JPH0472696B2 - - Google Patents
Info
- Publication number
- JPH0472696B2 JPH0472696B2 JP59027215A JP2721584A JPH0472696B2 JP H0472696 B2 JPH0472696 B2 JP H0472696B2 JP 59027215 A JP59027215 A JP 59027215A JP 2721584 A JP2721584 A JP 2721584A JP H0472696 B2 JPH0472696 B2 JP H0472696B2
- Authority
- JP
- Japan
- Prior art keywords
- perforated plate
- hot air
- nozzle
- continuous strip
- heat transfer
- 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 - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B13/00—Machines and apparatus for drying fabrics, fibres, yarns, or other materials in long lengths, with progressive movement
- F26B13/10—Arrangements for feeding, heating or supporting materials; Controlling movement, tension or position of materials
Landscapes
- Engineering & Computer Science (AREA)
- Textile Engineering (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
- Drying Of Solid Materials (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はグラビア印刷機、オフセツト輪転印刷
機又は塗工機において、紙、フイルム等の連続帯
状物に印刷、塗工した後、これを乾燥或いは熱処
理するための乾燥装置に関する。Detailed Description of the Invention [Field of Industrial Application] The present invention uses a gravure printing machine, an offset rotary printing machine, or a coating machine to print and coat a continuous strip of paper, film, etc., and then dry it. Or it relates to a drying device for heat treatment.
連続帯状物の乾燥方法としては、熱風による方
法、赤外線による方法、加熱ドラムによる方法等
があるが、印刷機や塗工機では、紙、フイルムの
印刷物、塗工物を敏速に乾燥する必要上、熱風方
式が一般的であり、特に、走行中の帯状物の面に
熱風を直角に高速で吹き付けるノズルジエツト方
式が熱伝達性能が最良であると考えられ多く用い
られるいる。このノズルジエツト方式に用いられ
ている熱風吹出ノズルは細長いスリツト状の熱風
吹出口を有するスリツトノズルであり、通常、第
１図に示すように、このようなスリツトノズル１
が帯状物（以下被乾燥物という）２の移転方向に
沿つて多数配置されて用いられる。
Methods for drying continuous strips include methods using hot air, infrared rays, heated drums, etc. However, in printing machines and coating machines, it is necessary to quickly dry paper, film prints, and coated products. The hot air method is common, and in particular, the nozzle jet method, which blows hot air at right angles to the surface of the moving strip at high speed, is widely used because it is thought to have the best heat transfer performance. The hot air blowing nozzle used in this nozzle jet method is a slit nozzle having an elongated slit-shaped hot air blowing outlet, and normally, as shown in FIG.
A large number of these are arranged along the transfer direction of the strip-like material (hereinafter referred to as the material to be dried) 2 and used.
最近、印刷速度、塗工速度等の高速化が望まれ
ており、また、乾燥装置の能力向上も望まれてい
る。そこで、本発明者等はノズルジエツト方式の
乾燥装置における乾燥性能を向上させるべく検討
した結果、乾燥性能は紙、フイルム等への伝熱性
能に大きく依存しており、その伝熱性能を向上さ
せれば良いことを見出した。そこで、従来のスリ
ツトノズルによる伝熱性能を検討したところ、第
２図に示すように被乾燥物表面での伝熱係数ｈ
（kcal／m2hr℃）は、ノズル直下の熱風が当たる
部所は高いがそこから遠ざかるにつれて小さくな
つており、全体としての平均伝熱係数は低くなつ
ていることを確認した。この伝熱性能を向上させ
るには、ノズルからの吹出速度を増すとかノズル
の使用個数を増してノズル間隔を挟めることが有
効であると考えられるが、これらの解決手段は熱
風作成及び吹出に要するエネルギを増大させた
り、装置を高価にするため好ましくない。
Recently, there has been a desire to increase the printing speed, coating speed, etc., and there is also a desire to improve the performance of drying equipment. Therefore, the present inventors investigated ways to improve the drying performance of nozzle jet type drying equipment, and found that the drying performance largely depends on the heat transfer performance to paper, film, etc. I found something good. Therefore, when we investigated the heat transfer performance of the conventional slit nozzle, we found that the heat transfer coefficient h on the surface of the dried material is as shown in Figure 2.
It was confirmed that (kcal/m 2 hr°C) is high in the area directly below the nozzle where the hot air hits, but decreases as you move away from there, and that the overall average heat transfer coefficient is low. In order to improve this heat transfer performance, it is thought to be effective to increase the blowing speed from the nozzle or increase the number of nozzles used to narrow the distance between the nozzles, but these solutions reduce the amount of time required to create and blow hot air. This is undesirable because it increases energy consumption and makes the device expensive.
本発明者等はノズルジエツト方式の乾燥装置に
おける伝熱性能を更に向上させるべく種々検討し
た結果、従来のスリツトノズルに代えて、ノズル
先端に、多数の空気吹出孔を備えた多孔板を設け
た多孔板ノズルを用い、該多孔板ノズルの空気吹
出孔から熱風を高速で吹き出して被乾燥物表面を
衝突させることにより、被乾燥物表面に伝熱係数
を高い多数の小さなピーク部分を作ることがで
き、その時の被乾燥物表面全体の平均伝熱係数は
スリツトノズルを用いた場合に比べて向上するこ
とを見い出した。また、多孔板ノズルの各孔から
吹き出す熱風は細い棒状であり、被乾燥物に衝突
した後の熱風（排気）に干渉されて速度が低下し
勝ちであるが、排気流路を適切に配置することに
より、十分な高速で被乾燥物に衝突し、良好な伝
熱を行い得ることも見い出した。 As a result of various studies to further improve the heat transfer performance of nozzle jet type drying equipment, the inventors of the present invention discovered that, in place of the conventional slit nozzle, a perforated plate with a large number of air blowing holes was installed at the tip of the nozzle. By using a nozzle to blow out hot air at high speed from the air outlet of the perforated plate nozzle and colliding with the surface of the object to be dried, it is possible to create a large number of small peak portions with a high heat transfer coefficient on the surface of the object to be dried, It has been found that the average heat transfer coefficient of the entire surface of the dried object at this time is improved compared to when a slit nozzle is used. In addition, the hot air blown out from each hole of the perforated plate nozzle is in the shape of a thin rod, and after colliding with the object to be dried, the hot air (exhaust air) tends to interfere with the speed and reduce the speed, but it is important to arrange the exhaust flow path appropriately. It has also been found that by doing so, the material can collide with the material to be dried at a sufficiently high speed and good heat transfer can be achieved.
本発明はかかる知見に基づいてなされたもの
で、その目的とするところは、熱風作成や吹き出
しに要するエネルギを増大させることなく、従来
のスリツトノズルを用いた乾燥装置よりも伝熱性
能のよい乾燥装置を提供するにある。 The present invention was made based on this knowledge, and its purpose is to provide a drying device with better heat transfer performance than conventional drying devices using slit nozzles without increasing the energy required for creating and blowing hot air. is to provide.
本発明は上記目的を達成するため、グラビア印
刷機、オフセツト輪転印刷機、又は塗工機の連続
帯状物の熱風乾燥装置において、前記連続帯状物
の移送方向に沿つて複数の熱風吹出部と排気流路
とを交互に配列し、その熱風吹出部の各々を、先
端に多孔板を有する多孔板ノズルで構成し、その
多孔板ノズルの多孔板に、連続帯状物の移送方向
に対して複数列に多数の孔を配置するという構成
を備えたものである。
In order to achieve the above object, the present invention provides a hot air drying device for a continuous strip of a gravure printing machine, an offset rotary printing press, or a coating machine, in which a plurality of hot air blowing parts and an exhaust gas are provided along the transport direction of the continuous strip. Each of the hot air blowing sections is composed of a perforated plate nozzle having a perforated plate at the tip, and the perforated plate of the perforated plate nozzle is arranged in a plurality of rows in the direction of conveyance of the continuous strip. It has a structure in which a large number of holes are arranged in the hole.
更に、本発明は、その多孔板と連続帯状物との
距離ｚを15mmよりも小さく設定し、前記多孔板に
形成している多数の孔の、孔と孔との距離ｌを15
〜45mmとし、多孔板と連続帯状物との距離ｚと孔
径ｄの比（ｚ／ｄ）を１〜３とし、更に、前記多
孔板ノズルの連続帯状物の移送方向の長さＬを50
〜250mmとするという構成も備えている。 Furthermore, in the present invention, the distance z between the perforated plate and the continuous strip is set to be smaller than 15 mm, and the distance l between the holes of the large number of holes formed in the perforated plate is set to 15 mm.
~45 mm, the ratio of the distance z between the perforated plate and the continuous strip to the hole diameter d (z/d) is 1 to 3, and the length L of the perforated plate nozzle in the conveying direction of the continuous strip is 50 mm.
It also has a configuration of ~250mm.
上記構成の乾燥装置では、多孔板に形成されて
いる多数の孔から熱風が高速で吹き出し、連続帯
状物に衝突してそれを加熱、乾燥させる。この
時、各孔から吹き出す熱風は細い棒状ではある
が、連続帯状物に衝突してその周囲に広がるた
め、多孔面よりは遥かに大きい面積の、伝熱係数
の大きいピーク部分が生じる。このピーク部分の
広さは、第２図に示すスリツトノズルによるもの
よりも小さいが、孔を連続帯状物の移送方向に対
して複数列に多数設けているので、ピーク部分の
数が極めて多く、このため、熱風量を増加させる
ことなく平均伝熱係数を大幅に向上させることが
できる。
In the drying device configured as described above, hot air is blown out at high speed from a large number of holes formed in the perforated plate, collides with the continuous strip, and heats and dries it. At this time, although the hot air blown out from each hole is in the shape of a thin rod, it collides with the continuous strip and spreads around it, resulting in a peak portion with a large heat transfer coefficient that has a much larger area than the porous surface. The width of this peak part is smaller than that of the slit nozzle shown in Figure 2, but since many holes are provided in multiple rows in the direction of conveyance of the continuous strip, the number of peak parts is extremely large. Therefore, the average heat transfer coefficient can be significantly improved without increasing the amount of hot air.
ここで、多孔板と連続帯状物との距離ｚを15mm
よりも小さくしたことにより、孔から噴出する細
い棒状の熱風でも高速で連続帯状物に衝突するこ
とが可能であり、ピーク部分の伝熱係数が大きく
なると共にピーク部分の広がりが大きくなり、全
体としての平均伝熱係数を大きくできる。 Here, the distance z between the perforated plate and the continuous strip is 15 mm.
By making the diameter smaller than that, even a thin rod-shaped hot air ejected from the hole can collide with the continuous band at high speed, and the heat transfer coefficient at the peak part becomes larger and the spread of the peak part becomes larger. The average heat transfer coefficient can be increased.
多孔板ノズルにおける孔と孔との距離ｌを15〜
45mmとしたことにより、多孔板ノズルの製作コス
トをあまり高くすることなく伝熱係数の高いピー
ク部分を効率良く分布させることができ、全体と
しての平均伝熱係数を大きくできる。 The distance l between the holes in the perforated plate nozzle is 15~
By setting the diameter to 45 mm, the peak portion with a high heat transfer coefficient can be efficiently distributed without increasing the manufacturing cost of the perforated plate nozzle, and the average heat transfer coefficient as a whole can be increased.
距離ｚと孔の直径ｄとの比ｚ／Ｄを１〜３とし
たことにより、熱風吹き出しに要するフアン動力
を過大にすることなく、熱風を高速で連続帯状物
に衝突させることが可能であり、エネルギ消費を
増大させることなく、平均伝熱係数を大きくでき
る。 By setting the ratio z/D between the distance z and the diameter d of the hole to be 1 to 3, it is possible to make the hot air collide with the continuous strip at high speed without increasing the fan power required to blow out the hot air. , the average heat transfer coefficient can be increased without increasing energy consumption.
多孔板の連続帯状物の移送方向に沿う寸法Ｌを
50〜250mmとしたことにより、伝熱係数の高いピ
ーク部分を多数形成することができると共に、多
数の孔から出た熱風の排気流路を確保でき、連続
帯状物に衝突した後の排気が孔から吹き出す熱風
の邪魔をすることがなく、この点からも全体とし
ての平均伝熱係数を大きくできる。 The dimension L along the transport direction of the continuous strip of perforated plate is
By setting the diameter to 50 to 250 mm, it is possible to form many peak parts with high heat transfer coefficients, and to secure an exhaust flow path for hot air coming out of many holes, so that the exhaust air after colliding with a continuous strip is passed through the holes. It does not interfere with the hot air blown out from the air, and from this point of view as well, the average heat transfer coefficient as a whole can be increased.
これらの結果、本発明の乾燥装置では、熱風作
成及び吹き出しに要するエネルギを増加させるこ
となく、平均伝熱係数を大きくでき、効率良く乾
燥を行うことができる。 As a result, in the drying apparatus of the present invention, the average heat transfer coefficient can be increased without increasing the energy required for creating and blowing hot air, and drying can be performed efficiently.
〔実施例〕
以下、第３図以下に示す本発明の実施例を説明
する。第３図は本発明の一実施例をなす乾燥装置
７を備えた塗工機の要部を概略的に示すもので、
２は帯状物（被乾燥物）、３は塗工用版胴、４は
塗工用圧胴、５は塗工液、６はガイドロールであ
る。乾燥装置７は複数の熱風吹出部即ち熱風吹出
ノズル８、熱風供給ダクト９、排気チヤンバ１０
を有しており、熱風吹出ノズル８は被乾燥物２の
移送方向に沿つて小さな間〓１１をあけて配置さ
れている。間〓１１は排気流路として作用する。
かくして、熱風吹出部８と排気流路１１とが被乾
燥物２の移送方向に沿つて交互に配列されてい
る。なお、排気流路１１は必ず熱風吹出ノズル８
の背後にまで貫通する必要はなく、適当な深さの
溝であつてもよい。[Example] Hereinafter, an example of the present invention shown in FIG. 3 and subsequent figures will be described. FIG. 3 schematically shows the main parts of a coating machine equipped with a drying device 7, which is an embodiment of the present invention.
2 is a strip (material to be dried), 3 is a coating plate cylinder, 4 is a coating impression cylinder, 5 is a coating liquid, and 6 is a guide roll. The drying device 7 includes a plurality of hot air blowing units, namely a hot air blowing nozzle 8, a hot air supply duct 9, and an exhaust chamber 10.
The hot air blowing nozzles 8 are arranged with a small gap 11 in the direction in which the material to be dried 2 is transported. The gap 11 acts as an exhaust flow path.
In this way, the hot air blowing sections 8 and the exhaust channels 11 are arranged alternately along the direction in which the material to be dried 2 is transported. Note that the exhaust flow path 11 is always connected to the hot air blowing nozzle 8.
It is not necessary to penetrate to the back of the groove, and the groove may be of an appropriate depth.
熱風吹出ノズル８は、その先端に第４図、第５
図に示すように、多数の孔１２を備えた多孔板１
３を有する多孔板ノズルである。この多数の孔１
２は被乾燥物２の幅方向に多数配置されるのみな
らず、被乾燥物２の移送方向に対しても複数列に
配置されている。 The hot air blowing nozzle 8 has a shape shown in FIGS. 4 and 5 at its tip.
As shown in the figure, a perforated plate 1 with a large number of holes 12
This is a perforated plate nozzle with 3. This large number of holes 1
2 are arranged in large numbers not only in the width direction of the object 2 to be dried, but also in a plurality of rows in the direction of transport of the object 2 to be dried.
上記構成の乾燥装置７によれば、熱風供給ダク
ト９からの熱風が各多孔板ノズル８に供給され、
多孔板の多数の孔から高速で、例えば、20〜50
ｍ／ｓで吹き出して被乾燥物２に衝突し、被乾燥
物を加熱する。かくして、第６図に示すように、
多孔板１３の各孔１２の直下に伝熱係数を大きい
ピーク部分が生じる。このピーク部分の広さは第
２図に示すスリツトノズルによるものも小さい
が、ピーク部分の数が極めて多いので、平均伝熱
係数は大幅に（場合によつては約1.5倍に）、向上
する。被乾燥物２に衝突した後の熱風は多孔板ノ
ズル８間の排気流路１１を通り、かつ排気ダクト
（図示せず）により放出される。 According to the drying device 7 having the above configuration, hot air is supplied from the hot air supply duct 9 to each perforated plate nozzle 8,
from a large number of holes in a perforated plate at high speed, e.g. 20-50
It blows out at m/s and collides with the object to be dried 2, thereby heating the object to be dried. Thus, as shown in Figure 6,
Directly below each hole 12 of the perforated plate 13, a peak portion with a large heat transfer coefficient occurs. Although the width of this peak portion is small due to the slit nozzle shown in Fig. 2, the number of peak portions is extremely large, so the average heat transfer coefficient is significantly improved (by about 1.5 times in some cases). After colliding with the material to be dried 2, the hot air passes through an exhaust flow path 11 between the perforated plate nozzles 8 and is discharged through an exhaust duct (not shown).
本発明は上記の如く多孔板ノズルを用いるもの
であるが、良好な伝熱性能を発揮するには、各孔
からの熱風が高速で被乾燥物に衝突する必要があ
り、そのためには、各部分の寸法が重要である。
以下、説明する。 The present invention uses a perforated plate nozzle as described above, but in order to exhibit good heat transfer performance, it is necessary for the hot air from each hole to collide with the material to be dried at high speed. The dimensions of the part are important.
This will be explained below.
(1) ノズル先端と被乾燥物表面との距離ｚは従来
のスリツトノズルの場合（15〜100mm）よりも
小さく、従つて、15mmよりも小さく設定するも
のであり、特に、４〜10mmが好ましい。この距
離ｚが大きいと、熱風の被乾燥物への衝突速度
が低下してピーク部分における伝熱係数が低下
し、また、ピーク部分の広がりが小さくなり、
結局全体としての平均伝熱係数が低下して好ま
しくない。一方、距離ｚが４mmよりも小さくな
ると、ノズルを出てから被乾燥物に衝突する部
分での圧力損失が大きくなり、必要以上に熱風
供給用のフアン動力を要し、エネルギ消費が増
大して好ましくない。(1) The distance z between the nozzle tip and the surface of the object to be dried is smaller than that of a conventional slit nozzle (15 to 100 mm), and is therefore set smaller than 15 mm, particularly preferably 4 to 10 mm. If this distance z is large, the speed at which the hot air impinges on the material to be dried decreases, the heat transfer coefficient at the peak portion decreases, and the spread of the peak portion decreases.
As a result, the average heat transfer coefficient as a whole decreases, which is not preferable. On the other hand, if the distance z is smaller than 4 mm, the pressure loss at the part where it collides with the material to be dried after exiting the nozzle will increase, requiring more fan power for supplying hot air than necessary, increasing energy consumption. Undesirable.
(2) 多孔板ノズルにおける孔と孔との距離ｌは15
〜45mmとする。この距離ｌが15mmよりも小さく
なると、孔数が多くなるため、適正な吹出速度
を確保するためには孔径を小さくせざるを得
ず、多数の小径の孔を加工するため製作コスト
が高くなり、また詰まり易くなつて清掃性が悪
くなる。これを避けるために孔径を大きくする
と、吹出速度が低下して平均伝熱係数が低下し
てしまう。一方、距離ｌが45mmよりも大きくな
ると、孔直下のピーク部分とピーク部分との伝
熱係数が非常に低くなり、平均伝熱係数が低下
する。従つて、この距離ｌを15〜45mmにするこ
とにより、多孔板ノズルの製作コストをあまり
高めることなく伝熱係数の高いピーク部分を効
率良く分布させることができ、全体としての平
均伝熱係数を大きくできる。(2) The distance l between the holes in the perforated plate nozzle is 15
~45mm. If this distance l is smaller than 15 mm, the number of holes will increase, so in order to ensure an appropriate blowing speed, the hole diameter must be made smaller, and manufacturing costs will increase as many small diameter holes are machined. Also, it becomes more likely to clog and becomes difficult to clean. If the hole diameter is increased to avoid this, the blowing speed will decrease and the average heat transfer coefficient will decrease. On the other hand, when the distance l is larger than 45 mm, the heat transfer coefficient between the peak portions directly under the hole and the peak portion becomes extremely low, and the average heat transfer coefficient decreases. Therefore, by setting this distance l to 15 to 45 mm, the peak portion with a high heat transfer coefficient can be efficiently distributed without increasing the production cost of the perforated plate nozzle, and the overall average heat transfer coefficient can be reduced. You can make it bigger.
(3) 上記距離ｚと孔の直径ｄとの比ｚ／ｄは１〜
３とする。この比ｚ／ｄが１よりも小さくなる
と、ノズルを出てから被乾燥物へ衝突する部分
での圧力損失が増大し、フアン動力が増大す
る。一方、比ｚ／ｄが３を越えて大きくなる
と、被乾燥物へ衝突する際の風速の低下が大き
くなり、平均伝熱係数が低下する。従つて、比
ｚ／ｄを１〜３にすることにより、エネルギ消
費を増大させることなく、熱風を高速で被乾燥
物に衝突させることが可能であり、平均伝熱係
数を大きくできる。(3) The ratio z/d between the above distance z and the diameter d of the hole is 1 to
Set it to 3. When this ratio z/d becomes smaller than 1, the pressure loss at the part where the material exits the nozzle and collides with the object to be dried increases, and the fan power increases. On the other hand, when the ratio z/d increases beyond 3, the wind speed decreases greatly when colliding with the object to be dried, and the average heat transfer coefficient decreases. Therefore, by setting the ratio z/d to 1 to 3, it is possible to make hot air collide with the material to be dried at high speed without increasing energy consumption, and the average heat transfer coefficient can be increased.
(4) 多孔板の孔の直径ｄは３〜６mmが好ましい。
孔径が３mmよりも小さいと風が通りにくくな
り、ノズルの圧力損失が増大し、必要以上に熱
風供給用のフアン動力を要し、一方、孔径が６
mmよりも大きくなるとノズル風速が低下し平均
伝熱係数が低下してしまう。(4) The diameter d of the holes in the perforated plate is preferably 3 to 6 mm.
If the hole diameter is smaller than 3 mm, it will be difficult for air to pass through, the pressure loss of the nozzle will increase, and more fan power will be required to supply hot air than necessary.
When it is larger than mm, the nozzle wind speed decreases and the average heat transfer coefficient decreases.
(5) 多孔板１３の被乾燥物の移送方向に沿う寸法
Ｌは50〜250mmとする。この寸法Ｌを50mmより
も小さくすると、多孔板ノズルの基本的考えで
ある伝熱係数の高いピーク部分を多数形成する
という観点から外れ、伝熱性能の向上効果が少
なくなる。一方、寸法Ｌを250mmよりも大きく
すると、多数の孔から出た熱風の排気流路の確
保が出来ず、被乾燥物に衝突した後の排気が孔
１２から吹き出す熱風の邪魔をして、伝熱性能
を低下させる。(5) The dimension L of the perforated plate 13 along the direction of transport of the material to be dried is 50 to 250 mm. If this dimension L is smaller than 50 mm, the basic idea of the perforated plate nozzle, which is to form many peak portions with high heat transfer coefficients, will be lost, and the effect of improving heat transfer performance will be reduced. On the other hand, if the dimension L is larger than 250 mm, it will not be possible to secure an exhaust flow path for the hot air coming out of the many holes, and the exhaust air after colliding with the material to be dried will get in the way of the hot air blowing out from the holes 12, causing the hot air to flow through the holes 12. Decreases thermal performance.
(6) 乾燥装置内の被乾燥物の表面積（ノズル幅×
乾燥装置長さ）に対する熱風吹出孔の総断面積
の比、即ち開口面積率A1.5〜３％が好ましい。
この開口面積率Ａが小さすぎると平均伝熱係数
は大きくなるが孔から出る風速が速くなり、必
要以上にノズルの圧力損失が増大し、フアン動
力費が増える。一方、開口面積率Ａが大きすぎ
ると風速が低下し、平均伝熱係数が低下してし
まう。(6) Surface area of the material to be dried in the dryer (nozzle width x
The ratio of the total cross-sectional area of the hot air blowing holes to the length of the drying device, that is, the opening area ratio A is preferably 1.5 to 3%.
If this opening area ratio A is too small, the average heat transfer coefficient will increase, but the wind speed coming out of the holes will increase, the pressure loss of the nozzle will increase more than necessary, and the fan power cost will increase. On the other hand, if the opening area ratio A is too large, the wind speed will decrease and the average heat transfer coefficient will decrease.
(7) 平均伝熱係数は風速が速いほど大きくなる
が、一方そのためにはフアン動力も大きくな
る。そこで目的の乾きを得るために要する熱エ
ネルギとフアン動力エネルギの総和を尺度とし
て、開口面積率Ａとｚ／ｄの間係を示したのが
第７図のグラフであり、E1〜E5はそれぞれエ
ネルギ線である。ここで、E1＜E2＜E3＜E4＜
E5である。第７図から明らかな如く、Ａと
ｚ／ｄとは線E1で囲まれた領域とすることが、
エネルギ消費上から好ましい。(7) The average heat transfer coefficient increases as the wind speed increases, but this also increases the fan power. Therefore, the graph in Figure 7 shows the relationship between the open area ratio A and z/d, using the sum of the thermal energy and fan power energy required to obtain the desired dryness as a measure . are energy lines. Here, E 1 <E 2 <E 3 <E 4 <
It is E5 . As is clear from Fig. 7, A and z/d can be defined as the area surrounded by line E1 .
This is preferable from the viewpoint of energy consumption.
本発明は上記した如く、従来のスリツトノズル
に代えて、連続帯状物（被乾燥物）の移送方向に
複数列に多数の孔を配列して多孔板を備えた多孔
板ノズルを用い且つ各ノズル間に排気流路を設
け、更に、その多孔板と連続帯状物との距離ｚを
15mmよりも小さく設定し、前記多孔板に形成して
いる多数の孔の、孔と孔との距離ｌを15〜45mmと
し、多孔板と連続帯状物との距離ｚと孔径ｄの比
（ｚ／ｄ）を１〜３とし、前記多孔板ノズルの連
続帯状物の移送方向の長さＬを50〜250mmとした
ものであるので、多孔板の多数の孔から噴出した
熱風が排気に邪魔されることなく連続帯状物に衝
突して熱伝達を行い、このため、熱風作成や吹き
出しに必要なエネルギを増大させることなく、多
数の伝熱係数の高いピーク部分を生じさせ、全体
としての平均伝熱係数を向上させることができ、
乾燥能力を高め、省エネルギに寄与すること大で
あるという優れた効果を有している。
As described above, the present invention uses, in place of the conventional slit nozzle, a perforated plate nozzle equipped with a perforated plate in which a large number of holes are arranged in multiple rows in the direction of transport of a continuous strip (material to be dried), and between each nozzle. An exhaust flow path is provided in , and the distance z between the perforated plate and the continuous strip is
The distance l between the holes of the large number of holes formed in the perforated plate is set to be smaller than 15 mm, and the distance l between the holes is 15 to 45 mm, and the ratio of the distance z between the perforated plate and the continuous strip to the hole diameter d (z /d) is set to 1 to 3, and the length L of the continuous strip of the perforated plate nozzle in the transport direction is set to 50 to 250 mm, so that the hot air blown out from the many holes of the perforated plate is not disturbed by the exhaust air. The heat transfer occurs by impinging on the continuous strip without any heat transfer, thus creating multiple peaks with high heat transfer coefficients and reducing the overall average transfer without increasing the energy required to create or blow the hot air. can improve the thermal coefficient,
It has the excellent effect of increasing drying ability and greatly contributing to energy saving.
第１図は従来のスリツトノズルの配列を示す概
略図、第２図は従来のスリツトノズルによる伝熱
係数の分布を示すグラフ、第３図は本発明の一実
施例の乾燥装置７を備えた塗工機の要部斜視図、
第４図は乾燥装置７に用いる多孔板ノズルの配列
を示す概略図、第５図は多孔板ノズルの多孔板の
部分平面図、第６図は多孔板ノズルによる伝熱係
数の分布を示すグラフ、第７図は開口面積率Ａと
ｚ／ｄと消費エネルギとの関係を示すグラフであ
る。
１……スリツトノズル、２……被乾燥物、６…
…ガイドロール、７……乾燥装置、８……多孔板
ノズル、１１……排気流路、１２……孔、１３…
…多孔板。
FIG. 1 is a schematic diagram showing the arrangement of conventional slit nozzles, FIG. 2 is a graph showing the distribution of heat transfer coefficient by the conventional slit nozzles, and FIG. 3 is a coating device equipped with a drying device 7 according to an embodiment of the present invention. A perspective view of the main parts of the machine,
Fig. 4 is a schematic diagram showing the arrangement of perforated plate nozzles used in the drying device 7, Fig. 5 is a partial plan view of the perforated plate of the perforated plate nozzle, and Fig. 6 is a graph showing the distribution of the heat transfer coefficient by the perforated plate nozzle. , FIG. 7 is a graph showing the relationship between the aperture area ratio A, z/d, and energy consumption. 1... Slit nozzle, 2... Material to be dried, 6...
... Guide roll, 7 ... Drying device, 8 ... Perforated plate nozzle, 11 ... Exhaust channel, 12 ... Hole, 13 ...
...Perforated plate.
Claims (1)
は塗工機の連続帯状物の熱風乾燥装置において、
前記連続帯状物の移送方向に沿つて複数の熱風吹
出部と排気流路とが交互に配列されており、前記
熱風吹出物の各々が先端に多孔板を有する多孔板
ノズルであり、前記多孔板ノズルの多孔板が、連
続帯状物の移送方向に対して複数列に配置された
多数の孔を備えており、多孔板と連続帯状物との
距離ｚが15mmよりも小さく設定されており、前記
多孔板ノズルの多孔板に形成している多数の孔
の、孔と孔との距離ｌが15〜45mmで、多孔板と連
続帯状物との距離ｚと孔径ｄの比ｚ／ｄが１〜３
であり、前記多孔板ノズルの連続帯状物の移送方
向の長さＬが50〜250mmであることを特微とする
乾燥装置。 ２ 乾燥装置内の連続帯状物の表面積に対する熱
風吹出孔の総断面積の比、即ち開口面積率が1.5
〜３％である事を特徴とする特許請求の範囲第１
項記載の乾燥装置。[Claims] 1. In a hot air drying device for a continuous strip of a gravure printing machine, an offset rotary printing machine, or a coating machine,
A plurality of hot air blowing units and exhaust channels are arranged alternately along the direction of transport of the continuous strip, and each of the hot air blowing units is a perforated plate nozzle having a perforated plate at its tip, and the perforated plate nozzle The perforated plate is provided with a large number of holes arranged in multiple rows in the direction of transport of the continuous strip, the distance z between the perforated plate and the continuous strip is set to be smaller than 15 mm, and the perforated The distance l between the many holes formed in the perforated plate of the plate nozzle is 15 to 45 mm, and the ratio z/d of the distance z between the perforated plate and the continuous strip to the hole diameter d is 1 to 3.
A drying device characterized in that the length L of the perforated plate nozzle in the direction of transport of the continuous strip is 50 to 250 mm. 2. The ratio of the total cross-sectional area of the hot air outlet to the surface area of the continuous strip in the drying device, that is, the open area ratio is 1.5.
Claim 1 characterized in that it is ~3%.
Drying equipment as described in section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2721584A JPS60172542A (en) | 1984-02-17 | 1984-02-17 | Dryer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2721584A JPS60172542A (en) | 1984-02-17 | 1984-02-17 | Dryer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60172542A JPS60172542A (en) | 1985-09-06 |
| JPH0472696B2 true JPH0472696B2 (en) | 1992-11-18 |
Family
ID=12214874
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2721584A Granted JPS60172542A (en) | 1984-02-17 | 1984-02-17 | Dryer |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60172542A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6293196B1 (en) * | 1993-10-06 | 2001-09-25 | Howard W. DeMoore | High velocity, hot air dryer and extractor |
| DE102005017152B4 (en) * | 2005-04-13 | 2007-02-08 | Lindauer Dornier Gmbh | Process for drying preferably plate-shaped products and continuous dryers in multi-day construction |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS513427A (en) * | 1974-07-01 | 1976-01-12 | Mitsubishi Heavy Ind Ltd | TEISOON PAIROTSUTOBAANA |
| JPS57102357A (en) * | 1980-12-16 | 1982-06-25 | Kyoei Nekki Kogyo Kk | Drying device for printing sheet |
| IT1153853B (en) * | 1982-09-22 | 1987-01-21 | Cerutti Spa Off Mec | VENTILATION DEVICE FOR PRINTING MACHINES, IN PARTICULAR FOR ROTOCALCO ROTARY MACHINES |
-
1984
- 1984-02-17 JP JP2721584A patent/JPS60172542A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60172542A (en) | 1985-09-06 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |