507010 Α7 Β7 五、發明說明（1 ) 發明領域： (請先閱讀背面之注意事項再填寫本頁) 本發明係關於一種垂直連續退火爐之隔熱設備’當金 屬板被連續地輸送時其在該退火爐中被熱處理。 發明背景= 最近，一種用來在鋼板接受冷輥軋之後對其再結晶及 用來對該鋼板付予良好的可加工性的退火處理主要是藉由 連續的退火而非整批退火來實施。關於一用來實施連續退 火之連續退火爐則有習知的水平連續退火爐，其中退火係 實施於一沿著水平路徑移動的鋼板上，及垂直的連續退火 爐，其中多個輥子被安排在該爐子的上及下部且退火係被 實施於沿著一垂直的路徑移動的鋼板上。在這些連續退活 爐中，對於一大量生產處理而言，即可提高鋼板的通過（ 處理）速度，垂直爐是較有利的。 而且，在目前，使用幅射管之間接加熱對於作爲垂直 連續退火爐的加熱源而言是較流行的，且鋼板主要是被來 自於該加熱源之幅射熱所加熱。 經濟部智慧財產局員工消費合作社印製 在有多個輥子被安排在該爐子的上及下部且退火係被 實施於被該等輥子輸送於一垂直方向上的鋼板上之一垂直 連續退火爐中，當鋼板在每一輥子周圍運轉時改變其移動 方向，即由往上改爲往下或由往下改爲往上，防止鋼板蛇 形扭曲或跑錯路徑及確保鋼板之穩定的路徑是很重要的。 通常，如第1 1圖所示，每一被安排在該爐子中之輥子 1 2被設計成具有一外突輥子凸面其兩個肩部朝向兩端ί頃 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 B7 五、發明說明（2 ) (請先閱讀背面之注意事項再填寫本頁) 斜。此設計是爲了要讓該鋼板通過該爐子使得鋼板藉由利 用一中心力量（箭頭F )作用於該鋼板上來使其一直是以 與輥子的中心接觸的方式來移動，該中心力騎跨於一傾斜 部分上，且根據以一角度纏繞在該輥子的傾斜部分上之鋼 板的一自行定心運動作用在一從輥子邊緣朝向輥子中心的 方向上。 經濟部智慧財產局員工消費合作社印製 然而，如第1 2圖所示的，來自一設在該爐子內之加 熱源（如，一幅射管）1 4之幅射熱不只加熱鋼板1 0， 而且加熱安排在該爐子內的輥子1 2。因此，安排在該爐 子中之輥子的實際輥子凸面爲該輥子之最初凸面（稱爲初 始凸面）加上由來自於加熱源的幅射熱所造成的凸面（稱 爲熱凸面）的總和。其結果爲，當該鋼板的溫度低於輥子 的溫度及當熱凸面大於初始凸面時，輥子中心部分的溫度 被相對地降低且該輥子凸面被成爲下凹，如第1 2圖的實 線所示。如果鋼板1 0移動於具有此一下凹凸面的輥子 1 2上的話，一被產生於該鋼板的寬度方向上的力從輥子 的中心朝向輥子邊作用。因此，當鋼板遭遇蛇形彎曲或脫 離路徑時，鋼板被迫使鋼板騎跨超越該輥子邊緣，這會造 成在鋼板通過時會與爐壁接觸的問題。 爲了要解決此一問題，某些裝置被提出來防止輥子溫 度高過鋼板溫度，如在日本未審之實用新案申請案公開第 6 3 - 1 1 9 6 6 1號中一遮板被提供於來阻擋從加熱源 1 4到該輥子1 2的熱幅射。而且，在日本未審之專利申 請案公開第5 7 - 7 9 1 2 3號中揭示了一種隔熱設備其 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 __ B7 五、發明說明（3 ) 使用一抗熱管讓空氣，氮氣或類此者能夠流過其間以進行 冷卻。 (請先閱讀背面之注意事項再填寫本頁) 再者，因爲發現只使用遮板並不足以抑制熱凸面，所 以在日本未審之專利申請案公開第5 2 — 7 1 3 1 8號中 揭示了一種用來噴灑冷卻氣體至輥子用以控制熱凸面的技 術。甚者，爲了相同的目的，在日本未審之專利申請案公 開第5 3 1 1 9 2 0 8號中揭示了一種用來水冷卻一輥子 邊緣部分，或改變介該輥子中心部分與輥子邊緣部分之間 導熱性的技術。此外，在日本未審之專利申請案公開第 53—130210及第57—23733號中揭示了安 排一與該等輥子分離之冷卻設備以形成一冷卻流路的技術 〇 在上述的這些相關前技的例子中，以正面的方式來抑 制該等輥子的熱凸面的技術在防止鋼板的蛇行彎曲上是有 效的，但卻具有需要大量的設備投資的缺點。另一項問題 在於，因爲該設備本身的尺寸變大，所以該設備的熱容量 需要被增加，這會降低在該加熱區中燃料的單元消耗。 經濟部智慧財產局員工消費合作社印製 發明目的及槪沭： 本發明即著眼於克服上述相關前技之問題而硏發完成 。本發明的一項目的是要在使用一冷卻管的幅射熱隔熱設 備，如揭示於日本未審之專利申請案公開第5 7 -7 9 1 2 3號中者，的基礎上提供一種便宜且更加有效率 的設備。507010 Α7 Β7 V. Description of the invention (1) Field of invention: (Please read the precautions on the back before filling out this page) The present invention relates to a type of vertical continuous annealing furnace's thermal insulation equipment. This annealing furnace is heat-treated. BACKGROUND OF THE INVENTION Recently, an annealing treatment for recrystallizing a steel sheet after it has been subjected to cold rolling and for providing good workability to the steel sheet is mainly performed by continuous annealing rather than batch annealing. As for a continuous annealing furnace for performing continuous annealing, there are conventional horizontal continuous annealing furnaces, in which annealing is performed on a steel plate moving along a horizontal path, and vertical continuous annealing furnaces, in which a plurality of rollers are arranged in The upper and lower parts of the furnace are annealed on a steel plate that moves along a vertical path. Among these continuous deactivation furnaces, for a mass production process, the passing (processing) speed of the steel plate can be increased, and a vertical furnace is more advantageous. Moreover, the use of indirect heating of radiant tubes is currently popular as a heating source for vertical continuous annealing furnaces, and steel plates are mainly heated by radiant heat from the heating source. The Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs is printed in a vertical continuous annealing furnace in which a plurality of rollers are arranged above and below the furnace and the annealing system is implemented on a steel plate conveyed by the rollers in a vertical direction. When the steel plate is running around each roller, change its moving direction, that is, from upward to downward or from downward to upward, to prevent the plate from serpentine distortion or run the wrong path and to ensure the stable path of the plate important. Generally, as shown in Figure 11, each of the rollers 12 arranged in the furnace is designed to have a convex protruding roller surface with two shoulders facing both ends. The paper dimensions are applicable to Chinese national standards (CNS ) A4 size (210 X 297 mm) 507010 A7 B7 5. Description of the invention (2) (Please read the precautions on the back before filling this page) Oblique. This design is to allow the steel plate to pass through the furnace so that the steel plate is always moved in contact with the center of the roller by using a central force (arrow F) to act on the steel plate. A self-centering movement of the steel plate wound on the inclined portion of the roller at an angle acts on the inclined portion in a direction from the edge of the roller toward the center of the roller. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs However, as shown in Fig. 12, the radiant heat from a heating source (such as a radiant tube) 14 installed in the furnace does not only heat the steel plate 1 0 Moreover, the rollers 12 arranged in the furnace are heated. Therefore, the actual convex surface of the roller arranged in the furnace is the sum of the original convex surface of the roller (called the initial convex surface) plus the convex surface (called the thermal convex surface) caused by the radiant heat from the heating source. As a result, when the temperature of the steel plate is lower than the temperature of the roller and when the thermal convex surface is larger than the initial convex surface, the temperature of the central portion of the roller is relatively lowered and the convex surface of the roller becomes concave, as shown by the solid line in FIG. 12 Show. When the steel plate 10 is moved on the roller 12 having the uneven surface below, a force generated in the width direction of the steel plate acts from the center of the roller toward the roller side. Therefore, when the steel plate encounters a serpentine bending or disengagement path, the steel plate is forced to ride over the edge of the roller, which causes a problem that the steel plate will contact the furnace wall when the steel plate passes. In order to solve this problem, some devices have been proposed to prevent the roller temperature from exceeding the temperature of the steel plate. For example, in Japanese Unexamined Utility Model Application Publication No. 6 3-1 1 9 6 6 1 a shutter is provided in To block heat radiation from the heating source 14 to the roller 12. Moreover, Japanese Unexamined Patent Application Publication No. 5 7-7 9 1 2 3 discloses a thermal insulation device whose paper size is applicable to Chinese National Standard (CNS) A4 (210 X 297 mm) 507010 A7 __ B7 V. Description of the invention (3) Use a heat-resistant tube to allow air, nitrogen or the like to flow through it for cooling. (Please read the precautions on the back before filling in this page.) Furthermore, because it was found that using only a shield is not sufficient to suppress thermal convexity, it is disclosed in Japanese Unexamined Patent Application Publication No. 5 2 — 7 1 3 1 8 A technique for spraying cooling gas onto a roller to control a thermal convexity is disclosed. Furthermore, for the same purpose, Japanese Unexamined Patent Application Publication No. 5 3 1 9 2 0 8 discloses a method for cooling the edge portion of a roller with water, or changing the center portion of the roller and the edge of the roller. Thermal conductivity between parts. In addition, Japanese Unexamined Patent Application Publication Nos. 53-130210 and 57-23733 disclose the technology of arranging a cooling device separated from the rollers to form a cooling flow path. In the example, the technique of suppressing the thermal convexity of the rollers in a positive manner is effective in preventing the meandering of the steel plate, but it has the disadvantage of requiring a large amount of equipment investment. Another problem is that as the size of the device itself becomes larger, the heat capacity of the device needs to be increased, which reduces the unit consumption of fuel in the heating zone. Printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economics Purpose of the Invention and the Invention: The present invention was developed with the aim of overcoming the aforementioned problems of the related art. An object of the present invention is to provide a radiant heat insulation device using a cooling pipe, such as disclosed in Japanese Unexamined Patent Application Publication No. 5 7 -7 9 1 2 3, Cheaper and more efficient equipment.
本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297 H 507010 A7 B7 五、發明說明（4 ) (請先閱讀背面之注意事項再填寫本頁) 爲了要達到上述的目的’本發明提供一種垂直連續退 火爐之幅射熱隔熱設備’其中有多個輥子被安排在該爐子 的上及下部分中及熱處理是在金屬板被該等輕子連繪輸送 時被施加於金屬板上。當金屬板在每一輥子周圍轉彎而由 向上變爲向下，或由向下變爲向上地改變其移動方向時， 金屬板該等輥子連續輸送於垂直方向上。最好是’該幅射 熱隔熱設備被設置在該爐子的上部中的一輥子的底下’及 /或在該爐子的下部中的一輕子之上的位置’用以阻隔由 一設在該爐子內的一加熱源所幅射出之熱。該幅射熱隔熱 設備包含一雙壁管’其包括一內管具有一外部大氣抽吸埠 水平地或向下地突伸出用以露在一外部的大氣中，及一外 管具有排放埠向上地突伸出用以露在該外部的大氣中。 在該幅射熱隔熱設備中，該雙壁管之外管的外徑D最 好是不小於6 0公釐，介於該外部大氣抽吸埠與該排放埠 之間的水平差Η不小於1 5 0公釐，及該雙壁管之外管的 外徑D (單位：公尺）與該水平差Η (單位公尺）滿足以 下的關係式： 經濟部智慧財產局員工消費合作社印製 Ό2χ^(Η) . 2x10^ (1) 再者，根據本發明，該幅射熱隔熱設備的某些實施例 包含多根如上所述之雙壁管。該等雙壁管可被水平地設置 在該爐子的上部中的該輥子底下及/或該爐子的下部中的 該輥子之上的位置處。 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 Α7 Β7 五、發明說明（5 ) (請先閱讀背面之注意事項再填寫本頁) 或者，在某些實施例中，該幅射熱隔熱設備包含一或 多根如上所述之雙壁管，且該等雙壁管被用作爲支撐管及 一遮板被固定於支撐管上。 圖式簡單說明： 第1圖爲一垂直剖面圖，其顯示使用於本發明的一該 幅射熱隔熱設備的一第一實施例中之雙壁管的結構； 第2圖包含側視圖及正視圖，其顯示使用一平板之傳 統例子，使用一單純的冷卻管之對照例，及使用根據本發 明的雙壁管的形式之冷卻管的第一實施例； 第3圖爲一圖表，其顯示冷卻氣體的流率（Q)與每 一雙壁管的外管的表面溫度之間及與一平板的表面溫度之 間的關係用以說明本阿明之原理； 第4圖爲一圖表，其顯示冷卻氣體的流率，在一輥子 上於鋼板的寬度方向上的溫度差（A T )，及鋼板發生蛇形 彎曲之間的關係； 第5圖爲一圖表，其顯示在冷卻氣體的流率與外管的 外徑（D )的平方乘水平差（Η )的平方根之間的關係； 經濟部智慧財產局員工消費合作社印製 第6圖爲一圖表，其顯示冷卻氣體流率（Q )與水平 差（Η )之間的關係； 第7圖爲一側視圖，其顯示根據本阿發的幅射熱隔熱 設備的一第二實施例的結構； 第8圖爲一側視圖，其顯示根據本發發的幅射熱隔熱 設備的一第三實施例的結構； -8- 本紙張尺度適用中國國家標準（CNS)A4規格（210 Χ 297公釐） 507010 A7 B7 五、發明說明（6 ) (請先閱讀背面之注意事項再填寫本頁) 第9圖爲一圖表，其顯示在使用一平板之傳統例子中 ，在使用一單純的冷卻管的對照例中，及在本發明中之蛇 形彎曲的發生； 第1 0圖爲一圖表，其顯示在傳統例，在對照例及在 本發明中該幅射熱隔熱設備的更換頻率； 第1 1圖爲一正視圖，其顯示一輥子其被安排在一爐 子中且具有一外突的莞子凸面； 第1 2圖爲一正視圖，其顯示一鋼板被一設在一爐子 中且具有一導因於施加至該輥子熱凸面之內凹凸面之輥子 所輸送的狀態； 第1 3圖爲一退火爐的示意圖，其包括本發明之幅射 熱隔熱設備的一實施例。 主要元件對照 10 鋼板 12 輥子 14 加熱源 20 雙壁管 經濟部智慧財產局員工消費合作社印製 22 內管 23 外部大氣抽吸埠 24 外管 25 排放埠 D 外管之外徑 Η 水平差This paper size applies to China National Standard (CNS) A4 specifications (210 X 297 H 507010 A7 B7 V. Description of the invention (4) (Please read the precautions on the back before filling this page) In order to achieve the above purpose, the present invention provides A radiation continuous thermal insulation device of a vertical continuous annealing furnace 'in which a plurality of rollers are arranged in the upper and lower parts of the furnace and the heat treatment is applied to the metal plate when the metal plate is conveyed by the continuous lepton painting When the metal plate turns around each roller and changes its moving direction from upward to downward, or from downward to upward, the rollers of the metal plate are continuously conveyed in the vertical direction. It is best to 'the frame The thermal radiation insulation device is disposed under a roller in the upper part of the furnace and / or in a position above a lepton in the lower part of the furnace to block heating by a heater provided in the furnace The heat radiated from the source. The radiant heat insulation device includes a double-walled tube, which includes an inner tube with an external atmospheric suction port protruding horizontally or downwardly for exposure in an external atmosphere. , And an outer tube has a row The port protrudes upward to be exposed to the outside atmosphere. In the radiant heat insulation equipment, the outer diameter D of the outer tube of the double-walled tube is preferably not less than 60 mm, between The horizontal difference between the external atmospheric suction port and the discharge port is not less than 150 mm, and the outer diameter D (unit: meter) of the outer tube of the double-walled pipe and the horizontal difference (unit meter) ) Satisfies the following relationship: printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs Ό2χ ^ (Η). 2x10 ^ (1) Furthermore, according to the present invention, some embodiments of the radiation heat insulation device include multiple Double-walled tubes as described above. The double-walled tubes can be placed horizontally under the roller in the upper part of the furnace and / or above the roller in the lower part of the furnace. This paper size applies to China National Standard (CNS) A4 Specification (210 X 297 mm) 507010 Α7 Β7 V. Description of Invention (5) (Please read the precautions on the back before filling this page) Or, in some embodiments, the radiant heat Insulation equipment comprises one or more double-walled pipes as described above, and these double-walled pipes are used as support pipes and A shutter is fixed on the support tube. Brief description of the drawings: Figure 1 is a vertical cross-sectional view showing a double-walled tube used in a first embodiment of the radiation heat insulation device of the present invention. Fig. 2 contains a side view and a front view showing a conventional example using a flat plate, a comparative example using a simple cooling tube, and a first implementation using a cooling tube in the form of a double-walled tube according to the present invention Example; Figure 3 is a graph showing the relationship between the flow rate (Q) of the cooling gas and the surface temperature of the outer tube of each double-walled tube and the surface temperature of a flat plate to illustrate Ben Amin's Principle; Figure 4 is a graph showing the relationship between the flow rate of the cooling gas, the temperature difference (AT) in the width direction of the steel plate on a roller, and the meandering of the steel plate; Figure 5 is a A graph showing the relationship between the flow rate of the cooling gas and the square root of the outer diameter (D) of the outer tube times the square root of the level difference (Η); printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs. Figure 6 is a graph , Which shows the cooling gas flow rate (Q) The relationship between the level differences (；); FIG. 7 is a side view showing the structure of a second embodiment of the radiation heat insulation device according to Ben Afa; FIG. 8 is a side view showing According to the structure of a third embodiment of the radiation heat insulation equipment according to the present invention; -8- This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 507010 A7 B7 V. Description of the invention ( 6) (Please read the precautions on the back before filling out this page) Figure 9 is a chart showing the traditional example of using a flat plate, the comparative example using a simple cooling tube, and in the present invention The occurrence of the serpentine bending; Fig. 10 is a graph showing the replacement frequency of the radiant heat insulation equipment in the conventional example, the comparative example and the present invention; Fig. 11 is a front view, A roller is shown which is arranged in a furnace and has a convex convex surface. Figure 12 is a front view showing a steel plate which is set in a furnace and has a cause due to being applied to the roller. Conveying state of the concave and convex surface rollers in the hot convex surface; A schematic view of an annealing furnace, comprising a radiation heat insulating device of the present invention in one embodiment. Comparison of main components 10 Steel plate 12 Roller 14 Heating source 20 Double-walled tube Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs 22 Inner tube 23 External air suction port 24 Outer tube 25 Drain port D Outer tube outer diameter Η Level difference
本紙張^度適用中國國家標準（CNS)A4規格（210 X 297公H 507010 Α7 ______ Β7 五、發明說明（7 ) 發明詳細說明： 本發明的實施例將參照附圖於下文中詳細說明。 (請先閱讀背面之注意事項再填寫本頁) 本發明之一幅射熱隔熱設備被設置在一位在一垂直連 續退火爐的上部的輥子底下（最好是正下方），及/或被 設置在一位在一垂直連續退火爐的下部的輥子上方（最好 是正上方），用以阻隔從一設在該爐子中之加熱源幅射出 的熱，且該隔熱設備幾乎與該輥子平行。 在如第1圖所示之本發明的一第一實施例中，該幅射 熱隔熱設備具有一雙壁管2 0結構，其包括一內管2 2具 有一外部大氣抽吸埠2 3水平地或向下地突伸出用以露在 一外部的大氣中，及一外管2 4具有排放埠2 5向上地突 伸出用以露在該外部的大氣中。藉由此一結構，一種便宜 且更有效率之幅射熱隔熱設備可藉著有效地應用外部大氣 (如空氣的自然對流來達成。 經濟部智慧財產局員工消費合作社印製 再者，藉由對於流經該雙壁管2 0的冷卻氣體（空氣 )的流率，一幅射熱阻隔效果，及雙壁管之高溫蠕變阻力 之重復的實驗，本案發明人發現最適當之阻隔幅射熱的# 數範圍爲該雙壁管2 0之外管2 4的外徑D不小於6 〇 & 釐，介於該外部大氣抽吸埠2 3與該排放埠2 5之間的7jc 平差（距離）Η不小於1 5 0公釐，及該雙壁管之外管 2 4的外徑D (單位··公尺）與該水平差Η (單位公尺> 滿足以下的關係式： 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 B7 五、發明說明（8 ) Ό 2 X (H)^2.2xl0-3 (1) (請先閱讀背面之注意事項再填寫本頁) 耐熱合金鋼爲適合用來形成該雙壁管2 〇的材料的一 個例子。例如’具有C r含量不少於1 8重量百分比及 N i含量不少於8重量百分比之不銹鋼或具有高耐熱性之 特殊鋼都是較佳的材料。 本案發明人發現，使用揭示於日本未審之專利申請案 公開第5 7 — 7 9 1 2 3號中之一傳統的冷卻管在其利用 一外部大氣（空氣的自然對劉的冷卻能力上有所限制。該 日本未審之專利申請案公開第5 7 — 7 9 1 2 3號揭示用 於冷卻的空氣係藉由一抽吸鼓風機或一壓力鼓風機而被迫 使流入該冷卻管中。然而，當一鼓風機被提供於該抽吸側 時，該鼓風機會吸入高溫的排放氣體，因此該鼓風機本身 必需由耐熱材質所製成，否則的話一用來冷卻抽吸氣體的 裝置必需被設置在該鼓風機的上游處。無論何種情形，該 設備的成本必會增加。在另一方面，當一壓力鼓風機被用 來迫使冷卻氣體流入該冷卻管時，即存在著導因於空氣從 冷卻管漏入該爐中之一金屬（或鋼）板被氧化的危險。 經濟部智慧財產局員工消費合作社印製 根據以上的發現，本案發明人製造了具有三種示於第 2圖中之結構的幅射熱隔熱設備並對實際的設備進行測試 〇 第2圖的左側代表一傳統的例子其使用一單純的平板 形式之遮板1 6。一板材（典型地爲一鋼板）；一輕子 1 2被設置於一爐子內；及一加熱源1 4 (典型地爲一幅 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 B7 五、發明說明（9 ) (請先閱讀背面之注意事項再填寫本頁) 射管）被示出。第2圖的中因代表一對照例其使用一單純 的直的雙壁管形式之冷卻管1 8。第2圖的右側代表本發 明的第一實施例其包括如第1圖所示之雙壁管形式的冷卻 管2 0。 第3圖爲一圖表，其顯示藉由測量每一雙壁管的一外 管及一平板的表面溫度（面向被設置於該爐中的輥子1.2 的一側）所得的結果，其由垂直軸來表示，相對於在每一 雙壁管的外管的排放埠所測得的冷卻氣體（空氣）的流率 ，其由水平軸來表示，的關係。測量條件被設定爲，爐子 溫度爲9 0 0°C，外部大氣（冷卻氣體）的溫度爲3 0 0 t，該雙壁管的外管直徑爲1 0 0公釐，該雙壁管的內管 直徑爲4 0公釐，及介於該雙壁管的該外部大氣抽吸埠 2 3與該排放璋2 5之間的水平差爲2 0 0公釐。 在對照例中，其所使用的冷卻管（單純直的雙壁管） ，在該雙壁管中對於外部大氣抽吸埠及排放埠，如第3圖 中的記號Δ所標示者，沒有任何的改善，導因於自然對流之 冷卻氣體的流率很小且該雙壁管的外管表面溫度達到 8 0 0 〇C。 經濟部智慧財產局員工消費合作社印製 在此該傳統的例子中（使用平板），如記號□所標示 者，該平板的表面溫度達到8 6 0 °C。 相反的，在本發明之第一實施例中，其中該雙壁管被 改良使而具有分別向下及向上突身出而露在該外部大氣中 之外部大氣抽吸埠及排放埠，如第3圖中之記號〇所標示 者，該冷卻氣體流率達到5 · ΟΧΙΟ-3 (Nm3/s) 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 B7 五、發明說明（ίο ) 且該外管的表面溫度則被降至約5 0 0 °C。 (請先閱讀背面之注意事項再填寫本頁) 第4圖爲一圖表，其顯示在根據本發明的雙壁管的外 管的排放埠所測得之冷卻氣體（空氣）的流率與輥子在板 材寬度方向上的溫度差△ T之間的關係。所測得之輥子溫 度是由埋在該輥子內的寬度方向上且被置於該該幅射熱隔 熱設備的正上方，大致與輥子平行的熱電耦所測得。測量 條件被設定爲，輥子筒的長度爲2 0 0 0公釐，通過該爐 子的鋼板平均寬度爲1 2 6 0公釐，及平均爐溫爲9 0 0 °C。此處，溫度差ΔΤ被定義爲ΔΤ = Τ e (輥子上在與 輥子邊緣距離1 0 0公釐的點之表面溫度）一 T c (輥子 中心之表面溫度）。第4圖的圖表顯示最小的溫度差△ T 約爲1 5 0 t，在該處輥子凸面被內凹地減小且該鋼板遭 遇到蛇形彎曲，及防止鋼板蛇形彎曲所需之冷卻氣體流率 應不小於 3 · 0 X 1 0 — 3 ( N m 3 / s )。 在上述之本發明的第一實施例中，該外部大氣抽吸璋 被描述爲向下突出。然而，該外部大氣抽吸埠並不侷限此 種設計。該外部大氣抽吸埠可突伸於不同的方向’如水平 方向。 經濟部智慧財產局員工消費合作社印製 在根據此一實施例之幅射熱隔熱設備中，其包含一雙 壁管其具有一外部大氣抽吸部水平地或向下地突伸出以露 出外部大氣中及一向上突伸出的的排放埠以露出在該外部 大氣中，在該雙壁管中所發展之由該外部大氣抽吸埠至該 排放埠之煙囪效應被用來滿足上述所需之冷卻氣體流率。 藉由一流體之質量守恆定律，該冷卻氣體的流率 -Ί3- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 A7 B7 五、發明說明（11 ) Q (m3/s )是由下面的等式被導出： (請先閱讀背面之注意事項再填寫本頁) Q:Vg X 7Γ x(D/2)2 ( 2 ) 其中Vg爲冷卻氣體在排放埠的流速（m/s )及D爲 外管的外徑（m )。 而且，藉由一流體能量守恆定律，該冷卻氣體在排放 埠的流速（m/s )可由下面的等式導出=This paper is compliant with China National Standard (CNS) A4 specifications (210 X 297 male H 507010 A7 ______ B7 V. Description of the invention (7) Detailed description of the invention: The embodiments of the present invention will be described in detail below with reference to the drawings. Please read the precautions on the back before filling this page.) One of the radiant heat insulation equipment of the present invention is set under a roller (preferably directly below) in the upper part of a vertical continuous annealing furnace, and / or is set Above a roller (preferably directly above) in the lower part of a vertical continuous annealing furnace to block the heat radiated from a heating source provided in the furnace, and the heat insulation device is almost parallel to the roller In a first embodiment of the present invention as shown in FIG. 1, the radiant heat insulation device has a double-walled tube 20 structure, which includes an inner tube 2 2 and an external atmospheric suction port 2. 3 protrudes horizontally or downwardly to be exposed in an external atmosphere, and an outer tube 24 has a discharge port 25 and protrudes upwardly to be exposed to the external atmosphere. With this structure , A cheaper and more efficient radiation heat insulation device This can be achieved by the effective application of the external atmosphere (such as natural convection of air.) Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs, by the flow rate of the cooling gas (air) flowing through the double-walled tube 20 A repeated experiment of radiant heat blocking effect and high-temperature creep resistance of double-walled tubes. The inventor of the present case found that the most suitable range of # for blocking radiant heat is from the double-walled tube 20 to the tube 2 4 The outer diameter D is not less than 60%, and the 7jc adjustment (distance) between the external atmospheric suction port 23 and the discharge port 25 is not less than 150 mm, and the double-walled pipe The outer diameter D (unit ·· meter) of the outer tube 2 4 and the horizontal difference (unit meter >) satisfy the following relationship: This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 meters) (Centi) 507010 A7 B7 V. Description of the invention (8) Ό 2 X (H) ^ 2.2xl0-3 (1) (Please read the precautions on the back before filling this page) Heat-resistant alloy steel is suitable for forming the double wall An example of the material of the tube 2 0. For example, 'having a Cr content of not less than 18 weight percent and a Ni content of not less than 8 weight Fractional stainless steel or special steel with high heat resistance are preferred materials. The inventors of this case have found that using one of the traditional ones disclosed in Japanese Unexamined Patent Application Publication No. 5 7-7 9 1 2 3 The cooling pipe is limited in its use of an external atmosphere (the nature of air to Liu's cooling capacity. The Japanese Unexamined Patent Application Publication No. 5 7 — 7 9 1 2 3 discloses that the air used for cooling is by A suction blower or a pressure blower is forced to flow into the cooling pipe. However, when a blower is provided on the suction side, the blower may inhale high-temperature exhaust gas, so the blower itself must be made of a heat-resistant material If not, a device for cooling the suction gas must be provided upstream of the blower. In either case, the cost of the equipment is bound to increase. On the other hand, when a pressure blower is used to force the cooling gas into the cooling pipe, there is a danger that a metal (or steel) plate oxidized due to air leaking from the cooling pipe into the furnace. Printed by the Consumer Cooperative of Intellectual Property Bureau of the Ministry of Economic Affairs Based on the above findings, the inventor of this case manufactured a radiation thermal insulation device with three structures shown in Figure 2 and tested the actual device. Left side of Figure 2 Representing a traditional example, it uses a shield 16 in the form of a simple flat plate. A plate (typically a steel plate); a lepton 12 is set in a furnace; and a heating source 1 4 (typically a paper size that applies the Chinese National Standard (CNS) A4 specification (210 X 297) (Mm) 507010 A7 B7 V. Description of the invention (9) (Please read the notes on the back before filling this page) The shot tube is shown. The middle cause in Fig. 2 represents a comparative example which uses a cooling pipe 18 in the form of a simple straight double-walled pipe. The right side of FIG. 2 represents the first embodiment of the present invention, which includes a cooling pipe 20 in the form of a double-walled tube as shown in FIG. Fig. 3 is a graph showing the results obtained by measuring the surface temperature of an outer tube and a flat plate of each double-walled tube (facing the side of the roller 1.2 provided in the furnace), which is represented by the vertical axis The relationship between the flow rate of the cooling gas (air) measured at the discharge port of the outer pipe of each double-walled pipe is represented by the horizontal axis. The measurement conditions were set as follows: the furnace temperature was 900 ° C, the temperature of the external atmosphere (cooling gas) was 300 t, the diameter of the outer tube of the double-walled tube was 100 mm, and the inner diameter of the double-walled tube was 100 mm. The diameter of the tube is 40 mm, and the level difference between the external atmospheric suction port 23 and the discharge port 25 of the double-walled tube is 200 mm. In the comparative example, the cooling pipe (simple straight double-wall pipe) used in the double-wall pipe has no external air suction port and discharge port, as indicated by the symbol Δ in FIG. 3. The improvement is due to the low convection cooling gas flow rate and the outer tube surface temperature of the double-walled tube reaching 800 ° C. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs. In this traditional example (using a flat plate), as indicated by the mark □, the surface temperature of the flat plate reaches 860 ° C. In contrast, in the first embodiment of the present invention, the double-walled tube is modified so as to have an external atmospheric suction port and a discharge port protruding downward and upward, respectively, and exposed in the external atmosphere. As indicated by the symbol 〇 in the figure 3, the cooling gas flow rate reaches 5 · 〇ΧΙΟ-3 (Nm3 / s). The paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) 507010 A7 B7 V. DESCRIPTION OF THE INVENTION (ίο) and the surface temperature of the outer tube is reduced to about 50 ° C. (Please read the precautions on the back before filling this page) Figure 4 is a chart showing the cooling gas (air) flow rate and roller measured at the discharge port of the outer pipe of the double wall pipe according to the present invention The relationship between the temperature difference ΔT in the width direction of the plate. The measured temperature of the roller is measured by a thermocouple which is buried in the width direction of the roller and placed directly above the radiant heat insulation device, which is approximately parallel to the roller. The measurement conditions were set such that the length of the roller cylinder was 2000 mm, the average width of the steel plate passing through the furnace was 1260 mm, and the average furnace temperature was 900 ° C. Here, the temperature difference ΔΤ is defined as ΔΤ = T e (surface temperature of the roller at a point at a distance of 100 mm from the edge of the roller)-T c (surface temperature of the center of the roller). The graph in Figure 4 shows that the minimum temperature difference ΔT is about 150 °, where the convex surface of the roller is concavely reduced and the steel plate encounters serpentine bending, and the cooling gas flow required to prevent the steel plate from serpentine bending. The rate should not be less than 3 · 0 X 1 0 — 3 (N m 3 / s). In the above-described first embodiment of the present invention, the external atmospheric suction 璋 is described as protruding downward. However, the external atmospheric suction port is not limited to this design. The external atmospheric suction port may protrude in different directions', such as a horizontal direction. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs in the radiation heat insulation device according to this embodiment, which includes a double-walled tube having an external atmospheric suction portion protruding horizontally or downwardly to expose the outside The atmosphere and an upwardly protruding discharge port are exposed to the external atmosphere. The chimney effect developed in the double-walled pipe from the external atmosphere suction port to the discharge port is used to meet the above requirements. The cooling gas flow rate. By the law of conservation of the mass of a fluid, the flow rate of the cooling gas-Ί3- This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) 507010 A7 B7 V. Description of the invention (11) Q (m3 / s) is derived from the following equation: (Please read the precautions on the back before filling this page) Q: Vg X 7Γ x (D / 2) 2 (2) where Vg is the flow rate of the cooling gas at the discharge port (M / s) and D are the outer diameters (m) of the outer tube. Moreover, by a law of conservation of fluid energy, the flow velocity (m / s) of the cooling gas at the discharge port can be derived from the following equation =
Vg （2gH) (3) 其中g爲重力加速度（二9 · 8m/s2)及Η爲介於 該雙壁管的外部大氣抽吸部與排放埠之間的水平差（m ) 〇 將等式（2 )及（3 )結合得到以下的公式： (2gH) X π X (D/2) 2 (4) 經濟部智慧財產局員工消費合作社印製 根據公式（4 )，冷卻氣體體流率Q與外管的外徑成 正比且亦與介於該雙壁管的外部大氣抽吸埠與排放埠之間 的水平差Η的平方根成正比。 第5圖爲一圖表，其繪出代表介於參數D2x/~ (Η) (水平軸），與冷卻氣體流率Q ( N m 3 / s )之間的關係 實際測得的資料。第5圖的圖表顯示需要D 2 X y( Η ) ^ _本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ^ - 507010 A7 _______________ B7 五、發明說明（12 )Vg (2gH) (3) where g is the acceleration of gravity (two 9 · 8m / s2) and Η is the level difference (m) between the external atmospheric suction part and the discharge port of the double-walled tube. (2) and (3) combined to get the following formula: (2gH) X π X (D / 2) 2 (4) Printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs According to formula (4), the cooling gas volume flow rate Q It is proportional to the outer diameter of the outer tube and is also proportional to the square root of the horizontal difference between the external atmospheric suction port and the discharge port of the double-walled tube. Figure 5 is a graph that plots the actual measured data representing the relationship between the parameter D2x / ~ (Η) (horizontal axis) and the cooling gas flow rate Q (N m 3 / s). The chart in Figure 5 shows the need for D 2 X y (Η) ^ _ This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) ^-507010 A7 _______________ B7 V. Description of the invention (12)
2 · 2 X 1 0 — 3來滿足冷卻氣體的流率不小於3 . Ο X (請先閱讀背面之注意事項再填寫本頁) 1 0—3 (Nm3/s )的要求。換言之，一般已知在實際 的操作期間爐子的溫度約在5 〇 〇 °C至9 〇 〇 °c的範圍之 間，不小於上述値之冷卻氣體流率足以達到所需的冷卻。 因此，如果D2x/ (H) 22 · 2xl〇~3被滿足的話 ，則一足夠的冷卻效果可在實際的操作期間被提供。 第6圖爲一圖表，其顯示介於該冷卻氣體的流率 Q ( N m 3 / s )與該雙壁管的外部抽吸埠與排放埠間的水 平差Η (公釐）之間的關係。第6圖的圖表顯示，如果該 水平差小於1 5 0公釐的話，則該冷卻氣體就會變得很難 流動因爲水平差Η大致在與對應的雙壁管的直徑相同的水 平上。因此，介於該雙壁管的外部抽吸埠與排放埠間的水 平差Η最好是被設定在不小於1 5 0公釐。 而且，如果該雙壁管的的外管的外徑小的話，則該外 管更易於承受導因於幅射熱之蠕變。由目前經歷之本發明 的實際操作來看’已被確認的是該外管的外徑最好是不小 於6 0公釐。 再者，在該雙壁管的外徑與內徑的外技比例最好是在 經濟部智慧財產局員工消費合作社印製 2 · 0至4 · 0之間。 該外徑最好是由具有C r含量不少於1 8重量百分比 及N i含量不少於8重量百分比之不銹鋼製成’根據 J I S (日本公業標準），該不銹鋼爲SUS304， SUS316 及 SUS316L。 當安裝該雙壁管時，該雙壁管之外部大氣抽吸埠最好 -15- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 507010 Α7 Β7 五、發明說明（13 ) 是與該爐壁間隔1 0 0公釐或更多。 當裝設於該爐子中之輥子具有比該幅射熱隔設備的雙 壁管的直徑大好幾倍的直徑時，使用包含一雙壁管單元很 難重充分地將由該加熱源朝向輥子表面的幅射熱加以阻隔 。在此一例子中，該幅射熱可藉由示於第7及8圖中之本 發明的其它實施例來加以有效的阻隔。在示於第7圖中之 本發明的第二實施例中，多個雙壁管2 0被水平並排地安 排在位在該爐子上部中之輥子的正下方，及/或在位在在 該爐子下部中之輥子的正上方。 在示於第7圖中之本發明的第三實施例中，一或多個 (兩個被示出）雙壁管2 0被用作爲支撐管且一遮板3 0 如所示的被固定於該等支撐管上。第7及8圖亦顯示輥子 1 2，加熱源1 4及鋼板1 0的配置。 例子 根據上述對於實際設備所實施之測試的結果，示於第 1圖中之雙壁管係使用SUS 3 1 6來製造。該雙壁管之 外管的外徑爲114·3公釐’該外管的內徑爲97·1 公釐，該內管的外徑爲48·0公釐’及該內管的內徑爲 4 1 · 2公釐。介於該雙壁管的外部大氣抽吸埠與排放淳 之間的水平差Η爲2 0 0公釐。多個幅射熱隔熱設備，每 一個都包含如此被製造的雙壁管’被安裝在一垂直連續退 火爐的加熱區的上及下部中，如第1 3圖所示。該幅射熱 隔熱設備被安裝在該加熱區的上部中的一距離其底下的每 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公爱） (請先閱讀背面之注意事項再填寫本頁) . --線· 經濟部智慧財產局員工消費合作社印製 507010 A7 _ B7 五、發明說明（14 ) (請先閱讀背面之注意事項再填寫本頁) 一輥子4 0 0公釐的水平位置上。而且該幅射熱隔熱設備 被安裝在該加熱區的下部中的一距離其上面的每一輥子 4 0 0公釐的水平位置上。該實際被安裝之該幅射熱隔熱 設備的隔熱效果是藉由在一般的條件下操作該爐子兩年來 加以測量的。 測量的結果被示於第9圖（蛇形彎曲的發生）中及第 1 0圖（該幅射熱隔熱設備的更換頻率）中。在本發明中 ，如第9圖所示的，蛇形彎曲的發生被降低到分別使用一 平板及一單純的冷卻管之傳統及對照幅射熱隔熱設備的 1/3。而且，如第10圖中所示的，與傳統的及對照的 設備比較起來，本發明之該幅射熱隔熱設備的有效壽命被 延長，因爲在本發明中藉由有效地利用在一冷卻管中從該 外部抽吸埠至排放埠所發展的一氣流的煙囪效應而使得冷 卻作用被加強。 此外，在第1 3圖的結構中，本發明之包括該雙壁管 2 0的該幅射熱隔熱設備被設置於該上部中之介於相鄰路 徑之間的位置，即不單是在每一輥子1 2底下的位置。該 隔熱效應可藉由如此安排的幅射熱隔熱設備而被加強。 經濟部智慧財產局員工消費合作社印製 如上所述的，本發明可提供一幅射熱隔熱設備，其相 當便宜，在防止一板材的蛇形彎曲上相當有效，且具有力口 長的有效壽命，因爲有效地利用在一冷卻管中從該外部抽 吸埠至排放埠所發展的一氣流的煙囪效應。 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐）2 · 2 X 1 0-3 to meet the cooling gas flow rate of not less than 3. 〇 X (Please read the precautions on the back before filling in this page) 1 0-3 (Nm3 / s) requirements. In other words, it is generally known that the temperature of the furnace during actual operation is in the range of about 500 ° C to 9000 ° C, and the cooling gas flow rate of not less than the above mentioned temperature is sufficient to achieve the required cooling. Therefore, if D2x / (H) 22 · 2x10 ~ 3 is satisfied, a sufficient cooling effect can be provided during actual operation. Fig. 6 is a graph showing the difference between the flow rate Q (N m 3 / s) of the cooling gas and the level difference (mm) between the external suction port and the discharge port of the double-walled pipe. relationship. The graph in Figure 6 shows that if the level difference is less than 150 mm, the cooling gas becomes difficult to flow because the level difference is approximately at the same level as the diameter of the corresponding double-walled pipe. Therefore, the level difference between the external suction port and the discharge port of the double-walled pipe is preferably set to not less than 150 mm. Moreover, if the outer diameter of the outer tube of the double-walled tube is small, the outer tube is more likely to withstand creep caused by radiant heat. Judging from the actual operation of the present invention, it has been confirmed that the outer diameter of the outer tube is preferably not less than 60 mm. Furthermore, the external technology ratio of the outer diameter to the inner diameter of the double-walled pipe is preferably printed between 2 · 0 and 4 · 0 by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs. The outer diameter is preferably made of stainless steel having a Cr content of not less than 18% by weight and a Ni content of not less than 8% by weight. 'According to JIS (Japanese Public Standard), the stainless steel is SUS304, SUS316, and SUS316L. . When installing the double-walled pipe, the external atmospheric suction port of the double-walled pipe is preferably -15- This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) 507010 Α7 Β7 V. Description of the invention ( 13) It is 100 mm or more spaced from the furnace wall. When the roller installed in the furnace has a diameter several times larger than the diameter of the double-walled tube of the radiant heat insulation device, it is difficult to fully and sufficiently direct the heating source toward the surface of the roller using a double-walled tube unit. Radiation heat is blocked. In this example, the radiant heat can be effectively blocked by other embodiments of the present invention shown in Figs. In the second embodiment of the present invention shown in FIG. 7, a plurality of double-walled tubes 20 are arranged horizontally side by side directly under a roller positioned in the upper part of the furnace, and / or positioned in the Just above the rollers in the lower part of the stove. In the third embodiment of the invention shown in Fig. 7, one or more (two are shown) double-walled tubes 20 are used as support tubes and a shutter 30 is fixed as shown On these support tubes. Figures 7 and 8 also show the arrangement of the rollers 12, the heating source 14, and the steel plate 10. Example Based on the results of the tests performed on the actual equipment described above, the double-walled pipe system shown in Figure 1 was manufactured using SUS 3 16. The outer diameter of the outer tube of the double-walled tube is 114 · 3 mm ', the inner diameter of the outer tube is 97.1 mm, the outer diameter of the inner tube is 48.0 mm', and the inner diameter of the inner tube It is 4 1 · 2 mm. The horizontal difference between the external atmospheric suction port of the double-walled pipe and the discharge temperature is 200 mm. A plurality of radiant heat insulation devices, each including the double-walled tube thus manufactured, are installed in the upper and lower portions of a heating zone of a vertical continuous annealing furnace, as shown in Fig. 13. The radiant heat insulation equipment is installed in the upper part of the heating zone at a distance from each paper standard below it to the Chinese National Standard (CNS) A4 specification (210 X 297 public love) (Please read the precautions on the back first (Fill in this page again.).-Printed by the Consumers' Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs 507010 A7 _ B7 V. Description of Invention (14) (Please read the precautions on the back before filling this page) One roller 4 0 0 In the horizontal position. Furthermore, the radiant heat insulation device is installed at a horizontal position of 400 mm from each of the rollers in the lower part of the heating zone. The thermal insulation effect of the radiant heat insulation equipment actually installed was measured by operating the furnace under normal conditions for two years. The results of the measurements are shown in Figure 9 (the occurrence of serpentine bending) and Figure 10 (the frequency of replacement of the radiant thermal insulation device). In the present invention, as shown in Fig. 9, the occurrence of serpentine bending is reduced to one third of that of a conventional and control radiation heat insulation device using a flat plate and a simple cooling pipe, respectively. Moreover, as shown in FIG. 10, the effective life of the radiant heat insulation device of the present invention is extended compared with the conventional and comparative devices, because in the present invention, by effectively utilizing a cooling The cooling effect is enhanced by the chimney effect of a stream of air flowing from the external suction port to the discharge port in the tube. In addition, in the structure of FIG. 13, the radiant heat insulation device of the present invention including the double-walled tube 20 is disposed in the upper part between adjacent paths, that is, not only in Position under each roller 1 2. This thermal insulation effect can be enhanced by the radiant thermal insulation device thus arranged. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs as described above, the present invention can provide a radiant heat insulation device, which is relatively cheap, is quite effective in preventing the serpentine bending of a plate, and has a powerful force. Lifetime, because the chimney effect of an airflow developed from the external suction port to the discharge port in a cooling pipe is effectively used. This paper size applies to China National Standard (CNS) A4 (210 X 297 mm)