JPH0650165B2 - Swirl flow generator - Google Patents
Swirl flow generatorInfo
- Publication number
- JPH0650165B2 JPH0650165B2 JP9443485A JP9443485A JPH0650165B2 JP H0650165 B2 JPH0650165 B2 JP H0650165B2 JP 9443485 A JP9443485 A JP 9443485A JP 9443485 A JP9443485 A JP 9443485A JP H0650165 B2 JPH0650165 B2 JP H0650165B2
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- Prior art keywords
- flow
- movable
- swirl flow
- fluid
- wall
- Prior art date
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Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は旋回流発生装置に係り、主に燃焼装置に用いら
れ、燃焼用空気等の流体に旋回力を付与するのに好適な
いわゆる半径流式の旋回流発生装置に関する。Description: TECHNICAL FIELD The present invention relates to a swirling flow generation device, and is mainly used in a combustion device and is suitable for giving a swirling force to a fluid such as combustion air. TECHNICAL FIELD The present invention relates to a flow type swirl flow generator.
油、ガス、微粉炭等の燃焼装置においては、燃焼空気を
旋回させて燃料との混合を制御することが行われてお
り、適性な旋回により、逆流域の形成による保炎機能の
強化、燃料と空気との混合状況制御による窒素酸化物及
び未燃分の低減化を図ることができる。In a combustion device for oil, gas, pulverized coal, etc., the combustion air is swirled to control the mixing with the fuel, and by appropriate swirling, the flame holding function is enhanced by the formation of a reverse flow region, It is possible to reduce the amount of nitrogen oxides and unburned components by controlling the mixed state of air and air.
すなわち、窒素酸化物の低減と未燃分の抑制とは相反す
るものであり、通常、未燃分を抑制するために燃料と空
気との混合を良好ならしめると、局所的に温度が上昇し
て窒素酸化物が増加し、逆に燃料と空気との混合を遅ら
せると、窒素酸化物が増加し、逆に燃料と空気との混合
を遅らせると、窒素酸化物は減少するが、未燃分は増加
する。That is, reduction of nitrogen oxides and suppression of unburned matter are contradictory. Normally, if mixing of fuel and air is made good to suppress unburned matter, the temperature locally rises. Nitrogen oxides increase and conversely delay the mixing of fuel and air, the amount of nitrogen oxides increases, conversely delaying the mixing of fuel and air decreases the amount of nitrogen oxides. Will increase.
しかるに、燃焼用空気に適正な旋回を与えると、バーナ
出口近傍では、逆流域の形成と相俟つて燃焼用空気の主
流が外側に向かい、燃料との混合が遅れるため、窒素酸
化物の発生が抑制される。一方、バーナから離れると、
逆流域が消滅しているため、燃焼用空気の主流が中心部
に向かい、先のバーナ近傍の燃焼域で生成した未燃分を
完全燃焼せしめることができる。すなわち、燃焼用空気
に対する適正な旋回力の付与は、環境保全及び高効率燃
焼の面から非常に重要であり、特に燃焼性の悪い微粉炭
等を燃料とする場合には、旋回力の微妙な調整を必要と
するものである。However, if a proper swirl is given to the combustion air, the main flow of the combustion air will flow outward in the vicinity of the burner outlet due to the formation of a backflow region, and the mixing with the fuel will be delayed, resulting in the generation of nitrogen oxides. Suppressed. On the other hand, when you leave the burner,
Since the reverse flow region has disappeared, the main flow of the combustion air is directed to the central portion, and the unburned components generated in the combustion region near the burner can be completely burned. That is, it is very important to give an appropriate swirling force to the combustion air in terms of environmental protection and high-efficiency combustion, and especially when using pulverized coal or the like having poor combustibility as a fuel, the swirling force is delicate. It needs adjustment.
従来、燃焼装置等に用いられている旋回流発生装置には
いわゆる軸流式と半径流式とがある。前者の軸流式は、
流体の入口流路と出口流路とが円柱状空間（すなわち、
円柱状或いは正多角形状空間）の同一直線軸上に存在
し、入口と出口の間に螺旋状の案内羽根を配して、通過
する流体に旋回力を与える方式である。一方、後者の半
径流式は、前記円柱状空間の側面相当部から流体が流入
し、その円柱状空間の少なくとも一方の底面から流出す
る方式で、通常、流体は流入部から半径方向に中心部へ
向かい、その後、円柱状空間の中心軸の方向に向きを転
じて底面部出口へ向かうものである。その際、前記注入
部に案内羽根を設けることにより、流入流体を円周方向
に向けて旋回力を付与するため、流体は一端渦巻状に中
心部へ向かい、次に方向を転じて螺旋状に出口へ向かう
ものである。Conventionally, there are a so-called axial flow type and a radial flow type in a swirl flow generation device used in a combustion device or the like. The former axial flow type is
The fluid inlet channel and the outlet channel are cylindrical spaces (that is,
It is a system that exists on the same straight axis of a cylindrical or regular polygonal space) and has a spiral guide vane between the inlet and the outlet to give a swirling force to the passing fluid. On the other hand, the latter radial flow method is a method in which a fluid flows in from a portion corresponding to the side surface of the cylindrical space and flows out from at least one bottom surface of the cylindrical space. And then turns toward the central axis of the cylindrical space toward the bottom surface outlet. At this time, by providing guide vanes in the injection part, a swirling force is applied to the inflowing fluid in the circumferential direction, so that the fluid is first spirally directed to the central part, and then is turned to spirally. It goes to the exit.
第６図及び第７図に従来の半径流式旋回流発生装置を付
設した燃焼装置の例を示す。同図において、旋回流発生
装置２４，２４′は火炉壁２に設けたバーナポート１１
の中心軸を中心として取り付けられている。本例は微粉
炭バーナの場合のもので、バーナポート１１には中心部
から外側に向かつて微粉炭ノズル８、二次空気ノズル
９、三次空気流路１０が各々設けてあり、旋回流発生装
置２４，２４′と共に風箱３内に納められている。この
微粉炭ノズル８にはインペラ７を備えた助燃バーナ６が
設置されており、また風箱３にはダンパ５を擁した空気
ダスト４が接続されている。FIG. 6 and FIG. 7 show an example of a combustion device provided with a conventional radial flow swirl flow generator. In the figure, the swirl flow generators 24 and 24 ′ are burner ports 11 provided on the furnace wall 2.
It is attached around the central axis of. This example is for a pulverized coal burner. The burner port 11 is provided with a pulverized coal nozzle 8, a secondary air nozzle 9, and a tertiary air flow passage 10 from the center to the outside. It is housed in the wind box 3 together with 24 and 24 '. An auxiliary combustion burner 6 having an impeller 7 is installed in the pulverized coal nozzle 8, and an air dust 4 having a damper 5 is connected to the wind box 3.
旋回流発生装置２４，２４′は、円柱状空間の底面をな
す旋回装置側壁１２ａ，１２ｂ、複数の可動羽根（案内
羽根）２５、回転軸２６、リンク２７，３０、操作軸２
８及び操作ハンドル２９により構成されている。The swirl flow generators 24 and 24 'include swirl device side walls 12a and 12b forming a bottom surface of a cylindrical space, a plurality of movable vanes (guide vanes) 25, a rotary shaft 26, links 27 and 30, and an operating shaft 2.
8 and the operation handle 29.
この種の半径流式旋回流発生装置では、燃焼用空気は可
動羽根２５を通つて流入するが、操作ハンドル２９を操
作して操作軸２８を回転させると、リンク２７，３０を
介して回転軸２６を回転させることができる。そして、
回転軸２６が回転すれば、回転軸２６に取り付けられて
いる可動羽根２５も回転し、第８図に示す如く、回転軸
中心円３１の接線３２と可動羽根２５とのなす角θが変
化し、旋回流発生装置に流入する燃焼用空気の流入方向
を変えることができる。また、可動羽根２５の角度θの
変化は、同時に可動羽根間の最小流路幅をも変化させ
る。したがつて、可動羽根角度θが小さくなれば、流入
方向が接線方向に近づき、流入速度の円周方向成分が増
加すると共に流入速度そのものも大幅に増加し、旋回力
は飛躍的に増加するはずのものである。In this type of radial flow type swirl flow generator, the combustion air flows in through the movable blades 25, but when the operation handle 29 is operated to rotate the operation shaft 28, the rotation shaft is rotated via the links 27 and 30. 26 can be rotated. And
When the rotary shaft 26 rotates, the movable blade 25 attached to the rotary shaft 26 also rotates, and as shown in FIG. 8, the angle θ between the tangent 32 of the rotary shaft center circle 31 and the movable blade 25 changes. The inflow direction of the combustion air flowing into the swirl flow generation device can be changed. Further, the change in the angle θ of the movable blades 25 also changes the minimum flow path width between the movable blades. Therefore, if the movable blade angle θ becomes smaller, the inflow direction will approach the tangential direction, the circumferential component of the inflow speed will increase, and the inflow speed itself will also increase significantly, and the swirling force should increase dramatically. belongs to.
しかるに、第９図に示す如く、可動羽根２５と旋回流発
生装置側壁１２ａ，１２ｂとの間には隙間３３が存在す
るので、流体の一部がリークする。この隙間３３は、可
動羽根２５をなるべく小さな動力で可動させる必要があ
ること、火炉壁２からの輻射熱によつて装置が熱歪を受
けても可動できるようにしておく必要があること、更に
はいたずらに工作精度を上げると製作費がかさむこと等
の理由により、可動羽根構造である限り、必ず存在する
隙間である。However, as shown in FIG. 9, a gap 33 exists between the movable blade 25 and the side walls 12a and 12b of the swirl flow generator, so that a part of the fluid leaks. The gap 33 needs to move the movable blades 25 with a power as small as possible, needs to be movable even if the device receives thermal strain due to radiant heat from the furnace wall 2, and further This is a gap that is always present as long as it has a movable blade structure because, for example, the manufacturing cost is increased if the work precision is unnecessarily increased.
前述した如く、旋回力を増すために可動羽根角度θを小
さくして最小流路幅を小さくすれば、旋回流発生装置
における羽根部分の断面積は減少し、隙間部分の面積は
変化しないから、結果的には、全流路面積に占める隙間
部分の面積割合が増加する。そのため、周方向成分を含
まないリーク流体の割合が増加し、可動羽根角度θを小
さくしても、期待される程の旋回力の増加は得られな
い。しかも、圧力損失だけは確実に増加するという望ま
しくない結果をもたらすことになる。As described above, if the movable vane angle θ is reduced to reduce the minimum flow passage width in order to increase the swirling force, the cross-sectional area of the vane portion in the swirling flow generator is reduced, and the area of the gap portion does not change. As a result, the area ratio of the gap portion to the total flow passage area increases. Therefore, the proportion of the leak fluid that does not include the circumferential component increases, and even if the movable blade angle θ is reduced, the expected increase in the turning force cannot be obtained. Moreover, the pressure loss alone has the undesired result of increasing reliably.
また、複数の可動羽根をリンクによつて結合して可動さ
せるため、個々の可動羽根における羽根角度θがそれぞ
れ異なり、偏流の原因となつたり、またリンク部に遊び
があるため、操作ハンドル２９を動かしても可動羽根２
５が追従しない等、旋回力を適正に制御する際に不都合
な事態を招くことになる。In addition, since the plurality of movable blades are linked and moved by the links, the blade angles θ of the individual movable blades are different from each other, which causes uneven flow, and there is play in the link portion. Movable blade 2 even if moved
This causes an inconvenient situation in properly controlling the turning force, such as 5 not following.
本発明の目的は、前述の従来技術の欠点を解消し、流体
のリーク量を減じ、効率良く旋回流を発生させることが
できる半径流式の旋回流発生装置を提供することにあ
る。It is an object of the present invention to provide a radial flow type swirl flow generation device which eliminates the above-mentioned drawbacks of the prior art, reduces the amount of fluid leak, and can efficiently generate a swirl flow.
本発明は、上記半径流式旋回流発生装置において、前記
可動式の案内羽根を固定式とし、かつ、円柱状空間の底
面に相当する壁のうち、少なくとも一方の壁を円柱状空
間の中心軸方向に移動可能な摺動壁にて構成するもので
ある。According to the present invention, in the above radial flow type swirl flow generating device, the movable guide vanes are fixed, and at least one of the walls corresponding to the bottom surface of the cylindrical space is a central axis of the cylindrical space. The sliding wall is movable in any direction.
以下、本発明を図示の実施例に基づいて詳細に説明す
る。Hereinafter, the present invention will be described in detail based on the illustrated embodiments.
第１図乃至第３図は本発明の一実施例に係る半径流式旋
回流発生装置１，１′を微粉炭バーナに適用した例を示
している。1 to 3 show an example in which the radial flow type swirl flow generators 1 and 1'according to an embodiment of the present invention are applied to a pulverized coal burner.
同図において、火炉壁２にバーナポート１１が設けられ
ており、バーナポート１１にはその中心部から外側に向
かつて微粉炭ノズル８、二次空気ノズル９及び三次空気
流路１０が設けられている。二次空気ノズル９及び三次
空気流路１０にはそれぞれ半径流式旋回発生装置１，
１′が取り付けられ、それらは風箱３内に納められてい
る。風箱３にはダンパ５を擁した空気ダクトが接続さ
れ、また微粉炭ノズル８内にはインペラ７が取り付けた
助燃バーナ６が設けられている。In the figure, a burner port 11 is provided on the furnace wall 2, and the burner port 11 is provided with a pulverized coal nozzle 8, a secondary air nozzle 9 and a tertiary air flow passage 10 outward from the center thereof. There is. The secondary air nozzle 9 and the tertiary air flow passage 10 respectively have a radial flow type swirl generator 1,
1'are attached and they are housed in a wind box 3. An air duct having a damper 5 is connected to the wind box 3, and an auxiliary combustion burner 6 to which an impeller 7 is attached is provided in the pulverized coal nozzle 8.
半径流式旋回発生装置１，１′は、旋回装置側壁１２
ａ，１２ｂと、複数の固定案内羽根１３と、この固定案
内羽根１３が貫通可能な切り欠き部を有する可動側壁
（摺動側壁）１４と、この可動側壁１４と接続されてい
る円筒１５と、この円筒１５の内側に設けたパッキン１
６と、一端が円筒１５に取り付けられ、他端が風箱３の
外壁を貫通している操作ロッド１７とを備えている。The radial flow type swirl generators 1 and 1'include swirler side walls 12
a, 12b, a plurality of fixed guide vanes 13, a movable side wall (sliding side wall) 14 having a cutout portion through which the fixed guide vane 13 can penetrate, a cylinder 15 connected to the movable side wall 14, Packing 1 provided inside this cylinder 15
6 and an operation rod 17 having one end attached to the cylinder 15 and the other end penetrating the outer wall of the wind box 3.
旋回装置側壁１２ａと可動側壁１４との間は円柱状空間
を形成し、操作ロット１７により可動側壁１４は旋回装
置側壁１２ａと可動側壁１４との間の円柱状空間の中心
軸方向に移動可能である。A cylindrical space is formed between the swivel device side wall 12a and the movable side wall 14, and the movable side wall 14 can be moved in the central axis direction of the cylindrical space between the swivel device side wall 12a and the movable side wall 14 by the operation lot 17. is there.
なお、複数の固定案内羽根１３は、この羽根先端の内接
円に接するように取り付けるのが普通であるが、場合に
よつては前記内接円の接線と任意の角度をもたせてもよ
い。The plurality of fixed guide blades 13 are usually attached so as to be in contact with the inscribed circle of the tip of the blades, but in some cases, they may have an arbitrary angle with the tangent line of the inscribed circle.
次に、上記構成の半径流式旋回流発生装置１，１′の作
用を示す。Next, the operation of the radial flow type swirl flow generators 1 and 1'having the above-described configuration will be described.
まず、空気ダクト４から風箱３内に供給された燃焼用空
気等の流体は、旋回流発生装置１，１′に供給される。
次いでその流路１８を通つて三次空気流路１０及び二次
空気ノズル９に達し、更にバーナポート１１を通つて火
炉内に噴出する。First, a fluid such as combustion air supplied from the air duct 4 into the wind box 3 is supplied to the swirl flow generators 1 and 1 '.
Then, it passes through the flow passage 18 to reach the tertiary air flow passage 10 and the secondary air nozzle 9, and further passes through the burner port 11 to be ejected into the furnace.
旋回流発生装置流路１８の入口部分には固定案内羽根１
３があり、ここに流入してきた流体は、固定案内羽根１
３の角度の方向（通常は円周方向）へ流れの向きを変え
られ、旋回力を与えられる。そのため、渦巻状の流れと
なつて旋回流発生装置１，１′の中心部へ向かう。とこ
ろで、旋回装置側壁はａの中心部は旋回流発生装置１，
１′の出口である三次空気流路１０又は二次空気ノズル
９に連つているため、再び方向を変えられ、螺旋状の流
れとなつてバーナポート１１へ向かうことになる。The fixed guide vane 1 is provided at the inlet of the swirl flow generator passage 18.
3 and the fluid that has flowed in here is fixed guide vane 1
The direction of the flow is changed in the direction of the angle of 3 (usually the circumferential direction), and the turning force is given. Therefore, the spiral flow is directed toward the center of the swirl flow generators 1, 1 '. By the way, the side wall of the swirl device is a and the central part of the swirl flow generating device 1,
Since it is connected to the tertiary air flow path 10 or the secondary air nozzle 9 which is the outlet of 1 ', the direction is changed again, and it becomes a spiral flow toward the burner port 11.
ここで、旋回流発生装置流路１８の幅は、操作ロツド１
７の操作により、可動側壁１４を軸方向に摺動させると
任意に設定できるので、流体の流入速度は任意に変化さ
せることができ、旋回力を変えることができる。また、
固定案内羽根１３と側壁１２ａ，１２ｂとの間には隙間
がないので、リークする流体がない。更に、固定案内羽
根１３は、通常、流体の流入方向がその羽根先端の内接
円の接線方向とできるだけ一致するように配されている
ため、流体のもつ速度ベリトルの殆どが旋回力に変える
ことができ、旋回流発生の効率が良い。Here, the width of the swirl flow generator passage 18 is determined by the operation rod 1
Since the movable side wall 14 can be slid in the axial direction by the operation of 7, the inflow speed of the fluid can be arbitrarily changed, and the turning force can be changed. Also,
Since there is no gap between the fixed guide vane 13 and the side walls 12a and 12b, there is no fluid to leak. Further, since the fixed guide vanes 13 are usually arranged so that the inflow direction of the fluid coincides with the tangential direction of the inscribed circle of the vane tip as much as possible, most of the velocity velocity of the fluid is converted into the swirling force. The efficiency of swirling flow generation is good.
次に、第４図に本発明の第２の実施例を示す。本実施例
は、可動側壁１４に設けた切り欠き部１９にパツキン２
０を設けたものである。これにより、切り欠き部１９の
シールを行うことができるため、切り欠き部１９の工作
精度が多く悪くても摺動部の気密性を保つことができ
る。Next, FIG. 4 shows a second embodiment of the present invention. In this embodiment, the packing 2 is provided in the notch 19 provided in the movable side wall 14.
0 is provided. As a result, since the cutout portion 19 can be sealed, the airtightness of the sliding portion can be maintained even if the workability of the cutout portion 19 is poor.
第５図は本発明の第３の実施例を示したもので、固定案
内羽根１３が挿入できる溝２３を環状ブロツク２２を操
作ロツド１７により摺動させて、旋回流発生装置の流路
１８の幅を変化させるようにしたもので、その効果は第
１の実施例と同等である。FIG. 5 shows a third embodiment of the present invention, in which the annular block 22 is slid by the operation rod 17 in the groove 23 into which the fixed guide vane 13 can be inserted, so that the flow path 18 of the swirling flow generating device is formed. The width is changed, and the effect is the same as that of the first embodiment.
なお、前述の各実施例は微粉炭バーナに適用した例であ
るが、他の燃料を用いるバーナ、或いはアフタエアポー
ト等、旋回流を必要とする全ての場合に適用できること
は云うまでもない。In addition, although each of the above-described embodiments is an example applied to a pulverized coal burner, it goes without saying that it can be applied to all cases where a swirl flow is required, such as a burner using another fuel or an after-air port.
以上詳述したように、本発明によれば、半径流式旋回流
発生装置において、案内羽根を最も効率の良い接続方向
に固定し、可動側壁を摺動させて旋回流発生装置の流路
幅を変化させることによつて旋回力を調整できるので、
従来の可動案内羽根の使用にみられるような旋回力に寄
与しないリーク流体をなくことができ、更に案内羽根の
角度が一定であるため、大きな旋回力を得たい場合に
も、従来のように可動案内羽根の羽根角度を減じること
による有効羽根長の減少のためにシヨートパス量が増加
し、所定の旋回力が得られなくなるというようなことが
なく、旋回力の変化幅を非常に大きくとることができ
る。また、可動案内羽根の羽根角度のバラツキに基づく
流動状態の偏りをも少なくすることができる。したがつ
て、旋回流を発生させるに際して無駄が少なく、きめ細
かい旋回力の制御が可能となる等々の効果を奏する。As described in detail above, according to the present invention, in the radial flow type swirl flow generator, the guide vanes are fixed in the most efficient connection direction, and the movable side wall is slid to make the flow path width of the swirl flow generator. Since the turning force can be adjusted by changing
It is possible to eliminate leak fluid that does not contribute to the swirling force found in the use of conventional movable guide vanes, and the angle of the guide vanes is constant. The amount of change in swivel force should be very large without the specified swivel force becoming unachievable due to the increase in short path due to the decrease in the effective vane length by reducing the vane angle of the movable guide vanes. You can Further, it is possible to reduce the deviation of the flow state due to the variation of the blade angle of the movable guide blade. Therefore, when the swirl flow is generated, there is little waste, and fine swivel force control is possible.
第１図乃至第３図は本発明の第１の実施例に係る半径流
式旋回流発生装置を付設した微粉炭バーナの例を示す図
で、第１図は断面図、第２図は第１図のＡ−Ａ′断面
図、第３図は第２図のＢ部の部分拡大図、 第４図及び第５図は各々本発明の第２，第３の実施例の
一部分を示す図、 第６図乃至第９図は従来の半径流式旋回流発生装置を付
設した微粉炭バーナの例を示す図で、第６図は断面図、
第７図は第６図のＣ−Ｃ′断面図、第８図及び第９図は
部分図である。 １，１′……半径流式旋回流発生装置、３……風箱、４
……空気ダクト、５……ダンパ、６……助燃バーナ、８
……微粉炭ノズル、９……二次空気ノズル、１０……三
次空気流路、１１……バーナポート、１２ａ，１２ｂ…
…旋回装置側壁、１３……固定案内羽根、１４……可動
側壁（摺動側壁）、１５……円筒、１６，２０……パツ
キン、１７……操作ロツド、１８……旋回流発生装置流
路、１９……切り欠き部、２１……空気流、２２……環
状ブロツク、２３……溝。1 to 3 are views showing an example of a pulverized coal burner provided with a radial flow type swirl flow generating device according to a first embodiment of the present invention. FIG. 1 is a sectional view and FIG. 1 is a sectional view taken along the line AA ', FIG. 3 is a partially enlarged view of a portion B in FIG. 2, and FIGS. 4 and 5 are views showing parts of the second and third embodiments of the present invention. 6 to 9 are views showing an example of a pulverized coal burner provided with a conventional radial flow type swirl flow generator, and FIG. 6 is a sectional view,
FIG. 7 is a sectional view taken along the line CC ′ of FIG. 6, and FIGS. 8 and 9 are partial views. 1, 1 '... Radial flow type swirl flow generator, 3 ... Wind box, 4
...... Air duct, 5 ...... Damper, 6 ...... Auxiliary burner, 8
... Pulverized coal nozzle, 9 ... Secondary air nozzle, 10 ... Tertiary air flow path, 11 ... Burner port, 12a, 12b ...
... Swirl device side wall, 13 ... Fixed guide vanes, 14 ... Movable side wall (sliding side wall), 15 ... Cylinder, 16,20 ... Packing, 17 ... Operation rod, 18 ... Swirl flow generator flow path , 19 ... notch, 21 ... air flow, 22 ... annular block, 23 ... groove.
Claims (1)
底面はその中心部に流体の出口流路を配すると共にその
外側の環状部を壁となし、側面相当部には流体の入口流
路を配し、かつ、前記入口流路に案内羽根を設けた所謂
半径流式旋回流発生装置において、前記案内羽根を固定
すると共に、該円柱状空間の両底面をなす前記壁のう
ち、少なくとも一方の壁を該円柱状空間の中心軸方向に
移動可能な摺動壁にて構成したことを特徴とする旋回流
発生装置。1. A cylindrical space having one bottom surface as a wall, the other bottom surface having a fluid outlet flow passage in its center and an outer annular portion as a wall, and the side surface corresponding portion being fluid. In a so-called radial flow type swirl flow generating device in which the inlet flow passage is arranged and guide vanes are provided in the inlet flow passage, the guide vane is fixed and the wall of the wall forming both bottom surfaces of the cylindrical space is fixed. At least one of the walls is a sliding wall that is movable in the direction of the central axis of the cylindrical space.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9443485A JPH0650165B2 (en) | 1985-05-01 | 1985-05-01 | Swirl flow generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9443485A JPH0650165B2 (en) | 1985-05-01 | 1985-05-01 | Swirl flow generator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61252412A JPS61252412A (en) | 1986-11-10 |
| JPH0650165B2 true JPH0650165B2 (en) | 1994-06-29 |
Family
ID=14110140
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9443485A Expired - Lifetime JPH0650165B2 (en) | 1985-05-01 | 1985-05-01 | Swirl flow generator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0650165B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04273912A (en) * | 1991-02-28 | 1992-09-30 | Kobe Steel Ltd | Ash melting-solidifying apparatus |
| JP3140299B2 (en) * | 1994-06-30 | 2001-03-05 | 株式会社日立製作所 | Pulverized coal burner and its use |
| JP5332389B2 (en) * | 2008-08-08 | 2013-11-06 | 株式会社Ｉｈｉ | Burner |
| JP5369899B2 (en) | 2009-05-27 | 2013-12-18 | 株式会社Ｉｈｉ | Burner |
| CN102434877B (en) * | 2011-12-26 | 2014-07-09 | 上海锅炉厂有限公司 | Micro oil mass ignition gradual combustor |
| JP6273758B2 (en) * | 2013-10-15 | 2018-02-07 | 株式会社Ihi | Vane opening measurement device, hysteresis curve creation method, and hysteresis calculation method |
-
1985
- 1985-05-01 JP JP9443485A patent/JPH0650165B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61252412A (en) | 1986-11-10 |
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