JPS638174B2 - - Google Patents
Info
- Publication number
- JPS638174B2 JPS638174B2 JP23498483A JP23498483A JPS638174B2 JP S638174 B2 JPS638174 B2 JP S638174B2 JP 23498483 A JP23498483 A JP 23498483A JP 23498483 A JP23498483 A JP 23498483A JP S638174 B2 JPS638174 B2 JP S638174B2
- Authority
- JP
- Japan
- Prior art keywords
- nozzle
- strip
- cooling
- header
- plate
- 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
- 238000001816 cooling Methods 0.000 claims description 43
- 239000000112 cooling gas Substances 0.000 claims description 26
- 239000007789 gas Substances 0.000 claims description 18
- 239000002184 metal Substances 0.000 description 20
- 229910000831 Steel Inorganic materials 0.000 description 10
- 239000010959 steel Substances 0.000 description 10
- 238000002474 experimental method Methods 0.000 description 6
- 230000007547 defect Effects 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000000137 annealing Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000005246 galvanizing Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
- C21D9/52—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor for wires; for strips ; for rods of unlimited length
- C21D9/54—Furnaces for treating strips or wire
- C21D9/56—Continuous furnaces for strip or wire
- C21D9/573—Continuous furnaces for strip or wire with cooling
Landscapes
- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Crystallography & Structural Chemistry (AREA)
- Mechanical Engineering (AREA)
- Materials Engineering (AREA)
- Metallurgy (AREA)
- Organic Chemistry (AREA)
- Heat Treatment Of Strip Materials And Filament Materials (AREA)
Description
【発明の詳細な説明】
本発明は帯板を走行中に冷却するガスジエツト
冷却装置の改良に関し、特に鋼板の連続焼鈍や亜
鉛メツキの際に用いて好適なものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a gas jet cooling device for cooling a strip while it is running, and is particularly suitable for use in continuous annealing or galvanizing of steel plates.
鋼板等の帯板の製造に際して行なわれる連続焼
鈍や亜鉛メツキを連続して行なう亜鉛メツキライ
ンにあつては、帯板の冷却が必要であり、この冷
却の良否により製品の特性や品質が大きな影響を
受けるため種々の冷却装置が提案されている。 In galvanizing lines that perform continuous annealing and continuous galvanizing when manufacturing strips such as steel plates, it is necessary to cool the strips, and the quality and characteristics of the product are greatly affected by the quality of this cooling. Various cooling devices have been proposed to accommodate this problem.
例えば、連続焼鈍炉等における金属ストリツプ
の冷却装置のひとつに、第１図に示すようなガス
ジエツト冷却装置が知られている。このガスジエ
ツト冷却装置では、所定の間隔を隔てて２つの支
持ロール１，１ａが設置され、この２つの支持ロ
ール１，１ａ間を金属ストリツプ２が走行するよ
うになつており、２つのロール１，１ａ間に位置
し且つ金属ストリツプ２の表裏面を挾んで一対の
ヘツダ３，３ａが設置されヘツダ３，３ａの表面
に形成されたスリツト状もしくは円形のノズル４
から図示しないブロワ等で圧送される冷却ガス５
を噴出させて冷却している。 For example, a gas jet cooling device as shown in FIG. 1 is known as one of the cooling devices for metal strips in continuous annealing furnaces and the like. In this gas jet cooling device, two support rolls 1, 1a are installed at a predetermined interval, and a metal strip 2 runs between the two support rolls 1, 1a. A pair of headers 3, 3a are installed between the metal strip 2 and the front and back surfaces of the metal strip 2, and a slit-shaped or circular nozzle 4 is formed on the surface of the headers 3, 3a.
Cooling gas 5 is pumped by a blower or the like (not shown) from
It is cooled by ejecting water.
このようなガスジエツト冷却装置における冷却
能力は冷却ガス５と金属ストリツプ２間の熱伝達
率に左右され、この熱伝達率に対してはノズル４
と金属ストリツプ２との距離、すなわちノズル間
隙Ｌが大きな影響を与える。つまり、ノズル４か
ら噴射された冷却ガス５の速度はノズル間隙Ｌが
大きくなるにしたがつて減少し、金属ストリツプ
２の表面に衝突する冷却ガス５の速度が小さくな
つて熱伝達率が小さくなる。 The cooling capacity of such a gas jet cooling device depends on the heat transfer coefficient between the cooling gas 5 and the metal strip 2, and for this heat transfer coefficient, the nozzle 4
The distance between the nozzle and the metal strip 2, that is, the nozzle gap L, has a large influence. In other words, the velocity of the cooling gas 5 injected from the nozzle 4 decreases as the nozzle gap L increases, the velocity of the cooling gas 5 colliding with the surface of the metal strip 2 decreases, and the heat transfer coefficient decreases. .
したがつて、効果的に冷却を行なうためには、
このノズル間隙Ｌを小さくすることが肝要であ
る。 Therefore, for effective cooling,
It is important to make this nozzle gap L small.
ところが、上記ガスジエツト冷却装置では冷却
後の金属ストリツプ２の反り等の変形や金属スト
リツプ２の表裏面とそれぞれ対向するヘツダ３，
３ａ内の圧力バランスや冷却装置前後の設備によ
つて起因する振動等による金属ストリツプの振れ
により金属ストリツプ２がノズル４に接触し、い
わゆるすりきずが発生する恐れがあるためノズル
間隔Ｌを小さくすることに限度があり、通常100
mm以下とすることができず熱伝達率も小さい。こ
のため所定の冷却能力を得るためには、大きなブ
ロワと大動力を必要とする欠点がある。 However, in the above-mentioned gas jet cooling device, the metal strip 2 may be deformed after cooling, such as warping, or the headers 3, which face the front and back surfaces of the metal strip 2, respectively.
The nozzle interval L is made small because there is a risk that the metal strip 2 may come into contact with the nozzle 4 due to vibrations caused by the pressure balance in the nozzle 3a or the equipment before and after the cooling device, causing so-called scratches. There is a limit, usually 100
mm or less, and the heat transfer coefficient is also low. Therefore, in order to obtain a predetermined cooling capacity, a large blower and a large amount of power are required.
そこで、金属ストリツプの変形や振れを吸収し
てノズル間隙Ｌを小さくできるものとして第２図
に示すようなガスジエツト冷却装置が提案されて
いる。 Therefore, a gas jet cooling device as shown in FIG. 2 has been proposed as a device that can reduce the nozzle gap L by absorbing the deformation and vibration of the metal strip.
このガスジエツト冷却装置では、冷却位置に大
径の回転ドラム６を設置し、この回転ドラム６に
金属ストリツプ２を巻き掛けると共に張力を与え
ながら走行させ、この回転ドラム６と金属ストリ
ツプ２を挾んで対向する位置に回転ドラム６と同
心の円弧を有し断面が略扇形とされたヘツダ７が
設置され、ヘツダ７の表面に形成したスリツト状
ないし円形のノズル８から図示しないブロワー等
で圧送される冷却ガス５を噴出させて冷却してい
る。 In this gas jet cooling system, a large-diameter rotating drum 6 is installed at a cooling position, a metal strip 2 is wound around the rotating drum 6, and the metal strip 2 is run while applying tension, and the rotating drum 6 and the metal strip 2 are sandwiched between the drum 6 and the metal strip 2. A header 7 having an arc concentric with the rotary drum 6 and having a substantially sector-shaped cross section is installed at a position where the header 7 has a circular arc concentric with the rotating drum 6, and cooling is pumped through a slit-shaped or circular nozzle 8 formed on the surface of the header 7 by a blower or the like (not shown). It is cooled by blowing out gas 5.
このようなガスジエツト冷却装置では金属スト
リツプ２がノズル８と接触する恐れが無いことか
らノズル間隙Ｌを小さくでき、高い熱伝達率が得
られるという利点があるが、金属ストリツプ２の
板幅方向の熱伝達率分布が大きくなる。 Such a gas jet cooling device has the advantage that the nozzle gap L can be made small because there is no risk of the metal strip 2 coming into contact with the nozzle 8, and a high heat transfer coefficient can be obtained. The transmissibility distribution becomes larger.
これは、第３図に金属ストリツプ２表面での冷
却ガス５の流れを示すように、ノズル８から噴射
された冷却ガス５は金属ストリツプ２の表面に衝
突したのちノズル間隙Ｌ部分を図中、矢印で示す
ように板幅方向端部に向つて流れ、端部にて排出
されるため端部に近い程冷却ガス５の排出速度が
大きくなつて熱伝達率も大きくなる。この傾向は
ノズル８と金属ストリツプ２との距離、すなわち
ノズル間隙Ｌが小さくなればなる程冷却ガス５の
流路が狭くなるため著しくなり、不均一冷却の度
合が大きくなる。 This is because, as shown in FIG. 3, which shows the flow of cooling gas 5 on the surface of metal strip 2, cooling gas 5 injected from nozzle 8 collides with the surface of metal strip 2, and then passes through the nozzle gap L in the figure. As shown by the arrow, the cooling gas 5 flows toward the ends in the width direction of the plate and is discharged at the ends, so that the closer to the ends the discharge speed of the cooling gas 5 increases and the heat transfer coefficient also increases. This tendency becomes more pronounced as the distance between the nozzle 8 and the metal strip 2, that is, the nozzle gap L, becomes smaller, because the flow path of the cooling gas 5 becomes narrower, and the degree of non-uniform cooling increases.
本発明はかかる従来の欠点を解消し、ノズルを
金属ストリツプ等の帯板に接近させることで冷却
能力を高くできると共に板幅方向にも均一に冷却
することのできる帯板のガスジエツト冷却装置の
提供を目的とする。かかる目的を達成する本発明
の構成は高温の帯板が巻き掛けられる回転ドラム
と対向して冷却ガスが圧送されるヘツダを設置す
ると共にヘツダから突き出してノズルを前記帯板
の板幅方向に取付ける一方、ノズルの前記帯板の
走行方向の開口幅をｄ、ヘツダからのノズルの突
出長をｌ、ノズル先端から帯板までのノズル間隙
をＬとしたときＬ≦6d且つｌ≧（10d−Ｌ）なる
関係としたことを特徴とする。 The present invention eliminates such conventional drawbacks and provides a gas jet cooling device for a strip, which can increase the cooling capacity by bringing the nozzle close to the strip such as a metal strip, and can uniformly cool the strip in the width direction. With the goal. The structure of the present invention that achieves this object is to install a header through which cooling gas is pumped facing a rotating drum around which a high-temperature strip is wound, and to install a nozzle protruding from the header in the width direction of the strip. On the other hand, when the opening width of the nozzle in the running direction of the strip plate is d, the protrusion length of the nozzle from the header is l, and the nozzle gap from the nozzle tip to the strip plate is L, L≦6d and l≧(10d−L ).
以下、本発明の実施例を図面に基づき詳細に説
明する。 Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
第４図は本発明の帯板のガスジエツト冷却装置
の一実施例にかかる横断面図である。 FIG. 4 is a cross-sectional view of one embodiment of the strip gas jet cooling device of the present invention.
高温の帯板１０が巻き掛けられる大径の回転ド
ラム１１が冷却位置に対応して設置され、この回
転ドラム１１と帯板１０を挾んで対向して断面が
回転ドラム１１と同心の円弧で略扇形とされたヘ
ツダ１２が設置してあり、ヘツダ１２の回転ドラ
ム１１と対向面に長さｌだけ突き出したスリツト
状のノズル１３が帯板１０の板幅方向と平行でし
かも先端が回転ドラム１１の中心に向くよう多数
（図示例では９個）並設してある。そして、ノズ
ル１３先端と回転ドラム１１に所定の張力が付与
されて巻き掛けられる帯板１０の表面との距離、
すなわちノズル間隙がＬとしてあり、ノズル１３
のスリツト幅をｄとしたとき上記ノズル１３の突
出長ｌとノズル間隙Ｌとの間で次式(1)，(2)の関係
を満足するようにしてある。 A large-diameter rotating drum 11 on which the high-temperature strip plate 10 is wound is installed corresponding to the cooling position, and the rotating drum 11 and the strip plate 10 are opposed to each other, and the cross section is approximately an arc concentric with the rotating drum 11. A fan-shaped header 12 is installed, and a slit-shaped nozzle 13 protruding by a length l from the surface facing the rotating drum 11 of the header 12 is parallel to the width direction of the strip plate 10, and the tip thereof is connected to the rotating drum 11. A large number (nine in the illustrated example) are arranged in parallel so as to face the center of the figure. The distance between the tip of the nozzle 13 and the surface of the band plate 10 that is wound around the rotating drum 11 with a predetermined tension applied thereto,
That is, the nozzle gap is L, and the nozzle 13
When the slit width is d, the relationship between the protruding length l of the nozzle 13 and the nozzle gap L satisfies the following equations (1) and (2).
Ｌ≦6d ……(1)
ｌ＋Ｌ≧10d ……(2)
また、ヘツダ１２には、図示しないブロワ等が
接続され冷却ガスが圧送されるようになつてい
る。L≦6d (1) l+L≧10d (2) Further, a blower (not shown) or the like is connected to the header 12 so that cooling gas is fed under pressure.
かように構成した帯板のガスジエツト冷却装置
では、高温の帯板１０を回転ドラム１１に巻き掛
け所定の張力を与えながら走行させておき、ヘツ
ダ１２に図示しないブロワ等から冷却ガスを圧送
してノズル１３から噴射される冷却ガス１４によ
つて走行中の帯板１０を冷却する。 In the strip gas jet cooling device constructed as described above, the hot strip 10 is wound around the rotating drum 11 and run while applying a predetermined tension, and cooling gas is force-fed to the header 12 from a blower or the like (not shown). The running strip 10 is cooled by the cooling gas 14 injected from the nozzle 13.
こうしてヘツダ１２から突出長ｌだけ突き出し
たノズル１３で冷却することで、冷却ガス１４は
帯板１０の表面に衝突したのち、隣接するノズル
１３間およびヘツダ１２表面と帯板１０で形成さ
れる空間を流路として帯板１０の板幅方向に流れ
端部にて排出される。 In this way, by cooling with the nozzle 13 protruding from the header 12 by the protruding length l, the cooling gas 14 collides with the surface of the strip plate 10, and then the space formed between adjacent nozzles 13 and between the surface of the header 12 and the strip plate 10. is used as a flow path in the width direction of the strip plate 10 and is discharged at the end.
このようにして本冷却装置では、帯板１０を回
転ドラム１１に巻き掛けた状態で冷却するので、
帯板１０の反り等の変形や振れが吸収されるノズ
ル１３との接触の心配がなく、ノズル１３先端を
帯板１０に接近して設けることができ小さなノズ
ル間隙Ｌで高い熱伝達率が得られる。 In this way, in this cooling device, since the strip plate 10 is cooled while being wrapped around the rotating drum 11,
There is no need to worry about contact with the nozzle 13, which absorbs deformation such as warpage or vibration of the strip plate 10, and the tip of the nozzle 13 can be provided close to the strip plate 10, resulting in a high heat transfer coefficient with a small nozzle gap L. It will be done.
この場合のノズル間隙Ｌはノズル１３のスリツ
ト幅ｄ（円孔ノズルではノズル径ｄ）に対し最適
な範囲がある。そこで、これらノズル間隙Ｌおよ
びスリツト幅ｄに対する熱伝達率αの変化を調
べ、この結果を第５図に示した。同図において横
軸はノズル間隙Ｌとスリツト幅ｄとの比Ｌ／ｄ
を、縦軸はノズル間隙ＬをＬ＝6dとしたときの
熱伝達率α0を基準とした熱伝達率比α／α0をとつ
たものであり、同図から明らかなように、Ｌ／ｄ
≦６の範囲、すなわちＬ≦6dの範囲で最も高い
熱伝達率αが得られる。 In this case, the nozzle gap L has an optimum range with respect to the slit width d of the nozzle 13 (the nozzle diameter d in the case of a circular hole nozzle). Therefore, changes in the heat transfer coefficient α with respect to the nozzle gap L and the slit width d were investigated, and the results are shown in FIG. In the same figure, the horizontal axis is the ratio L/d of the nozzle gap L and the slit width d.
The vertical axis is the heat transfer coefficient ratio α/α 0 based on the heat transfer coefficient α 0 when the nozzle gap L is L=6d, and as is clear from the figure, L/α d
The highest heat transfer coefficient α is obtained in the range of ≦6, that is, in the range of L≦6d.
尚、第１図に示した従来装置では、ノズル間隙
Ｌが100mm以上とせざるを得ず、スリツト幅ｄが
例えば３mmのノズルを用いたとしてもＬ／α≒33
となり、第５図から最大冷却能力の60％弱となつ
てしまつていたことがわかる。 In the conventional device shown in Fig. 1, the nozzle gap L has to be 100 mm or more, and even if a nozzle with a slit width d of, for example, 3 mm is used, L/α≒33
As can be seen from Figure 5, the cooling capacity was less than 60% of the maximum.
また、ノズル１３がヘツダ１２から突出長ｌだ
け突き出して取付けてあるので、冷却ガス１４は
帯板１０に衝突したのち隣接するノズル１３間お
よびヘツダ１２表面と帯板１０で形成される広い
空間に流出するためその流速が急激に減少し、こ
の衝突後の冷却ガス１４の熱伝達率αを極めて小
さくでき事実上均一に冷却することができるので
ある。 In addition, since the nozzle 13 is installed so as to protrude from the header 12 by a length l, the cooling gas 14 collides with the strip plate 10 and then flows between adjacent nozzles 13 and into the wide space formed by the surface of the header 12 and the strip plate 10. As the cooling gas 14 flows out, its flow velocity decreases rapidly, and the heat transfer coefficient α of the cooling gas 14 after the collision can be made extremely small, making it possible to cool the cooling gas 14 virtually uniformly.
ここで、帯板１０を均一に冷却することは形状
不良等の発生防止に有効であるが、この冷却には
帯板１０の板幅方向の温度差ΔTが大きな影響を
及ぼす。そこで、この温度差ΔTに対する帯板の
形状不良発生に及ぼす影響について調べるため実
験を行ないその結果を第６図に示した。本実験は
板厚が0.5〜1.2mm、板幅が1200mmの多数の鋼帯を
0.5〜３Kg／mm2の張力で回転ドラム１１に巻き掛
けながらガスジエツトで冷却を行なつたものであ
り、図中の〇印は形状が良好な場合を、△印はや
や不良の場合で、冷却後の鋼帯に多少の反りが生
じた程度を、×印は不良の場合で、大きな耳波や
絞りが発生した程度をそれぞれ示す。本実験結果
によれば形状不良の発生に関して板厚や張力はさ
ほど大きな影響を及ぼさず、また、第６図から明
らかなように、温度差ΔTがΔT≦20℃の範囲で
あれば鋼帯温度Ｔによらず常に形状が良好な鋼帯
が得られることがわかる。 Here, uniformly cooling the strip 10 is effective in preventing the occurrence of shape defects, but the temperature difference ΔT in the width direction of the strip 10 has a large effect on this cooling. Therefore, an experiment was conducted to investigate the influence of this temperature difference ΔT on the occurrence of shape defects in the strip, and the results are shown in FIG. In this experiment, a large number of steel strips with a thickness of 0.5 to 1.2 mm and a width of 1200 mm were used.
It was cooled by a gas jet while being wrapped around a rotating drum 11 with a tension of 0.5 to 3 Kg/ mm2 . In the figure, ○ marks indicate cases in which the shape is good, and △ marks indicate cases in which the shape is slightly defective. The mark "x" indicates the extent to which some warping occurred in the subsequent steel strip, and the mark "x" indicates the extent to which large ear waves or apertures occurred. According to the results of this experiment, the plate thickness and tension do not have a very large effect on the occurrence of shape defects, and as is clear from Figure 6, if the temperature difference ΔT is in the range ΔT≦20℃, the steel strip temperature It can be seen that a steel strip with a good shape can always be obtained regardless of T.
次に、この範囲に温度差ΔTを抑えるために必
要な熱伝達率αの範囲について調べるため、初期
温度800℃の鋼板を冷却した場合の板幅方向中央
の熱伝達率αcと端部の熱伝達率αeの違いによつて
生ずる鋼板の温度差ΔTについて調べ、その結果
を第７図に示した。同図において、横軸は鋼板の
平均温度Ｔ、縦軸は板幅方向の最大温度差ΔTで
あり、実験には板幅1200mmのものを用いた。同図
から明らかなように、最大温度差ΔTをΔT≦20
℃とするためには、熱伝達率比αe／αcをαe／αc≦
1.08にする必要がある。つまり、板幅方向端部の
熱伝達率αeの増大を８％以内にすれば常に形状の
良好な鋼板が得られるのである。 Next, in order to investigate the range of heat transfer coefficient α required to suppress the temperature difference ΔT within this range, we will investigate the heat transfer coefficient α c at the center in the width direction and the The temperature difference ΔT between steel plates caused by the difference in heat transfer coefficient α e was investigated, and the results are shown in FIG. In the figure, the horizontal axis is the average temperature T of the steel plate, and the vertical axis is the maximum temperature difference ΔT in the width direction of the steel plate, and a plate width of 1200 mm was used in the experiment. As is clear from the figure, the maximum temperature difference ΔT is ΔT≦20
To set the heat transfer coefficient ratio α e /α c to α e /α c ≦
It needs to be 1.08. In other words, if the increase in the heat transfer coefficient α e at the ends in the sheet width direction is kept within 8%, a steel sheet with a good shape can always be obtained.
さらに、第８図には、ノズル１３と帯板１０と
の距離、すなわちノズル間隙Ｌをスリツト幅ｄの
６倍（Ｌ＝6d）とした場合において、ノズル１
３のヘツダ１２からの突出長ｌを変化させた場合
の熱伝達率αの変化を示した。同図において、横
軸はヘツダ１２から帯板１０表面までの長さｌ＋
Ｌとスリツト幅ｄとの比（ｌ＋Ｌ）／ｄを、縦軸
は板幅方向中央の熱伝達率αcと端部の熱伝達率αe
の比αe／αcをそれぞれ示し、冷却ガス噴出速度ｖ
をパラメータとしたものである。 Furthermore, in FIG. 8, when the distance between the nozzle 13 and the strip plate 10, that is, the nozzle gap L, is six times the slit width d (L=6d), the nozzle 1
The change in the heat transfer coefficient α when the protrusion length l from the header 12 of No. 3 is changed is shown. In the figure, the horizontal axis is the length l+ from the header 12 to the surface of the strip plate 10.
The ratio (l+L)/d of L and slit width d is shown, and the vertical axis is the heat transfer coefficient α c at the center in the plate width direction and the heat transfer coefficient α e at the edge.
The ratio α e /α c is respectively shown, and the cooling gas ejection velocity v
is the parameter.
尚、実験はスリツト幅ｄ＝３mm、スリツトピツ
チ10mm、板幅1200mmとした場合である。 The experiment was conducted with a slit width d = 3 mm, a slit pitch of 10 mm, and a plate width of 1200 mm.
同図より、均一な冷却に必要な熱伝達率比αe／
αc≦1.08とするには、少なくとも（ｌ＋Ｌ）／ｄ
≒10とする必要があることがわかる。すなわち、
（ｌ＋Ｌ）／ｄ≧10とすることにより板幅方向に
均一に冷却することができ形状不良の生じない冷
却ができるのである。 From the same figure, the heat transfer coefficient ratio α e / required for uniform cooling is
To make α c ≦1.08, at least (l+L)/d
It can be seen that it is necessary to set it to ≒10. That is,
By setting (l+L)/d≧10, uniform cooling can be achieved in the width direction of the plate, and cooling can be performed without causing shape defects.
以上のように、ヘツダ１２からノズル１３を突
出長ｌだけ突き出させると共にノズル１３と帯板
１０との距離であるノズル間隙をＬとした場合に
ノズル１３のスリツト幅ｄとの間で
Ｌ≦6d、ｌ≧10d―Ｌ
なる関係を満足するようガスジエツト冷却装置を
構成することで、常に形状不良が生ずることなく
均一に冷却できると共に熱伝達率を高くして冷却
能力を増大できる。 As described above, when the nozzle 13 is made to protrude from the header 12 by the protrusion length l, and the nozzle gap, which is the distance between the nozzle 13 and the strip plate 10, is L, the slit width d of the nozzle 13 is L≦6d. , l≧10d−L By configuring the gas jet cooling device so as to satisfy the following relationship, it is possible to uniformly cool the cooling device without causing shape defects at all times, and to increase the cooling capacity by increasing the heat transfer coefficient.
次に、本発明の他の実施例について第９図によ
り説明する。 Next, another embodiment of the present invention will be described with reference to FIG.
本実施例はノズル１３での圧力損失を低減でき
るようにしたものであり、ヘツダ１２とノズル１
３との連結部１３ａを滑らかな曲面としてある。
尚、他の構成は上記実施例と同一であり、ノズル
１３の突出長ｌ、ノズル間隙Ｌ、ノズル１３のス
リツト幅ｄの関係も上記(1)，(2)式を満足するよう
にしてある。 This embodiment is designed to reduce the pressure loss at the nozzle 13, and the header 12 and nozzle 1
The connecting portion 13a with 3 is a smooth curved surface.
Note that the other configurations are the same as in the above embodiment, and the relationship among the protrusion length l of the nozzle 13, the nozzle gap L, and the slit width d of the nozzle 13 is also made to satisfy the above equations (1) and (2). .
本実施例装置によれば、ヘツダ１２とノズル１
３とを曲面で連結することで、曲面としない第１
０図の場合のようにノズル１３内で縮流が起り圧
力損失が増大することなく、冷却ガスが曲面に沿
つて剥離することなく流れてノズル１３先端から
噴射されるので圧力損失が低減でき、実験によれ
ば、第１０図のものに比べ約20％圧力損失が低減
できた。 According to the device of this embodiment, the header 12 and the nozzle 1
By connecting 3 with a curved surface, the first
Unlike the case in Figure 0, the pressure loss does not increase due to contracted flow within the nozzle 13, and the cooling gas flows along the curved surface without separation and is injected from the tip of the nozzle 13, reducing the pressure loss. According to experiments, the pressure loss could be reduced by about 20% compared to the one shown in Figure 10.
また、第１１図に示す実施例では、ヘツダ１２
とノズル１３との連結部１３ａを滑らかな曲面と
すると共にノズル１３を先細ノズルとしたもので
あり、他の構成は上記実施例と同一で、ノズル１
３の突出長ｌ、ノズル間隙Ｌ、ノズル１３のスリ
ツト幅ｄの関係も上記(1)，(2)式を満足するように
してある。 Further, in the embodiment shown in FIG. 11, the header 12
The connecting portion 13a between the nozzle 13 and the nozzle 13 has a smooth curved surface, and the nozzle 13 is a tapered nozzle.The other configuration is the same as that of the above embodiment.
The relationship among the protrusion length l of Nozzle 3, the nozzle gap L, and the slit width d of the nozzle 13 is also set to satisfy the above equations (1) and (2).
本実施例装置によれば、ノズル１３の連結部１
３ａを曲面とすると共に先細ノズルとしたので、
ノズル先端までの平均流速を減ずることによつて
一層の圧力損失の低減がはかれる。 According to the device of this embodiment, the connecting portion 1 of the nozzle 13
Since 3a has a curved surface and a tapered nozzle,
By reducing the average flow velocity to the nozzle tip, pressure loss can be further reduced.
さらに第１２図ａ，ｂに示す実施例では、ヘツ
ダ１２に取付けられるノズル１３を先細のノズル
本体１３ｂとこのノズル本体１３ｂの先端に取付
けられ且つスリツト幅ｄより広幅Ｄのノズル板１
３ｃとで構成し、このノズル板１３ｃに滑らかな
曲面で連通するスリツト幅ｄのスリツト１３ｄが
形成してある。尚、他の構成は上記実施例と同一
であり、ノズル１３の突出長ｌ、ノズル間隙Ｌ、
ノズル１３のスリツト幅ｄの関係も上記(1)，(2)式
を満足するようにしてある。 Furthermore, in the embodiment shown in FIGS. 12a and 12b, the nozzle 13 attached to the header 12 is attached to a tapered nozzle body 13b, and a nozzle plate 1 is attached to the tip of this nozzle body 13b and has a width D wider than the slit width d.
3c, and a slit 13d with a slit width d is formed in the nozzle plate 13c and communicates with the nozzle plate 13c through a smooth curved surface. Note that the other configurations are the same as the above embodiment, including the protrusion length l of the nozzle 13, the nozzle gap L,
The relationship between the slit width d of the nozzle 13 is also set to satisfy the above equations (1) and (2).
本実施例装置によれば、ノズル１３をノズル本
体１３ｂとノズル板１３ｃとで構成し、ノズル板
１３ｃに曲面で連通するスリツト１３ｄを形成し
たので、この場合にも第１１図に示した実施例と
同様、一層の圧力損失の低減がはかれる。 According to the device of this embodiment, the nozzle 13 is composed of a nozzle body 13b and a nozzle plate 13c, and a slit 13d communicating with the curved surface is formed in the nozzle plate 13c. Similarly, pressure loss can be further reduced.
尚、上記各実施例では、ノズルとしてスリツト
ノズルを用いそのスリツト幅をｄとし、このスリ
ツト幅ｄを帯板の走行方向の開口幅として説明し
たが、円形の噴孔を有するノズルとしてこれを帯
板の板幅方向に並設するようにしても良く、この
場合は帯板の走行方向の開口幅として噴孔径ｄを
用い、ノズルの突出長ｌ、ノズル間隙Ｌとの関係
も
Ｌ≦6d、ｌ≧10d―Ｌ
なる関係を満足するように設置すれば良い。 In each of the above embodiments, a slit nozzle is used as the nozzle, and the slit width is d, and the slit width d is the opening width in the running direction of the strip. In this case, the nozzle diameter d is used as the opening width in the running direction of the strip, and the relationship between the nozzle protrusion length l and the nozzle gap L is also as follows: L≦6d, l It is sufficient to install it so that the relationship ≧10d−L is satisfied.
以上、実施例とともに具体的に説明したように
本発明によれば、高温の帯板が巻き掛けられる回
転ドラムと対向して冷却ガスが圧送されるヘツダ
を設置すると共にヘツダから突き出してノズルを
帯板の板幅方向に取付へ、ノズルの帯板の走行方
向の開口幅をｄ、ノズルの突出長をｌ、ノズル間
隙をＬとしたときＬ≧6d且つｌ≧（10d―Ｌ）な
る関係を満足するよう構成したので、ノズル間隙
Ｌを小さくして熱伝達率を高くし冷却能力を増大
させることができると共に板幅方向への冷却ガス
の排出速度分布を均一化でき帯板を均一に冷却し
て変形を生じさせることがない。 As described above in detail with the embodiments, according to the present invention, a header through which cooling gas is fed under pressure is installed opposite to a rotating drum around which a high-temperature strip is wound, and a nozzle is protruded from the header. When the plate is installed in the width direction of the plate, the opening width of the nozzle strip in the running direction is d, the protrusion length of the nozzle is l, and the nozzle gap is L, the relationship L≧6d and l≧(10d−L) is established. Since the configuration satisfies the above requirements, it is possible to reduce the nozzle gap L, increase the heat transfer coefficient, and increase the cooling capacity, as well as equalize the discharge velocity distribution of the cooling gas in the width direction of the plate, thereby uniformly cooling the strip. This will not cause deformation.
第１図および第２図はそれぞれ従来のガスジエ
ツト冷却装置の横断面図、第３図は第２図に示し
た装置での冷却ガスの流れの説明図、第４図は本
発明の帯板のガスジエツト冷却装置の一実施例に
かかる横断面図、第５図〜第８図はそれぞれ本発
明装置の冷却特性の説明図、第９図は本発明の他
の実施例の要部の拡大断面図、第１０図はノズル
内の冷却ガスの流れの説明図、第１１図は本発明
の他の実施例の要部の拡大断面図、第１２図ａ，
ｂは本発明のさらに他の実施例にかかり、同図ａ
は要部の拡大断面図、同図ｂはノズル板の拡大断
面図である。
図面中、１０は帯板、１１は回彫ドラム、１２
はヘツダ、１３はノズル、１４は冷却ガス、ｌは
ノズルの突出長、Ｌはノズル間隙、ｄは開口幅
（スリツト幅もしくは噴孔径）である。
1 and 2 are cross-sectional views of a conventional gas jet cooling device, FIG. 3 is an explanatory diagram of the flow of cooling gas in the device shown in FIG. 2, and FIG. 4 is a cross-sectional view of a conventional gas jet cooling device. A cross-sectional view of one embodiment of a gas jet cooling device, FIGS. 5 to 8 are explanatory diagrams of the cooling characteristics of the device of the present invention, and FIG. 9 is an enlarged sectional view of a main part of another embodiment of the present invention. , FIG. 10 is an explanatory diagram of the flow of cooling gas in the nozzle, FIG. 11 is an enlarged sectional view of the main part of another embodiment of the present invention, and FIG. 12 a,
Fig. b relates to still another embodiment of the present invention, and Fig. a
is an enlarged sectional view of the main part, and FIG. In the drawing, 10 is a strip plate, 11 is a turning drum, 12
is the header, 13 is the nozzle, 14 is the cooling gas, l is the protrusion length of the nozzle, L is the nozzle gap, and d is the opening width (slit width or nozzle hole diameter).
Claims (1)
向して冷却ガスが圧送されるヘツダを設置すると
共にヘツダから突き出してノズルを前記帯板の板
幅方向に取付ける一方、ノズルの前記帯板の走行
方向の開口幅をｄ、ヘツダからのノズルの突出長
をｌ、ノズル先端から帯板までのノズル間隙をＬ
としたときＬ≦6d且つｌ≧（10d−Ｌ）なる関係
としたことを特徴とする帯板のガスジエツト冷却
装置。1. A header to which cooling gas is pumped is installed opposite to a rotating drum around which a high-temperature strip is wound, and a nozzle is installed in the width direction of the strip by protruding from the header, while a nozzle is installed in the width direction of the strip. The opening width in the direction is d, the protrusion length of the nozzle from the header is l, and the nozzle gap from the nozzle tip to the strip plate is L.
A strip gas jet cooling device characterized in that the relationship L≦6d and l≧(10d−L) is satisfied.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23498483A JPS60128218A (en) | 1983-12-15 | 1983-12-15 | Gas jet cooler for hoop |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23498483A JPS60128218A (en) | 1983-12-15 | 1983-12-15 | Gas jet cooler for hoop |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60128218A JPS60128218A (en) | 1985-07-09 |
| JPS638174B2 true JPS638174B2 (en) | 1988-02-22 |
Family
ID=16979319
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23498483A Granted JPS60128218A (en) | 1983-12-15 | 1983-12-15 | Gas jet cooler for hoop |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60128218A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005256093A (en) * | 2004-03-11 | 2005-09-22 | Nippon Steel Corp | Thermal crown control device |
-
1983
- 1983-12-15 JP JP23498483A patent/JPS60128218A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005256093A (en) * | 2004-03-11 | 2005-09-22 | Nippon Steel Corp | Thermal crown control device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60128218A (en) | 1985-07-09 |
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