JPS61252412A - Circulation flow generating device - Google Patents
Circulation flow generating deviceInfo
- Publication number
- JPS61252412A JPS61252412A JP9443485A JP9443485A JPS61252412A JP S61252412 A JPS61252412 A JP S61252412A JP 9443485 A JP9443485 A JP 9443485A JP 9443485 A JP9443485 A JP 9443485A JP S61252412 A JPS61252412 A JP S61252412A
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- Prior art keywords
- fluid
- guide vanes
- flow
- cylindrical space
- movable
- 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.)
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Links
Abstract
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。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a swirling flow generating device, which is mainly used in combustion devices, and has a so-called radius that is suitable for imparting swirling force to a fluid such as combustion air. This invention relates to a flow-type swirling 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
、適正な旋回により、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 combustion equipment for oil, gas, pulverized coal, etc., combustion air is swirled to control its mixing with fuel. Proper swirling strengthens the flame-holding function by forming a backflow area, and improves the fuel flow. Nitrogen oxides and unburned substances can be reduced by controlling the mixing condition of the fuel 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、窒素酸化物は減少するが、未燃分は増加する。In other words, the reduction of nitrogen oxides and the suppression of unburned matter are contradictory, and normally, when the mixture of fuel and air is improved to suppress unburned matter, the temperature locally increases. Conversely, if the mixing of fuel and air is delayed, nitrogen oxides will decrease but unburned matter 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って燃焼用空気の主
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 proper swirl is given to the combustion air, a backflow area is formed near the burner outlet, and the main flow of the combustion air is directed outwards, delaying mixing with the fuel, resulting in the generation of nitrogen oxides. is suppressed. On the other hand, when you leave the burner,
Since the backflow region has disappeared, the main flow of combustion air heads toward the center, making it possible to completely burn the unburned matter generated in the previous combustion region near the burner. In other words, applying an appropriate swirling force to the combustion air is extremely important from the viewpoint of environmental protection and high efficiency combustion. Especially when using pulverized coal, etc., which has poor combustibility, as fuel, the subtle swirling force is extremely important. This requires 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 two types of swirl flow generation devices used in combustion devices and the like: an axial flow type and a radial flow type. The former axial flow type is
The inlet flow path and the outlet flow path of the fluid form a cylindrical space (i.e.
This system exists on the same linear axes of a cylindrical or regular polygonal space, and a spiral guide vane is placed between the inlet and the outlet to apply swirling force to the fluid passing through. On the other hand, in the latter radial flow type, fluid flows in from a portion corresponding to the side surface of the cylindrical space and flows out from the bottom surface of at least one side of the cylindrical space. Usually, the fluid flows radially from the inlet to the center. After that, it turns in the direction of the central axis of the cylindrical space and heads toward the bottom exit. At this time, by providing a guide vane in the injection part, a swirling force is applied to the inflowing fluid in the circumferential direction, so that the fluid heads toward the center in a spiral shape at one end, then reverses direction and spirals. It is heading for 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1
1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、/(−ナボート11には中
心部から外側に向かって微粉炭ノズル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。FIGS. 6 and 7 show an example of a combustion apparatus equipped with a conventional radial swirl flow generating device. In the same figure, the swirl flow generator 24, 24' is a burner port 1 provided on the furnace wall 2.
It is attached around the central axis of 1. This example is for a pulverized coal burner. /(-Navot 11 is provided with a pulverized coal nozzle 8, a secondary air nozzle 9, and a tertiary air passage 10 from the center to the outside, and a swirling flow The pulverized coal nozzle 8 is housed in the wind box 3 together with the generator 24, 24'.
is installed, 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11i
lit′なす旋回装置側壁12a、12b、複数)可動
羽根(案内羽根)25、回転軸26、リンク27゜30
、操作軸28及び操作ハンドル29により構成されてい
る。The swirl flow generator 24, 24' is located at the bottom 11i of the cylindrical space.
lit' rotating device side walls 12a, 12b, multiple movable blades (guide blades) 25, rotating shaft 26, link 27°30
, an operating shaft 28 and an operating 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を通って流入するが、操作ハンドル29t−
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250角度θ
の変化は、同時に可動羽根間の最小流路幅tをも変化さ
せる。したがって、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 swirling flow generating device, combustion air flows through the movable vane 25, but the operating handle 29t-
When the operation shaft 28 is rotated, the link 27.30
The rotary shaft 26 can be rotated via. When the rotating shaft 26 rotates, the movable blade 25 attached to the rotating shaft 26 also rotates, and as shown in FIG. It is possible to change the inflow direction of the combustion air flowing into the swirl flow generating device. In addition, the movable blade 250 angle θ
At the same time, the change in t also changes the minimum flow path width t between the movable vanes. Therefore, if the movable blade angle θ becomes smaller, the inflow direction approaches the tangential direction, the circumferential component of the inflow velocity increases, and the inflow velocity itself also increases significantly, which should dramatically increase the turning force. It is.
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。However, as shown in FIG. 9, there is a gap 33 between the movable blade 25 and the side walls 12a, 12b of the swirl flow generator, so that some of the fluid leaks.
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がらの輻射熱によ
っ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。This gap 33 is created because it is necessary to move the movable blade 25 with as little power as possible, it is necessary to be able to move even if the device is subjected to thermal distortion due to radiant heat from the furnace wall 2, and it is also necessary to avoid mischief. For reasons such as increasing the manufacturing cost if the machining accuracy is increased, this gap will always exist as long as the blade has a movable blade structure.
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+111 t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1)−り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。As mentioned above, if the movable blade angle θ is made smaller to increase the swirling force and the minimum flow path +111t is made smaller, the cross-sectional area of the blade portion in the swirling flow generator decreases, and the area of the gap portion remains unchanged. As a result, the area ratio of the gap portion to the total flow path area increases. Therefore, the ratio of 1)-ri fluid that does not include a circumferential component increases, and even if the movable blade angle θ is reduced, the expected increase in swirling force cannot be obtained.
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。Moreover, this brings about the undesirable result that only the pressure loss increases without fail.
また、複数の可動羽根をリンクによって結合して可動さ
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、偏流の原因となったり、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 a plurality of movable vanes are connected and moved by links, the vane angle θ of each movable vane is different, which may cause drift, and there is play in the links, so it is difficult to move the operating handle 29. movable blade 2
5 may not follow suit, which may lead to inconvenient situations when controlling the turning force appropriately.
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
。SUMMARY OF THE INVENTION An object of the present invention is to provide a radial flow type swirling flow generation device that can eliminate the drawbacks of the prior art described above, reduce the amount of fluid leakage, and efficiently generate swirling 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。In the radial swirl flow generating device, the movable guide vanes are fixed, and at least one of the walls corresponding to the bottom of the cylindrical space is connected to the central axis of the cylindrical space. It is composed of a sliding wall that can be moved in different directions.
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 explained in detail based on 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 a radial swirl flow generator 1.1' according to an embodiment of the present invention is applied to a pulverized coal burner.
同図において、火炉壁2にバーナボート11が設けられ
ており、バーナボート11にはその中心部から外側に向
かって微粉炭ノズル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。In the figure, a burner boat 11 is provided on a furnace wall 2, and a pulverized coal nozzle 8, a secondary air nozzle 9, and a tertiary air flow path 10 are provided in the burner boat 11 from the center toward the outside. There is.
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5t−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
イノペラ7を取り付けた助燃バーナ6が設けられている
。A radial swirl generator 1.1' is attached to the secondary air nozzle 9 and the tertiary air channel 10, respectively, and these are housed in the wind box 3. An air duct having a damper 5t is connected to the wind box 3, and an auxiliary combustion burner 6 to which an inopeller 7 is attached is provided in the pulverized coal nozzle 8.
半径流式旋回発生装置1,1′は、円柱状空間の底面を
なす旋回装置側壁12!l、12bと、複数の固定案内
羽根13と、この固定案内羽根13がに通可能な切り欠
き部を有する可動側壁(摺動側壁)14と、この可動側
壁14を一方の底面となす円柱状空間の側面部に相当し
、かつ、可動側壁14と接続されている円筒15と、こ
の円筒15の内側に設けたパツキン16と、一端が前記
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により構成されている。The radial flow type swirl generating device 1, 1' has a swirl device side wall 12 which forms the bottom surface of a cylindrical space! 1, 12b, a plurality of fixed guide vanes 13, a movable side wall (sliding side wall) 14 having a notch through which the fixed guide vanes 13 can pass, and a cylindrical column with the movable side wall 14 as one bottom surface. A cylinder 15 corresponding to the side surface of the space and connected to the movable side wall 14, a packing 16 provided inside the cylinder 15, one end attached to the cylinder 15, and the other end attached to the wind box/3. It is constituted by an operating rod 17 penetrating the outer wall of.
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
よっ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 vanes 13 are usually attached so as to be in contact with the inscribed circle of the tip of the vane, but depending on the case, they may be attached at an arbitrary angle with the tangent to 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 swirl flow generator 1°1' having the above structure 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。First, fluid such as combustion air supplied from the air duct 4 into the wind box 3 is supplied to the swirl flow generator 1.1'.
次いで七〇流路18を通って三次空気流路10及び二次
空気ノズル9に達し、更にバーナボート11t−通って
火炉内に噴出する。The air then passes through the 70 flow path 18 to reach the tertiary air flow path 10 and the secondary air nozzle 9, and further passes through the burner boat 11t and is 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。A fixed guide vane 1 is installed at the inlet of the swirl flow generator flow path 18.
3, and the fluid flowing into the fixed guide vane 1
The direction of the flow is changed in the direction of an angle of 3 (usually in the circumferential direction), and a swirling force is applied.
そのため、渦巻状の流れとなって旋回流発生装置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に連っているため、再び方
向を変えられ、螺旋状の流れとなってバーナボート11
へ向かうことになる。Therefore, the flow becomes a spiral and the swirling flow generator 1.1
Go to the center of '. By the way, since the central part of the side wall of the swirling device a is connected to the tertiary air flow path 10 or the secondary air nozzle 9, which is the outlet of the swirling flow generating device 1.1', the direction is changed again and a spiral shape is formed. Burna boat 11 becomes the flow
I will be heading to.
ここで、旋回流発生装置流路18の幅は、操作ロッド1
7の操作により、可動側壁14t−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K、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 swirling flow generator flow path 18 is the width of the operating rod 1
By the operation in step 7, the movable side wall 14t can be arbitrarily set by sliding in the axial direction, so that the inflow velocity of the fluid can be arbitrarily changed and the turning force can be changed. Moreover, since there is no gap between the fixed guide vane 13 and the side walls 12a, 12b, there is no leakage of fluid. Additionally, the fixed guide vanes 13 are usually arranged so that the inflow direction of the fluid coincides as much as possible with the tangential direction of the inscribed circle at the tip of the vane, so most of the velocity of the fluid is converted into swirling force. The efficiency of swirl flow generation is high.
次に、第4図に本発明の第2の実施例を示す。Next, FIG. 4 shows a second embodiment of the present invention.
本実施例は、可動側壁14に設けた切や欠き部19にパ
ツキン20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1
9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。In this embodiment, a gasket 20 is provided in a notch or notch 19 provided in the movable side wall 14. This allows the notch 19 to be sealed, so the notch 19 can be sealed.
Even if the machining accuracy of No. 9 is poor, the airtightness of the sliding part can be maintained.
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を環状ブロック22を操
作ロッド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 an annular block 22 is slid by an operating rod 17 into a groove 23 into which a fixed guide vane 13 can be inserted, and a flow path 18 of the swirl flow generator is opened. 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。Although each of the above-mentioned embodiments is an example applied to a pulverized coal burner, it goes without saying that it can be applied to any case that requires a swirling flow, such as a burner using other fuels 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っ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
よる有効態根長の減少のためにショ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つようなことがな
く、旋回力の変化幅を非常に大きくとることができる。As described in detail above, according to the present invention, in a radial flow type swirling flow generator, the guide vanes are fixed in the most efficient connection direction, and the movable side wall is slid to increase the flow path width of the swirling flow generator. The turning force can be adjusted by changing the
It is possible to eliminate leakage fluid that does not contribute to the turning force, which is seen when using conventional movable guide vanes, and since the angle of the guide vanes is constant, even when you want to obtain a large turning force, it is possible to eliminate the leakage fluid that does not contribute to the turning force. Due to the reduction in the effective root length due to the reduction of the blade angle of the movable guide vane, the amount of short passes increases, and if the specified turning force cannot be obtained, it will not happen at any time, and the range of change in the turning force can be greatly reduced. It can be made large.
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。しだがって、
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。Furthermore, it is possible to reduce deviations in the flow state due to variations in the vane angle of the movable guide vanes. Therefore,
There is less waste when generating a swirling flow, and the swirling force can be precisely controlled.
第1図乃至#IJ3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、lO・・・三次空気流路、 11・・・
バーナボート、12a、12b・・・旋回装置側壁、
13・・・固定稟内羽根、 14・・・可動側壁(摺動
側壁)、 15・・・円筒、 16.20・・・パツキ
ン、 17・・・操作ロッド、 18・・・旋回流発生
装置流路、 19・・・切り欠き部、 21・・・空気
流、 22・・・環状ブロック、 23・・・溝。Figures 1 to #IJ3 are views showing an example of a pulverized coal burner equipped with a radial swirl flow generating device according to the first embodiment of the present invention, with Figure 1 being a sectional view and Figure 2 being a pulverized coal burner. 1, FIG. 3 is a partially enlarged view of section B in FIG. 2, and FIGS. 6 to 9 are views showing an example of a pulverized coal burner equipped with a conventional radial swirl flow generating device; FIG. 6 is a cross-sectional view;
FIG. 7 is a sectional view taken along line cc' in FIG. 6, and FIGS. 8 and 9 are partial views. 1.1'... Radial swirl flow generator, 3... Wind box, 4... Air duct, 5... Damper, 6...
- Auxiliary combustion burner, 8... Pulverized coal nozzle, 9... Secondary air nozzle, lO... Tertiary air flow path, 11...
Burner boat, 12a, 12b...Swivel device side wall,
13...Fixed circular inner blade, 14...Movable side wall (sliding side wall), 15...Cylinder, 16.20...Puttlekin, 17...Operation rod, 18...Swirling flow generator Flow path, 19... Notch, 21... Air flow, 22... Annular block, 23... Groove.
Claims (1)
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。One bottom surface of the cylindrical space serves as a wall, the other bottom surface has a fluid outlet channel in its center, an annular portion on the outside thereof serves as a wall, and a fluid inlet channel is provided in a portion corresponding to the side surface. In a so-called radial flow swirling flow generating device in which a guide vane is provided in the inlet flow path, the guide vane is fixed, and the guide vane is fixed.
A swirling flow generating device characterized in that at least one of the walls forming both bottom surfaces of the cylindrical space is constituted by a sliding wall 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 true JPS61252412A (en) | 1986-11-10 |
JPH0650165B2 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) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04273912A (en) * | 1991-02-28 | 1992-09-30 | Kobe Steel Ltd | Ash melting-solidifying apparatus |
US5806443A (en) * | 1994-06-30 | 1998-09-15 | Hitachi, Ltd. | Pulverized coal burner and method of using same |
WO2010016168A1 (en) * | 2008-08-08 | 2010-02-11 | 株式会社Ihi | Burner |
JP2010276236A (en) * | 2009-05-27 | 2010-12-09 | Ihi Corp | Burner |
CN102434877A (en) * | 2011-12-26 | 2012-05-02 | 上海锅炉厂有限公司 | Micro oil mass ignition gradual combustor |
JP2015078783A (en) * | 2013-10-15 | 2015-04-23 | 株式会社Ihi | Vane opening measuring apparatus and hysteresis curve formation method |
-
1985
- 1985-05-01 JP JP9443485A patent/JPH0650165B2/en not_active Expired - Lifetime
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04273912A (en) * | 1991-02-28 | 1992-09-30 | Kobe Steel Ltd | Ash melting-solidifying apparatus |
US5806443A (en) * | 1994-06-30 | 1998-09-15 | Hitachi, Ltd. | Pulverized coal burner and method of using same |
WO2010016168A1 (en) * | 2008-08-08 | 2010-02-11 | 株式会社Ihi | Burner |
JP2010038519A (en) * | 2008-08-08 | 2010-02-18 | Ihi Corp | Burner |
US8726819B2 (en) | 2008-08-08 | 2014-05-20 | Ihi Corporation | Burner |
JP2010276236A (en) * | 2009-05-27 | 2010-12-09 | Ihi Corp | Burner |
US8646394B2 (en) | 2009-05-27 | 2014-02-11 | Ihi Corporation | Burner |
US8820249B2 (en) | 2009-05-27 | 2014-09-02 | Ihi Corporation | Burner |
CN102434877A (en) * | 2011-12-26 | 2012-05-02 | 上海锅炉厂有限公司 | Micro oil mass ignition gradual combustor |
JP2015078783A (en) * | 2013-10-15 | 2015-04-23 | 株式会社Ihi | Vane opening measuring apparatus and hysteresis curve formation method |
Also Published As
Publication number | Publication date |
---|---|
JPH0650165B2 (en) | 1994-06-29 |
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