JP2002136855A - Fluid mixer - Google Patents
Fluid mixerInfo
- Publication number
- JP2002136855A JP2002136855A JP2000336307A JP2000336307A JP2002136855A JP 2002136855 A JP2002136855 A JP 2002136855A JP 2000336307 A JP2000336307 A JP 2000336307A JP 2000336307 A JP2000336307 A JP 2000336307A JP 2002136855 A JP2002136855 A JP 2002136855A
- Authority
- JP
- Japan
- Prior art keywords
- pipe
- main pipe
- fluid
- main
- branch
- 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】本発明は流体混合器に関し、
詳細には、例えば高温蒸気と低温蒸気などのように性質
の異なる２つの流体の流れを、短い距離で均一に混合す
ることが可能な流体混合器に関する。TECHNICAL FIELD The present invention relates to a fluid mixer.
More specifically, the present invention relates to a fluid mixer capable of uniformly mixing two fluid streams having different properties such as high-temperature steam and low-temperature steam over a short distance.
【０００２】[0002]
【従来の技術】この種の流体混合器とは、例えば高温の
蒸気流と低温の蒸気流とを短い配管距離で均一に混合す
るために用いられる。例えば、蒸気冷却ガスタービンを
使用したコンバインドサイクルガスタービンプラント等
では、ガスタービン高温部を冷却して高温になった蒸気
を他の低温蒸気と混合してスチームタービンに供給する
ために流体混合器が使用される。2. Description of the Related Art A fluid mixer of this type is used, for example, for uniformly mixing a high-temperature steam flow and a low-temperature steam flow with a short piping distance. For example, in a combined cycle gas turbine plant or the like using a steam-cooled gas turbine, a fluid mixer is used to cool the high-temperature portion of the gas turbine and mix the high-temperature steam with another low-temperature steam to supply the steam turbine. used.
【０００３】このように、スチームタービンに混合蒸気
を供給する場合には、高温蒸気と低温蒸気とが完全に均
一に混合していないと、タービンの静翼や動翼などの蒸
気に接する部分は蒸気温度の変動にさらされることにな
り、繰り返し熱応力により障害を生じる場合がある。ま
た、特にスチームタービン用蒸気の混合の場合には、高
温蒸気と低温蒸気とが流入するものであるため、混合器
各部分に大きな温度差が生じ、破損が生じる場合があ
る。このため、蒸気用流体混合器では、各部の強度や材
料もこれを考慮する必要があり、製作コストが高くなる
問題がある。また、蒸気の混合に長い流路長さを要する
と混合器が大型化してしまうため、装置コストが更に増
大する。As described above, when the mixed steam is supplied to the steam turbine, if the high-temperature steam and the low-temperature steam are not completely and uniformly mixed, the portions of the turbine that come into contact with the steam such as the stationary blades and the moving blades. Exposure to fluctuations in steam temperature may cause failures due to repeated thermal stress. Particularly, in the case of mixing steam for a steam turbine, since high-temperature steam and low-temperature steam flow, a large temperature difference occurs in each part of the mixer, which may cause breakage. For this reason, in the steam fluid mixer, it is necessary to consider the strength and material of each part, and there is a problem that the manufacturing cost is increased. Further, if a long flow path length is required for mixing steam, the size of the mixer is increased, so that the apparatus cost is further increased.
【０００４】この種の流体混合器の例としては、例えば
特開平１０−３７７１４号公報に記載されたものがあ
る。同公報の流体混合器は、コンバインドサイクルガス
タービンの高温冷却蒸気と低温蒸気とを混合してスチー
ムタービンに供給するためのものであり、高温蒸気が流
れる円管状の本管と、この本管の側部から低温蒸気を本
管内に導入する蒸気導入口とを備えた構成となってい
る。An example of this type of fluid mixer is described in, for example, Japanese Patent Application Laid-Open No. Hei 10-37714. The fluid mixer disclosed in this publication is for mixing high-temperature cooling steam and low-temperature steam of a combined cycle gas turbine and supplying the mixed steam to a steam turbine. And a steam inlet for introducing low-temperature steam into the main pipe from the side.
【０００５】図１０はこの種の流体混合器の一般的な構
成を示す断面図である。図１０において、１０１は流体
混合器全体、１０３は円管状の混合器本管、１０５は、
本管１０３の側部に接続された支管を示す。本管１０３
には高温蒸気配管に接続された入り口１１５から高温蒸
気が流入する。また、支管１０５は低温蒸気配管に接続
され、本管１０３に低温蒸気を流入させる。支管１０５
は本管内に突出して対向する本管内壁に当接する内管１
０７と、支管１０５外壁と本管１０３外壁とを滑らかに
接合するコーン（拡管）形状の外管１０９とから構成さ
れる二重管構造とされている。また、内管１０７の本管
１０３内に位置する部分の管壁外周には多数の蒸気噴出
孔１１１が設けられている。FIG. 10 is a sectional view showing a general structure of this type of fluid mixer. In FIG. 10, 101 is the entire fluid mixer, 103 is a circular mixer main pipe, and 105 is
The branch pipe connected to the side of the main pipe 103 is shown. Main 103
High-temperature steam flows from an inlet 115 connected to the high-temperature steam pipe. Further, the branch pipe 105 is connected to a low-temperature steam pipe, and allows the low-temperature steam to flow into the main pipe 103. Branch pipe 105
Is an inner pipe 1 that projects into the main pipe and abuts on the inner wall of the main pipe facing the main pipe.
07 and a cone (expanded) outer tube 109 that smoothly joins the outer wall of the branch tube 105 and the outer wall of the main tube 103. Further, a large number of steam ejection holes 111 are provided on the outer periphery of the tube wall of the portion of the inner tube 107 located inside the main tube 103.
【０００６】低温蒸気配管から支管１０５に流入した低
温蒸気は、支管１０５内を流れて内管１０７の外周の蒸
気噴出孔１１１から、本管１０３内を流れる高温蒸気中
に噴射されて、高温蒸気と混合する。高温蒸気と低温蒸
気とは本管１０３内を流れる間に均一に混合して出口１
１７に接続された混合蒸気配管に流入する。内管１０７
から噴出した低温蒸気と本管１０３内を流れる高温蒸気
とが本管１０３内で均一に混合することを保証するた
め、内管１０７の蒸気噴出孔１１１は内管１０７の全長
にわたって設けられており、混合を良好にするために周
方向の穴間隔は高温蒸気の入り口に面した側では出口に
面した側より小さくなっている。これにより、内管１０
７を流れる低温蒸気のうち、高温蒸気流の上流側に向け
て噴射される割合が増大し、噴射された蒸気が均一に高
温蒸気流に拡散するようになる。The low-temperature steam flowing into the branch pipe 105 from the low-temperature steam pipe flows through the branch pipe 105, and is injected into the high-temperature steam flowing through the main pipe 103 from the steam ejection hole 111 on the outer periphery of the inner pipe 107. Mix with. The high-temperature steam and the low-temperature steam are uniformly mixed while flowing through the main pipe 103, and the outlet 1
It flows into the mixed steam pipe connected to 17. Inner tube 107
In order to assure that the low-temperature steam blown out of the main pipe 103 and the high-temperature steam flowing in the main pipe 103 are uniformly mixed in the main pipe 103, the steam jet holes 111 of the inner pipe 107 are provided over the entire length of the inner pipe 107. In order to improve the mixing, the gap between the holes in the circumferential direction is smaller on the side facing the inlet of the high-temperature steam than on the side facing the outlet. Thereby, the inner pipe 10
The ratio of the low-temperature steam flowing through the high-temperature steam flow to the upstream side of the high-temperature steam flow is increased, and the injected steam is uniformly diffused into the high-temperature steam flow.
【０００７】蒸気用の流体混合器では、例えば高温蒸気
（６５０℃程度）と低温蒸気（４００℃程度）との温度
差が大きくなる。このため、支管１０５を直接本管１０
３外壁を貫通させると接合部には本管１０３と支管１０
５との温度差により大きな熱応力が生じる。このため、
図１０の流体混合器では本管１０３外壁と支管１０５と
を外管１０９で滑らかに接続し、外管１０９内に直管状
の内管１０７を配置した二重管構造を採用することによ
り、支管１０５と本管１０３外壁との接続部に大きな熱
応力が生じることを防止している。また、この接続部に
本管１０３を流れる高温蒸気が直接接触することを防止
するために、内管１０７が本管１０３壁面を貫通する部
分には、円板状のサーマルシールド１１３を設けてい
る。In a steam fluid mixer, for example, the temperature difference between high-temperature steam (about 650 ° C.) and low-temperature steam (about 400 ° C.) increases. Therefore, the branch pipe 105 is directly connected to the main pipe 10.
3 When the outer wall is penetrated, the main pipe 103 and the branch pipe 10
5 causes a large thermal stress. For this reason,
In the fluid mixer of FIG. 10, the outer wall of the main pipe 103 and the branch pipe 105 are smoothly connected by the outer pipe 109, and the straight pipe inner pipe 107 is disposed inside the outer pipe 109 to adopt a double pipe structure. A large thermal stress is prevented from being generated at a connection portion between the main tube 103 and the outer wall of the main pipe 103. In order to prevent the high-temperature steam flowing through the main pipe 103 from directly contacting this connection part, a disc-shaped thermal shield 113 is provided at a portion where the inner pipe 107 penetrates the wall surface of the main pipe 103. .
【０００８】また、内管１０７が対向する本管内壁に当
接する部分にも、本管１０３壁面に内管１０７内の低温
蒸気が本管壁面に直接接触することを防止するためにサ
ーマルシールド１１５が設けられている。The thermal shield 115 is also provided at the portion where the inner pipe 107 is in contact with the inner wall of the main pipe facing the main pipe 103 in order to prevent the low-temperature steam in the inner pipe 107 from directly contacting the wall of the main pipe. Is provided.
【０００９】[0009]
【発明が解決しようとする課題】ところが、上述した従
来の流体混合器は、支管１０５から供給される低温蒸気
を本管１０３の高温蒸気流中に分散させて均一な混合を
得るために低温蒸気を内管１０７管壁に設けた多数の小
径の噴射孔１１１から噴射する構成となっているため、
小径の噴射孔１１１を通過する際の低温蒸気の圧力損失
が大きくなってしまう。更に、内管１０７が本管１０３
内を横断する構造となっているため、本管側の第１の流
体流れに対する抵抗も大きくなり、圧損増大を防止する
ために本管の径を大きく設定する必要が生じ、混合器が
大型化して製造コストが上昇する問題がある。However, in the above-mentioned conventional fluid mixer, the low-temperature steam supplied from the branch pipe 105 is dispersed in the high-temperature steam flow of the main pipe 103 to obtain uniform mixing. Is injected from a large number of small-diameter injection holes 111 provided in the inner pipe 107 tube wall.
The pressure loss of the low-temperature steam when passing through the small-diameter injection hole 111 increases. Further, the inner pipe 107 is
Since the structure crosses the inside, the resistance to the first fluid flow on the main pipe side also increases, and it is necessary to set the diameter of the main pipe large in order to prevent an increase in pressure loss. Therefore, there is a problem that the manufacturing cost increases.
【００１０】また、上述した従来の流体混合器では、内
管１０７に小径噴射孔１１１を要する点や、サーマルシ
ールド１１３、１１５等を設ける必要があり、構造が複
雑となるため製造コストが更に増大する問題がある。本
発明は、上記問題に鑑み、構造が簡易かつ小型で製造コ
ストが低く、しかも流体の混合を均一に行うことが可能
な流体混合器を提供することを目的としている。Further, in the above-mentioned conventional fluid mixer, the small diameter injection hole 111 is required in the inner pipe 107, and the thermal shields 113 and 115 need to be provided. There is a problem to do. In view of the above problems, an object of the present invention is to provide a fluid mixer that has a simple structure, is small in size, has low manufacturing cost, and can uniformly mix fluids.
【００１１】[0011]
【課題を解決するための手段】請求項１に記載の発明に
よれば、性質の異なる二種類の流体の流れを均一に混合
する流体混合器であって、第１の流体が流れる円管状の
本管と、該本管に接続され、第２の流体を前記本管内を
流れる第１の流体に合流させる支管とを備え、前記支管
の前記本管への接続部は、前記支管の外壁と前記本管の
外壁とを滑らかに接合する拡管形状の外管と、前記支管
に連続して前記外管内を延びるとともに本管内に開口す
る端部を有する直管状の内管とを備え、前記内管と外管
との間には支管と外管との接合部から前記内管開口部に
向けて拡がる環状空隙が形成され、前記支管開口端は前
記本管の内壁面と同一高さもしくは本管内に突出してい
る流体混合器が提供される。According to the first aspect of the present invention, there is provided a fluid mixer for uniformly mixing flows of two kinds of fluids having different properties, wherein the fluid mixer has a tubular shape through which a first fluid flows. A main pipe, and a branch pipe connected to the main pipe and joining a second fluid to the first fluid flowing in the main pipe, wherein a connecting portion of the branch pipe to the main pipe includes an outer wall of the branch pipe; An outer pipe having an expanded shape for smoothly joining the outer wall of the main pipe to the outer pipe, and a straight pipe inner pipe having an end that opens into the main pipe while extending inside the outer pipe continuously to the branch pipe; An annular gap is formed between the pipe and the outer pipe, extending from the junction between the branch pipe and the outer pipe toward the inner pipe opening, and the branch pipe opening end is at the same height as the inner wall surface of the main pipe or the main pipe. A fluid mixer protruding into the tube is provided.
【００１２】すなわち、請求項１の発明では従来の流体
混合器と同様、円管状の本管側壁に支管が接続され、本
管内を流れる第１の流体中に第２の流体を混合する構成
されている。また、支管の本管との接続部は拡管状の外
管と直管状の内管とからなる二重管構造とされている点
も同様である。しかし、本発明では、内管は本管の対向
する壁面に当接するまで突出しておらず、内壁面と同一
高さまたは内壁面より本管内に突出した位置に開口端を
形成して終了している。また、外管は拡管形状とされて
いるため、内管の本管管壁貫通部では内管の周囲と本管
の管壁との間には環状の空隙が形成されている。内管を
流れて開口端から本管内に流入する第２の流体は上記環
状の空隙があるため、開口部から出た直後に内管下流側
の本管内壁面に付着して流れることが防止され、本管中
央部分に到達する。このため、本管内を流れる第１の流
体と開口から流出した第２の流体との混合が良好にな
り、開口から出た第２の流体が短い流路長さで本管内の
第１の流体と均一に混合するようになる。That is, in the first aspect of the present invention, similarly to the conventional fluid mixer, the branch pipe is connected to the side wall of the main pipe, and the second fluid is mixed with the first fluid flowing in the main pipe. ing. Also, the connection between the branch pipe and the main pipe has a double pipe structure including an expanded outer pipe and a straight pipe inner pipe. However, in the present invention, the inner pipe does not protrude until it comes into contact with the opposing wall face of the main pipe, and the opening ends at the same height as the inner wall face or at a position protruding into the main pipe from the inner wall face, and ends. I have. Further, since the outer pipe has an expanded pipe shape, an annular gap is formed between the periphery of the inner pipe and the pipe wall of the main pipe at the penetrating portion of the main pipe wall of the inner pipe. The second fluid flowing through the inner pipe and flowing into the main pipe from the opening end is prevented from adhering to the inner wall surface of the main pipe on the downstream side of the inner pipe immediately after exiting the opening due to the annular gap. , Reaches the central part of the main pipe. Therefore, mixing of the first fluid flowing through the main pipe with the second fluid flowing out of the opening is improved, and the second fluid flowing out of the main pipe flows through the first fluid in the main pipe with a short flow path length. Will be mixed uniformly.
【００１３】更に、第２の流体は従来のように小径の噴
射孔から噴出するのではなく、内管の開口端から本管内
に流入するため、第２の流体の圧力損失が低減される。
また、内管は従来のように本管内を横断して対向壁まで
到達していないため、従来に比べて本管内を流れる第１
の流体の圧力損失が低減される。更に、外管と内管との
間には環状の空隙が形成されており、この空隙は本管内
壁面より外側に位置することになるため、本管内を流れ
る第１の流体は空隙内でよどみを形成し、空隙内の流体
温度は第１の流体の温度と第２の流体の温度との中間の
温度となる。このため、第１の流体と第２の流体との温
度差が大きい場合でも、外管と本管との接続部は第１の
流体と第２の流体の温度との中間の温度に維持されるよ
うになり、流体温度が高い場合にも接続部にに大きな熱
応力が発生することが防止される。Further, the second fluid flows into the main pipe from the opening end of the inner pipe instead of being ejected from the small-diameter injection hole as in the related art, so that the pressure loss of the second fluid is reduced.
In addition, since the inner pipe does not reach the opposing wall across the main pipe unlike the related art, the first pipe flowing in the main pipe is different from the related art.
The pressure loss of the fluid is reduced. Further, an annular gap is formed between the outer pipe and the inner pipe, and this gap is located outside the inner wall surface of the main pipe, so that the first fluid flowing in the main pipe is stagnated in the gap. And the temperature of the fluid in the gap is intermediate between the temperature of the first fluid and the temperature of the second fluid. Therefore, even when the temperature difference between the first fluid and the second fluid is large, the connection between the outer pipe and the main pipe is maintained at an intermediate temperature between the temperatures of the first fluid and the second fluid. As a result, even when the fluid temperature is high, a large thermal stress is prevented from being generated in the connecting portion.
【００１４】請求項２に記載の発明によれば、前記支管
は、支管中心軸線が前記本管の中心軸線と本管内壁面と
の間の、本管中心軸線から外れた位置を通過するように
配置されている、請求項１に記載の流体混合器が提供さ
れる。すなわち、請求項２の発明では、支管は本管中心
軸線から外れた偏心位置に接続されている。このため、
内管から流入する第２の流体は本管断面で見て本管の円
弧上内壁面にそって流れる二次流れを形成する。このた
め、さらに第２の流体と第１の流体との混合が促進され
る。According to the second aspect of the present invention, the branch pipe is arranged such that the branch pipe central axis passes through a position between the central axis of the main pipe and the inner wall surface of the main pipe and deviated from the main pipe central axis. A fluid mixer according to claim 1, wherein the fluid mixer is arranged. That is, in the second aspect of the invention, the branch pipe is connected to an eccentric position deviated from the main pipe center axis. For this reason,
The second fluid flowing from the inner pipe forms a secondary flow that flows along the inner wall surface on the arc of the main pipe when viewed in cross section of the main pipe. Therefore, the mixing of the second fluid and the first fluid is further promoted.
【００１５】請求項３に記載の発明によれば、前記支管
の内管は、前記開口端近傍に、内管から本管に流入する
第２の流体に内管中心軸線まわりの旋回方向の速度成分
を付与する旋回流生成手段を備えた、請求項１に記載の
流体混合器が提供される。すなわち、請求項３の発明で
は、開口端から本管内に流入する第２の流体に旋回方向
の速度成分が付与される。このため、第２の流体は本管
内の第１の流体とさらに均一に混合するようになる。内
管に設ける旋回流生成手段としては、たとえばねじりを
有する固定羽根などが使用可能である。According to the third aspect of the present invention, the inner pipe of the branch pipe has a second fluid flowing from the inner pipe into the main pipe near the opening end in the direction of rotation about the center axis of the inner pipe. A fluid mixer according to claim 1, comprising a swirl flow generating means for imparting components. That is, in the third aspect of the invention, the velocity component in the turning direction is given to the second fluid flowing into the main pipe from the opening end. Therefore, the second fluid mixes more uniformly with the first fluid in the main pipe. As the swirling flow generating means provided in the inner pipe, for example, a fixed blade having a twist can be used.
【００１６】請求項４に記載の発明によれば、前記支管
の前記外管と本管との接合部の下流側の本管内壁面に
は、本管内に向けて突出し、支管から流入する第２の流
体が支管下流側の本管内壁面に沿って流れることを阻止
する邪魔板が配置された、請求項１に記載の流体混合器
が提供される。すなわち、請求項４の発明では、支管接
合部下流側の本管内壁面に邪魔板が設けられているた
め、支管から本管に流入する第２の流体が支管下流側の
本管内壁に沿って下流側に流れる、壁面付着流が形成さ
れることが防止される。これにより、流入した第２の流
体と本管内を流れる第１の流体との接触面積が増加する
ため、流体の混合が促進される。According to the fourth aspect of the present invention, the second inner wall of the main pipe protrudes toward the inside of the main pipe on the downstream side of the junction between the outer pipe and the main pipe and flows into the main pipe. The fluid mixer according to claim 1, wherein a baffle plate is arranged to prevent the fluid from flowing along the main pipe inner wall surface on the downstream side of the branch pipe. That is, in the invention of claim 4, since the baffle plate is provided on the inner wall surface of the main pipe on the downstream side of the branch pipe joint, the second fluid flowing from the branch pipe into the main pipe flows along the inner wall of the main pipe on the downstream side of the branch pipe. The formation of a wall-adhered flow that flows downstream is prevented. This increases the contact area between the inflowing second fluid and the first fluid flowing in the main pipe, thereby promoting the mixing of the fluids.
【００１７】請求項５に記載の発明によれば、前記支管
の内管は、前記開口近傍に、内管から本管に流入する第
２の流体を前記開口の本管横断方向両側の本管内壁面に
沿って、第１の流体の流れに対して垂直方向に流入させ
る偏向板を備えた、請求項１に記載の流体混合器が提供
される。すなわち、請求項５の発明では、開口近傍に偏
向板が設けられているため、支管から本管に流入した第
２の流体は、本管の円弧状の内壁面に沿って第１の流体
流れ方向に対して垂直な方向に流れる二次流れを形成す
る。このため、流入した第２の流体と第１の流体との混
合が促進される。According to the fifth aspect of the present invention, the inner pipe of the branch pipe, near the opening, allows the second fluid flowing from the inner pipe to the main pipe into the main pipe on both sides of the opening in the main pipe transverse direction. The fluid mixer according to claim 1, further comprising: a deflection plate that flows along a wall surface in a direction perpendicular to a flow of the first fluid. That is, in the fifth aspect of the present invention, since the deflection plate is provided near the opening, the second fluid flowing into the main pipe from the branch pipe flows along the arc-shaped inner wall surface of the main pipe. Form a secondary flow that flows in a direction perpendicular to the direction. For this reason, the mixing of the inflowing second fluid and the first fluid is promoted.
【００１８】請求項６に記載の発明によれば、前記第１
と第２の流体は、温度の異なる水蒸気である、請求項１
から請求項５のいずれか１項に記載の流体混合器が提供
される。すなわち、請求項５の発明では、第１と第２の
流体として、たとえば高温蒸気と低温蒸気のように温度
差のある蒸気が使用され、温度分布のない均一な温度の
混合蒸気が形成される。According to the sixth aspect of the present invention, the first
The first fluid and the second fluid are steam having different temperatures.
A fluid mixer according to any one of claims 5 to 5 is provided. That is, in the invention of claim 5, steam having a temperature difference such as high-temperature steam and low-temperature steam is used as the first and second fluids, and a mixed steam having a uniform temperature without a temperature distribution is formed. .
【００１９】[0019]
【発明の実施の形態】以下、添付図面を用いて本発明の
実施形態について説明する。図１は、本発明の流体混合
器の第１の実施形態の概略構成を示す断面図である。図
１において、１は流体混合器全体、３は第１の流体が流
れる本管、５は第２の流体が流れる支管を示す。本実施
形態では、第１の流体としては高温蒸気（例えば６５０
℃程度）が使用されており、本管３の上流側端部１５は
高温蒸気供給配管（図示せず）に、下流側端部１７は混
合蒸気出口配管（図示せず）に、それぞれ接続されてい
る。また、本実施形態では、第２の流体としては低温蒸
気（例えば４００℃程度）が使用されており、支管５の
入り口側端部１３は低温蒸気配管（図示せず）に接続さ
れている。Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a sectional view showing a schematic configuration of a first embodiment of the fluid mixer of the present invention. In FIG. 1, reference numeral 1 denotes an entire fluid mixer, 3 denotes a main pipe through which a first fluid flows, and 5 denotes a branch pipe through which a second fluid flows. In this embodiment, high temperature steam (for example, 650) is used as the first fluid.
° C), the upstream end 15 of the main pipe 3 is connected to a high-temperature steam supply pipe (not shown), and the downstream end 17 is connected to a mixed steam outlet pipe (not shown). ing. In the present embodiment, low-temperature steam (for example, about 400 ° C.) is used as the second fluid, and the inlet-side end 13 of the branch pipe 5 is connected to a low-temperature steam pipe (not shown).
【００２０】本実施形態では、支管５の管壁５ａと本管
３の管壁３ａとは外管９により接続されている。外管９
は、支管５との接続部９ａから本管３との接続部９ｂに
向けて径が拡がる拡管（コーン）形状とされ、支管５、
本管３との接続部９ａ、９ｂは円弧状に形成され、支管
５、本管３と滑らかに接続されている。支管５の外管９
ａ内に位置する部分は、外管接続部９ａから直線状に外
管９内を延びて本管内に突出する内管７を形成してい
る。支管入り口１３から流入した低温蒸気は、直線状に
内管７内を流れ、内管の開口端１１から本管３内に流入
して本管３内を流れる高温蒸気と合流、混合する。In the present embodiment, the tube wall 5a of the branch pipe 5 and the tube wall 3a of the main tube 3 are connected by an outer tube 9. Outer tube 9
Has an expanded tube (cone) shape whose diameter increases from a connecting portion 9a to the branch pipe 5 to a connecting portion 9b to the main pipe 3.
The connecting portions 9a and 9b with the main pipe 3 are formed in an arc shape, and are smoothly connected to the branch pipe 5 and the main pipe 3. Outer pipe 9 of branch pipe 5
The portion located inside the inner pipe 7 forms an inner pipe 7 extending linearly inside the outer pipe 9 from the outer pipe connecting portion 9a and protruding into the main pipe. The low-temperature steam flowing from the branch pipe inlet 13 linearly flows through the inner pipe 7, flows into the main pipe 3 from the open end 11 of the inner pipe, and joins and mixes with the high-temperature steam flowing through the main pipe 3.
【００２１】内管７の、本管３内壁面からの突出長さＬ
（図１）は、０≦Ｌ≦Ｄ／２（Ｄは本管３の内径）の範
囲とされ、詳細には後述するように支管７内の第２の流
体の流速ｖに対する本管３内の第１の流体の流速Ｖの比
Ｒ（Ｒ＝ｖ／Ｖ）に基いて決定される。図２は、本実施
形態の流体混合器１の混合性能を表す図である。図２の
横軸は、本管３に沿った支管５の中心軸線からの距離Ｆ
Ｌ、縦軸は各距離における本管３の断面上各点における
混合流体の温度分布の最高値Ｔmaxを示している。Projection length L of the inner pipe 7 from the inner wall surface of the main pipe 3
(FIG. 1) is in the range of 0 ≦ L ≦ D / 2 (D is the inner diameter of the main pipe 3), and as will be described in detail later, the inside of the main pipe 3 with respect to the flow velocity v of the second fluid in the branch pipe 7. Is determined based on the ratio R (R = v / V) of the flow velocity V of the first fluid. FIG. 2 is a diagram illustrating the mixing performance of the fluid mixer 1 of the present embodiment. The horizontal axis in FIG. 2 is the distance F from the central axis of the branch pipe 5 along the main pipe 3.
L and the vertical axis indicate the maximum value Tmax of the temperature distribution of the mixed fluid at each point on the cross section of the main pipe 3 at each distance.
【００２２】図２に示すように、温度分布最高値Ｔmax
はＦＬ≦０（混合前）では第１の流体温度（６５０℃）
となり、ＦＬ＞０では、徐々に低下し完全混合後の温度
Ｔmi xに近づく。温度分布最高値Ｔmaxは各断面における
２つの流体の混合の均一さの程度を表しており、Ｔmax
とＴmixとの差が小さいほど、その断面での流体の混合
が均一になっている。As shown in FIG. 2, the temperature distribution maximum value Tmax
Is the first fluid temperature (650 ° C.) when FL ≦ 0 (before mixing)
When FL> 0, the temperature gradually decreases and the temperature after complete mixing
Tmi xApproach. Maximum temperature distribution TmaxIs in each section
T represents the degree of uniformity of mixing of the two fluids, Tmax
And TmixThe smaller the difference is, the more the fluid mixes at that section
Is uniform.
【００２３】図２において、実線は本発明の流体混合器
１を使用した場合、点線は図１０の従来型の流体混合器
を使用した場合を示しており、本実施形態、従来型とも
第１と第２の流体の温度、流量を同一条件として測定し
たものである。従来型の流体混合器では、内管１０７
（図１０）に設ける噴出孔１１１の数が多いほど第１と
第２の流体が完全に混合するまでの距離（完全混合距
離）ＦＬ0が短くなる。ところが、噴出孔１１１の数を
増大させると流体混合器の製作コストが増大するため、
通常、内管の噴出孔１１１の数は製作コストを考慮して
所定の範囲の数に設定されるため、従来の流体混合器を
用いた場合には完全混合距離ＦＬ0は図２に斜線で示し
た領域になる。In FIG. 2, the solid line shows the case where the fluid mixer 1 of the present invention is used, and the dotted line shows the case where the conventional fluid mixer of FIG. 10 is used. And the temperature and flow rate of the second fluid were measured under the same conditions. In a conventional fluid mixer, the inner tube 107
Distance (complete mixing distance) FL 0 of a large number as the first and to the second fluid are mixed thoroughly ejection holes 111 provided in (Fig. 10) is shortened. However, increasing the number of the ejection holes 111 increases the manufacturing cost of the fluid mixer,
Usually, the number of ejection holes 111 of the inner tube in consideration of the manufacturing cost is set to the number of the predetermined range, in the case of using a conventional fluid mixer complete mixing distance FL 0 is by hatching in FIG. 2 This is the area shown.
【００２４】一方、図１に示した本実施形態の流体混合
器１を用いた場合には、図２に実線で示すように、従来
型の流体混合器とほぼ同等の混合性能が得られる。本実
施形態の流体混合器が高い混合性能を示すのは以下の理
由によると考えられる。すなわち、図１に示すように本
実施形態では外管９を用いて、支管５と本管３との管壁
を接続し、それぞれの接続部９ａ、９ｂを円弧（アー
ル）で接続している。接続部９ａ、９ｂをアールを用い
て滑らかに接続するようにしたのは、温度の異なる高温
蒸気の混合に流体混合器を使用するような場合に、温度
差による熱応力が発生し、接続部９ａ、９ｂに応力集中
が生じることを防止するためである。On the other hand, when the fluid mixer 1 of the present embodiment shown in FIG. 1 is used, as shown by the solid line in FIG. 2, the mixing performance almost equivalent to that of the conventional fluid mixer is obtained. It is considered that the fluid mixer of the present embodiment exhibits high mixing performance for the following reasons. That is, as shown in FIG. 1, in the present embodiment, the outer pipe 9 is used to connect the pipe walls of the branch pipe 5 and the main pipe 3, and the respective connecting portions 9a and 9b are connected by an arc. . The reason why the connecting portions 9a and 9b are smoothly connected by using a radius is that when a fluid mixer is used for mixing high-temperature steams having different temperatures, thermal stress is generated due to a temperature difference, and the connecting portions are connected. This is to prevent stress concentration from occurring at 9a and 9b.
【００２５】この場合、流体混合器の構成を簡易にする
ためには、図１のように内管９を設けずに、通常のＴ継
ぎ手類似の構成（例えば、図３の構成）とすることも考
えられる。しかし、高温の流体に使用する場合を考慮す
ると、この場合にも応力集中を防止するため、図３に示
すように支管３０５と本管３０３との接続部３０３ｂに
はアールを設ける必要がある。ところが、このように接
続部３０３ｂにアールを設けた構成とすると、図３に斜
線で示すように支管３０５から本管に流入した第２の流
体は本管３０３の内壁に沿った付着流れを形成してしま
い、完全混合距離が極めて長くなることが判明してい
る。In this case, in order to simplify the structure of the fluid mixer, a structure similar to a normal T-joint (for example, the structure of FIG. 3) is used without providing the inner pipe 9 as shown in FIG. Is also conceivable. However, considering the case of using a high-temperature fluid, it is necessary to provide a radius at the connecting portion 303b between the branch pipe 305 and the main pipe 303 as shown in FIG. However, if the connecting portion 303b is provided with a radius as described above, the second fluid flowing into the main pipe from the branch pipe 305 forms an adherent flow along the inner wall of the main pipe 303 as shown by hatching in FIG. It has been found that the complete mixing distance becomes extremely long.
【００２６】本実施形態の流体混合器１では、これを防
止するために外管９内に内管５を設け、内管の開口端を
本管内壁面と面一もしくは本管内に突出した構成（０≦
Ｌ≦Ｄ／２）としている。拡管状の外管９内に直管状の
内管５を設けたことにより、外管９内壁と内管５の外壁
との間には接合部９ａから９ｂに向けて拡がる間隙１５
が形成されることになる。このため、開口１１周囲には
付着すべき本管内壁面が存在しなくなり、開口１１から
流出した第２の流体による付着流れの形成が阻止され
る。この場合、内管５の開口端が本管３内壁面から突出
していると、内管下流側で第１の流体の流れに乱れが生
じ、本管内壁面からの流れの剥離が生じやすくなる。こ
のため、開口１１が本管内に突出している場合には、更
に第２の流体の付着流れ形成の防止効果が大きくなる。In the fluid mixer 1 of this embodiment, in order to prevent this, the inner pipe 5 is provided in the outer pipe 9, and the open end of the inner pipe is flush with the inner wall surface of the main pipe or protrudes into the main pipe. 0 ≦
L ≦ D / 2). By providing the straight inner tube 5 in the expanded outer tube 9, a gap 15 extending from the joining portion 9 a to 9 b is provided between the inner wall of the outer tube 9 and the outer wall of the inner tube 5.
Is formed. Therefore, the inner wall surface of the main pipe to be attached does not exist around the opening 11, and the formation of the attached flow by the second fluid flowing out of the opening 11 is prevented. In this case, if the open end of the inner pipe 5 protrudes from the inner wall surface of the main pipe 3, the flow of the first fluid is disturbed on the downstream side of the inner pipe, and the flow is easily separated from the inner wall surface of the main pipe. Therefore, when the opening 11 protrudes into the main pipe, the effect of preventing the formation of the adhered flow of the second fluid is further increased.
【００２７】図４（Ａ）は図３のように付着流れが生じ
た場合の本管３０３内の流れの状態を模式的に示す本管
３０３の中心軸線に垂直な断面図である。付着流れが形
成されると、図４（Ａ）に斜線で示すように、支管３０
５から流入した第２の流体は本管壁面に沿って流れるた
め、第１の流体と第２の流体との接触は短い境界線ＢＤ
に限られることになる。このため、第１と第２の流体と
の混合が悪化する。FIG. 4A is a cross-sectional view perpendicular to the central axis of the main pipe 303 schematically showing the state of the flow in the main pipe 303 when the adhesion flow occurs as shown in FIG. When the adhesion flow is formed, as shown by hatching in FIG.
5 flows along the main pipe wall, so that the first fluid and the second fluid come into contact with the short boundary line BD.
It is limited to. For this reason, the mixing of the first and second fluids deteriorates.
【００２８】これに対して、図４（Ｂ）は図１の流体混
合器１を使用した場合の図４（Ａ）に対応する図であ
る。本実施形態では、内管５を本管３内に突出させると
ともに、内管５の開口端１１周囲に本管壁面が存在しな
いため、第２の流体は付着流を形成することなく、本管
内を流れるようになる。このため、第１の流体と第２の
流体との境界線は、第２の流体の流れの全周に形成され
るようになり、境界線が付着流れが形成された場合に比
べて大幅に長くなる。このため、境界線を通じた第１と
第２の流体の混合が促進され、完全混合距離が短くなる
のである。FIG. 4B is a view corresponding to FIG. 4A when the fluid mixer 1 of FIG. 1 is used. In this embodiment, since the inner pipe 5 is made to protrude into the main pipe 3 and the main pipe wall surface does not exist around the open end 11 of the inner pipe 5, the second fluid does not form an adherent flow, and Will flow through. For this reason, the boundary between the first fluid and the second fluid is formed on the entire circumference of the flow of the second fluid, and the boundary is significantly larger than when the adhered flow is formed. become longer. Therefore, the mixing of the first and second fluids through the boundary line is promoted, and the complete mixing distance is shortened.
【００２９】更に、本実施形態では第２の流体は本管内
の第２の流れに直角に、すなわち本管の軸線に垂直な方
向に内管から流出する。このため、内管７からの第２の
流体の流出速度が大きい場合には、図５に示すように、
第２の流体の一部が内管７開口と対向する本管内壁に当
たり、その後本管３に垂直な断面上で本管の内壁に沿っ
て流れる二次流れが形成されるようになり、第１の流体
との混合効果が更に向上するようになる。Furthermore, in the present embodiment, the second fluid flows out of the inner pipe at right angles to the second flow in the main pipe, that is, in a direction perpendicular to the axis of the main pipe. For this reason, when the outflow speed of the second fluid from the inner pipe 7 is high, as shown in FIG.
A part of the second fluid hits the inner wall of the main pipe facing the opening of the inner pipe 7, and then a secondary flow is formed along the inner wall of the main pipe on a cross section perpendicular to the main pipe 3, The effect of mixing with the first fluid is further improved.
【００３０】また、支管５と本管３との接続部を二重管
構造として、外管９と内管７との間に空隙１５を設けた
ことは、上述の付着流形成防止以外にも利点がある。こ
の場合、空隙１５は、本管３内の第１の流体の流れから
外れた位置に形成されることになるため、空隙１５内に
は第１の流体のよどみ領域が形成され、空隙１５内の第
１の流体の流速はきわめて遅くなる。このため、第１の
流体の温度が高い場合には空隙１５内で第１の流体が冷
却され、空隙１５内の温度は第１の流体と第２の流体と
の中間の温度となる。このため、接続部９ａ、９ｂの温
度は従来の温度より低くなり、温度差により発生する熱
応力が小さくなる。これにより、本実施形態では、従来
のようにサーマルシールドを設けることなく、熱応力の
値を低減することが可能となり、従来に比べて流体混合
器１の構成が極めて簡易になるため、製作コストが極め
て低くなる。The connection between the branch pipe 5 and the main pipe 3 has a double pipe structure, and the space 15 is provided between the outer pipe 9 and the inner pipe 7 in addition to the above-described prevention of adhesion flow formation. There are advantages. In this case, since the gap 15 is formed at a position deviating from the flow of the first fluid in the main pipe 3, a stagnation region of the first fluid is formed in the gap 15, and the inside of the gap 15 is formed. Is very slow. Therefore, when the temperature of the first fluid is high, the first fluid is cooled in the gap 15, and the temperature in the gap 15 is an intermediate temperature between the first fluid and the second fluid. For this reason, the temperature of the connection parts 9a and 9b becomes lower than the conventional temperature, and the thermal stress generated by the temperature difference becomes small. As a result, in the present embodiment, the value of the thermal stress can be reduced without providing a thermal shield as in the related art, and the configuration of the fluid mixer 1 is extremely simplified as compared with the related art. Is extremely low.
【００３１】次に、内管７の突出長さＬの設定について
説明する。内管の突出長さＬは、支管７内の第２の流体
の流速ｖに対する本管３内の第１の流体の流速Ｖの比Ｒ
（Ｒ＝ｖ／Ｖ）に基いて決定される。例えば、第２の流
体の流速ｖが第１の流体の流速Ｖより極めて大きいよう
な場合には、突出長さＬを小さく（０≦Ｌ）設定して
も、第２の流体の壁面付着流れは形成されない。一方、
逆に第２の流体の流速が第１の流体の流速に比べて小さ
いような場合には、突出長さＬをできるだけ大きく（た
だしＬ≦Ｄ／２）設定しないと壁面付着流れが形成され
てしまい、混合性能が低下してしまう。また、突出長さ
Ｌをあまりに大きくすると、本実施形態の構成では内管
７の開口１１から流出した第２の流体の大部分が開口に
対向する本管３壁面に衝突するようになり、この部分が
冷却されてしまい、周囲の高温部分との温度差により熱
応力が発生する場合がある。Next, the setting of the protruding length L of the inner tube 7 will be described. The projection length L of the inner pipe is determined by the ratio R of the flow velocity V of the first fluid in the main pipe 3 to the flow velocity v of the second fluid in the branch pipe 7.
(R = v / V). For example, when the flow velocity v of the second fluid is much higher than the flow velocity V of the first fluid, even if the protrusion length L is set to be small (0 ≦ L), the flow of the second fluid adhering to the wall surface is not affected. Is not formed. on the other hand,
Conversely, when the flow velocity of the second fluid is smaller than the flow velocity of the first fluid, the wall-adhered flow is formed unless the protrusion length L is set as large as possible (L ≦ D / 2). As a result, the mixing performance is reduced. If the projection length L is too large, most of the second fluid flowing out of the opening 11 of the inner pipe 7 collides with the wall surface of the main pipe 3 facing the opening in the configuration of the present embodiment. The portion is cooled, and a thermal stress may be generated due to a temperature difference from a surrounding high-temperature portion.
【００３２】厳密には、突出長さＬは実験により設定す
ることが好ましいが、最適な突出長さＬは概略、以下の
式で表されることが実験的に判明している。 Ｌ＝ａ／Ｒc＋ｂ ここで、Ｒは速度比（Ｒ＝ｖ／Ｖ）、ａ、ｂ、ｃは、そ
れぞれ正の定数であり、流体の種類、本管３と支管５の
径等により定まる。また、Ｌは本管半径（Ｄ／２）以下
とされる。Strictly speaking, it is preferable to set the protrusion length L by an experiment. However, it has been experimentally found that the optimum protrusion length L is roughly represented by the following equation. L = a / R c + b Here, R is a speed ratio (R = v / V), and a, b, and c are positive constants, respectively, depending on the type of fluid, the diameter of the main pipe 3 and the branch pipe 5, and the like. Is determined. L is set to be equal to or less than the main pipe radius (D / 2).
【００３３】上述のように、本実施形態によれば、２つ
の流体を短い混合距離で均一に混合することができ、し
かも構成が簡易で製作コストの低い流体混合器を実現す
ることができる。以下に、本発明の流体混合器の別の実
施形態を示す。以下に説明する実施形態は、いずれも、
支管５の本管３との接続部を二重管として、本管内に突
出する内管７を設けた点で図１の実施形態と共通する
が、内管５から流入する第２の流体の壁面付着流れ形成
の阻止、および図５で説明した二次流れの形成促進を考
慮した構成とされている。As described above, according to the present embodiment, it is possible to realize a fluid mixer which can mix two fluids uniformly with a short mixing distance, has a simple structure, and has a low production cost. Hereinafter, another embodiment of the fluid mixer of the present invention will be described. In each of the embodiments described below,
Although the connecting portion of the branch pipe 5 with the main pipe 3 is a double pipe and an inner pipe 7 protruding into the main pipe is provided, this embodiment is common to the embodiment of FIG. The configuration is designed to prevent formation of the flow adhering to the wall surface and to promote formation of the secondary flow described with reference to FIG.
【００３４】図６は、本管３断面で見て、支管５が偏心
した位置に接続された実施形態である。すなわち、図６
の実施形態では、支管５（および内管７）は、その中心
軸線ＣＬは、本管３の中心軸線と内壁面との間の、本管
中心軸線から外れた位置を通過するように配置されてい
る。このように、支管５を偏心位置に接続することによ
り、図６に矢印Ａで示したように、本管の横断面上で見
て、本管の湾曲した内壁面に沿って流れる第２の流体の
二次流れが形成されやすくなるため、第１と第２の流体
の混合性能が向上するようになる。FIG. 6 shows an embodiment in which the branch pipe 5 is connected to an eccentric position when viewed from the cross section of the main pipe 3. That is, FIG.
In the embodiment, the branch pipe 5 (and the inner pipe 7) is disposed such that the central axis CL passes through a position between the central axis of the main pipe 3 and the inner wall surface and deviated from the main axis. ing. In this way, by connecting the branch pipe 5 to the eccentric position, as shown by the arrow A in FIG. 6, the second pipe flowing along the curved inner wall surface of the main pipe when viewed on the cross section of the main pipe. Since the secondary flow of the fluid is easily formed, the mixing performance of the first and second fluids is improved.
【００３５】図７は、図１の実施形態の内管７開口１１
近傍にねじり角を有する固定羽根７１を設けた実施形態
である。固定羽根７１は、内管７を流れる第２の流体に
内管７軸線周りの旋回方向（接線方向）の速度を付与す
るものである。このように、開口１１から本管３に流入
する第２の流体に旋回方向速度成分を付与することによ
り、第２の流体の乱れが大きくなり、第１の流体との混
合効果が大幅に向上することが判明している。FIG. 7 shows the inner tube 7 opening 11 of the embodiment of FIG.
This is an embodiment in which a fixed blade 71 having a twist angle is provided in the vicinity. The fixed blade 71 imparts a velocity in a turning direction (tangential direction) around the axis of the inner pipe 7 to the second fluid flowing through the inner pipe 7. As described above, by imparting the turning velocity component to the second fluid flowing into the main pipe 3 from the opening 11, the turbulence of the second fluid is increased, and the mixing effect with the first fluid is greatly improved. Has been found to be.
【００３６】図８（Ａ）、図８（Ｂ）は図１の実施形態
の内管７下流側の本管内壁面に邪魔板８１を設けた実施
形態である。邪魔板８１は、図８（Ｂ）に示すように、
本管３の内壁面に合致する半径を有する円板の一部を切
り取った形状とされ、本管３内壁面に溶接される。邪魔
板８１の高さｈは、邪魔板８１を通過する第１の流体の
流れに乱れを生じ、内管７から流入する第２の流体が本
管内壁面に付着することを防止できる高さであり、詳細
には実験により決定される。FIGS. 8A and 8B show an embodiment in which a baffle plate 81 is provided on the inner wall surface of the main pipe downstream of the inner pipe 7 in the embodiment of FIG. The baffle plate 81 is, as shown in FIG.
A circular plate having a radius matching the inner wall surface of the main pipe 3 is cut out and welded to the inner wall surface of the main pipe 3. The height h of the baffle plate 81 is a height that can prevent the flow of the first fluid passing through the baffle plate 81 from being disturbed and prevent the second fluid flowing from the inner pipe 7 from adhering to the inner wall surface of the main pipe. Yes, specifically determined by experiment.
【００３７】このように、内管７下流側の本管壁面に邪
魔板８１を設けることにより第２の流体の壁面付着流が
形成されにくくなるため、内管７の突出長さＬは第１の
実施形態に比べて小さく設定することが可能となり、第
２の流体の流速ｖが小さい場合にも内管突出長さＬをゼ
ロに設定することも可能となる。図９（Ａ），（Ｂ）
は、内管７の開口端１１近傍に偏向板９１を配置した実
施形態を示す。偏向板９１は２枚の平板を逆Ｖ字型に接
合した形状であり内管の中央部に直径に沿って配置され
る。As described above, since the baffle plate 81 is provided on the wall surface of the main pipe downstream of the inner pipe 7, the flow of the second fluid adhering to the wall face is less likely to be formed. It is possible to set the inner pipe protrusion length L to zero even when the flow velocity v of the second fluid is small as compared with the embodiment. FIG. 9 (A), (B)
Shows an embodiment in which a deflecting plate 91 is arranged near the opening end 11 of the inner tube 7. The deflection plate 91 has a shape in which two flat plates are joined in an inverted V-shape, and is arranged along the diameter at the center of the inner tube.
【００３８】偏向板８１を内管７の開口端近傍に設けた
ことにより、内管７内を流れる第２の流体は開口１１両
側の本管３壁面に向かって流出するようになる。これに
より、本管３の軸線に垂直な断面で見て、第２の流体の
一部が開口１１両側の本管内壁面に沿って流れるように
なり、二次流れが形成されやすくなる。このため、本実
施形態では、二次流れによる第１と第２の流体の混合が
促進され、完全混合距離がさらに短縮される効果があ
る。Since the deflecting plate 81 is provided near the opening end of the inner pipe 7, the second fluid flowing in the inner pipe 7 flows out toward the wall surface of the main pipe 3 on both sides of the opening 11. As a result, when viewed in a cross section perpendicular to the axis of the main pipe 3, a part of the second fluid flows along the inner wall surface of the main pipe on both sides of the opening 11, and a secondary flow is easily formed. For this reason, in the present embodiment, the mixing of the first and second fluids by the secondary flow is promoted, and there is an effect that the complete mixing distance is further reduced.
【００３９】[0039]
【発明の効果】各請求項に記載の発明によれば、流体混
合器の混合性能を低下させることなく、構造を小型かつ
簡易なものとすることができるため、流体混合器の製造
コストを大幅に低減することが可能となる共通の効果を
奏する。According to the invention described in each of the claims, the structure can be made small and simple without lowering the mixing performance of the fluid mixer, so that the manufacturing cost of the fluid mixer is greatly increased. A common effect can be achieved.
【図１】本発明の流体混合器の第１の実施形態の構成を
説明する図である。FIG. 1 is a diagram illustrating a configuration of a first embodiment of a fluid mixer of the present invention.
【図２】図１の実施形態の流体混合性能を示す図であ
る。FIG. 2 is a diagram showing fluid mixing performance of the embodiment of FIG.
【図３】壁面付着流れを説明する図である。FIG. 3 is a diagram illustrating a flow of attaching to a wall surface.
【図４】図３の壁面付着流れ（図４（Ａ））と図１の実
施形態の流体の流れ（図４（Ｂ））とを比較対照する図
である。FIG. 4 is a diagram comparing and contrasting the flow of adhering to the wall surface in FIG. 3 (FIG. 4A) with the flow of the fluid in the embodiment of FIG.
【図５】第１の実施形態の二次流れを説明する図であ
る。FIG. 5 is a diagram illustrating a secondary flow according to the first embodiment.
【図６】本発明の流体混合器の第２の実施形態の構成を
説明する図である。FIG. 6 is a diagram illustrating a configuration of a second embodiment of the fluid mixer of the present invention.
【図７】本発明の流体混合器の第３の実施形態を説明す
る図である。FIG. 7 is a diagram illustrating a third embodiment of the fluid mixer of the present invention.
【図８】本発明の流体混合器の第４の実施形態を説明す
る図である。FIG. 8 is a view for explaining a fourth embodiment of the fluid mixer of the present invention.
【図９】本発明の流体混合器の第４の実施形態を説明す
る図である。FIG. 9 is a diagram illustrating a fourth embodiment of the fluid mixer of the present invention.
【図１０】従来の流体混合器の構成を説明する図であ
る。FIG. 10 is a diagram illustrating a configuration of a conventional fluid mixer.
１…流体混合器 ３…本管 ５…支管 ７…内管 ９…外管 １１…開口端 DESCRIPTION OF SYMBOLS 1 ... Fluid mixer 3 ... Main pipe 5 ... Branch pipe 7 ... Inner pipe 9 ... Outer pipe 11 ... Open end
Claims (6)
に混合する流体混合器であって、 第１の流体が流れる円管状の本管と、該本管に接続さ
れ、第２の流体を前記本管内を流れる第１の流体に合流
させる支管とを備え、前記支管の前記本管への接続部
は、前記支管の外壁と前記本管の外壁とを滑らかに接合
する拡管形状の外管と、前記支管に連続して前記外管内
を延びるとともに本管内に開口する端部を有する直管状
の内管とを備え、前記内管と外管との間には支管と外管
との接合部から前記内管開口部に向けて拡がる環状空隙
が形成され、前記内管開口端は前記本管の内壁面と同一
高さもしくは本管内に突出している流体混合器。1. A fluid mixer for uniformly mixing two types of fluid flows having different properties, comprising: a circular main pipe through which a first fluid flows; and a second fluid connected to the main pipe. And a branch pipe that joins the first fluid flowing in the main pipe, and a connecting portion of the branch pipe to the main pipe has an expanded pipe shape that smoothly joins an outer wall of the main pipe to an outer wall of the main pipe. A pipe, a straight tubular inner pipe extending in the outer pipe continuously to the branch pipe and having an end opening into the main pipe, and a branch pipe and an outer pipe between the inner pipe and the outer pipe. A fluid mixer in which an annular space extending from a joint portion toward the inner pipe opening is formed, and the inner pipe opening end is flush with the inner wall surface of the main pipe or protrudes into the main pipe.
中心軸線と本管内壁面との間の、本管中心軸線から外れ
た位置を通過するように配置されている、請求項１に記
載の流体混合器。2. The branch pipe according to claim 1, wherein the branch pipe passes through a position between the central axis of the main pipe and an inner wall surface of the main pipe, the position deviating from the central axis of the main pipe. A fluid mixer as described.
内管から本管に流入する第２の流体に内管中心軸線まわ
りの旋回方向の速度成分を付与する旋回流生成手段を備
えた、請求項１に記載の流体混合器。3. The inner pipe of the branch pipe, near the open end,
2. The fluid mixer according to claim 1, further comprising a swirling flow generating unit that imparts a velocity component in a swirling direction about the center axis of the inner pipe to the second fluid flowing into the main pipe from the inner pipe. 3.
下流側の本管内壁面には、本管内に向けて突出し、支管
から流入する第２の流体が支管下流側の本管内壁面に沿
って流れることを阻止する邪魔板が配置された、請求項
１に記載の流体混合器。4. A main pipe inner wall surface on the downstream side of the junction between the outer pipe and the main pipe of the branch pipe projects toward the inside of the main pipe, and a second fluid flowing from the branch pipe flows into the main pipe on the downstream side of the main pipe. The fluid mixer of claim 1, wherein a baffle is disposed to block flow along the wall.
管から本管に流入する第２の流体を前記開口の本管横断
方向両側の本管内壁面に沿って、第１の流体の流れに対
して垂直方向に流入させる偏向板を備えた、請求項１に
記載の流体混合器。5. An inner pipe of the branch pipe, in the vicinity of the opening, causes a second fluid flowing into the main pipe from the inner pipe to flow along the inner wall surface of the main pipe on both sides of the opening in the main pipe transverse direction. The fluid mixer according to claim 1, further comprising a deflector plate for flowing in a direction perpendicular to the flow of the fluid.
水蒸気である、請求項１から請求項５のいずれか１項に
記載の流体混合器。6. The fluid mixer according to claim 1, wherein the first and second fluids are steam having different temperatures.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000336307A JP2002136855A (en) | 2000-11-02 | 2000-11-02 | Fluid mixer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000336307A JP2002136855A (en) | 2000-11-02 | 2000-11-02 | Fluid mixer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002136855A true JP2002136855A (en) | 2002-05-14 |
Family
ID=18811905
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000336307A Pending JP2002136855A (en) | 2000-11-02 | 2000-11-02 | Fluid mixer |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002136855A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006272150A (en) * | 2005-03-29 | 2006-10-12 | Jfe Steel Kk | Gas mixer and gas mixing method |
| JP2013521123A (en) * | 2010-03-10 | 2013-06-10 | ウエテンド テクノロジーズ オサケユキチュア | Method and apparatus for mixing various streams in a process liquid stream |
| JP2015123384A (en) * | 2013-12-25 | 2015-07-06 | 月島機械株式会社 | Continuous reaction unit, and method for continuous crystallization reaction of inorganic particle |
| JP2015208706A (en) * | 2014-04-25 | 2015-11-24 | 住友金属鉱山株式会社 | Converter |
| US10092886B2 (en) | 2011-10-11 | 2018-10-09 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid mixer and heat exchange system using same |
| CN109046181A (en) * | 2018-09-18 | 2018-12-21 | 中国恩菲工程技术有限公司 | Combined fluid distributor |
| CN113883350A (en) * | 2020-07-01 | 2022-01-04 | 中国石油化工股份有限公司 | Sleeve type mixer for high temperature and large caliber |
| KR102443325B1 (en) * | 2021-10-05 | 2022-09-14 | 안형일 | In-Line Mixer for Uniformization 3D Distribution of Concectration in Fluid |
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| JPS5948732U (en) * | 1982-09-20 | 1984-03-31 | 三菱重工業株式会社 | Mixing flow path structure for two fluids |
| JPH02184330A (en) * | 1989-01-12 | 1990-07-18 | Mitsubishi Heavy Ind Ltd | Method and device for mixing fluids and air conditioner utilizing this device |
| JPH05337352A (en) * | 1992-06-11 | 1993-12-21 | Fujitsu Ltd | Apparatus for mixing liquids in nongraviation environment |
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| JPS56111027A (en) * | 1980-02-05 | 1981-09-02 | Ishikawajima Harima Heavy Ind Co Ltd | Fluid mixing device |
| JPS5948732U (en) * | 1982-09-20 | 1984-03-31 | 三菱重工業株式会社 | Mixing flow path structure for two fluids |
| JPH02184330A (en) * | 1989-01-12 | 1990-07-18 | Mitsubishi Heavy Ind Ltd | Method and device for mixing fluids and air conditioner utilizing this device |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006272150A (en) * | 2005-03-29 | 2006-10-12 | Jfe Steel Kk | Gas mixer and gas mixing method |
| JP2013521123A (en) * | 2010-03-10 | 2013-06-10 | ウエテンド テクノロジーズ オサケユキチュア | Method and apparatus for mixing various streams in a process liquid stream |
| US9339774B2 (en) | 2010-03-10 | 2016-05-17 | Wetend Technologies Oy | Method and apparatus for mixing various flows into a process liquid flow |
| US10092886B2 (en) | 2011-10-11 | 2018-10-09 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid mixer and heat exchange system using same |
| JP2015123384A (en) * | 2013-12-25 | 2015-07-06 | 月島機械株式会社 | Continuous reaction unit, and method for continuous crystallization reaction of inorganic particle |
| JP2015208706A (en) * | 2014-04-25 | 2015-11-24 | 住友金属鉱山株式会社 | Converter |
| CN109046181A (en) * | 2018-09-18 | 2018-12-21 | 中国恩菲工程技术有限公司 | Combined fluid distributor |
| CN109046181B (en) * | 2018-09-18 | 2023-12-22 | 中国恩菲工程技术有限公司 | Combined fluid distributor |
| CN113883350A (en) * | 2020-07-01 | 2022-01-04 | 中国石油化工股份有限公司 | Sleeve type mixer for high temperature and large caliber |
| KR102443325B1 (en) * | 2021-10-05 | 2022-09-14 | 안형일 | In-Line Mixer for Uniformization 3D Distribution of Concectration in Fluid |
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