ3−ｄ2）（ｄ3：ディ
フェーザ出口部内径）が示されている。また、ノズル１
の漏斗形状の先端部の外側端面と混合器部３の上記一定
内径部の入側端部との間の距離ｌが流れの閉塞や、循環
比Ｇ2/G1に関係し、エジェクターの効率を決定する要素
であるということは知られているが、具体的にこの距離
ｌをいくらにすれば良いかは未だ分かっていない。For example, in CRYOGENICS, August (1978), p. 494, as the optimum ejector dimensions, the inlet angle θ 1 : 60 ° to 90 ° of the funnel shape of the mixer section and the outlet angle θ 2 : 8 of the dephaser are used.
° to 10 °, the length L 1 of a constant inner diameter portion following the inlet portion of the mixer section: (6 to 10) × d 2 (d 2 : inner diameter of the mixer section), the length L 2 of the dephaser: (6 to 7) (d 3 −d 2 ) (d 3 : inside diameter of the outlet of the dephaser) is shown. Also, nozzle 1
Efficiency of the occlusion and the distance l is flow between the entry end of the constant diameter portion of the outer end face mixer section 3 of the tip of the funnel-shaped, associated to the circulation ratio G 2 / G 1, the ejector Is known to be a factor for determining the distance, but it is not yet known how much the distance l should be set.
本考案は、この距離ｌの最適値を求めることを課題と
してなされたもので、最大の循環比を得ることを可能と
した液体ヘリウム液化冷凍装置冷媒循環用エジェクター
を提供しようとするものである。The present invention has been made to provide an optimum value of the distance l, and an object of the present invention is to provide an ejector for circulating a liquid helium liquefaction refrigeration system which can obtain a maximum circulation ratio.
（課題を解決するための手段） 上記課題を解決するために、本考案は、漏斗形状の先
端部を有するノズルの上記先端部に至る一定内径部での
ノズル内径dNを1.0〜3.0mm,ノズル内径dNと漏斗形状の
入口部を有する混合器部の上記入口部の先に続く一定内
径部での混合器内径dMとの比の平方（dN/dM）2＝0.02〜
0.04,上記ノズルの上記先端部の外側端面とこれに対向
する上記混合器の上記一定内径部の入側端部との間の距
離ｌを２〜8mmとして形成した。(Means for Solving the Problems) In order to solve the above problems, the present invention provides a nozzle having a funnel-shaped tip with a nozzle inner diameter dN of 1.0 to 3.0 mm at a constant inner diameter reaching the tip. Square (dN / dM) 2 = 0.02 from the ratio of the inner diameter dN to the mixer inner diameter dM at a constant inner diameter portion following the inlet portion of the mixer portion having the funnel-shaped inlet portion.
0.04, and the distance l between the outer end face of the tip of the nozzle and the entry end of the constant inner diameter part of the mixer opposed thereto was set to 2 to 8 mm.
（実施例） 次に、本考案の一実施例を図面にしたがって説明す
る。Next, an embodiment of the present invention will be described with reference to the drawings.
本考案に係る液体ヘリウム液化冷凍装置冷媒循環用エ
ジェクターは、形態に関する限り、第１図に示すエジェ
クターと実質的に変わることろはなく、上記同様にノズ
ル1,2次流体の入口2,混合器部3,ディフェーザ４とを備
えている。The ejector for circulating the liquid helium liquefaction refrigeration system according to the present invention is substantially the same as the ejector shown in FIG. 1 as far as the form is concerned. A section 3 and a diffuser 4 are provided.
寸法に関しては、ノズル１の一定内径部のノズル内径
dNは1.0〜3.0mm,ノズル内径dNと混合器部３の一定内径
部の混合器内径dMとの比の平方（dN/dM）2は約0.025,ノ
ズル１の漏斗形状の先端部の外側端面と混合器部３の一
定内径部の入側端部との間の距離ｌは２〜8mmである。Regarding the dimensions, the nozzle inner diameter of the fixed inner diameter part of the nozzle 1
dN is 1.0 to 3.0 mm, the square of the ratio of the nozzle inner diameter dN to the mixer inner diameter dM of the constant inner diameter part of the mixer part 3 (dN / dM) 2 is about 0.025, and the outer end face of the funnel-shaped tip part of the nozzle 1 The distance 1 between the inner end of the mixer section 3 and the fixed inner diameter section is 2 to 8 mm.
ここで、ノズル内径は１次流体の流量を定める因子で
あり、この流量の実用的範囲よりノズル径の寸法が定ま
っている。また、（dN/dM）2はノズル１の断面積と混合
器部３の断面積の比を示しており、この値が小さい程、
循環比（Ｇ2/G1）は大きくなり、好ましいが、製造上の
制約から無制限には小さくできず、上記の値となってい
る。Here, the nozzle inner diameter is a factor that determines the flow rate of the primary fluid, and the size of the nozzle diameter is determined from the practical range of this flow rate. (DN / dM) 2 indicates the ratio of the sectional area of the nozzle 1 to the sectional area of the mixer section 3.
Although the circulation ratio (G 2 / G 1 ) is large and preferable, it cannot be reduced without limitation due to manufacturing restrictions, and has the above value.
さらに、距離ｌについては、第２図（横軸：ノズル／
混合器部間距離，縦軸：循環比Ｇ2/G1，混合器部内径d
M:9.00mm）に示すグラフに基き定めてあり、同図中各曲
線は第３図〜第８図に示す各種形状のノズル1a,・・・1
gに対応するデータを示している。Further, regarding the distance l, FIG. 2 (horizontal axis: nozzle /
Mixer section distance, vertical axis: circulation ratio G 2 / G 1 , mixer section inner diameter d
M: 9.00 mm), and each curve in the figure is a nozzle 1a,... 1 of various shapes shown in FIGS.
The data corresponding to g is shown.
図から明らかなように、どの曲線もｌが約５のときに
最大になっている。As is clear from the figure, all the curves are maximum when l is about 5.
現実には、必ずしも正確にｌ＝5mmに製造できるとは
限らず、通常は数mmの誤差が生じる。In reality, it is not always possible to accurately manufacture the device at l = 5 mm, and an error of several mm usually occurs.
そこで、本考案ではｌ＝２〜8mmとしてある。 Therefore, in the present invention, l = 2 to 8 mm.
（考案の効果） 以上の説明より明らかなように、本考案によれば、漏
斗形状の先端部を有するノズルの上記先端部に至る一定
内径部でのノズル内径dNを1.0〜3.0mm,ノズル内径dNと
漏斗形状の入口部を有する混合器部の上記入口部の先に
続く一定内径部での混合器内径dMとの比の平方（dN/d
M）2＝0.02〜0.04,上記ノズルの上記先端部の外側端面
とこれに対向する上記混合器の上記一定内径部の入側端
部との間の距離ｌを２〜8mmとして形成してある。(Effects of the Invention) As is apparent from the above description, according to the present invention, the nozzle inner diameter dN at a constant inner diameter part reaching the above-mentioned tip part of the nozzle having the funnel-shaped tip part is 1.0 to 3.0 mm, and the nozzle inner diameter is The square (dN / d) of the ratio of dN to the inner diameter dM of the mixer at a constant inner diameter following the inlet of the mixer having a funnel-shaped inlet.
M) 2 = 0.02 to 0.04, formed so that the distance 1 between the outer end face of the tip of the nozzle and the entry end of the constant inner diameter part of the mixer opposed thereto is 2 to 8 mm. .
このため、上述のデータによって示されるように、最
大の循環比、即ち循環効率が得られるという効果を奏す
る。For this reason, as shown by the above-mentioned data, there is an effect that the maximum circulation ratio, that is, the circulation efficiency is obtained.
第１図はエジェクターの断面図、第２図は距離ｌと循環
比との関係を示すグラフ、第３図〜第９図は各種形状の
ノズルを示す部分拡大断面図である。 1,1a,1b,1c,1d,1e,1f,1g……ノズル、dN……ノズル内径
dM……混合器部内径、ｌ……ノズルと混合器部間の距離1 is a sectional view of the ejector, FIG. 2 is a graph showing the relationship between the distance 1 and the circulation ratio, and FIGS. 3 to 9 are partially enlarged sectional views showing nozzles of various shapes. 1,1a, 1b, 1c, 1d, 1e, 1f, 1g ... Nozzle, dN ... Nozzle inner diameter
dM: Inside diameter of mixer part, l: Distance between nozzle and mixer part
Claims (1)
端部に至る一定内径部でのノズル内径dNを1.0〜3.0mm,
ノズル内径dNと漏斗形状の入口部を有する混合器部の上
記入口部の先に続く一定内径部での混合器内径dMとの比
の平方（dN/dM）2＝0.02〜0.04,上記ノズルの上記先端
部の外側端面とこれに対向する上記混合器の上記一定内
径部の入側端部との間の距離ｌを２〜8mmとしたことを
特徴とする液体ヘリウム液化冷凍装置冷媒循環用エジェ
クター。A nozzle having a funnel-shaped tip has a nozzle inner diameter dN of 1.0 to 3.0 mm at a constant inner diameter reaching the tip.
The square (dN / dM) 2 = 0.02-0.04 of the ratio of the inner diameter dN of the nozzle to the inner diameter dM of the mixer at a constant inner diameter following the inlet of the mixer having a funnel-shaped inlet (dN / dM) 2 = 0.02-0.04, An ejector for circulating a liquid helium liquefaction refrigeration system, wherein a distance 1 between an outer end surface of the tip portion and an inlet end portion of the constant inner diameter portion of the mixer opposed thereto is 2 to 8 mm. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14448189U JP2557216Y2 (en) | 1989-12-12 | 1989-12-12 | Liquid helium liquefaction refrigeration system Ejector for refrigerant circulation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14448189U JP2557216Y2 (en) | 1989-12-12 | 1989-12-12 | Liquid helium liquefaction refrigeration system Ejector for refrigerant circulation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0382900U JPH0382900U (en) | 1991-08-23 |
| JP2557216Y2 true JP2557216Y2 (en) | 1997-12-10 |
Family
ID=31691176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14448189U Expired - Lifetime JP2557216Y2 (en) | 1989-12-12 | 1989-12-12 | Liquid helium liquefaction refrigeration system Ejector for refrigerant circulation |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2557216Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007275816A (en) * | 2006-04-10 | 2007-10-25 | Nippon Tokushu Rozai Kk | Thermal spraying apparatus |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR200201414Y1 (en) * | 2000-04-17 | 2000-11-01 | 주식회사태백종합환경기술단 | Assembling injector for motive with liquid |
| US8142169B2 (en) * | 2009-01-06 | 2012-03-27 | General Electric Company | Variable geometry ejector |
| JP6083330B2 (en) * | 2012-11-16 | 2017-02-22 | 株式会社デンソー | Ejector |
-
1989
- 1989-12-12 JP JP14448189U patent/JP2557216Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007275816A (en) * | 2006-04-10 | 2007-10-25 | Nippon Tokushu Rozai Kk | Thermal spraying apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0382900U (en) | 1991-08-23 |
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