JPH07186368A - Nozzle device - Google Patents
Nozzle deviceInfo
- Publication number
- JPH07186368A JPH07186368A JP33513693A JP33513693A JPH07186368A JP H07186368 A JPH07186368 A JP H07186368A JP 33513693 A JP33513693 A JP 33513693A JP 33513693 A JP33513693 A JP 33513693A JP H07186368 A JPH07186368 A JP H07186368A
- Authority
- JP
- Japan
- Prior art keywords
- air
- sheet
- heat transfer
- distance
- perforated 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.)
- Pending
Links
Landscapes
- Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
- Nozzles (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、例えば、フィルム、紙
等のシート状物の製造装置、印刷装置、塗工装置のよう
に、シート状物の乾燥、加熱、冷却等の目的でシート状
物表面に熱風や冷風を吹き付けるノズル装置の改良に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sheet-shaped product for the purpose of drying, heating and cooling the sheet-shaped product such as a manufacturing device for a sheet-shaped product such as film and paper, a printing device and a coating device. The present invention relates to improvement of a nozzle device that blows hot air or cold air onto the surface of an object.
【０００２】[0002]
【従来の技術】従来のノズル装置としては、例えば特公
平４−７２６９６号公報に記載された乾燥装置のノズル
装置が知られている。2. Description of the Related Art As a conventional nozzle device, for example, a nozzle device for a drying device described in Japanese Patent Publication No. 4-72696 is known.
【０００３】このノズル装置は、走行するシート状物に
対し、所定高さの位置に設けられた箱状のエア吹出部か
ら熱風を高速で吹き付けるもので、エア吹出部には、複
数のエア吹出孔を有する多孔板が設けられおり、上記多
孔板からシート状物までの距離Ｚを１５ｍｍよりも小さ
くし、それぞれのエア吹出孔間の間隔を１５〜４５ｍ
ｍ、上記距離Ｚと孔径ｄとの比Ｚ／ｄを１〜３とし、多
孔板のシート状物移送方向の長さＬを５０〜２５０ｍｍ
としたことを特徴とするものである。This nozzle device blows hot air at a high speed onto a traveling sheet-like object from a box-shaped air blowing portion provided at a predetermined height position, and a plurality of air blowing portions are blown to the air blowing portion. A perforated plate having holes is provided, the distance Z from the perforated plate to the sheet-like material is set to be smaller than 15 mm, and the distance between the air blowing holes is set to 15 to 45 m.
m, the ratio Z / d between the distance Z and the pore diameter d is 1 to 3, and the length L of the perforated plate in the sheet-like material transfer direction is 50 to 250 mm.
It is characterized by that.
【０００４】[0004]
【発明が解決しようとする課題】ところが上記従来装置
は、多孔板からシート状物までの距離Ｚが一定であって
も、エア吹出孔の孔径ｄが採り得る範囲が１〜３倍と広
い範囲であるため、多孔板からシート状物までの距離Ｚ
に対するエア吹出孔の孔径ｄが適切でないと、ノズル装
置からシート状物への伝熱性能、具体的には両者間で熱
の授受を規定する熱伝達率、温度差、伝熱面積のうち、
伝熱性能に最も大きく影響する吹出しエアとシート状物
間の熱伝達率ｈが低くなり、エア吹き出しのためのファ
ン動力もこの分だけ浪費するという問題がある。すなわ
ち、従来装置のように多孔板の孔径ｄを上記比Ｚ／ｄを
満足するように選んでも、孔径ｄの最適値が明確でな
く、また最適値がその範囲に存在しない場合もあること
から、伝熱性能が十分に発揮されないという問題があっ
た。However, in the above-mentioned conventional apparatus, even if the distance Z from the perforated plate to the sheet-like object is constant, the range in which the hole diameter d of the air blowout hole can be set is a wide range of 1 to 3 times. Therefore, the distance Z from the perforated plate to the sheet
If the hole diameter d of the air blowout hole with respect to is not appropriate, among the heat transfer performance from the nozzle device to the sheet-like material, specifically, the heat transfer coefficient, the temperature difference, and the heat transfer area that regulate the transfer of heat between the two,
There is a problem that the heat transfer coefficient h between the blown air and the sheet-like object, which has the greatest effect on the heat transfer performance, becomes low, and the fan power for blowing the air is wasted by this amount. That is, even if the pore size d of the perforated plate is selected so as to satisfy the ratio Z / d as in the conventional apparatus, the optimum value of the pore size d may not be clear, and the optimum value may not exist in that range. However, there was a problem that the heat transfer performance was not fully exhibited.
【０００５】発明者らは、かかる問題を解決するため種
々のテストを行った結果、吹き出しエアとシート状物間
の熱伝達率ｈを極力高くするには、多孔板からシート状
物までの距離Ｚに対して最も好ましい孔径ｄの値が一つ
だけ存在するという知見を得るに至った。As a result of various tests carried out by the inventors in order to solve such a problem, the distance from the perforated plate to the sheet-like material is required to maximize the heat transfer coefficient h between the blowing air and the sheet-like material. We have come to the knowledge that there is only one value of the most preferable pore diameter d for Z.
【０００６】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、ノズル装置からのエ
アの吹き出しに要するエネルギを増大させることなく、
従来装置よりも伝熱性能の高いノズル装置を提供するこ
とにある。The present invention has been made on the basis of such knowledge, and its object is to increase the energy required for blowing air from the nozzle device without increasing the energy.
It is to provide a nozzle device having a higher heat transfer performance than a conventional device.
【０００７】[0007]
【課題を解決するための手段】本発明は、上記目的を達
成するため、ノズル部の多孔板に設けられた複数のエア
吹出孔から、走行するシート状物に対してエアを吹き付
けるノズル装置であって、（イ）多孔板からシート状物
までの距離Ｚは、３０ｍｍよりも小さく設定されてお
り、（ロ）多孔板の表面積Ａに対するエア吹出孔の総面
積Ｂの百分率は、１．５〜４％であり、（ハ）個々のエ
ア吹出孔の孔径ｄ（ｍｍ）は、多孔板からシート状物ま
での距離Ｚ（ｍｍ）に対して、下記式よりなることを特
徴とする。 ｄ＝０．７７・Ｚ0.49±０．３ （ｍｍ） ここで、上記（イ）の距離Ｚを３０ｍｍよりも小さく設
定する理由は、エアの広がりによる風量の損失を防いで
有効に活用するためであり、距離Ｚを３０ｍｍ以上とす
るのは、高い伝熱性能を得るためには好ましくない。In order to achieve the above-mentioned object, the present invention is a nozzle device for blowing air to a traveling sheet-like object from a plurality of air blowing holes provided in a perforated plate of a nozzle portion. Therefore, (a) the distance Z from the perforated plate to the sheet-like material is set to be smaller than 30 mm, and (b) the percentage of the total area B of the air outlet holes to the surface area A of the perforated plate is 1.5. Is 4%, and (c) the hole diameter d (mm) of each air blowout hole is represented by the following formula with respect to the distance Z (mm) from the perforated plate to the sheet-like material. d = 0.77 · Z 0.49 ± 0.3 (mm) Here, the reason why the distance Z in (a) above is set to be smaller than 30 mm is to prevent the loss of air volume due to the spread of air and to effectively utilize it. Therefore, it is not preferable to set the distance Z to 30 mm or more in order to obtain high heat transfer performance.
【０００８】また、上記（ロ）の百分率を１．５〜４％
の範囲にする理由は、所定のファン動力に対し効率良く
伝熱性能を高めるためであり、この値を１．５％未満と
することはノズル部での圧力損失が増大することから省
エネルギーに反し、逆にこの値が４％を越えると同じ風
量であっても風速が落ち、伝熱性能が低下してしまうか
らである。The percentage of (b) above is 1.5-4%.
The reason why the range is set is to efficiently enhance the heat transfer performance with respect to the predetermined fan power. Setting this value to less than 1.5% increases the pressure loss at the nozzle portion, which is against energy saving. On the contrary, if this value exceeds 4%, the wind speed will drop and the heat transfer performance will decrease even with the same air volume.
【０００９】上記（イ）〜（ハ）の三条件のうち、熱伝
達率ｈのアップに最も大きく寄与するのは、（ハ）の孔
径ｄと距離Ｚとの関係であり、その理由は以下の如くと
考えられる。すなわち、ノズル部から吹き出されるエア
風量が等しく、さらに多孔板の表面積に対するエア吹出
孔の総面積の百分率が等しいという条件、すなわちエア
吹出孔から吹き出されるエアの平均風速が孔径ｄに関係
なく等しいという条件下では、上記式によって選ばれた
孔径ｄよりも小さい孔径を有する多孔板を用いると、式
から選ばれた孔径ｄの多孔板に比べて孔と孔の距離Ｌが
小さくなるため、広い範囲にエアを吹付けることがで
き、熱伝達が有利となるにもかかわらず、孔径ｄが小さ
くなったことによって吹出しエアの風速が隣接する孔か
ら吹き出されるエアの剪断力によって減衰する。その結
果、シート状物表面に到達するエアの速度が遅くなって
熱伝達に不利になる影響の方が強くなり、同じエア風量
であるにもかかわらず熱伝達は低下する。なお、式中の
±０．３は、この発明の作用効果を奏することのできる
好ましい孔径ｄの範囲であり、この範囲は発明者らの実
験によって得られたものである。一方、式から選ばれた
孔径ｄよりも大きい孔径を有する多孔板を用いると、式
から選ばれた孔径ｄの多孔板と比べて孔径が大きくなる
ため、吹出しエアの風速が周囲のエアの剪断力によって
減衰しにくくなり、シート状物表面に到達するエアの速
度が高く維持される。その結果、熱伝達に有利となるに
もかかわらず、孔と孔の距離Ｌが大きくなったことによ
ってエアの吹付けられる範囲が狭くなって熱伝達に不利
になる影響の方が強くなり、この場合も熱伝達率は低下
する。つまり、ファン動力が一定であるという条件下で
熱伝達率を最大にし得る、上記距離Ｚに応じた好ましい
孔径ｄが存在するのであり、かかる熱伝達率を最大にし
得る因子は、シート状物表面での吹出しエアの風速であ
ると考えられる。このような具体的な風速は、遅すぎる
と自然対流熱伝達による熱伝達が支配的になって多孔板
の孔径ｄによる熱伝達率の効果がなくなるため、１０ｍ
／ｓ以上の風速が必要であり、逆にエア風速が速すぎる
とノズル装置内での圧力損失が増してファン動力が増大
するため、結局２０〜６０ｍ／ｓの範囲内にするのが好
ましい。Among the above three conditions (a) to (c), it is the relationship between the hole diameter d and the distance Z in (c) that contributes most to the increase in the heat transfer coefficient h, for the following reasons. It is thought to be like. That is, the amount of air blown from the nozzles is equal, and the percentage of the total area of the air blowout holes to the surface area of the perforated plate is equal, that is, the average wind speed of the air blown out from the air blowout holes is independent of the hole diameter d. Under the condition of equality, if a perforated plate having a pore size smaller than the pore size d selected by the above formula is used, the distance L between the pores becomes smaller than that of the perforated plate having the pore size d selected from the formula. Although the air can be blown to a wide range and heat transfer is advantageous, the wind velocity of the blown air is attenuated by the shearing force of the air blown from the adjacent holes due to the small hole diameter d. As a result, the speed of the air reaching the surface of the sheet-like object becomes slower, which is more adversely affected by heat transfer, and the heat transfer decreases even with the same air volume. It should be noted that ± 0.3 in the formula is a preferable range of the hole diameter d capable of exhibiting the action and effect of the present invention, and this range is obtained by the experiment of the inventors. On the other hand, when a perforated plate having a pore size larger than the pore size d selected from the formula is used, the pore size becomes larger than that of the perforated plate having the pore size d selected from the formula, so that the wind velocity of the blown-out air is sheared by the surrounding air. It becomes difficult for the force to damp, and the velocity of the air that reaches the surface of the sheet-like material is kept high. As a result, although it is advantageous for heat transfer, the distance L between the holes is increased, so that the range in which the air is blown is narrowed and the adverse effect on heat transfer becomes stronger. Also in this case, the heat transfer rate is lowered. That is, there is a preferable hole diameter d according to the distance Z that can maximize the heat transfer coefficient under the condition that the fan power is constant, and the factor that can maximize the heat transfer coefficient is the sheet surface. It is considered to be the wind speed of the blowing air at. If such a specific wind speed is too slow, heat transfer due to natural convection heat transfer becomes dominant and the effect of the heat transfer coefficient due to the hole diameter d of the perforated plate disappears, so that it is 10 m.
A wind speed of / s or more is required, and conversely, if the air wind speed is too high, pressure loss in the nozzle device increases and fan power increases. Therefore, it is preferable to set the wind speed within the range of 20 to 60 m / s.
【００１０】なお、本発明においては、エア吹出孔を千
鳥状配列にするか格子状配列にするか等の配列態様や、
エア吹出孔の孔と孔間の距離については特に限定される
ものではない。In the present invention, the arrangement of the air outlets in a staggered arrangement or a lattice arrangement, and the like,
The distance between the air blowing holes is not particularly limited.
【００１１】[0011]
【作用】本発明のノズル装置によれば、走行されてきた
シート状物に対し多孔板に設けられている複数のエア吹
出孔からエアが吹き付けられると、多孔板からシート状
物までの距離Ｚが３０ｍｍよりも小さくされているの
で、エアの広がりによる風量の損失が少なく、また、多
孔板の表面積Ａに対するエア吹出孔の総面積Ｂの百分率
が１．５〜４％の範囲とされているので、ファン動力に
対する効率が高く、更にこの多孔板の孔径ｄは、上記式
から選ぶため、シート状物表面での熱伝達率が最も高く
なる作用が生じる。結局、これら三つの作用によって本
発明のノズル装置は、走行するシート状物に対して最大
限の伝熱性能を発揮し、ファン動力が無駄なく使用され
る。According to the nozzle device of the present invention, when air is blown to a running sheet-like object from a plurality of air outlets provided in the perforated plate, the distance Z from the porous plate to the sheet-like object is increased. Is less than 30 mm, the loss of air volume due to the spread of air is small, and the percentage of the total area B of the air outlet holes to the surface area A of the perforated plate is in the range of 1.5 to 4%. Therefore, the efficiency with respect to the fan power is high, and since the hole diameter d of the perforated plate is selected from the above formula, the heat transfer coefficient on the surface of the sheet-like material is maximized. After all, the nozzle device of the present invention exerts the maximum heat transfer performance to the traveling sheet-like object by these three actions, and the fan power is used without waste.
【００１２】[0012]
【実施例及び比較例】以下、本発明の一実施例を図面に
よって説明する。EXAMPLES AND COMPARATIVE EXAMPLES An example of the present invention will be described below with reference to the drawings.
【００１３】図１は、本発明に係るノズル装置のノズル
部１の部分側面図で、距離Ｚの下方に図示しない搬送手
段で矢印Ａ方向に移送されるシート状物５を乾燥させる
ため、その表面に熱風を吹き付けている状態を示してい
る。FIG. 1 is a partial side view of a nozzle portion 1 of a nozzle device according to the present invention, which is for drying a sheet-like material 5 which is transported in a direction of an arrow A by a conveying means (not shown) below a distance Z. It shows a state in which hot air is blown onto the surface.
【００１４】図において、ノズル部１は、シート状物５
の幅より若干広い幅を有する箱状のノズル箱２と、その
底部のノズル板３とからなる。ノズル板３は、複数のエ
ア吹出孔４を有し、シート状物５の移送平面と平行にノ
ズル箱２に固定されている。ノズル板３には、式で求め
た孔径を有する複数のエア吹出孔４が格子状に設けられ
ており、この孔に熱風が上方から図示しないファンによ
って供給されてシート状物表面に吹き付けられるように
なっている。なお、図示を省略したが、本実施例のノズ
ル装置は、かかる構成のノズル部１がシート状物５の移
送方向に沿って複数配列されてなるものである。In the figure, the nozzle portion 1 is a sheet-like material 5.
The box-shaped nozzle box 2 has a width slightly wider than the width of the nozzle box, and the nozzle plate 3 at the bottom thereof. The nozzle plate 3 has a plurality of air blowing holes 4 and is fixed to the nozzle box 2 in parallel with the plane of transfer of the sheet-like material 5. The nozzle plate 3 is provided with a plurality of air blowout holes 4 having a hole diameter obtained by a formula in a lattice shape, and hot air is supplied to the holes from above by a fan (not shown) so as to be blown onto the surface of the sheet-like material. It has become. Although not shown, in the nozzle device of this embodiment, a plurality of nozzle portions 1 having such a configuration are arranged along the transport direction of the sheet-like material 5.
【００１５】かかる構成のノズル装置に対して、多孔板
３からシート状物５までの距離Ｚに対する最も好ましい
孔径ｄを求めるため、以下に述べる試験装置を製作し
た。In order to obtain the most preferable hole diameter d with respect to the distance Z from the porous plate 3 to the sheet-like object 5 with respect to the nozzle device having such a structure, the following test device was manufactured.
【００１６】すなわち、距離Ｚを例えば、フレキシブル
ダクトなどにより５〜３０ｍｍの範囲で伸縮できるよう
にノズルを調整すると共に、多孔板３として、エア吹出
孔４の孔径ｄが１．５ｍｍ、２．０ｍｍ、２．５ｍｍ、
３．０ｍｍ、３．５ｍｍの０．５ｍｍ刻みで合計５種類
のものを作り、これをノズル箱２の底部に着脱できるよ
うにした。この場合、多孔板３の表面積Ａに対するエア
吹出孔４の総面積Ｂの比Ｂ／Ａは、２％とし、エア吹出
孔４での風速は図示しないダンパーと風速計により３０
ｍ／ｓに調節した。このような試験装置を用いて上記孔
径ｄの異なる５種類の多孔板３毎に距離Ｚを代えて、シ
ート状物５表面での熱伝達率ｈ（ｋｃＡｌ／ｍ2 ｈｒ
℃）を計算して求めたのが図２である。なお、この場合
いずれの多孔板の場合でもダンパ調整により、各ノズル
部１での風量が一定となるように調節した。また、熱伝
達率ｈの測定は、図３に示すようにノズル部１とほぼ同
程度の平面積を有する発泡シート製の断熱材６の上に１
００℃に加熱した鉄製の金属薄板７を両部材の表面が水
平となるように埋め込み、シート状物５の表面に見立て
た薄板７の表面にノズル部１から室温（Ｔａ＝２０℃）
のエアを吹き付け、金属薄板７の温度ＴがＴ１＝８０℃
からＴ２＝４０℃に冷却されるのに要する時間ｔ（秒）
を測定し、ノズル部１からの熱伝達量Ｑ１と、薄板７に
よる放熱量Ｑ２の熱収支の関係から、熱伝達率ｈを逆算
して求めた。That is, the nozzle is adjusted so that the distance Z can be expanded and contracted within a range of 5 to 30 mm by a flexible duct or the like, and the hole diameter d of the air blowout hole 4 as the perforated plate 3 is 1.5 mm and 2.0 mm. , 2.5 mm,
A total of 5 types were made in 0.5 mm increments of 3.0 mm and 3.5 mm, and these were made attachable to and detachable from the bottom of the nozzle box 2. In this case, the ratio B / A of the total area B of the air blowout holes 4 to the surface area A of the perforated plate 3 is set to 2%, and the wind speed at the air blowout holes 4 is set to 30% by a damper and anemometer not shown.
It was adjusted to m / s. Using such a test apparatus, the distance Z is changed for each of the five types of perforated plates 3 having different pore diameters d, and the heat transfer coefficient h (kcAl / m 2 hr) on the surface of the sheet-like material 5 is changed.
FIG. 2 shows the calculated value. In this case, in any of the porous plates, the damper volume was adjusted so that the air volume at each nozzle portion 1 was constant. In addition, the heat transfer coefficient h is measured by placing 1 on a heat insulating material 6 made of a foamed sheet having a plane area substantially the same as that of the nozzle portion 1 as shown in FIG.
A thin iron metal plate 7 made of iron heated to 00 ° C. is embedded so that the surfaces of both members are horizontal, and the surface of the thin plate 7 is regarded as the surface of the sheet-like material 5 from the nozzle portion 1 to room temperature (Ta = 20 ° C.).
Of air, the temperature T of the thin metal plate 7 is T1 = 80 ° C.
To T2 = 40 ° C from time t (sec)
Was measured, and the heat transfer coefficient h was calculated by back calculation from the relationship between the heat transfer amount Q1 from the nozzle part 1 and the heat balance of the heat release amount Q2 from the thin plate 7.
【００１７】すなわち、図２は、横軸に多孔板３から薄
板７までの距離Ｚを、横軸に熱伝達率ｈを取り、上記孔
径の異なる５種類の多孔板毎に求めた熱伝達率ｈをイン
プットしたものである。この図から明らかなように、ノ
ズル部１からのエア吹き出し風量が一定でも、多孔板か
らシート状物までの距離Ｚに対し最も熱伝達率ｈが高く
なる孔径ｄが一つ存在することが分る。このように最も
熱伝達率ｈが高くなる孔径ｄと距離Ｚとの関係を一つの
図に纏めてインプットしたのが図４であり、図中の領域
Ａを近似式として表してみたところ、下記の式が得られ
た。 ｄ＝０．７７・Ｚ0.49±０．３ （ｍｍ） 図中、斜線部Ｂは、上記従来技術（特公平４−７２６９
６号公報）のノズル装置の孔径ｄと距離Ｚとの関係式ｄ
／Ｚ＝１／３〜１であり、この領域の下方が平坦になっ
ているのは、孔径ピッチが１５〜４５ｍｍ、開孔面積率
が１．５〜３％であるので、孔径ｄが２．０７ｍｍより
も大きい領域に限定されるからである。図から明らかな
ように、従来技術の孔径ｄの領域Ｂは、本発明の孔径ｄ
の領域Ａとは明らかに異なるものである。That is, in FIG. 2, the horizontal axis represents the distance Z from the perforated plate 3 to the thin plate 7 and the horizontal axis represents the heat transfer coefficient h, and the heat transfer coefficient is obtained for each of the five kinds of porous plates having different hole diameters. It is an input of h. As is clear from this figure, even if the amount of air blown from the nozzle portion 1 is constant, there is one hole diameter d that maximizes the heat transfer coefficient h with respect to the distance Z from the perforated plate to the sheet-like material. It FIG. 4 shows the relationship between the hole diameter d and the distance Z at which the heat transfer coefficient h is the highest in one figure, and the area A in the figure is expressed as an approximate expression. Was obtained. d = 0.77 · Z 0.49 ± 0.3 (mm) In the figure, the shaded portion B indicates the above-mentioned conventional technique (Japanese Patent Publication No. 4-7269).
No. 6), the relational expression d between the hole diameter d of the nozzle device and the distance Z.
/ Z = 1/3 to 1, and the lower part of this region is flat because the hole diameter pitch is 15 to 45 mm and the opening area ratio is 1.5 to 3%, so the hole diameter d is 2 This is because it is limited to a region larger than 0.07 mm. As is apparent from the figure, the area B of the hole diameter d of the prior art is the hole diameter d of the present invention.
It is clearly different from the area A of.
【００１８】因みに、上記試験装置において、多孔板３
からシート状物５までの距離Ｚを１０ｍｍに固定し、多
孔板３の表面積Ａに対するエア吹出孔４の総面積Ｂの比
Ｂ／Ａを２％、エア吹出孔４より吐出されるエアの風量
が等しいこと（平均風速３０ｍ／ｓ）を条件に、多孔板
３のエア吹出孔４の孔径ｄを上式から求めた２．５ｍｍ
と、上式から外れた１．５ｍｍ、３．５ｍｍとした計３
種類の多孔板３について熱伝達率ｈを求めた。これを示
したのが次の表１である。Incidentally, in the above test apparatus, the perforated plate 3 is used.
The distance Z from the sheet material 5 to the sheet material 5 is fixed to 10 mm, the ratio B / A of the total area B of the air blowing holes 4 to the surface area A of the perforated plate 3 is 2%, and the amount of air discharged from the air blowing holes 4 is 2.5 mm obtained by the above equation for the hole diameter d of the air blow-out holes 4 of the perforated plate 3 under the condition that the values are equal (average wind speed 30 m / s).
And a total of 3 with 1.5 mm and 3.5 mm out of the above formula
The heat transfer coefficient h was determined for each type of porous plate 3. This is shown in Table 1 below.
【表１】 この表１から明らかなように、エア吹出孔４の孔径ｄが
２．５ｍｍの実施例１の熱伝達率は、１４３ｋｃＡｌ／
ｍ2 ｈｒ℃であるのに対し、エア吹出孔４の孔径ｄが上
式から外れた比較例１の１．５ｍｍと比較例２の３．５
ｍｍの場合は、それぞれ１３８ｋｃＡｌ／ｍ2 ｈｒ℃、
１２８ｋｃＡｌ／ｍ2 ｈｒ℃となり、上式から得られた
実施例１の多孔板の熱伝達率ｈが最も高いものであっ
た。[Table 1] As is clear from Table 1, the heat transfer coefficient of Example 1 in which the hole diameter d of the air outlet hole 4 is 2.5 mm is 143 kcAl /
m 2 hr ° C., while the hole diameter d of the air blowout hole 4 was out of the above formula, 1.5 mm in Comparative Example 1 and 3.5 mm in Comparative Example 2.
mm, 138 kcAl / m 2 hr ℃,
It was 128 kcAl / m 2 hr ° C., and the heat transfer coefficient h of the porous plate of Example 1 obtained from the above formula was the highest.
【００１９】また、図２の横軸から明らかなように、多
孔板３からシート状物５までの距離Ｚが３０ｍｍを越え
ると非常に熱伝達率が低下するため、距離Ｚは３０ｍｍ
よりも小さく設定する必要があることが分った。Further, as is clear from the horizontal axis of FIG. 2, when the distance Z from the porous plate 3 to the sheet-like material 5 exceeds 30 mm, the heat transfer coefficient is extremely lowered, so the distance Z is 30 mm.
I found that it should be set smaller than.
【００２０】[0020]
【発明の効果】本発明のノズル装置によれば、多孔板か
らシート状物までの距離Ｚに対し、吹出しエアとシート
状物間の熱伝達率ｈを最大にする多孔板の孔径ｄが明ら
かとなるので、多孔板の伝熱性能を最大限に発揮するこ
とができる。According to the nozzle device of the present invention, the hole diameter d of the perforated plate that maximizes the heat transfer coefficient h between the blown air and the sheet-like object is clarified with respect to the distance Z from the perforated plate to the sheet-like object. Therefore, the heat transfer performance of the perforated plate can be maximized.
【００２１】従って、シート状物の走行速度の高速化や
ノズル装置からのエア吹き付け動力の省エネルギ化が達
成できる。Therefore, the traveling speed of the sheet-like material can be increased and the energy consumption of the air blowing power from the nozzle device can be reduced.
【図１】本発明の一実施例に係るノズル装置の正面図で
ある。FIG. 1 is a front view of a nozzle device according to an embodiment of the present invention.
【図２】図１の装置における孔径、距離、熱伝達率間の
関係を示した図である。FIG. 2 is a diagram showing a relationship among a hole diameter, a distance, and a heat transfer coefficient in the device of FIG.
【図３】図１の装置の熱伝達率測定装置の模式図であ
る。FIG. 3 is a schematic view of a heat transfer coefficient measuring device of the device of FIG.
【図４】図１の装置における孔径と距離との関係を示し
た図である。4 is a diagram showing a relationship between a hole diameter and a distance in the device of FIG.
１…ノズル部 ２…ノズル箱 ３…多孔板 ４…エア吹出孔 ５…シート状物 ６…断熱材 ７…金属薄板 Ａ…シート状物の走行方向 DESCRIPTION OF SYMBOLS 1 ... Nozzle part 2 ... Nozzle box 3 ... Perforated plate 4 ... Air blow-out hole 5 ... Sheet-like object 6 ... Heat insulating material 7 ... Metal thin plate A ... Sheet-like object traveling direction
Claims (1)
ア吹出孔から、走行するシート状物に対してエアを吹き
付けるノズル装置であって、 （イ）多孔板からシート状物までの距離Ｚは、３０ｍｍ
よりも小さく設定されており、 （ロ）多孔板の表面積Ａに対するエア吹出孔の総面積Ｂ
の百分率は、１．５〜４％であり、 （ハ）個々のエア吹出孔の孔径ｄ（ｍｍ）は、多孔板か
らシート状物までの距離Ｚ（ｍｍ）に対して、下記式よ
りなることを特徴とするノズル装置。◎ ｄ＝０．７７・Ｚ0.49±０．３ （ｍｍ）1. A nozzle device for blowing air to a traveling sheet-like object from a plurality of air outlets provided in a perforated plate of a nozzle section, comprising: (a) a distance from the porous plate to the sheet-like object. Z is 30 mm
(B) The total area B of the air outlet holes relative to the surface area A of the perforated plate.
Is from 1.5 to 4%, and (c) the hole diameter d (mm) of each air outlet is expressed by the following formula with respect to the distance Z (mm) from the perforated plate to the sheet-like material. A nozzle device characterized in that. ◎ d = 0.77 ・ Z 0.49 ± 0.3 (mm)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33513693A JPH07186368A (en) | 1993-12-28 | 1993-12-28 | Nozzle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33513693A JPH07186368A (en) | 1993-12-28 | 1993-12-28 | Nozzle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07186368A true JPH07186368A (en) | 1995-07-25 |
Family
ID=18285177
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33513693A Pending JPH07186368A (en) | 1993-12-28 | 1993-12-28 | Nozzle device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07186368A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1044813A2 (en) * | 1999-04-16 | 2000-10-18 | Paper Converting Machine Company | Dryer for flexographic and gravure printing |
| JP2012121327A (en) * | 2010-12-03 | 2012-06-28 | Heiderberger Druckmaschinen Ag | Sheet processing machine, in particular sheet printing machine |
| DE102021123678A1 (en) | 2021-09-14 | 2023-03-16 | Koenig & Bauer Ag | Drying device in a printing machine and printing machine with this drying device |
| WO2023041262A1 (en) | 2021-09-14 | 2023-03-23 | Koenig & Bauer Ag | Sheet-fed printing press having a dryer for drying sheets printed by a non-impact printing device |
| DE102023103172B3 (en) | 2023-02-09 | 2023-12-28 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or painted by a printing press by applying heat |
| DE102023103173B3 (en) | 2023-02-09 | 2023-12-28 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or painted by a printing press by applying heat |
| DE102023116857B3 (en) | 2023-06-27 | 2024-05-02 | Koenig & Bauer Ag | Conveyor system for conveying consecutive printed sheets in individual layers |
| DE102023003607A1 (en) | 2023-02-09 | 2024-08-14 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or varnished by a printing machine by applying heat |
-
1993
- 1993-12-28 JP JP33513693A patent/JPH07186368A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1044813A3 (en) * | 1999-04-16 | 2001-05-02 | Paper Converting Machine Company | Dryer for flexographic and gravure printing |
| EP1044813A2 (en) * | 1999-04-16 | 2000-10-18 | Paper Converting Machine Company | Dryer for flexographic and gravure printing |
| JP2012121327A (en) * | 2010-12-03 | 2012-06-28 | Heiderberger Druckmaschinen Ag | Sheet processing machine, in particular sheet printing machine |
| US11897251B2 (en) | 2021-09-14 | 2024-02-13 | Koenig & Bauer Ag | Sheet-fed printing press having a dryer for drying sheets printed by a non-impact printing device |
| DE102021123678A1 (en) | 2021-09-14 | 2023-03-16 | Koenig & Bauer Ag | Drying device in a printing machine and printing machine with this drying device |
| WO2023041262A1 (en) | 2021-09-14 | 2023-03-23 | Koenig & Bauer Ag | Sheet-fed printing press having a dryer for drying sheets printed by a non-impact printing device |
| CN116669962A (en) * | 2021-09-14 | 2023-08-29 | 柯尼格及包尔公开股份有限公司 | Sheet-fed printing press with dryer for drying sheets printed by a plateless printing unit |
| CN116669962B (en) * | 2021-09-14 | 2024-07-16 | 柯尼格及包尔公开股份有限公司 | Sheet-fed printing press with dryer for drying sheets printed by a plateless printing unit |
| DE102023103172B3 (en) | 2023-02-09 | 2023-12-28 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or painted by a printing press by applying heat |
| DE102023103173B3 (en) | 2023-02-09 | 2023-12-28 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or painted by a printing press by applying heat |
| EP4414179A1 (en) | 2023-02-09 | 2024-08-14 | Koenig & Bauer AG | Drying device for drying a surface of a sheet-like substrate printed and/or varnished by a printing machine by applying heat |
| DE102023003607A1 (en) | 2023-02-09 | 2024-08-14 | Koenig & Bauer Ag | Drying device for drying a surface of a sheet-shaped substrate printed and/or varnished by a printing machine by applying heat |
| DE102023116857B3 (en) | 2023-06-27 | 2024-05-02 | Koenig & Bauer Ag | Conveyor system for conveying consecutive printed sheets in individual layers |
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