JPS6330085B2 - - Google Patents
Info
- Publication number
- JPS6330085B2 JPS6330085B2 JP59222277A JP22227784A JPS6330085B2 JP S6330085 B2 JPS6330085 B2 JP S6330085B2 JP 59222277 A JP59222277 A JP 59222277A JP 22227784 A JP22227784 A JP 22227784A JP S6330085 B2 JPS6330085 B2 JP S6330085B2
- Authority
- JP
- Japan
- Prior art keywords
- nozzle
- flow
- flat
- header
- laminar
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- C—CHEMISTRY; METALLURGY
- C21—METALLURGY OF IRON
- C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
- C21D1/00—General methods or devices for heat treatment, e.g. annealing, hardening, quenching or tempering
- C21D1/62—Quenching devices
- C21D1/667—Quenching devices for spray quenching
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05C—APPARATUS FOR APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
- B05C5/00—Apparatus in which liquid or other fluent material is projected, poured or allowed to flow on to the surface of the work
- B05C5/005—Curtain coaters
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B45/00—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
- B21B45/02—Devices for surface or other treatment of work, specially combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills for lubricating, cooling, or cleaning
- B21B45/0203—Cooling
- B21B45/0209—Cooling devices, e.g. using gaseous coolants
- B21B45/0215—Cooling devices, e.g. using gaseous coolants using liquid coolants, e.g. for sections, for tubes
- B21B45/0233—Spray nozzles, Nozzle headers; Spray systems
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Crystallography & Structural Chemistry (AREA)
- Materials Engineering (AREA)
- Metallurgy (AREA)
- Organic Chemistry (AREA)
- Heat Treatment Of Strip Materials And Filament Materials (AREA)
- Heat Treatments In General, Especially Conveying And Cooling (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、高温鋼材の冷却に使用されるフラツ
トラミナーノズルヘツダの改良に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to improvements in flat laminar nozzle headers used for cooling high-temperature steel materials.
熱間圧延設備におけるオンライン熱鋼板又は再
加熱した熱鋼板の強制冷却又は焼入れには、冷却
能力が大きく板幅方向の冷却が均一なフラツトラ
ミナーフロー（平板状層流）の使用が適してお
り、従来このためには第４図ａに示す開放型ノズ
ルヘツダ１０又は同ｂに示すヘツダ内の空気をす
べて抜き出した密閉形ノズルヘツダ２０が使用さ
れている。開放型ノズルヘツダ１０においては、
給水管１１の下側に多数穿設された流出口１２よ
り注水された冷却水１３をスリツトノズル１４よ
り流出せしめて層流の吐出流１５を形成し、この
吐出流１５により熱鋼板を冷却させるのである。
又密閉型ノズルヘツダ２０においては、給水管２
２より給水された冷却水をタンク２１内に充満さ
せた上でスリツトノズル２３より流出させ、層流
の吐出流２４を得るものである。
For forced cooling or quenching of online hot steel sheets or reheated hot steel sheets in hot rolling equipment, it is suitable to use flat laminar flow, which has a large cooling capacity and uniform cooling in the width direction of the sheet. Conventionally, for this purpose, an open type nozzle header 10 shown in FIG. In the open nozzle header 10,
Cooling water 13 injected from a number of outlet ports 12 provided at the bottom of the water supply pipe 11 is made to flow out from the slit nozzle 14 to form a laminar discharge flow 15, and the hot steel plate is cooled by this discharge flow 15. be.
In addition, in the closed type nozzle header 20, the water supply pipe 2
A tank 21 is filled with cooling water supplied from a tank 21 and then discharged from a slit nozzle 23 to obtain a laminar discharge flow 24.
ところでこのスリツトノズルの構造では、第４
図のノズル間隙ｔによつて層流を維持できる最低
流量があり、それ以下まで流量を絞つてゆくと、
スリツトノズル１４，２３の出口から空気を巻き
込んでスリツトノズル１４，２３からの吐出流は
不連続、不均一粒径の滴下水となり層流状態が維
持されない。また流量を増加させてゆくとノズル
からの吐出流速が早くなりスリツトノズルからの
吐出流１５，２４が乱流状態となつてフラツトラ
ミナフローが得られなくなる。 By the way, in the structure of this slit nozzle, the fourth
There is a minimum flow rate that can maintain laminar flow depending on the nozzle gap t in the figure, and if the flow rate is reduced below this,
Air is drawn in from the outlets of the slit nozzles 14 and 23, and the discharge flow from the slit nozzles 14 and 23 becomes discontinuous and drops water with non-uniform particle sizes, and a laminar flow state is not maintained. Further, as the flow rate increases, the velocity of the discharge flow from the nozzle increases, and the discharge flows 15 and 24 from the slit nozzle become turbulent, making it impossible to obtain a flat laminar flow.
第５図はこの関係を示すグラフで、縦軸はスリ
ツトノズルを通る流量（m3／min.ｍ）、横軸はス
リツトノズルの間隙（ｔ）mmである。曲線Ａ，Ｂ
の間が層流領域で、Ｂはフラツトラミナフローを
維持するための下限水量を示す曲線、又曲線Ａよ
り上は乱流領域である。この関係から従来の単一
のスリツトノズルでは、流量を制御できる範囲は
最大／最小の流量比でせいぜい５倍程度である。 FIG. 5 is a graph showing this relationship, where the vertical axis is the flow rate (m 3 /min.m) passing through the slit nozzle, and the horizontal axis is the gap (t) mm between the slit nozzles. Curves A, B
The area between them is the laminar flow region, the curve B indicates the lower limit water amount for maintaining a flat laminar flow, and the area above curve A is the turbulent flow region. From this relationship, with a conventional single slit nozzle, the range in which the flow rate can be controlled is at most about five times the maximum/minimum flow rate ratio.
なお、ここで云う層流とは理論的な層流の定
義、例えばレイノズル数Re≒2000によつて規定
されるそれではなく、スリツトノズル中を水が充
満してかつ平板状に連続して流れることのできる
最低流速を下限とし、吐出流が被冷却体に衝突し
た際平板状流の殆んどが飛散してしまい、被冷却
体面上を平行流となつて流れなくなるような速い
流速を上限とする流れとして規定するものであ
る。 Note that the laminar flow referred to here is not the theoretical definition of laminar flow, for example, defined by the Ray-Nozzle number Re≒2000, but rather the flow that is defined by water filling a slit nozzle and flowing continuously in a flat plate shape. The lower limit is the minimum flow velocity that can be achieved, and the upper limit is a flow velocity that is so fast that when the discharge flow collides with the object to be cooled, most of the flat flow is scattered, becoming a parallel flow on the surface of the object to be cooled and no longer flowing. It is defined as a flow.
従来のフラツトラミナフローヘツダは上述の如
きものであり、制御しうる流量の範囲が比較的小
さいため、各種板厚の高温鋼板を所定の温度まで
冷却するのに不充分であつたり、冷却速度を調整
しようとしても調整しきれないことがあつた。こ
の改善策として例えば実願昭58−66897号に示す
ようなノズル先端部にスリツト状開口部を調整す
る押圧装置を設けたギヤツプ可変のスリツトノズ
ルが考案されているが、この方法によると構造が
複雑となり設備費も大きくなる欠点がある。
Conventional flat laminar flow headers are as described above, and because the range of flow rate that can be controlled is relatively small, it may be insufficient to cool high-temperature steel plates of various thicknesses to a predetermined temperature, or the cooling rate may be insufficient. Even when I tried to adjust the speed, there were times when I couldn't adjust it completely. As an improvement measure for this problem, a slit nozzle with a variable gap has been devised, as shown in Utility Application No. 58-66897, in which a pressing device is installed at the tip of the nozzle to adjust the slit-shaped opening, but this method requires a complicated structure. This has the disadvantage of increasing equipment costs.
またフラツトラミナフローによる高温鋼板の冷
却においては、板幅方向の流量分布が均等である
こと、すなわちスリツトノズルの間隙ｔを板幅方
向全幅に亘つて均一にすることが板幅方向の冷却
を均一ならしめるための条件であるが、被冷却高
温鋼板の板幅が広くなればなる程スリツトノズル
の長辺ｗも大きくなり、スリツトノズル加工中に
生じる熱歪などのため加工精度は低下し、スリツ
トノズルの間隙ｔを全幅に亘つて均等に製作する
ことは困難である。この結果板幅方向の流量分布
のバラツキは15％にも及んでいた。 In addition, when cooling a high-temperature steel plate using flat laminar flow, uniform cooling in the sheet width direction is achieved by making the flow rate distribution uniform in the sheet width direction, that is, making the gap t of the slit nozzle uniform over the entire width of the sheet. As for the conditions for smoothing, the wider the plate width of the high-temperature steel plate to be cooled, the larger the long side w of the slit nozzle becomes, and the processing accuracy decreases due to thermal distortion that occurs during slit nozzle processing, and the gap between the slit nozzles decreases. It is difficult to manufacture t uniformly over the entire width. As a result, the variation in flow rate distribution in the plate width direction was as much as 15%.
又第４図ｂに示す密閉型ノズルヘツダ構造にお
いては、ヘツダ内に外部から空気が侵入してくる
とノズルからの吐出流中に空気泡を巻き込み吐出
流が乱れて冷却能力が低下するだけでなく安定な
層流状態が維持できなくなる。従つてこのような
密閉型ノズルヘツダ構造においては、ノズルヘツ
ダの外部とのシールを強化するとともに、供給水
からの空気の侵入を防止する配慮が必要になつて
くる。 In addition, in the closed type nozzle header structure shown in Fig. 4b, if air enters the header from the outside, air bubbles will be drawn into the discharge flow from the nozzle, which will disrupt the discharge flow and not only reduce the cooling capacity. A stable laminar flow state cannot be maintained. Therefore, in such a closed nozzle header structure, it is necessary to strengthen the seal with the outside of the nozzle header and to take precautions to prevent air from entering from the supplied water.
本発明の目的は、以上述べたような種々な問題
点を解消した構造簡単で流量制御範囲の広い安定
したフラツトラミナフローヘツダを提供しようと
するものである。 An object of the present invention is to provide a stable flat laminar flow header with a simple structure and a wide flow control range, which solves the various problems described above.
以上の目的を達成するため、本発明はヘツダに
おいて一個の側壁の上辺に水平流路を形成する平
板状ノズルを設け、ヘツダ内の冷却水が該側壁を
オーバフローし、上記平板状ノズルを経てその先
端より層状の吐出流となつて落下するように構成
した。
In order to achieve the above object, the present invention provides a header with a flat nozzle forming a horizontal flow path on the upper side of one side wall, so that the cooling water in the header overflows the side wall and passes through the flat nozzle. It was configured so that it falls from the tip in a laminar discharge stream.
ヘツダを上述のように構成した結果、平板状ノ
ズルの先端より落下する吐出流は層流となるだけ
でなく、特に重要なことは冷却水水面が乱れない
ことである。一般に従来のヘツダでは供給水の動
圧の影響をうけ、ヘツダ内の冷却水は少なからず
乱流状態となり第４図ａの冷却水水面１６も乱れ
るものである。このような乱れがあるとノズルの
板幅方向の流量分布も不均一となる。この乱れを
防止する一方法としてヘツダの容積を供給水の動
圧が減衰して水面に影響を与えない程度にまで大
きくすることが考えられるが、ヘツダの構造が大
規模のものとなり、ライン上その他に設置するこ
とは困難である。しかし本発明のようにヘツダよ
りオーバフローした冷却水をほゞ水平方向に流す
ような水平流路を持つ平板状ノズルより落下させ
る方法では、このような問題は容易に解決され
る。たといヘツダ内の冷却水水面が乱れていても
オーバフローした冷却水が平板状ノズルを水平方
向に流れることにより整流化され平板状ノズルの
先端より落下する層流状吐出流の水膜の厚さは板
幅方向に均等となる。
As a result of configuring the header as described above, not only does the discharge flow falling from the tip of the flat nozzle become a laminar flow, but what is especially important is that the cooling water surface is not disturbed. Generally, in a conventional header, the cooling water inside the header is affected by the dynamic pressure of the supplied water, and the cooling water in the header becomes quite turbulent, and the cooling water surface 16 shown in FIG. 4a is also disturbed. When such disturbance occurs, the flow rate distribution in the nozzle plate width direction also becomes non-uniform. One way to prevent this turbulence is to increase the volume of the header to the extent that the dynamic pressure of the supplied water is attenuated and does not affect the water surface, but this would require a large-scale header structure and It is difficult to install it elsewhere. However, such problems can be easily solved by the method of the present invention, in which the cooling water that overflows from the header is dropped from a flat nozzle having a horizontal flow path that allows the cooling water to flow in a substantially horizontal direction. Even if the cooling water surface in the header is turbulent, the overflowing cooling water flows horizontally through the flat nozzle and is rectified, and the thickness of the water film of the laminar discharge flow that falls from the tip of the flat nozzle is It becomes uniform in the board width direction.
また平板状ノズルは、上面大気開放型であるか
ら従来のスリツトノズルのようにノズルの間隙ｔ
によつて最低流量が決つてしまうようなこともな
く、一個のノズルヘツダで流量を０〜５m3／
min.ｍの広い範囲で自由に調整できるので、冷
却能力の制御範囲も大幅に拡大できる。 In addition, since the flat plate nozzle has an upper surface open to the atmosphere, the nozzle gap t is different from that of the conventional slit nozzle.
The minimum flow rate is not determined by
Since it can be freely adjusted over a wide range of min.m, the control range of cooling capacity can be greatly expanded.
第１図ａ，ｂは本発明の実施例を示す側面図お
よび正面図である。１はノズルヘツダ、２は側
壁、３は平板状ノズル、４は給水管、５は流出
口、６は冷却水、７は冷却水水面、８は吐出流で
ある。
FIGS. 1a and 1b are a side view and a front view showing an embodiment of the present invention. 1 is a nozzle header, 2 is a side wall, 3 is a flat nozzle, 4 is a water supply pipe, 5 is an outlet, 6 is cooling water, 7 is a cooling water surface, and 8 is a discharge flow.
図のようにヘツダ１の側壁２の上辺にほゞ水平
な流路をもつ平板状ノズル３を設け、下面に多数
の流出口５を穿設した給水管４より供給された冷
却水６を側壁２をオーバフローし平板状ノズル３
を経てその先端より落下させると層流状の吐出流
８を得る。 As shown in the figure, a flat plate-shaped nozzle 3 with a nearly horizontal flow path is provided on the upper side of the side wall 2 of the header 1, and cooling water 6 supplied from a water supply pipe 4 having a number of outlet ports 5 perforated on the lower surface is applied to the side wall. 2 overflow and flat plate nozzle 3
When the discharge flow 8 is caused to fall from the tip thereof, a laminar discharge flow 8 is obtained.
ここで水平流路の必要長さＬについては、種々
実験の結果、次の(1)式で表わされる板幅方向の流
量分布のバラツキ
流量分布のバラツキ
＝最大流量−最少流量／平気流量×100 …(1)
を５％以内に収めるための最低必要長さＬは、次
の(2)式で表せることが判つた。 As a result of various experiments, the required length L of the horizontal flow path is determined by the following equation (1): It was found that the minimum required length L to keep (1) within 5% can be expressed by the following equation (2).
Ｌ＝25×Q1.7 ……(2)
ここで、Ｌ：水平流路の長さ、mm
Ｑ：流量 m3／min.ｍ
た上記最大流量、最少流量等は例えばノズル長
さ2500〜5000mmの場合、ノズル長さ方向100〜200
mm単位毎にノズルからの水量を適当な樋で受けて
測つたものである。 L = 25 In case, nozzle length direction 100~200
The amount of water from the nozzle was measured in units of mm by receiving it in an appropriate gutter.
第２図は上記(2)式をグラフで表わしたものであ
る。水平流路の長さＬはこの曲線Ｚよりも上の領
域であれば、板幅方向の流量分布のバラツキが５
％以内の均一なフラツトラミナーフローが得ら
れ、従来のものと比べはるかに優れたものとなる
から上記の関係を満す範囲のＬとすることが好ま
しい。 FIG. 2 is a graphical representation of the above equation (2). If the length L of the horizontal flow path is above this curve Z, the variation in flow rate distribution in the plate width direction will be 5.
It is preferable to set L within a range that satisfies the above relationship because a uniform flat laminar flow within 10% can be obtained and is far superior to conventional ones.
なお第３図は本発明の他の実施例を示すもの
で、ヘツダの側壁の上辺に設ける平板状ノズルの
位置は、第３図のようにヘツダの内側に位置して
もよい。また水平流路の取付け角度は水平方向に
対してプラス、マイナス15度以内の範囲にあれば
同じ結果が得られる。 Note that FIG. 3 shows another embodiment of the present invention, and the position of the flat nozzle provided on the upper side of the side wall of the header may be located inside the header as shown in FIG. Also, the same results can be obtained if the installation angle of the horizontal flow path is within a range of plus or minus 15 degrees with respect to the horizontal direction.
本発明はヘツダにおいてヘツダの側壁の上辺に
水平流路をもつ平板状ノズルを設けて、ヘツダの
冷却水を側壁をオーバフローさせ平板状ノズルを
経てその先端より落下させて層流状の吐出流を得
るように構成したので、
構造が簡単で製作が容易である。
In the present invention, a flat nozzle having a horizontal flow path is provided on the upper side of the side wall of the header in the header, and the cooling water of the header overflows the side wall and falls from the tip of the header through the flat nozzle, thereby creating a laminar discharge flow. The structure is simple and easy to manufacture.
製作上に起因する流量分布の不均一といつた
問題がない。 There are no problems such as uneven flow distribution caused by manufacturing.
平板状ノズルが上部開放型構造のため空気の
侵入に起因する吐出流の乱れがない。 Since the flat nozzle has an open top structure, there is no disturbance in the discharge flow due to air intrusion.
供給水の動圧に起因する乱れがない。 There is no turbulence caused by the dynamic pressure of the feed water.
などの優れた効果を上げることができた。We were able to achieve excellent results such as:
第１図ａ，ｂは本発明の一実施例を示す側面図
と正面図、第２図は水平流路の長さＬを求めるグ
ラフ、第３図ａ，ｂは本発明の他の実施例を示す
側面図および正面図である。又第４図ａ，ｂは従
来の装置を示す断面図および斜視図、第５図は従
来装置のスリツトキヤツプと流量に対する層流領
域を示すグラフである。
図中１はベツダ、２は側壁、３は平板状ノズ
ル、４は給水管、５はその流出口、６は冷却水、
７は冷却水水面、８は吐出流である。
Figures 1a and b are side and front views showing one embodiment of the present invention, Figure 2 is a graph for determining the length L of the horizontal flow path, and Figures 3a and b are other embodiments of the present invention. FIG. 2 is a side view and a front view showing the same. 4a and 4b are cross-sectional and perspective views of the conventional device, and FIG. 5 is a graph showing the laminar flow region with respect to the slot cap and flow rate of the conventional device. In the figure, 1 is the bed, 2 is the side wall, 3 is the flat nozzle, 4 is the water supply pipe, 5 is the outlet, 6 is the cooling water,
7 is the cooling water surface, and 8 is the discharge flow.
Claims (1)
の一個の側壁の上辺に水平流路を形成する平板状
ノズルを設け、上記フラツトラミナーノズルヘツ
ダ内の冷却水を上記側壁をオーバフローし上記平
板状ノズルを経て、その先端より落下せしめるよ
う構成するとともに、上記平板状ノズルの水平流
路の最低必要長さＬ（mm）を、流量をＱ（m3／
min，ｍ）としたとき、次式 Ｌ＝25×Q1.7 により規定したことを特徴とするフラツトラミナ
ーノズルヘツダ。[Claims] 1. In a flat laminar nozzle header, a flat nozzle forming a horizontal flow path is provided on the upper side of one side wall of the flat laminar nozzle header, and the cooling water in the flat laminar nozzle header overflows the side wall. In addition, the horizontal flow path of the flat nozzle is configured to have a minimum required length L (mm) and a flow rate Q (m 3 /
A flat laminar nozzle header characterized in that it is defined by the following formula L=25×Q 1.7 , where min, m).
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22227784A JPS61103616A (en) | 1984-10-24 | 1984-10-24 | Flat laminar nozzle header |
| GB08524678A GB2165784B (en) | 1984-10-24 | 1985-10-07 | Nozzle header for producing a flat laminar flow |
| DE19853537508 DE3537508A1 (en) | 1984-10-24 | 1985-10-22 | NOZZLE DISTRIBUTION HEAD FOR GENERATING A FLAT LAMINARY FLOW |
| FR8515657A FR2571984B1 (en) | 1984-10-24 | 1985-10-22 | ADJUSTABLE DISPENSER FOR PRODUCING A FLAT LAMINARY FLOW |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22227784A JPS61103616A (en) | 1984-10-24 | 1984-10-24 | Flat laminar nozzle header |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61103616A JPS61103616A (en) | 1986-05-22 |
| JPS6330085B2 true JPS6330085B2 (en) | 1988-06-16 |
Family
ID=16779850
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22227784A Granted JPS61103616A (en) | 1984-10-24 | 1984-10-24 | Flat laminar nozzle header |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61103616A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101128597B1 (en) * | 2008-02-20 | 2012-03-27 | 히로시 미치와키 | Double-end threaded body and internally-threaded body |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5512081B2 (en) * | 1974-04-24 | 1980-03-29 |
-
1984
- 1984-10-24 JP JP22227784A patent/JPS61103616A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61103616A (en) | 1986-05-22 |
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