201036721 六、發明說明： 【發明所屬之技術領域】 特別是一滾壓架的工 本發明關於一種用於將滾子一 作滾子--冷却的方法與裝置。 Ο 〇 在將金屬滾壓時，該參與滾壓程序的滾子――工作滾 子y—被加熱。為了作保護滾子以防損壞以及將使用㈣ 儘量延長，故將該滾子冷却。在大多數的滚遷廠中，使用 現代的冷却系統’它們制喷嘴〔且宜為爲平噴流喷嘴 (Flachstrah刷se，英：fiatjetn〇zzie)〕將一冷却液喷壤 到滾子表面，這種冷却作用稱為「喷壤冷却」。所選設的 壓力位準，各依滾子長度而定在6巴〜12巴，且在例子情 形可為2G巴。除了將滾子儘量密集地冷却的目的外，為了 將其熱負荷和幾何膨脹作限制’該工作滾子冷却作用須做 到使滾子保持不帶污染物、氧化物及錄垢粒子。冷卻作用 隨著冷却劑的量增加及冷却賴力增加而上。此系統之 缺點為需要大量之能量’且在較高廢力時’泵的維修成本 較高。 【先前技術】 、穿子的種可能之冷却方式為低壓冷却。在國際 〇 2GG8/1G4G37 A1發表了—種在低壓範圍用高奮冷 、气的冷却裝置，纟中利用喷嘴或孔（它們設在一凹形 的冷却彳毕y λ ΐί#· ψ、人 ’、 $出冷却劑將一滾子冷却。藉著冷却樑的設 置以及利用側板（ < 卩匕們i又在冷却樑的端侧）可形成一均勻 的水墊，並有一股冬、味 叹京教式無足向性的液流。但只有當滚子 3 201036721 的因磨損而漸改變的直徑範圍〔它係利用研磨（Ah·) 而造成〕配合冷却裝置的曲率設定，該冷却裝置才能以令 人滿意及可重S (reproducible)的方式工作。由於今日： 子一般的研磨範圍約為最大滚子直徑的1〇% ,因此;要= 個滾壓裝置以供不同之滾子直徑之用，這點使得^需要 有整套“mu缺點為：對於&袞壓架以及在每次 更換工作滾子後，不可能調整冷卻裝置的曲率以配合滾子 直徑的改變，0此喷嘴或孔距滚子表面的距離（且因此還 有冷却效果）在滾壓程序時從一次滾子更換時到下次滾更 換時都會改變。 在德專利DE 3616 070 C2提到一種呈流動冷却 (StMimingsktihlung ’ 英：fi〇w cooling )形式的低壓冷却法， 其中，在工作滾子表面與冷却殼之間一個一定之較狹窄的 縫隙中，將冷却液以一定朝向的方式用外界壓力在滾子表 面導流過去。這種方式的壓力位準較小且與縫隙寬度及液 流速度有關。此處，較高之冷却效果係利用較高流速達成。 由於壓力位準較低，此系統對滚子表面沒有洗淨效果。此 裝置的一缺點為，對各滚子需要有一個自己的冷却塊，因 為冷却塊係安裝在「滾子建入件」（Walzeneinbaustiick，英： roll budt-in Piece )中。因此一傳統的熱滾壓機需要多數的 這種冷却塊。縫隙寬度要配合不同的工作滾子直徑以及各 工作滾子位置的冷却塊的順序，這一點同樣顯得不利且很 麻煩，因為須用手在滾壓架外調整縫隙。 【發明内容】 4 201036721 、本孓月係針對上述先前技術著手，其目的在提供一種 種冷郃裝置，藉之可將一滾壓架的滾子最適當地 冷却’俾保護滾子以免受到熱機械性疲勞及磨損，其中要 考慮到節能的觀點（如將所需之冷却液流量及冷却液壓力 減到少，以及考慮到相關之結構與f成D 。 述目的在方法方面係利用申請專利範圍第1項的方 法的特徵達成，而在裝置方面則利用申請專利範圍第25項 Ο Ο 的特徵達H該滾子在沿其周圍的至少二個部分區域 用冷却液冷却，其中該部分區域利用該冷却殼的至少二個 冷却殼片段代表，該冷却殼片段和滾子表面的區域對立且 互相以柩接方式連接。 基本上—滾壓機的所有滾子可利用本發明的冷却裝置 冷却，但本發明特別用於工作滾子的場合。 利用上述的一冷却殼的個別片段之間的樞接，可有利 地使冷却殼最佳地配合滾子的各別直徑，並因此可使滾子 作較節能而有效的；^ h。k k ,, 7 P柘接的關節軸宜平行於滾子的縱 ° 依本發明一實施例，滾子在作低壓冷却的同時也作高 :冷：’其中滾子在高壓冷却時直接用_股在高壓 却液噴灑。 最好將全部冷却液體量的約聰送到高壓冷却級，並 ;:將全部冷却液體量的總量的約嶋送到該產生主冷却作 亀壓冷却級。此冷却液舉例而言，可從一 7到12公尺 =高容器取出 /由低壓栗直接產生。該低壓冷却的冷却 、之之所需壓力|巳圍與滾子的熱負荷有關’舉例而言，在從 201036721 0.5巴〜小於5巴的範圍，所使用之結構實施例可為—種喷 灑冷却級、冷却劑簾幕、縫隙冷却或流動冷却、高紊流式 冷却（圖2)系統’或各種不同低壓冷却系統的組合。 要作高壓滾子冷却（它同時可達成滾子表面洗淨或除 去銹垢的目的），可一如在傳統系統的場合使用單列式或 雙列式的喷灑喷嘴樑。全部冷却液量的一小部分（約2〇% ) 已足夠作這種目的’其中所需之冷却液的壓力範圍在5〜5〇 巴，且宜12巴。高壓滾子冷却之冷却液之所用壓力範圍和 以下滾壓參數有關：厚度縮減、滚壓縫隙中的比面積壓力 (Spezifische FUchenpressung，英：specific area pressure)、 滾壓速度、鋼帶溫度、滾子材料以及被滾壓的材料的種類。 基於環保觀點’要將泵消耗的總能量減少，同時就「綠 色植物技術」的方向實現所有系統目的，乃是很有利者。 如果我們將具較高壓力之傳統滾子冷却之使用的泵能量與 所主張之組合式低壓_高壓冷却系統比較，則有以下的不同： 泵的能量需求（不考慮泵效率），在具5000立方米/ 小時的總滾子冷却劑流的2米熱鋼帶滾壓道的例子〔泵功 率=體積流X壓力升高（指示：36為一換算因數）〕 <傳統滾子冷却方式> 壓力位準 例如12巴 泵功率=5000立方米//小時χ12巴/ 36 泵功率= 1667仵瓦 <組合式低壓-高壓冷却方式〉 壓力位準 例如12巴 高壓冷却劑量1000立方米/小時，以及 201036721 壓力位準 例如2巴 低壓冷却劑量 4000立方米/小時 泵功率=1000立方米/小時X12巴/ 36 + 4000立方米 小時x2巴/ 36 泵功率=333什瓦+ 222仟瓦=555仟瓦 利用此组合式低壓-高壓冷却所需之能量的量少得多。 依此’對於上述例子’泵的驅動功率減少約1丨百萬瓦。 當污染物或銹垢子增加以及例如滚子表面粗糙或在一 〇 燒裂痕模型（Brandrissmuster)的場合，壓力位準可對應地 提高。利用一攝影機可觀察滾子表面，俾由此推演出壓力 位準的變化。此外，為了影響滾子上氧化物層的厚度，壓 力位準可用分段式（例如將馬達啟動或關掉）或無段式個 別地匹配。 、、 汲σ式低壓-高壓冷却舉例而言可用於一熱鋼帶滾壓 道的前滾壓架。如此在後滾壓架也可使用純低壓冷却。 &高壓冷却樑可在近乎整個樑長度的範圍作用或設計 f可沿寬度方向移動並作局部冷却作用。如果只使用—簡 ^低壓冷却殼冷却方式’則可考慮及設置與日專利申請 喷ΓΓ-29012的冷却方式的組合。此處利用一馬達將二個 嘴樑部段沿軸向或沿寬度方向移動並h作滾子作 m + 八有螺杯的一電馬達或油壓 馬達或對應地用二個馬達分别/ 士 & 變更方々 違刀別在左右側調整，也可採另— 桿（G 成一用油麼方式運動之單節或多節式關節擺 轉動的嘴嘴單元的方式 麗梯）或可 將冷却劑喷流偏轉到工作滾子 7 201036721 之所要區域（在鋼帶範圍之内或之旁），以對鋼帶的廓形 (Bandprofil )及平坦度產生正面影響。 與可沿寬度方向移行的喷灑樑部段的實施例相似者， 舉例而言’對於低壓殼冷却系統的一個片段而言，可將例 如寬150毫米的短片段殼部分沿軸向沿寬度方向調整且做 成只有局部（例如對稱地在工作滾子二個位置）作用。 依本發明使用的低壓工作滾子冷却系統的目的在於作 最佳及有效的冷却，其中，儘管冷却液壓力低，但冷却效 果（熱從滾子傳到冷却液）仍要高。這點可造成較低的旁 子溫度，或可用於減少冷却液量。所用之有效低壓式滾子 冷却宜為流動冷却系統，其中冷却液在工作滾子與—弧形 設計的冷却殼之間的一較狹的縫隙中在滾子表面導流過 依本發明，該冷却裝置主要由互相樞接之可運動的冷 却殼片段構成。宜使用三個，但一般使用二個冷却殼片段。 但在特別情形也可只使用—冷却殼片段，個別的冷却殼片 段宜在側面或末端具有關節或關節半部，在中間的冷却殼 片段上至少有一旋轉點’它至少容納一個（且宜二個）2 缸（油壓缸或氣壓缸）。壓缸的二個保持點接在相鄰之冷 却殼片段的另外元件上，壓缸可設在冷却樑中點或在邊： 兩側。如不用缸將冷却殼調整，舉例而言，也可考慮用油 壓馬達或電馬達調整。在中間的冷却殼片段上有控制台 (K〇ns〇le)或具有固定孔的冷却樑載體，利用冷却樑载體口， 可使中間之冷却殼片段以及所有它連接的構件運動，其中 其作水平、垂直及旋轉的運動。纟置的調整利用一多節式 201036721 關即聯動器實施，它用氣壓、油壓或電機械方式動作。也 可經由例如一'縱導引件或長孔導引件及氣麼缸或油壓缸將 中間的冷却樑载體沿水平方向有利地調移。 壓缸具有路徑測量系統及壓力測量感測器，缸的位置 以及冷却殼片段與滾子間的縫隙調整或距離測定、以及所 調整的位置的監視作業可用以下不同的方法求出及實施， 其中以下所述方法也可組合： 〈冷却般的校準（Kalibderen，英：calibrating ) > 〇 要調整冷却殼片段的位置，將冷却樑載體調移件及冷 却殼片段利用相關之壓缸及關節聯動器用一定的壓力壓向 滾子。在此位置時，路徑感測器設定到零，由此開始，並 要知悉幾何的關係，隨後可將冷却殼片段及滾子之間調整 一定的縫隙。此冷却系統的校準程序可在滾壓架校準過程 實施。 <計算位置> 由於幾何關係（滾子直徑、滾子沿垂直方向的位置、 C)缸位置、關筇與旋轉點的距離、多節式關節聯動器的位置 等等）係已知，故可用很好的趨近（Naherung，英： approximation)方式計算出殼位置或平均縫隙寬度。因此在 滾壓過程時，滾子位置的每個相對變化（例如在鋼帶厚度 改變時）可以換算。 <使用感測器〉 藉著使用距離感測器，可直接測量縫隙，且缸與關節 驅動器可對應地用一調節系統作調整。 不同於先前技術的冷却系統，本發明的冷却系統可利 9 201036721 用既有的關節機構配合各種滾子直徑及滾子位置，因為冷 却樑的調移系統與厚度調整手段連接，且（例如在厚度轉 變時）追循工作滾子的垂直運動。當滾壓架上移行時；列 如在一種緊急上移（Not_Auf，英：emergency up)〕時， 冷却殼自動地略樞轉回去。 在-結構實施例中，冷却裝置利用一密封功能形成一 空間，只有極少冷却液能由該空間出來到周圍環境中。此 密封作用係由殼在上方及下方倚在工作滾子上達成，較工 作滾子可利用一預定壓力頂壓，及，或藉著施一種堆積壓 力在v却4邊緣而造成此密封作肖，利用這種設置可形成 一種近乎封閉的冷却循環。 與冷却殼之間的縫隙 冷却樑可隨冷却殼及傳統的高壓及/或低壓喷麗襟固 定在冷却^上。藉著將殼定位在滾子前方不遠處可形成 :縫隙’冷却劑流過該縫隙，冷却殼與工作滚子之間的縫 隙寬度在#作時，依標的以可重現的方式（不受滾子直徑 影響地）調整成2〜40毫米之間，例如5毫米。工作流子 傲 '人 士 rL '一一 沿切向看--可以大約和出口相 同或該殼調整成向出口變窄 却轡使用本發明的流動冷却系統時，可有二種不同之冷 士知更方向——部段式（absChnittsweise，英：secti〇nwise) 動冷却及诖垃+ , ^ zusammenhSngend，英：connecting) k動冷却。 部段式流動冷却分成多數部段。冷却劑由—（例如為 漏斗形的）長方形槽 ,^ 價孔/)IL出到冷却之各別區域流向滾子且 向兩側（分別向上及向下、，丄 工夂向下）或也可主要主向一側偏轉，其 10 201036721 中冷却破迫使體沿滾子流動，藉著使液流轉向以及沿滚子 以較局相對速度流動，該冷却液有效地吸收滾子的熱。此 受熱之冷却液隨後向下流回，並留下空間給新而冷的冷却 液來填補。因此，冷却樑做成使該向下（離開滾子）流動 的滾子主要可隨著斜地勢（Gefall )順利地流走。利用轉向 金屬板，使流回的冷却劑在二側另外向旁邊偏轉，以減少 刮器（Abstrifer )上的水池效應（P〇〇leffekt )。個別的冷 却區域利用對側的遮護件互相隔開，因此相鄰之冷却樑的 〇 冷却液幾乎不會互相對向作干擾。 在連接式流動冷却的場合，冷却液經滾子的一較大的 連接角度範圍導進。此處需要一個可配合的小縫隙寬度及 大的流速，以產生良好的熱傳遞作用。因此，縫隙寬度和 冷却液量須互相配合設定。連接式流動冷却系統可用逆向 流原理或順流原理操作。由於入口側及出口側之間路徑 長，故冷却殼須作側面密封。如不用逆流或順流原理，也 可用另一操作方式，其中冷却液在上方及下方冷却樑管路 〇 供應。如此，液體依標的流出列侧面。在此原理，和滚子 或切向流動之流動液先吸收熱然後向側面偏轉。如此，熱 的冷却液將鋼帶跑動範圍附近的滾子區域加熱且在該處對 於熱凸度（Crown)造成所要的正影響，如果作區域加熱（其 中在鋼帶旁的區域不直接冷却），則這種系統特別有效。 在作此區域冷却作業時，在滾子長度中在冷却樑的冷 却劑供應通道中只有特定的區域開放供流過，或者狹小= 冷却殼相鄰設置，互相隔著—些縫隙寬度（它們調整成不 同的缝隙寬度），受到不同的縫隙寬度影響，對於狹小的 11 201036721 ，却4 1生對應之不同的比冷却液流過量，因此各冷却 殼有不同之工作滾子的冷却作用，各依結構而定，將一種 阻斷冷却液加入在狭a I^ m 杜狄冷却喊間以將縫隙的不同通過量的冷 却液互相隔開。為了最佳地控制該冷却裝置，故使用一計 算模型（程序模型，位W卜該模㈣心下目的： ^ w依鋼帶!度減少度、滾錢隙令的比面積麼力、 =^鋼帶'皿度、滾子材料、被滾壓的材料、所測量 的及/或所計算的滾子溫声 以及同樣地依所調節的冷:劑作滾子表面而定 部分及高壓部分用的冷却劑量及壓力位準；；郎°亥低屋 與厚度調節級作信號交換（滚壓架調移）； ——描述該冷却裝置的可動的部分w # Μ/ 南# μ a 1刀的幾何關係以及老 慮该調移位置、配合線位置、 夏次展子直控以便最 位置’或計算位置的變化；以及 未出 使用έ亥壓力及路經咸泪丨哭 ^ 唬，利用該壓缸 疋該冷却載體的樞轉位f以及冷却殼調移位f ; 確 控制冷却殼位置之校準過程。 本發明之其他有利的實施例係 的標的。 L月專利乾圍依附項 本發明的其他細節在以下配合 丁忍圖式中所示的實施 ——藉著調整供應通道的出口開口（抛物線形、其他 ⑽或區域性）及/或依鋼帶寬度而定調整冷却殼與滾子 之間=隙寬度及/或調整該可沿寬度方向調整的嘴㈣ :樑部段的位置及’或沿鋼帶寬度範圍所測量的廓形狀雖 平坦度狀態而調整沿鋼帶寬度範圍的冷却劑的量；。 12 201036721 例詳細說a月 【實施方式】 〇 ❹ 圖1中顯不先前技術的—種噴灑冷却系統，其中一冷 却液⑺利用喷嘴⑼噴壤到工作滾子⑴⑺的滾子表面上。 由利喷嘴與滾子之間的距離較大，故選設一種較高之冷却 劑壓力範圍（例如6巴..···.U巴）。設置在人口側及出口 側的刮除器(17)用於使儘量少的冷却液態與滾壓物⑷接觸。 圖 2顯不另--種習去口夕、人i 为知之冷却工作滾子（1)(2)的可能方 式。它係在低壓範圍的-種高资流式冷却系統，利用單側 設置的噴嘴（27)以及利用在出口側設在弯成凹形的相關冷 却殼⑴）中的孔將水喷射紅作滾子⑴⑺的表面，並在工 作滾子前方形成一道具有紊流狀無定向液流的水墊。在這 種結構水交換較慢，這點對冷却效率有不良影響。 /依本發明之具有一相關冷却殼⑴）的相關之流動冷却 糸統示於圖3中。此處，本發明的冷却裝置⑽主要由互相 樞接的冷却殼片段⑼構成，它們隔一段距離圍住工作滚子 ⑴⑺，形成-較大角度範圍的縫隙⑼）。 冷却液⑺沿者與滾子旋轉方向（5)相反的流向經由—供 H⑼σ(2⑽入該縫隙⑼）中，俾隨後經出口 開口⑽及導離管⑽再流出。如果導離管（26)或出口開口 (24)在一特別情形關閉或不 於該滾子流出。如此，在此處可依標的使冷却劑垂直 如、A , 在此處，側邊的密封件只部分地存 在。冷却忒片段（13)之—些片 ⑽〕要近乎-樣大，因此度錯〔它們形成縫隙 田工作滾子（1)直徑改變時，冷却 13 201036721 ()可最佳地追隨滾子函殼面（6)的曲率的改變。個 的冷却喊片段(13)的末端有關節或關節半部，它們互相連 形成對應的數目的„旋轉點（22)及旋轉點（21)，它們利用 壓缸（20)(例如油壓缸或氣壓紅）互相連接。在中間的冷却 殼片段03)上有冷却樑載體⑽，它具有—樞接點㈣，藉 此可使冷却殼片段（13)以及所有與該片段連接的構件沿圖 式之冷却樑載體的調整方向(45)(水平、垂直及旋轉）利用 7多節式關節聯動器（此處未圖示）作運動。一設在冷却 成（11)下方的刮除裝置（1 7)用於使跑到滾壓物⑷上的冷 液（7)儘量少。 7 利用測距離的❹彳器（37)及缸接頭管路巾的壓力計（36) 以及設在壓缸（20)之上或之内的路徑測量器（39)，可將整個 冷却殼⑴）作定位。利用溫度感測器（38)(在滾子中央或沿 寬純圍）連續地測量滚子溫度以將縫隙⑽的尺寸對應地 調節以得到所要的冷却作用。 以下所述的冷却裝置的結構係用相似方式建構，因此 相關之結構細節不再贅述’而只在各情形使用上文已述的 圖號。 在圖4中的冷却裝置中顯示在縫隙（3〇χ它由冷却殼⑼ 的冷却殼片段（13)及滾子函殼面⑹形成〕内 3所示之液流的導引方式作導引。此處，要使用低塵：却液 供應管（ND)的冷却液（7)用的供應管（25)各設在上、下冷却 殼片段（13)上，因此在這裡冷却液的各部分量分別和滾子旋 轉方向成逆向及順向流過縫隙(3〇)，流動方向用箭頭⑹表 不。為了將缝隙（30)密封，冷却殼（11)的上、下邊緣設有一 14 201036721 倚罪面（46)，例如—硬布板，它對滚子函殼面（6)呈密封方式 ‘進口此，因於冷却流（7)只能有一側流出道從縫隙（3〇) 出來（導離管不存在），故縫隙（3〇)比圖3的縫隙寬度更大。 個冷却又的調整作用係一如圖3的情形利用壓缸（2〇)達 成。如不用壓缸’該處也可較簡單地使用螺旋彈簧，除了 在出口侧利用設在該處的冷却殼（丨丨）作冷却外，各工作滾子 (1)(2)也在入口側作冷却，由於此處能達成之冷却作用並非 最重要者，舉例而言’此處利用喷嘴(27)用低壓作喷灑冷却 〇 即足夠。 圖5中顯示具有一部段式低壓流動冷却系統的冷却裝 置，與圖3及圖4不同者〔其中冷却殼⑴)固然由冷却殼片 段（13)組成，但組合在一起形成單一個可動的冷却殼（11)〕， 在此處該冷却殼(12)(此處沿徑向分開）的冷却殼片段⑽ 也局部互相分開且形成分別的流動冷却區域（ai)(s2)(d)。 此處，冷却液由低壓（ND)供應管（25)流出經過冷却片段（13) 的中央區域中的-漏斗形輸出槽孔（44)從—出口開口㈣出 來机向工作滾子⑴(2)並向兩邊向下及向下偏轉。為了將橫 向（沿寬度方向）流動的水量限制，可設機械式側密封件。 各冷却殼片段（13)迫使液流對應於圖示箭頭（43)沿滾子函殼 流動，然後向後流回此，冷却殼片段（13)設計成使 付（從滾子離開）向後流動的冷却液可用斜坡（以如。順 利流走。利用轉向金屬& (圖未示）將流回的冷却液在上 侧另外偏轉到旁邊，以減少刮除器⑼上方的水池效應。冷 却殼片段(13)的出口開口 (24)可設以一可更換的嘴件（例： 長方形喷嘴），如此在必要時，橫截面與形狀可很容易地 15 201036721 配合改變的條件。在此實施例中，在刮除器（17)與冷却殼（12) 之間設有高壓冷却液供應管（HD)的喷嘴，利用它們可實施 本發明之組合式低壓-高壓冷却作用。高壓噴灑樑可如圖所 示分別設在冷却樑載體（16)上或固定在一冷却殼片段上，如 此它可隨冷却樑載體或冷却殼片段作調整。 圖6中顯示：有一可完全更換的冷却殼板（47)固定在冷 却裝置（10)的冷却樑上。由於此處，出口開口（24)的喷嘴開 口的嘴件也可更換，因此可將整個冷却殼隨嘴件更換，也 可將一者分別地更換。一流動冷却區域的冷却殼也可分成 赛 一部分，因此將該二半部作相對移動然後再固定，可很容 易將出口開口（24)作調整。此外可很容易調整不同的殼厚度 或縫隙寬度/每個冷却樑，且影響向上及向下流的冷却液 的量。 圖7中不採如圖3〜圖6實施例的方式使用壓缸將個別 殼作調移’在_ 7中的冷却裝置係揭示及顯示另一解決方 式i此處冷却樑載體（16)隨中間的冷却殼片段（13)定位在滾 子則方。二個另外的冷却殼片（13)利用一直或彎曲的橫樑、 =8)(匕可在一小的限定範圍内旋轉）用彈簧（8)之對應的「彈 f壓壓力」冑$住。如不採此方式，也可在壓缸的區域 中（見圖3〜6 )將螺旋彈簧用對應的保持件設在末端。 在此縫隙（30)係利用冷却殼（13)與工作滾子⑴⑺間的間隔 板(49)測定。適合作間隔板的材料，舉例而言，為硬布、鋁、 鑄鐵、自身潤滑的金屬或塑膠、間隔板（49)只設在冷却樑邊 緣區域俾不致干擾中央的冷却劑流。也可視需要使間隔 ()之伸過冷却樑的長度範圍。這些間隔板可用於調整間 16 201036721 隔或改變冷却劑的流動方向。這些間隔板也可設在中央之 冷却樑片段（13)上（圖未示）。藉著所產生之向側邊流過去 的冷却劑流，使工作滚子的邊緣區域（在鋼帶附近）受到 該加熱過的冷却劑依標的由中心加熱。 如果工作滾子之作冷却的直徑範圍很小，或者對每個 滾壓架都在相同區域，則特別的情形係設一種剛性的冷却 系統，亦即具有不能動的冷却殼〔或不具有殼之間的壓缸 或不具有彈簧（8)〕。如此也可用有利的方式使用剛性間隔 Ο 桿代替可動的壓缸（20)。如此，滚子與冷却殼間的縫隙略為 改變’但該具有部段式流動冷却作用的系統仍有效且此系 統製造上較簡單。只需將冷却樑載體工作滾子直徑和工作 滾子位置而定，定位在該滾子前方，如此該縫隙最適當地 設置，亦即出口開口較密封地設在滾子前方，因此該結構 對數個滾壓架都設計相同，且只要利用該長度可調整的桿 來配合一條滾壓道的不同的滾壓架直徑範圍。 在圖8的裝置中除了上述之組合式低壓-高壓冷却系統 外，在入口側還設一個具有整合的「滾壓縫隙潤滑手段」（19) 及「滾壓縫隙冷却手段（18)」的低壓流動冷却系統。同時在 圖8中揭示：不同的高壓及低壓系統如何互相組合。冷却 液（7)的液流可在一冷却殼下方分開，或者一如此處在入口 側及出口側所例示者，宜將較大量的冷却劑偏轉到—方 向。為了加強熱傳遞，故一般液流宜逆著旋轉方向。 設有「滾壓縫隙潤滑手段」（19)的那個區域受到工作滚 子冷却系統產生的流動方向以及受到設有彈性塑膠表面的 冷却设（50)或具有彈性塑膠板或硬布板的冷却殼（5 1)保持浐 17 201036721 舞，為此，由、人I , 由冷却樑載體機構產 板壓到滾子上，七丄 再座生—股輕的壓迫壓力經由 板本身做成延伸過 結構設計（圖夫+、 〆寬度粑圍，且由於其 潤滑劑」之前，予不主 、 用。在施加「滾子縫隙 喷霧手段（圖未示:、自區域可視需要地設以-壓縮空氣 用。 ’、，以將滾子表面吹氣作-定之乾燥作 如果不使用例如且 依圖9的冷却裝論 1嘴的三個冷却樑’也可 殼⑼，將許，1一 二個冷却樑設以可更換的冷却 夕又日6又置的洞（52)鑽到該冷却殼（47)中，個 ’、、却劑噴流由這些洞出來從短距離處喷向滾子⑴⑺。 如此也可建構成-種部段式的流動冷却系統。在此，這些洞 Μ度Μ交錯設置’使得沿寬度範圍產生的冷却作用儘 量均勻。洞（52)的橫截面與距離可沿滚子體寬度範圍做成不 同’俾可利用這種系統產生像滾子體的凸度（Crown) 一樣 的冷却劑刀佈的拱起曲線。在此’洞(52)可垂直地朝向滾子 (Ό(2)或也可將冷却劑斜斜噴向滚子（1)(2)。 在一個圖未示的變更例中，冷却殼設計成使冷却劑， 出口開口同時做成利用一長方形槽（24)或（44)與板中的孔 (52)組合，以提高該流動縫隙中的紊流度。 喷嘴及殼的設計的其他細節見於圖l〇a〜丨〇f，其中喷 嘴設在殼中央，或者在不對稱的設置方式中設有在一側（例 如設在上側）縮短之設計的殼。藉著改變上方/下方之喷 嘴的調移角度或不同的冷却殼厚度（圖未示），可同樣地 影響向上及向下的冷却液流的分佈。此處也顯示不同的喷 流形式（將噴流聚集或「噴霧分散」）。冷却殼之朝向滾 18 201036721 子的那一側可另外做成平滑狀或設有溝槽或框條（9)，r · 用所造成之奈流對冷却效果造成正面影響。 士 、】 σ 、、叫吕 < ,$全 些圖中： & 的對稱 圖l〇a係在冷却殼（11)(12)上的冷却樑（54)下部 設置’具有可更換的噴嘴； 圖l〇b係由喷嘴（27)出來的冷却液開口，對滾子斜斜成 一角度a， 圖10c係具有變更之橫截面形狀的喷嘴（2乃以及該框條 Ο 或溝槽（9)之可能之實施例， ” 圖l〇d係以對喷嘴（27)呈不對稱方式縮短或延長的冷 却殼。 該漏斗形出口開口（它沿流動方向形成）在必要時可 設有「引導金屬片」，以將冷却劑瞄準向内、向外或直線 狀轉向，如此最後沿冷却樑寬度範圍跑出一股封閉而均勻 的冷却液喷流，也可在冷却樑寬侧上將冷却液供應通道設 計成漏斗形，以將在殼下方向側邊（樑邊緣）流的冷却的 量減少。 此外也可將冷却樑呈部段式地沿冷却樑長度範圍設以 冷却液供應通道中的縫隙寬度調整作用，且因此可沿滚子 長度範圍改變冷却劑的分佈以及冷却作用。為了要能更簡 單地沿寬度範圍將出口開口的縫隙寬度作拋物線式的變 化’故依圖10e (侧視圖）及圖1 〇f (上視圖）的例子，在 漏斗形供應通道（55)内設以「彈簧金屬片」（53)，它可利用 一調整機構（圖未示）彎曲。此處在正常位置時，彈簧金 屬片倚靠在出口開口的側面上，如果在一側將中心調移， 19 201036721 則該處縫隙變小。在此， 另-…，當彈簧金屬片：持公在—長孔導引件中， 及圖l〇f的實施例只顯示原理，也可有 其他具相同作用的結構。 在供應通道（55)中，縫_㈣實施例的 〜1 lc以側視圖顯示， ^ 圖12中以相關之上視圖顯示。此 處’冷却樑的長形屮 ^出口㈣面⑽分成個別之寬度部段 ' ;度部段（59)，冷却液的流動開口 b及體積流 可調整。寬度部段⑽舉例而言可做成5〇〜5 不採此方式，也可將 宅卞見如 加 了將£域冷却的控制手段成對設置對滾壓 木中央ό免成對稱（縫胳、 )。一滾壓架的所有冷却樑可 ㈣㈣式㈣彳’且這些區域可對應地連接， 或將一滾壓架的個別的樑分別控制。料圖U的實施例， =又m截面的封閉機構係為—個用线壓力或液體 、一呆作的系統。依系統的壓力位準或依所測量的體積流 而定:該流動開n(b)可調整成從開放到部分開放或封閉。 如不知用部段式設置的可拉伸的塑膠舌片（6G)，也可使用可 拉伸或^移動的翻動蓋片或推桿、偏心輪調移手段或其他 機械式取終控制疋件，以呈片段式方式影響出口開的橫截 面。 在圖11a〜1 ic的實施例中，在供應通道（55)的側面設 有一壓力室⑽當作封閉元件，其可拉伸的塑膠軟管_形 成供應通道(55)的一部分。在圖】1 &的起始狀態中，空氣室 )^在.、，、壓力狀恶，因此，如圖12在寬度部段（州）所示 動開口（b)完全開放。在圖！ lb中，壓力室（56)經一壓 20 201036721 力苢路（57)用壓縮空氣或一液體部分地充滿，如此，塑膠軟 吕（60)。卩分地被壓入供應通道（55)進去，且該流動開口（6〇) 此時部分地封閉，如圖12在寬度部段（59b)所示者。圖12 在寬度部段（59c)顯示完全關閉的流動開口（b)。此處，依圖 iic’壓力室（56)完全充滿，且因此供應通道（55)在此區域被 阻塞藉著將這些區域封閉，可對滾子的熱膨脹及鋼帶廓 形及鋼帶平坦度造成正面影響。將鋼帶旁的冷却區域關閉 同時配13 (減少）水的需求量，可有利地進一步減少能量。 在圖13中顯示區域冷却的另一作用原理。在此，沿滾 子長度範圍有狹窄的冷却殼（14)相鄰設置，其縫隙 (3 1)(32)(33)可調整成不同縫隙寬度W1、w2、w3。因此， 用不同的縫隙寬度’以及將縫隙（3 ”（叫⑴）施以不同壓 力及冷却液的體積流，可沿滾子長度範圍產生不同的「比 冷却^過量㈤/每單位時間」。要將具不同之「冷却流 通過量（41)/每單位時間」的個別區域隔開，可將—種「阻 、P液」（匕產生一堵塞的壓力）加入冷却殼（丨4)之間的 縫隙（34)。也可不用調整裝置較簡單地造成一冑冷却殼，使 冷却设與滚子之間的縫隙沿滾子長度範圍可任意地不一樣 斤用之冷却喊（13)(14)地材料可有利地使用一種可倚靠 在滾子上而不損害滾子的彈性材料。舉例而言，可為-種 …"缚鐵、可滑動的塑膠、自身潤滑的金屬、銘或硬布。 圖14中顯不在縫隙邊緣將工作滚子⑴與冷却殼（μ)形 、的縫隙(30)猞封的一種可能方式’利用_管⑽或一噴嘴 股机體（例⑹$氣或冷却劑）#噴流瞎準吹入縫隙 21 201036721 冷却液（7)從縫隙（30)出來。 圖15a及15b顯示一種局部作用之可軸向調整的工作滚 子喷灑冷却系統，它可做成高壓及低壓冷却方方式。這種 冷却系統係一種附加冷却系統，且可和圖未示的低壓殼冷 却系統組合操作。冷却喷嘴的局部定位作用或冷却液（7)的 施加宜依廓形及平坦度的控制或調整而定而達成。為此， 在圖15a中，該喷灑喷嘴樑部段（4〇，）在一導引桿（63)上移 動。此處，該二喷灑噴嘴樑部段（4〇，）的定位係對滾子中心 成對稱利用一油壓缸（62)、關節桿（62)及喷嘴樑載體（64)達 成。如不用此方式也可用另一方式考慮二個油壓缸（61)，它 們將兩側（65)個別地定位。喷麗嘴嘴樑部段⑽，）的應係左右 邊及左邊㈣地利用供應管路（25)達成^圖15b顯示局部作 用的工作滚子冷却系統之一種類似的設置。此處，利用一 油壓紅（61)將關節桿及關節擺桿（62)隨固定在其上的喷灑喷 嘴樑部段（40，）經-旋轉點（66)在一圓形路線（64)上運動，因 此將冷却液噴流⑺偏轉到鋼帶範圍内或附近偏轉到工作滾 子（1)上。另一種與樞接的關銘披拍 一 ^ 的關即擺桿不同的變更方式（圖未 示）係將二喷灑噴嘴樑C4〇，、久田 ^ ）各用—聯接聯動器（4-關節弧） 運動〔如果要避免在一圓形路魂 深（64)上運動的話〕。也可使 嘴灑噴嘴樑部段（40，）上的噴喈置- „^ $嘴早疋使用電的或油壓式步進 馬達以經由圓形路線（64)上 狹始）上的—桿使噴嘴單元直接在圓形 路線（轨道）（64)上運動。 低壓冷却系統也可單獨妯r 人、你 獨地（亦即不與高壓冷却系統組 Q J使用。 相鄰之冷却殼片殼（13) 圖16顯示之彎曲彈簧（8)係當作 22 201036721 之間的彈性連接手段。 【圖式簡單說明】 圖1係依先前技術的一喷灑冷却系統； 圖2係依先前技術的一種高紊流式流動冷却裝置； 圖3係依本發明的一冷却裝置，具有數個冷却殼片段， 它們互相柩接； 圖4係圖3的裳置，具有另一種變更的冷却液流； 圖5係一本發明的冷却裝置，具有沿徑向分開的冷却 殼； 圖6係圖5的冷却裝置，具有可更換的冷却殼或冷却 板； 圖7係一種冷却裝置，具有利用彈簧壓迫的冷却殼片 段； 圖8係一冷却裝置，具有滚子縫隙冷却手段/滾子縫 隙淵滑手段以及組合或低壓滾子冷却系統；. 圖9係年重冷却裝置，具有設入在冷却殼中的孔； 圖l〇a〜l〇f為嘴嘴及冷却殼的設計； 圖11a〜11c為—種縫隙寬度調整手段； 圖12為一種縫隙寬度調整手段； 圖13為一種區域冷却系統； 圖14為一縫隙密封手段· 圖15a與15b為一插仏扣 植局α卩作用之可軸向調整的滾子冷却 件； 圖16為彎曲彈簧， 匕作為相鄰之冷却殼片段之間的關 23 201036721 節式/彈性方式連接件。 【主要元件符號說明】 (I) (2) 工作滾子 (3) 滾子寬度 (4) 滾壓物 (5) 滾子旋轉方向 (6) 滾子函殼面 (7) 冷却液 (8) 彈簧 (9) 槽式框條 (10) 冷却裝置 (II) 相關之冷却殼 (12) 沿徑向分開的冷却殼 (13) 冷却殼片段 (14) 狹窄之冷却殼 (15) 冷却殼的柩接點 (16) 冷却樑載體 (17) 刮除器 (18) 滾壓縫隙冷却手段 (19) 滾壓縫隙潤滑手段 (20) 壓缸 (21) 壓缸的旋轉點 (22) 冷却殼片段的關節旋轉點 (23) 冷却樑載體的枢接點 24 201036721 (24) 出口開口 (25) 供應管 (26) 導離管 (27) 喷嘴 (28) 流體喷流 (29) 入口開口 (30) 滾子函殼面與冷却殼之間的縫隙 (31) 具缝隙寬度W1的缝隙201036721 VI. Description of the Invention: TECHNICAL FIELD OF THE INVENTION The present invention relates to a method and apparatus for cooling a roller as a roller. Ο 时 When the metal is rolled, the roller involved in the rolling process, the working roller y, is heated. The roller is cooled in order to protect the roller from damage and to use (4) as much as possible. In most rolling plants, a modern cooling system is used, which uses a nozzle (and preferably a flat jet nozzle (Flachstrah brush se, English: fiatjetn〇zzie)) to spray a coolant onto the roller surface. The cooling effect is called "spray cooling". The selected pressure levels are set at 6 bar to 12 bar depending on the length of the roller, and may be 2 G bar in the example. In addition to the purpose of cooling the rollers as densely as possible, in order to limit their thermal load and geometric expansion, the work roller cooling action must be such that the rollers are kept free of contaminants, oxides and particulate matter. The cooling effect increases as the amount of coolant increases and the cooling drag increases. The disadvantage of this system is that it requires a large amount of energy 'and at higher waste forces' the maintenance cost of the pump is higher. [Prior Art] The possible cooling method for the wearer is low pressure cooling. In the international 〇 2GG8/1G4G37 A1, a kind of cooling device with high cold and gas in the low pressure range is used, and nozzles or holes are used in the sputum (they are arranged in a concave cooling 彳 y y ΐ # # · 人, person' , the coolant is cooled by a roller. By the setting of the cooling beam and the use of the side panels ( < We also have a uniform water pad on the end side of the chilled beam, and there is a winter, sigh of Beijing-style non-sufficient flow. However, only when the diameter range of the roller 3 201036721 which is gradually changed due to wear (which is caused by grinding (Ah·)) is matched with the curvature setting of the cooling device, the cooling device can be satisfactorily and reproducible. The way to work. Since today: the general grinding range is about 1% of the maximum roller diameter, therefore; to = a rolling device for different roller diameters, which makes ^ need a complete set of "mu defects: for & press frame and after each change of the work roller, it is not possible to adjust the curvature of the cooling device to match the change in roller diameter, 0 the distance of the nozzle or hole from the roller surface (and therefore the cooling effect) The rolling process is changed from the time of the one-roller change to the time of the next roll change. A low-pressure cooling method in the form of a flow cooling (StMimingsktihlung 'English: fi〇w cooling) is mentioned in DE 3616 070 C2, wherein In a certain narrow gap between the surface of the working roller and the cooling shell, the coolant is deflected in the direction of the roller with external pressure in a certain direction. The pressure level in this way is small and the gap The width is related to the flow rate. Here, the higher cooling effect is achieved with a higher flow rate. Due to the lower pressure level, the system has no cleaning effect on the roller surface. A disadvantage of this device is Need to have their own cooling block for each roller, because the cooling system is installed in the block "built into the roller assembly" (Walzeneinbaustiick, UK: roll budt-in Piece) in. Therefore, a conventional hot roll press requires a large number of such cooling blocks. The gap width is adapted to the different working roller diameters and the order of the cooling blocks at each working roller position, which is also disadvantageous and cumbersome because the gap must be adjusted outside the rolling frame by hand. SUMMARY OF THE INVENTION 4 201036721, this month is aimed at the above prior art, the purpose of which is to provide a kind of cold heading device, which can optimally cool the roller of a rolling frame to protect the roller from thermomechanical. Sexual fatigue and wear, taking into account the point of view of energy saving (such as reducing the required coolant flow and coolant pressure, and taking into account the relevant structure and f into D. The purpose of the method is to use the scope of patent application The feature of the method of item 1 is achieved, and in terms of the device, the feature of the 25th item of the patent application is used to achieve the H. The roller is cooled with a coolant in at least two partial regions along its circumference, wherein the partial area is utilized. The at least two cooling shell segments of the cooling jacket represent that the cooling shell segments and the surface of the roller surface are opposite and connected to each other in a splicing manner. Basically, all of the rollers of the roller press can be cooled by the cooling device of the present invention. However, the present invention is particularly useful in the context of working rollers. With the pivoting between individual segments of a cooling shell as described above, it is advantageous to optimally fit the cooling shell. The respective diameters of the children, and thus the rollers, are more energy efficient and effective; ^h.kk,, 7 P 的 joint axes are preferably parallel to the longitudinal direction of the rollers. According to an embodiment of the invention, the rollers are For low-pressure cooling, it is also high: cold: 'The roller is directly sprayed with high-pressure liquid during high-pressure cooling. It is best to send all the cooling liquid amount to the high-pressure cooling stage, and: Approximately the total amount of cooling liquid is sent to the main cooling unit for cooling. This cooling liquid can be taken, for example, from 7 to 12 meters = high container / directly produced by low pressure pump. Cooling, the required pressure | the circumference is related to the heat load of the roller. For example, in the range from 0.5367 to less than 5 bar from 201036721, the structural embodiment used may be a spray cooling level, Coolant curtain, gap cooling or flow cooling, high turbulent cooling (Figure 2) system' or a combination of various low pressure cooling systems. High pressure roller cooling (which also achieves roller surface cleaning or rust removal) The purpose of scale) can be used as in the case of traditional systems Single or double row spray nozzle beam. A small fraction (about 2%) of the total coolant volume is sufficient for this purpose. The required coolant pressure range is 5 to 5 mbar, and Preferably, the pressure range of the high-pressure roller-cooled coolant is related to the following rolling parameters: thickness reduction, specific area pressure in the rolling gap (Spezifische FUchenpressung, specific area pressure), rolling speed, steel strip Temperature, roller material, and type of material being rolled. Based on the environmental perspective, it is very beneficial to reduce the total energy consumed by the pump and to achieve all system objectives in the direction of "green plant technology." The pump energy used for conventional roller cooling with higher pressure is different from the proposed combined low pressure _ high pressure cooling system: the energy requirement of the pump (regardless of pump efficiency), with 5000 cubic meters / Example of a 2 meter hot steel belt rolling track for the total roller coolant flow in hours [pump power = volume flow X pressure increase (indicator: 36 is a conversion factor)] <Traditional roller cooling method> Pressure level, for example, 12 bar Pump power = 5000 cubic meters / / hour χ 12 bar / 36 pump power = 1667 watts <Combined low pressure-high pressure cooling mode> Pressure level such as 12 bar high pressure cooling dose 1000 cubic meters / hour, and 201036721 Pressure level such as 2 bar low pressure cooling dose 4000 cubic meters / hour pump power = 1000 cubic meters / hour X12 Bar / 36 + 4000 cubic meters hour x 2 bar / 36 pump power = 333 Shiva + 222 watts = 555 watts The amount of energy required to use this combined low pressure - high pressure cooling is much less. Accordingly, the drive power of the pump for the above example is reduced by about 1 megawatt. The pressure level can be correspondingly increased when contaminants or rust particles are increased and, for example, the surface of the roller is rough or in the case of a cracking model (Brandrissmuster). The surface of the roller can be observed with a camera, and the change in pressure level is thereby derived. In addition, to affect the thickness of the oxide layer on the rollers, the pressure levels can be individually matched in segments (e.g., the motor is turned on or off) or in a segmentless manner. The 汲σ type low pressure-high pressure cooling can be used, for example, for a front rolling frame of a hot steel belt rolling track. In this way, pure low pressure cooling can also be used in the rear rolling frame. & high-pressure chilled beams can act in the vicinity of the entire beam length or design f can move in the width direction and provide local cooling. If only the cooling method of the low pressure cooling case is used, the combination with the cooling method of the Japanese patent application sneezing -29012 can be considered. Here, a motor is used to move the two nozzle beam sections in the axial direction or in the width direction and h is used as an electric motor or a hydraulic motor for the m + eight screw cup or correspondingly two motors/six & change the 々 々 别 别 别 别 别 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 々 The jet deflects to the desired area of the working roller 7 201036721 (within or beside the steel strip) to positively influence the profile of the strip (Bandprofil) and flatness. Similar to the embodiment of the spray beam section that can be moved in the width direction, for example, for a segment of the low pressure shell cooling system, for example, a short segment shell portion having a width of 150 mm can be axially oriented in the width direction. Adjusted and made only partially (for example symmetrically at two positions of the working roller). The low pressure working roller cooling system used in accordance with the present invention is intended for optimum and efficient cooling wherein the cooling effect (heat transfer from the rollers to the coolant) is high despite the low coolant pressure. This can result in lower sub-temperatures or can be used to reduce the amount of coolant. The effective low pressure roller cooling used is preferably a flow cooling system in which the coolant is deflected at the surface of the roller in a narrow gap between the working roller and the cooling casing of the curved design, according to the invention, The cooling device is mainly composed of movable cooling shell segments that are pivotally connected to each other. Three should be used, but two cooling shell segments are generally used. However, in special cases, it is also possible to use only the cooling shell segments. The individual cooling shell segments should have joints or joint halves on the sides or ends, and at least one rotation point on the middle cooling shell segments. 2) cylinder (hydraulic cylinder or pneumatic cylinder). The two holding points of the cylinder are connected to the other elements of the adjacent cooling shell segments, which can be placed at the midpoint of the chilled beam or at the sides: on both sides. If the cooling jacket is not adjusted with a cylinder, for example, a hydraulic motor or an electric motor can also be considered for adjustment. On the middle of the cooling shell segment there is a console (K〇ns〇le) or a chilled beam carrier with fixed holes, with the cooling beam carrier opening, the intermediate cooling shell segment and all its connected components are moved, wherein Horizontal, vertical and rotational movements. The adjustment of the device utilizes a multi-section 201036721, that is, the actuator is implemented, which is operated by air pressure, oil pressure or electromechanical. The intermediate chilled beam carrier can also be advantageously shifted in the horizontal direction via, for example, a 'longitudinal guide or slot guide and a cylinder or hydraulic cylinder. The pressure cylinder has a path measuring system and a pressure measuring sensor, and the position of the cylinder and the gap adjustment or distance measurement between the cooling shell segment and the roller, and the monitoring operation of the adjusted position can be obtained and implemented by the following different methods, wherein The following methods can also be combined: <Cool-like calibration (Kalibderen, English: calibrating) > 调整 To adjust the position of the cooling shell segment, the cooling beam carrier shifting member and the cooling shell segment are linked by the relevant cylinder and joint The pressure is pressed against the roller with a certain pressure. In this position, the path sensor is set to zero, thereby starting, and to know the geometric relationship, and then a certain gap can be adjusted between the cooling shell segment and the roller. The calibration procedure for this cooling system can be implemented during the roll stand calibration process. <Calculation position> Since the geometric relationship (roller diameter, position of the roller in the vertical direction, C) cylinder position, distance between the point of rotation and the point of rotation, position of the multi-joint joint actuator, etc.) is known, Therefore, the shell position or average gap width can be calculated by means of a good approach (Naherung, approximation). Therefore, each relative change in the roller position (for example, when the thickness of the steel strip changes) can be converted during the rolling process. <Using the sensor> By using the distance sensor, the slit can be directly measured, and the cylinder and the joint driver can be adjusted correspondingly by an adjustment system. Unlike prior art cooling systems, the cooling system of the present invention can be used in conjunction with various joint diameters and roller positions with existing joint mechanisms because the transfer system of the chilled beam is connected to the thickness adjustment means (for example, When the thickness is changed, the vertical movement of the work roller is followed. When the rolling frame moves, as shown in an emergency up (Not_Auf, English: emergency up), the cooling shell automatically pivots back slightly. In a structural embodiment, the cooling device utilizes a sealing function to create a space from which very little coolant can exit the environment. The sealing action is achieved by the shell being placed on the working roller above and below, and the working roller can be pressed with a predetermined pressure, and or by applying a stacking pressure at the edge of the v but 4 With this arrangement, a nearly closed cooling cycle can be formed. The gap between the cooling shell and the cooling shell can be fixed to the cooling unit with the cooling shell and the conventional high pressure and/or low pressure spray. By positioning the shell not far in front of the roller, a gap can be formed: the coolant flows through the gap, and the gap width between the cooling shell and the working roller is in a reproducible manner (not Adjusted by the diameter of the roller) to be between 2 and 40 mm, for example 5 mm. The work flow is proud of 'people rL' - one by one tangentially - can be about the same as the exit or the shell is adjusted to narrow towards the exit, but when using the flow cooling system of the present invention, there are two different types of cold knowledge More direction - section type (absChnittsweise, English: secti〇nwise) Dynamic cooling and 诖 + + , ^ zusammenhSngend, English: connecting) k moving cooling. Segmental flow cooling is divided into most sections. The coolant is made up of - (for example, a funnel-shaped) rectangular groove, ^ price hole /) IL out to the respective areas of cooling, flowing to the roller and to the sides (upward and downward, respectively, down), or The main main deflection is to one side, and the cooling of 10 201036721 forces the body to flow along the rollers, which effectively absorbs the heat of the rollers by diverting the flow and flowing at a relatively constant speed along the rollers. This heated coolant then flows back down and leaves room for new and cold coolant to fill. Therefore, the chilled beam is made such that the roller that flows downward (away from the roller) can flow smoothly along with the oblique ground potential (Gefall). With the turning metal plate, the flowing coolant is deflected sideways on both sides to reduce the pool effect (P〇〇leffekt) on the scraper (Abstrifer). The individual cooling zones are separated from one another by the opposite side shields, so that the enthalpy coolant of adjacent chilled beams hardly interfere with each other. In the case of connected flow cooling, the coolant is introduced through a larger range of connection angles of the rollers. Here, a small gap width and a large flow rate are required to produce a good heat transfer. Therefore, the gap width and the amount of coolant must be set to match each other. The connected flow cooling system can be operated with the reverse flow principle or the downstream principle. Since the path between the inlet side and the outlet side is long, the cooling shell must be sealed sideways. If no countercurrent or downstream principle is used, another mode of operation may be used in which the coolant is supplied above and below the chilled beam line. In this way, the liquid flows out of the column side according to the standard. In this principle, the flowing fluid with the roller or tangential flow first absorbs heat and then deflects to the side. In this way, the hot coolant heats the roller zone near the running range of the steel strip and has a positive effect on the heat crown at this point if it is zone heated (where the zone next to the steel strip does not cool directly) ), this system is particularly effective. In the cooling operation of this area, only a certain area is opened for flow in the coolant supply passage of the chilled beam in the length of the roller, or narrow = the cooling shells are adjacently arranged, separated from each other - some slit widths (they are adjusted Different slit widths are affected by different slit widths. For the narrow 11 201036721, the different ratios of coolant flow are different for the 4 1 raw, so the cooling shells have different cooling functions of the working rollers. Depending on the structure, a blocking coolant is added to the narrow cooling chamber to separate the different throughput coolants of the gap from each other. In order to optimally control the cooling device, a calculation model (program model, bit W, the mode (4), the purpose of the heart is used: ^w by the steel band! Degree reduction degree, the specific area of the roll gap order, ^^ Steel strip's degree, roller material, rolled material, measured and/or calculated roller warmth and, similarly, the adjusted cold: agent for the roller surface and the high pressure portion Cooling dose and pressure level;; Lang ° Hai low house and thickness adjustment level for signal exchange (roller shifting); - describing the movable part of the cooling device w # Μ / South # μ a 1 knife Geometric relationship and old considerations of the position of the shift, the position of the line, the direct control of the summer show for the most position ' or the change of the position; and the use of the pressure of the sea and the tears of the salty tears ^, use the pressure Cylinder 枢 the pivoting position f of the cooling carrier and the cooling shell shifting f; the calibration process of controlling the position of the cooling shell. The other advantageous embodiments of the invention are the subject matter of the invention. The details are as follows in conjunction with the implementation shown in the figure - Adjusting the outlet opening of the supply channel (parabolic, other (10) or regional) and/or adjusting the gap between the cooling shell and the roller according to the width of the steel strip and/or adjusting the mouth that can be adjusted in the width direction (4) : The position of the beam section and the amount of coolant along the width of the steel strip are adjusted in the flatness state of the profile measured along the width of the steel strip; 12 201036721 Example details a month [Embodiment] 〇❹ Figure 1 shows a spray cooling system of the prior art, in which a coolant (7) is sprayed onto the surface of the roller of the working roller (1) (7) by means of a nozzle (9). The distance between the nozzle and the roller is large, so it is selected. A higher coolant pressure range (for example, 6 bar..····U bar). The scraper (17) on the population side and the outlet side is used to bring as little cooling liquid as possible to the rolling material (4). Figure 2 shows that there is no other way - it is possible to cool the working roller (1) (2). It is a high-flow cooling system in the low-pressure range, using one side. The nozzle (27) is provided and the phase is formed in a concave shape on the outlet side. The hole in the cold case (1)) sprays water onto the surface of the roller (1) (7) and forms a water pad with a turbulent, non-directional flow in front of the working roller. The water exchange in this structure is slow, which has an adverse effect on the cooling efficiency. An associated flow cooling system having an associated cooling jacket (1) according to the present invention is shown in FIG. Here, the cooling device (10) of the present invention is mainly composed of mutually cooled cooling casing segments (9) which enclose the working rollers (1) (7) at a distance to form a slit (9) of a larger angular range. The flow of the coolant (7) in the opposite direction to the direction of rotation of the roller (5) is via H (9) σ (2 (10) into the gap (9)), which is then recirculated through the outlet opening (10) and the outlet tube (10). If the deflecting tube (26) or the outlet opening (24) is closed or not in a particular situation. Thus, the coolant can be vertically oriented as shown here, A, where the side seals only partially exist. The cooling fins (13) - some of the sheets (10) are nearly large, so the degree of error [they form the gap field working roller (1) when the diameter is changed, the cooling 13 201036721 () can best follow the roller shell The change in the curvature of the face (6). The end of the cooling shouting segment (13) has joints or joint halves which are connected to each other to form a corresponding number of "rotation points (22) and rotation points (21), which utilize a pressure cylinder (20) (for example, a hydraulic cylinder) Or pneumatic red) connected to each other. On the middle of the cooling shell segment 03) there is a cooling beam carrier (10) which has a pivoting point (four), whereby the cooling shell segment (13) and all components connected to the segment can be viewed along the figure. The adjustment direction (45) (horizontal, vertical and rotational) of the chilled beam carrier is moved by a 7-joint joint joint (not shown here). A scraping device is provided below the cooling (11) ( 1 7) Used to minimize the amount of cold liquid (7) running on the rolling material (4). 7 Use the distance measuring device (37) and the pressure gauge (36) of the cylinder joint line towel and the pressure cylinder. A path gauge (39) on or above (20) that positions the entire cooling jacket (1). The roller is continuously measured using a temperature sensor (38) (in the center of the roller or along a wide circumference) The temperature is adjusted correspondingly to the size of the slit (10) to obtain the desired cooling effect. It is constructed in a similar manner, so the relevant structural details are not described again, and only the above-mentioned figure numbers are used in each case. The cooling device in Figure 4 is shown in the gap (3〇χ it is cooled by the cooling shell (9) The cooling shell segment (13) and the roller shell surface (6) are formed by guiding the liquid flow indicated by the inner portion 3. Here, the low dust: liquid supply tube (ND) coolant is used (7) The supply pipes (25) are respectively disposed on the upper and lower cooling shell segments (13), so that the amount of each portion of the cooling liquid flows backward and forward through the gap (3〇) respectively with the direction of rotation of the rollers. The flow direction is indicated by the arrow (6). In order to seal the gap (30), the upper and lower edges of the cooling shell (11) are provided with a 14 201036721 sin surface (46), for example, a hard cloth plate, which faces the roller shell surface. (6) In the sealed way 'import this, because the cooling flow (7) can only have one side outflow from the gap (3〇) (the guide tube does not exist), so the gap (3〇) is wider than the gap of Figure 3. Larger. The adjustment effect of cooling is achieved by using a pressure cylinder (2〇) as shown in Figure 3. If there is no pressure cylinder, The coil spring is used relatively simply, except that on the outlet side, the cooling coil (丨丨) provided there is used for cooling, and the working rollers (1) (2) are also cooled on the inlet side, since this can be achieved. Cooling is not the most important. For example, 'It is sufficient to use a nozzle (27) to spray cooling with a low pressure. Figure 5 shows a cooling device with a section of low pressure flow cooling system, and Figure 3 and 4 different [where the cooling shell (1)) is composed of the cooling shell segments (13), but combined to form a single movable cooling shell (11)], where the cooling shell (12) (here radial The separate cooling shell segments (10) are also partially separated from one another and form separate flow cooling zones (ai) (s2) (d). Here, the coolant flows from the low pressure (ND) supply pipe (25) through the funnel-shaped output slot (44) in the central region of the cooling segment (13) from the outlet opening (four) to the working roller (1) (2) ) and deflected downwards and downwards on both sides. In order to limit the amount of water flowing in the transverse direction (in the width direction), a mechanical side seal may be provided. Each of the cooling shell segments (13) forces the flow to flow along the roller envelope corresponding to the illustrated arrow (43) and then flows back there, and the cooling shell segments (13) are designed to move (from the rollers) backwards. The coolant can be ramped off (for example, smoothly. Use the steering metal & (not shown) to deflect the returned coolant to the side further to reduce the pool effect above the scraper (9). Cooling shell fragments The outlet opening (24) of (13) may be provided with a replaceable mouthpiece (for example: a rectangular nozzle) so that, if necessary, the cross section and shape can easily be adapted to the changing conditions of 15 201036721. In this embodiment A nozzle of a high-pressure coolant supply pipe (HD) is disposed between the scraper (17) and the cooling casing (12), and the combined low-pressure-high pressure cooling effect of the present invention can be implemented by using the same. They are shown either on the chilled beam carrier (16) or on a cooling shell segment so that it can be adjusted with the chilled beam carrier or the cooling shell segments. Figure 6 shows a fully replaceable cooling shell (47) ) fixed to the cooling device (10) On the chilled beam, since the mouth of the nozzle opening of the outlet opening (24) can also be replaced, the entire cooling shell can be replaced with the nozzle, or one can be replaced separately. A cooling shell of the flow cooling zone It can also be divided into a part of the race, so the two halves can be moved relative to each other and then fixed, the outlet opening (24) can be easily adjusted. In addition, different shell thicknesses or gap widths/each chilled beam can be easily adjusted, and The amount of coolant that affects the upward and downward flow. In Figure 7, the embodiment of the embodiment of Figures 3 to 6 is used to transfer the individual shells using a pressure cylinder. The cooling device in _ 7 reveals and displays another solution. Mode i here the chilled beam carrier (16) is positioned along the middle of the cooling shell segment (13) on the roller. The two additional cooling shells (13) utilize a straight or curved beam, =8) Rotating within a small limited range) is carried out by the corresponding "float pressure" of the spring (8). If this is not the case, the coil spring can also be placed at the end with the corresponding retaining member in the area of the cylinder (see Figures 3 to 6). The gap (30) is measured by a spacer (49) between the cooling jacket (13) and the working rollers (1) (7). Suitable materials for the spacers are, for example, hard cloth, aluminum, cast iron, self-lubricating metal or plastic, and spacers (49) located only in the edge of the chilled beam so as not to interfere with the central coolant flow. It is also possible to extend the spacing () through the length of the chilled beam as needed. These spacers can be used to adjust the spacing of the coolant or change the flow direction of the coolant. These spacers can also be placed on the central chilled beam section (13) (not shown). By the resulting flow of coolant flowing to the side, the edge region of the working roller (near the steel strip) is heated by the center of the heated coolant. If the working roller has a small diameter range for cooling, or if each rolling frame is in the same area, then in particular, a rigid cooling system is provided, that is, with a non-movable cooling casing (or without a casing). There is no pressure between the cylinders (8). It is thus also possible to use a rigid spacer shank in place of the movable cylinder (20) in an advantageous manner. Thus, the gap between the roller and the cooling jacket is slightly changed' but the system with segmental flow cooling is still effective and the system is relatively simple to manufacture. It is only necessary to position the cooling beam carrier working roller diameter and the working roller position in front of the roller, so that the gap is most appropriately arranged, that is, the outlet opening is relatively sealed in front of the roller, so the structure is several The rolling frames are all identical in design and only use the length adjustable rods to match the different rolling frame diameter ranges of one rolling track. In addition to the above-described combined low-pressure-high-pressure cooling system, the apparatus of Fig. 8 is provided with a low pressure on the inlet side with integrated "rolling gap lubrication means" (19) and "rolling gap cooling means (18)". Flow cooling system. Also shown in Figure 8 is how different high and low pressure systems are combined with one another. The liquid stream of the cooling liquid (7) may be separated below a cooling shell, or as exemplified herein on the inlet side and the outlet side, it is preferred to deflect a relatively large amount of coolant to the - direction. In order to enhance heat transfer, the general flow should be counter to the direction of rotation. The area with the "rolling gap lubrication means" (19) is subjected to the flow direction generated by the working roller cooling system and by a cooling device (50) provided with an elastic plastic surface or a cooling shell having an elastic plastic plate or a hard cloth plate. (5 1) Keep 浐17 201036721 Dance, for this reason, by, person I, the plate produced by the chilled beam carrier mechanism is pressed onto the roller, and the seven 丄 座 — — 股 股 — 股 股 股 股 股 股 股 股 股 股 股 股Design (Tough +, 〆 width ,, and because of its lubricant), before use, use the "roller gap spray means (not shown: from the area can be set to - compressed air Use ',, to blow the surface of the roller for drying. If you do not use, for example, the three cooling beams of the nozzle according to the cooling device of Fig. 9 can also be shell (9), which will be cooled by one or two. The beam is drilled into the cooling shell (47) with a replaceable cooling eve and a further hole (52), and the jets are sprayed from these holes from a short distance to the roller (1) (7). It is also possible to construct a flow cooling system of the segment type. Here, these The hole Μ Μ Μ ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' ' Crown-like arching curve of the coolant knives. Here the 'hole (52) can be oriented vertically towards the roller (Ό(2) or the coolant can also be slanted towards the roller (1) ( 2) In a modified example not shown, the cooling jacket is designed such that the coolant and outlet openings are simultaneously combined with a hole (52) in the plate by a rectangular groove (24) or (44) to enhance the Turbulence in the flow gap. Further details of the design of the nozzle and the casing are shown in Figures l〇a~丨〇f, where the nozzle is located in the center of the casing or is provided on one side in an asymmetrical arrangement (for example, Upper side) shortened design of the shell. By changing the transfer angle of the upper/lower nozzles or different cooling shell thicknesses (not shown), the distribution of the upward and downward coolant flow can be similarly affected. Show different spray patterns (aggregate the spray or "spray dispersion"). Cooling The side facing the roll 18 201036721 can be additionally smoothed or provided with grooves or frame strips (9), r · the flow caused by the flow has a positive effect on the cooling effect. 士,] σ,, Lu < , $ In all of the figures: the symmetry diagram of & is set in the lower part of the cooling beam (54) on the cooling shell (11) (12) with a replaceable nozzle; Figure l〇b is the nozzle (27) The resulting coolant opening is inclined at an angle a to the roller, and Figure 10c is a possible embodiment of a nozzle having a modified cross-sectional shape (2 and the frame strip or groove (9)," Figure 10〇d is a cooling shell which is shortened or elongated in an asymmetric manner to the nozzle (27). The funnel-shaped outlet opening (which is formed in the flow direction) may be provided with a "leading metal sheet" if necessary to provide a coolant Aiming at inward, outward or linear steering, so that a closed and uniform coolant jet is finally traversed along the width of the chilled beam. The coolant supply channel can also be designed as a funnel on the wide side of the chilled beam. The amount of cooling flowing in the side of the shell (beam edge) is reduced. In addition, the cooling beam can be sectioned along the length of the cooling beam to adjust the gap width in the coolant supply channel, and thus Change coolant distribution and cold along the length of the roller In order to make it easier to parabolically change the gap width of the outlet opening along the width range, the funnel-shaped supply channel is used in the example of Figure 10e (side view) and Figure 1 〇f (top view). ) is provided with a "spring metal piece" (53) which can be bent by an adjustment mechanism (not shown). Here, in the normal position, the spring metal piece rests on the side of the outlet opening, if the center is on one side Transfer, 19 201036721 where the gap becomes smaller. Here, another -..., when the spring metal piece: holding the male-long hole guide, and the embodiment of Figure l〇f only shows the principle, there may be Other structures having the same function. In the supply channel (55), the ~1 lc of the slit_(d) embodiment is shown in a side view, ^ is shown in the related top view in Fig. 12. Here, the long shape of the cooling beam 屮 ^ The outlet (4) face (10) is divided into individual width sections '; the section (59), the flow opening b of the coolant and the volume flow can be adjusted. The width section (10) can be made 5 〇 5, for example, not in this way. It is also possible to add the control means for cooling the field to the house. The slabs of the rolling wood are free from symmetry (slit, ). All the cooling beams of a rolling frame can be (4) (4) (4) 彳 ' and these areas can be connected correspondingly, or the individual beams of a rolling frame can be controlled separately. In the embodiment of the drawing U, the closed mechanism of the m-section is a line pressure or liquid, a system of staying. Depending on the pressure level of the system or according to the measured volume flow: the flow opens n (b) can be adjusted from open to partially open or closed. If you do not know the stretchable plastic tongue (6G) set by the section, you can also use the flipper or pusher that can be stretched or moved. The eccentric shifting means or other mechanical end control means affects the cross section of the outlet opening in a fragmented manner. In the embodiment of Figures 11a to 1ic, a pressure chamber is provided on the side of the supply passage (55). (10) As a closure element, its stretchable plastic hose _ forms part of the supply channel (55). In the initial state of Fig. 1 & the air chamber is in the range of ., , and pressure, so that the moving opening (b) is completely open as shown in Fig. 12 in the width section (state). In the picture! In lb, the pressure chamber (56) is pressurized by a pressure 20 201036721. The pressure road (57) is partially filled with compressed air or a liquid, thus, the plastic soft (60). The split is forced into the supply channel (55) and the flow opening (6〇) is now partially closed, as shown in Figure 12 in the width section (59b). Figure 12 shows the fully closed flow opening (b) in the width section (59c). Here, the pressure chamber (56) according to Fig. iic is completely filled, and therefore the supply passage (55) is blocked in this area by closing these areas, which can thermally expand the roller and the profile of the steel strip and the flatness of the steel strip. Have a positive impact. It is advantageous to further reduce the energy by closing the cooling zone beside the steel strip while at the same time providing 13 (reducing) the amount of water required. Another principle of operation of zone cooling is shown in FIG. Here, the cooling shells (14) having a narrow length along the length of the roller are disposed adjacent to each other, and the slits (31) (32) (33) can be adjusted to different slit widths W1, w2, w3. Therefore, using different slit widths ' and applying a different pressure and a volume flow of the coolant to the gap (3) (called (1)) can produce different "specific cooling excess (five) / unit time" along the length of the roller. To separate the individual areas with different "cooling excess (41) / unit time", the "resistance, P liquid" (the pressure that generates a blockage) can be added between the cooling shells (丨4). The gap (34). It is also possible to create a cooling shell without the adjustment device, so that the gap between the cooling device and the roller can be arbitrarily different depending on the length of the roller. (13) (14) The ground material can advantageously use an elastic material that can rest against the roller without damaging the roller. For example, it can be - typed iron, slidable plastic, self-lubricating metal, inscription or hard Figure 14. A possible way to seal the gap between the working roller (1) and the cooling shell (μ) in Figure 14 is to use the tube (10) or a nozzle body (example (6) $ gas or Coolant) #喷流瞎Quasi-blowing into the gap 21 201036721 Coolant (7) from The gaps (30) are shown. Figures 15a and 15b show a partially acting axially adjustable working roller spray cooling system which can be made into a high pressure and low pressure cooling mode. The cooling system is an additional cooling system, and It can be operated in combination with a low-pressure shell cooling system not shown. The local positioning of the cooling nozzle or the application of the cooling liquid (7) should be achieved according to the control or adjustment of the profile and flatness. For this purpose, in Fig. 15a The spray nozzle beam section (4〇,) moves on a guide rod (63). Here, the positioning of the two spray nozzle beam sections (4〇,) is symmetrically utilized by the center of the roller A hydraulic cylinder (62), an articulated rod (62) and a nozzle beam carrier (64) are achieved. If not in this way, two hydraulic cylinders (61) can be considered in another way, which will be separately (65) on both sides (65). Positioning. The spray nozzle section (10), the left and right sides of the nozzle (4), using the supply line (25) to achieve a similar arrangement of the working roller cooling system shown in Figure 15b. Here, the hydraulic rod red (61) is used to rotate the joint rod and the joint swing rod (62) along the spray nozzle beam section (40,) via the - rotation point (66) in a circular path ( 64) The upper movement, thus deflecting the coolant jet (7) into or out of the steel strip to the working roller (1). Another type of change that is different from the pivotal Guanyin Bianyi is the change of the swinging rod (not shown). The two spray nozzle beams C4〇, 久田^) are used—the coupling is connected (4-joint Arc) Movement (if you want to avoid moving on a circular path (64)). It is also possible to sprinkle the spout on the nozzle beam section (40,) - the opening of the nozzle or the hydraulic stepping motor via the circular path (64). The rod moves the nozzle unit directly on the circular path (track) (64). The low pressure cooling system can also be used separately, you are not alone (ie not used with the high pressure cooling system group QJ. The adjacent cooling shell shell (13) Figure 16 shows the bending spring (8) as a means of elastic connection between 22 201036721. [Schematic description of the drawings] Figure 1 is a spray cooling system according to the prior art; Figure 2 is according to the prior art A high turbulent flow cooling device; FIG. 3 is a cooling device according to the present invention having a plurality of cooling shell segments which are spliced to each other; FIG. 4 is a skirt of FIG. 3 with another modified coolant flow; Figure 5 is a cooling device of the present invention having a cooling shell that is radially separated; Figure 6 is a cooling device of Figure 5 having a replaceable cooling shell or cooling plate; Figure 7 is a cooling device having a spring compression Cooling shell segment; Figure 8 is a cooling device with Sub-slot cooling means / roller gap-slip means and combined or low-pressure roller cooling system; Figure 9 is an annual heavy cooling device having a hole provided in the cooling shell; Figure l〇a~l〇f is a mouthpiece And the design of the cooling shell; Figures 11a to 11c are a slit width adjusting means; Fig. 12 is a slit width adjusting means; Fig. 13 is a zone cooling system; Fig. 14 is a slit sealing means; Figs. 15a and 15b are a plug The axially adjustable roller cooling element acts as a bending spring; Figure 16 shows the bending spring, 匕 as the closing between adjacent cooling shell segments. 23 201036721 Sectional/elastic connection. [Main component symbol Description] (I) (2) Working roller (3) Roller width (4) Rolling material (5) Roller rotation direction (6) Roller shell surface (7) Coolant (8) Spring (9) Slotted frame strips (10) Cooling device (II) Related cooling shells (12) Radially separated cooling shells (13) Cooling shell segments (14) Narrow cooling shells (15) Cooling shell joints (16 Cooling beam carrier (17) scraper (18) rolling gap cooling means (19) rolling gap lubrication means (20) pressure cylinder (21) pressure Rotation point (22) joint rotation point of cooling shell segment (23) pivot point of cooling beam carrier 24 201036721 (24) outlet opening (25) supply tube (26) outlet tube (27) nozzle (28) fluid spray Flow (29) inlet opening (30) gap between the roller shell surface and the cooling shell (31) slit with slit width W1
(32) 具缝隙寬度W2的縫隙 (33) 具縫隙寬度W3的缝隙 (34) 在狹窄冷却殼間的縫隙 (36) 壓力測量計 (37) 測量距離用的感測器 (38) 溫度感測器 (39) 路徑測量器 (40) 高壓冷却用的喷灑噴嘴 (40’） 喷灑喷嘴樑部段 (41) 每單位時間的比冷却液通過量 (42) 用於隔開冷却殼條帶的阻斷冷却液 (43) 冷却液的流動方向 (44) 漏斗形輸出槽孔 (45) 冷却樑載體之可能的調整方向 (46) 倚靠面 (47) 可更換的冷却板 (48) 橫樑 25 201036721 (49) 間隔板 (50) 具有彈性塑膠表面的冷却殼 (51) 具有彈性塑膠板的冷却殼 (52) 具有洞的冷却殼 (53) 彈簧金屬板(32) Slot with gap width W2 (33) Slot with gap width W3 (34) Slot between narrow cooling shells (36) Pressure gauge (37) Sensor for measuring distance (38) Temperature sensing (39) Path Measurer (40) Spray nozzle for high pressure cooling (40') Spray nozzle beam section (41) Specific coolant throughput per unit time (42) Used to separate the cooling shell strip Blocking coolant (43) Flow direction of coolant (44) Funnel-shaped output slot (45) Possible adjustment direction of cooling beam carrier (46) Relief surface (47) Replaceable cooling plate (48) Beam 25 201036721 (49) Spacer (50) Cooling shell with elastic plastic surface (51) Cooling shell with elastic plastic plate (52) Cooling shell with holes (53) Spring metal plate
(54) 冷却樑的下 (55) 漏斗形供應 (56) 壓力室 (57) 壓力管路 (58) 出口橫截面 (59) 出口橫截面 (60) 可拉伸的塑 (61) 壓缸 (62) 關節桿 (63) 導引桿 (64) 運動執道（ (65) 可動之喷嘴 (66) 旋轉點 b 流動開口 ND 冷却液供應 HD 冷却液供應 s 1 〜s3 冷却殼片段 部 通道 的寬部段 膠軟管 路線） 樑載體 管（低壓冷却系統） 管（高壓冷却系統） 的冷却區域 26(54) Lower chilled beam (55) Funnel shaped supply (56) Pressure chamber (57) Pressure line (58) Outlet cross section (59) Outlet cross section (60) Stretchable plastic (61) Pressure cylinder ( 62) Joint rod (63) Guide rod (64) Movement obstruction ((65) Movable nozzle (66) Rotation point b Flow opening ND Coolant supply HD Coolant supply s 1 ~ s3 Cooling shell section channel width Section rubber hose route) Beam carrier tube (low pressure cooling system) Cooling area for tube (high pressure cooling system) 26