201036907 六、發明說明： 【發明所屬之技術領域】 本發明係關於—種於線鑛機用鋸線之横動褒置中㈣橫 動親之移動速度之方法及其裝置。 【先前技術】 送出側之難包含賴線整聽繞之狀態，以對線鑛機供 給鑛線。鑛線自送出側之捲盤經由送出側之横動裝置而被供 〇 給至線鋸機之切斷位置，並於切斷位置處切斷半導體等工: 後，經由捲取側之橫域置而讀繞之_捲取至捲取 侧之捲盤上。 如此，检動裝置被設置於送出侧之捲盤、捲取侧之捲盤之 雙方上’於錢各㈣狀位置處，使橫輪在相對於鑛線 之移動方向為橫方向、換言之在捲盤之轴方向往復移動，藉 此可一邊將鋸線維持於相對於各個捲盤之軸方向為直角方 〇 向，一邊自送出側之捲盤將鋸線送出至線鋸機，並將來自線 鋸機之鋸線捲取至捲取側之捲盤上。 尤其於送出側之捲盤中，當鋸線之整列捲繞不正確時，鋸 線之送出位置與橫動數值控制之橫動輥之位置相錯開，因而 - 送出側捲盤上之鋸線送出位置與橫動輥之往復移動之同步 發生偏離。因此，必須對橫動親之往復移動進行速度之修正 控制。 專利文獻1及專利文獻2中揭示有一種接觸輥式橫動控制 099104968 3 201036907 技術。該控制技術係配置一對接觸輥使於靠近捲盤處插入鋸 線’並根據任一接觸輥與鋸線之接觸而修正橫動用導輥往復 移動之速度，以使橫動用導輥之位置追隨銀線之位置。 於習知接觸輥式橫動控制中，直至鋸線與任一 觸為止’均减行速度之修正控制，因㈣乎紐因應捲盤 上鑛線之較小偏離，而當捲盤之局部位置處鑛線之捲繞間距 錯誤增大時’因控制系統之延遲’橫動用導輥無法快速地追 隨較大捲繞間距之變化’而會發生鑛線自導減落或鑛線斷 線之不良情況。 [先行技術文獻] [專利文獻] [專利文獻1]曰本專利特開平6_29732〇號公報 [專利文獻2]日本專利特開平7·2378丨6號公報 【發明内容】 (發明所欲解決之問題） 因此，本發明之課題在於提供一種解決習知技術之缺點、 即亦可追祕線較大捲_距之變化的横馳髓術，而可 預防鋸線之脫落或斷線。 (解決問題之手段） 根據上述課題，本發明之橫動控制方法，係於將_機⑺ 用之捲盤⑷之鑛線(3)捲繞於橫動姉)及張力姉4)、並在 使橫動親(5)於㈣⑷之軸方向往復移動之過程巾在捲盤(句 099104968 4 201036907 與橫動輥(5)之間將鋸線(3)之目標位置設為相對於捲盤(4) 之軸方向為直角方向的橫動裝置（丨）中，於張力輥（14)之位置 處檢測錯線(3)之基準合力（F1)，同時於橫動輥(5)之位置處 - 根據鋸線(3)離目標位置之位移檢測變動合力（F2)，根據基準 合力（F1)與變動合力（F2)之差（△!?)之變動而控制橫動輥(5) 之往復移動速度(V)(第1發明）。 於上述橫動控制方法中’修正速度(AV)係根據基準合力 0 (F1)與變動合力（F2)之差（AF)之變動而求出，橫動輥(5)之往 復移動速度(V)係對橫動輥(5)之往復移動之基準速度(VI)進 行修正速度（Δν)之加減運算而算出（第2發明）。 又，本發明之橫動控制裝置（10)，係於將線鋸機(2)用之捲 盤(4)之鋸線(3)捲繞於橫動輥(5)及張力輥（14)、並在使橫動 輥(5)於捲盤(4)之軸方向往復移動之過程中在捲盤(4)與橫 動輥(5)之間將鋸線(3)之目標位置設為相對於捲盤(4)之軸 〇 方向為直角方向的橫動裝置（1)中，包括有：於張力軺 之位置.處檢測鋸線（3)之基準合力（F1)之基準合力檢測器 (11);於橫動輥(5)之位置處根據鋸線(3)離目標位置之位移 ’ 檢測變動合力（F2)之變動合力檢測器（12);及根據基準合力 (F1)與變動合力（F2)之差（ΔΡ)之變動求出橫動輥(5)往復移 動之速度(V)，並根據所求出之速度(V)賦予橫動馬達(6)速度 指令之速度控制器（13)(第3發明）。 於上述橫動控制裝置（10)中，速度控制器（13)係設定往復 099104968 5 201036907 移動之基準速度(V1)，根據基準合力（F1)與變動合力(F2)之 差⑽)之變動求出修正速度(Λν)，並對基準速度(νι)進行 仏正速度(Λν)之加減運异，而算出橫動輥(5)之往復移動之 速度(V)(第4發明）。 於上述橫動㈣裝置⑽中，將鑛線(3)之直線狀路徑設為 1區間，張力輥(Μ)係配置於上述i區間之，，基準合 力檢測11(11)係設置於張力姉彳)之位置處，_橫動副 系又置於上述1區間之另—端側，變動合力檢測器（12)係設 置於橫動輥(5)之位置處（第5發明）。 於上述橫動控難置⑽中，橫動輥(5)位置處之据線(3) =捲制度與張力_4)位置處之料(3)之捲録度係設 疋為相等之角度值（第6發明）。 於上述橫動控制裝置⑽)中，橫動輥(5)之報軸⑺係相對 於捲盤(4)之轴方向為直角方向（第7發明）。 ==動㈣裝置⑽中，橫動謂之鄉⑺係藉由擺 _，獅f(9)係II由相躲謎(4)之軸方向為 平订之擺動師）而可擺動自如地受支持（第8發 (發明效果） ) 根據本發明之橫動控制方法，於橫動裝置⑴中，於張力 輥（14)之位置處檢測鋸線 ' ^ ™ . )之基皁&力（？1)，同時於橫動輥 处根據錫線（3)離目標位置之位移而 (F2)，根據基準合力卬 m 力（υ與交動合力（F2)之差(簡之變動而 099104968 201036907 控制橫動輥(5)往復移動之速度(V)，因此鋸線(3)離目標位置 之位移可以合力值於橫動輥(5)位置處之連續變動值而把 握。藉此’即便捲繞間距有較大變化，橫動輥亦可追隨， 除可增大鋸線(3)捲繞間距之容許範圍外，亦無鋸線(3)之脫 . 落、鋸線(3)之斷線等不良情況，因此可提高鋸線(3)在線鋸 機(2)上移動之可靠性（第1發明）。 對松動辕(5)往復移動之基準速度(vi)，將根據基準合力 〇 (F1)與變動合力（F2)之差（AF)之變動所求出之修正速度（△ V)作為變動部分而進行加減運算，而算出橫動輥(5)往復移 動之速度(V) ’因此變動部分修正速度（△▽)不會有較大變 化，可抑制速度(V)之較大變動，速度控制變得穩定，響應 性亦提高（第2發明）。 又’根據本發明之橫動控制裝置（1〇)，鋸線⑺離目標位置 之位移可以變動合力（F2)而連續地把握，藉此，即便捲繞間 Ο 距有較大變化，橫動輥(5)亦可追隨，除鑛線(3)捲繞間距之 容許範圍增大外，亦無鋸線(3)之脫落、鋸線(3)之斷線等不 良情況，鋸線(3)於線鋸機(2)上移動之可靠性提高，並且藉 由基準合力檢測器（11)、變動合力檢測器（12)、速度控制器 (13)之簡單構成，可進行橫動輥往復移動之速度調節，因 此可容易且廉價地實現最佳控制（第3發明）。 於上述橫動控制裝置（1〇)中，對往復移動之固定基準速度 (VI)進行變動部分修正速度(^v)之加減運算，而算出橫動 099104968 201036907 輥(5)之往復移動速度(V)，因此變動部分修正速度(AV)無較 大變化，可抑制速度(V)之較大變動，速度(v)之速度控制變 得穩定，控制之響應性亦提高（第4發明）。 於上述検動控制裝置（10)中，於鋸線(3)之直線狀路徑之j 區間一端側設置張力輥（14)、基準合力檢測器（11),於上述 1區間之另一端側没置橫動輥(5)、變動合力檢測器（12)，因 此鋸線(3)於1區間兩端幾乎無張力變化，結果，當測定基 準合力（F1)及變動合力（F2)時’ *會出現因}區間兩端之張 力差異而引起之檢測誤差，因此速度控制之精度變佳（第5 發明）。 於上述橫動控制置（1〇)中，若將橫動輕⑺位置處及張力 輥（14)位置處之鋸線(3)捲繞角度設定為相等值，則基準合力 檢測器（11)之輸出及變動合力檢測器（12)之輸出無須換算， 可直接將料進行崎而求出差（的，因此錢處理變得 容易（第6發明）。 於上述橫動控制裝置⑽中，若將橫_(5)之親轴⑺設 為相對於難(4)之轴方向為直肖方向，顺城⑺之溝槽 朝向與謎(4)上麟(3)之位移方向相—致，因此即便鑛線 (3)中財位移，料⑶料會自縣_)脫落且鑛線⑶ 之斷線亦可減少（第7發明）。 於上述橫動控難置⑽中，若設為藉由軸f⑼保持橫 動輥(5)之輥軸(7) ’且藉由相對於捲盤(4)之軸方向為平行之 099104968 。 201036907 擺動轴（8)相對於往復移動用之滑件（17)可擺動自如地支持 擺動臂（9)的構成，則當捲盤(4)上鋸線(3)之捲徑發生變化 時’藉由擺動臂（9)之擺動使橫動輥(5)之溝槽方向經常與鋸 線(3)之方向相一致，因此可確實地防止由鋸線(3)之捲徑之 變化而引起鋸線(3)之脫落（第8發明）。 【實施方式】 圖1係表示橫動裝置1與作為編入對象之線鋸機2之關 〇 係。橫動襞置1相對於線鋸機2除設置於鋸線3之送出側之 外’亦設置於鋸線3之捲取侧。 圖1中，送出側之橫動裝置1係將鋸線3纏繞並貯存於送 出侧之捲盤4，在自該捲盤4抽出鋸線3而將其捲繞於附有 溝槽之橫動輥5後，經由附有溝槽之張力輥14、附有溝槽 之跳動輥I5、進而1個或2個以上附有溝槽之導輥18而朝 線鑛機2之方向被導引，以將鋸線3供給至線鋸機2。線錄 Θ 機2藉由移動之鋸線3而切斷工件。然後，鋸線3自1個或 2個以上附有溝槽之導輥18而朝捲取侧被導引，並經由附 有溝槽之跳動輥15、附有溝槽之張力輥14、捲取側橫動裝 置1之附有溝槽之橫動輥5而被捲取至捲取側之捲盤4。 圖示之具體例中，送出側之橫動裴置1與捲取侧之橫動裝 置1為相同構成。因此，如上述，亦歟予捲取側之橫動裝置 1與送出側之橫動裝置1相同之元件符號，於以下記载中， 說明特別重要的送出側之橫動裝置1，而適當省略捲取側之 099104968 9 201036907 橫動裝置1之說明。 送出側之捲盤4可由框架20之支持輪19而旋轉自如地受 支持。於送出時，捲盤4藉由鋸線3之抽出而從動旋轉、或 者視需要藉由未圖示之驅動馬達一邊將鋸線3之張力維持 為既定值，一邊朝送出方向積極驅動旋轉。 而且’橫動輥5藉由橫動馬達6及旋轉.往復直線運動變 換手段16而於鋸線3移動方向之橫方向、換言之於捲盤4 之軸方向往復移動，以於捲盤4與横動輥5之間將鋸線3 維持於目標位置。此處’鑛線3之目榡位置被設定為於捲盤 4之位置處不會干涉相鄰之鑛線3且不會相互摩擦之位置 處、即設定為相對於捲盤4之轴方向為直角方向。 ㈣·往復直線運動變換手段16實際上由饋進螺桿式直 動單元所駭。㈣，橫動馬達6對作為補.減直線運 動變換手⑨16之饋進螺桿式直動單元經由旋轉方向之轉 換、固定之旋轉速度錢轉速度之變化，而料驅動對象之 滑件17既定往復移動。 。…者旋轉往復直線運動變換手段Μ亦可為滑件曲柄式 早凡構成。於上述滑件曲柄式單元構成之情形時，橫動馬達 朝同旋轉方向驅動曲柄，曲柄之旋轉經由連桿而賦予滑 件17既定之直線往復運動。 示圖1夕卜圖2係表示橫動輥5之支持例。滑件ρ由相 ’於捲盤4之軸方向為平行之縣軸8可縣自如地保持擺 099104968 201036907 動臂9之一端以支持橫動輥5，擺動臂9之另一端則藉由相 對於捲盤4之轴方向較佳為直角方向且不與其相交之輥軸7 而可旋轉自如地支持橫動親5。再者，橫動報5之輥轴7可 直接安裝於安裝在擺動臂9的變動合力檢測器12之檢測 部、或於可朝鋸線3之合力產生方向位移之狀態下而安裝於 擺動臂9之另一端，抵接於變動合力檢測器12之檢測部以 檢測合力。 〇 其次，張力輥14相對於輥轴24可旋轉自如地受支持。張 力輥14之輥軸24可直接安裝於安裝在框架20的基準合力 檢測器11之檢測部、或於可朝鋸線3之合力產生方向位移 之狀態下而安裝於框架20，抵接於基準合力檢測器11之檢 測部以檢測合力。 又，跳動輥15係藉由轉動賦勢手段21之賦勢臂22、賦 勢臂22之前端輥軸23而可朝圓弧方向位移自如地受支持。 Ο 轉動賦勢手段21容許跳動輥15朝圓弧方向之擺動位移，由 此一邊吸收鋸線3之路徑長度變化，一邊經常賦予鋸線3 既定張力。再者，跳動輥15可由採用直動式賦勢手段而非 轉動賦勢手段21構成，關於其具體例，之後將與圖10 —併 進行說明。 於圖示例中，橫動輥5與張力輥14相鄰接，且鋸線3於 該等之間被拉伸為直線狀，而形成鋸線路徑之1區間。張力 輥14被配置於該1區間之一端側，橫動輥5則被設置於同 099104968 11 201036907 一 1區間之另一端側。因此，於橫動輥5之位置及張力輥 14之位置處，鋸線3之張力T為相等值。 又，關於橫動輥5位置處之鋸線3之捲繞角度與張力輥 14位置處之鋸線3之捲繞角度，考慮到於各自位置處檢測 合力時之測定方便性，較佳態樣係設定為相等之角度值，其 一例為直角。 而且，圖3係表示本發明之橫動控制裝置10。橫動控制 裝置10係以上述橫動裝置1為前提，而具有基準合力檢測 器11、變動合力檢測器12及速度控制器13，以修正橫動輥 5之往復移動速度V。 基準合力檢測器11由負載單元、磁性放大式感測器等力 一電信號變換感測器而構成，其在張力輥14之位置處抵接 於可朝以鋸線3之張力T為分力之合力產生方向位移之輥 軸24，張力輥14位置之合力經檢測為鋸線3之基準合力 F1，而將與基準合力F1成比例之電信號S1發送至速度控 制器13。 此處，基準合力F1係以鋸線3相對於張力輥14捲繞狀態 之張力T為分力，因此，利用捲繞角度為90°之1/2而求出 鋸線3之張力T為T = F110545°。該張力T係受到張力控 制，以使於鋸線3之移動中經常成為目標值，因此基準合力 F1於鋸線3移動中亦經常成為固定值。 另一方面，變動合力檢測器12與上述相同地由力一電信 099104968 12 201036907 號變換感測器而構成，其在橫動輥5之位置處抵接於可朝合 力產生方向位移之輕軸7，檢測出鑛線3相對於橫動親5捲 繞狀態之合力為鋸線3實際之變動合力F2，並將與變動合 .力F2成比例之電信號S2發送至速度控制器13。 .如上述般’橫動輥5位置處域線3張力τ亦與張力親 位置處之張力τ相等。因此，若鑛線3於橫動輥5與捲 C1 盤4之間相對於目標位置、即捲盤4之轴方向為直角，則橫 動輥5之捲繞角度與張力觀14位置處之捲繞角度為相同之 角度值因此即便換動輥5發生橫向移動（朝捲盤*之轴方 向移動）\該位置處之變動合力F2亦與基準合力F1相等。 …、、而’右ϋ線3於横動輥5與捲盤4之間自目標位置位 ]鑛線3對於㈣輥5之捲繞角度偏離直角，而會朝銳 向或鈍角之方向變化。因此’儘管張力Τ於橫動輥5 ❹ 2置處未有任何變化’㈣動合力F2在銳角之捲繞角度 时會產生大於基準人力 尺女 干77 H之變動’而於鈍角之捲繞角度時 會產生小於基準合力Π之變動。 於&動輥5之橫向移動中，鑛線3之捲繞角度在橫 之變^位置處產生變動’由此變動合力F2會與捲繞角度 《比你丨地'^動，故可作為檢測鑛.線 3離目標位置位 於上、）之參數。橫動馬達6之速度控制(轉速控制）係著眼 ;乂方面’於;^動親5之位置處由鑛線3之捲繞角度變化 而檢測鑛線3離目標位置之位移(偏移）。 099104968 13 201036907 速度控制器13比較根據信號S1之基準合力F1與根據信 號S2之變動合力F2，根據其差Δ]ρ之變動而求出橫動輥5 之往復移動速度V，根據所求出之速度V賦予橫動馬達6 速度指令信號S3。由圖具體所示，於速度控制器13中藉由 基準速度設定器25設定往復移動之基準速度vi，速度控制 器13根據差AF之正負符號而決定加速或減速，根據差八^^^ 之絕對值求出修正速度△▽，並對基準速度V1進行修正速 度Δν之加法運算或減法運算，而產生速度指令之信號S3， 错由5亥"fa ?虎S 3來驅動橫動馬達6。 如上述，將橫動輕5位置處錯線3之捲繞角度與張力親 14位置處鑛線3之捲繞角度設定為相等。因此，基準合力 檢測器11之輸出信號S1及變動合力檢測器12之輸出信號 S2為可直接進行比較之狀態。藉此，可容易進行信號處理。 然而，當橫她5位置處之麟3捲繞角度與張力親14 位置處之减3捲繞肖度被設定^相等之肖度值時，則對 基準合力檢測器11或變動合力檢測器12之輸出乘以係數、 或者於信號Si、S2之傳達路徑中插人換算器，藉此將該等 信號S卜S2轉換為可比較之位準而進行比較。該等捲繞角 度被設定為不相等角度值之具體例將例示於後述圖7至圖 10中。 送出側之橫動控制裝置10係根據 速度指令之信號S3指 令，一邊使橫動馬達6 週期性地轉換旋轉方向一邊以既定速 099104968 14 201036907 度對其進行驅動，藉由旋轉.往復直線運動變換手段16使滑 件17於捲盤4之轴方向進行往復直線移動，藉由使滑件17 之往復運動與捲繞間距同步，而於捲盤4與橫動輥5之間將 鑛線3之位置維持在相對於捲盤4之軸方向成直角方向之目 標位置處。再者，往復移動之行程係被設定在捲盤4之捲體 範圍内。 於此種橫動控制之過程中，若鋸線3之捲繞間距於送出側 〇 之捲盤4錯誤增大，而鋸線3之位置於捲盤4與橫動輥5 之間偏移目標位置時’速度控制器13朝解除鋸線3偏移目 標位置之方向調節往復移動之速度v，藉此於捲盤4與橫動 報5之間使鋸線3之位置回到目標位置。 圖4至圖6係表示在橫動輥5之往復移動行程中捲盤4 與杈動輥5之間之鋸線3之位置變化、根據此時信號S1之 基準合力F1與根據信號S2之變動合力F2之大小比較關 ◎係。於該等圖中，作為一例，將橫動輥5接近張力輥14方 向之速度v設為+符號，反之，將橫動輥5離開張力輥14 方向之速度V設為-符號。 如圖4所示，於橫動輥5朝任一方向移動之過程中，若鋸 線3位於目標位置，則於橫動輥5及張力輥14各自之位置 處’張力T相等且鋸線3之捲繞角度為相同值，因此基準 合力F1與變動合力F2相等。因此，基準合力fi與變動合 力F2之差Μ為零、即F1 —F2=AF=〇。只要將鑛線3維 099104968 15 201036907 持在目標位置，則△? = 〇之關係將保持不變。此時，無須 對橫動輥5之往復移動速度v進行速度修正之控制。該狀 態為理想之控制態樣。 其次，如圖5所示，於橫動輥5朝往復移動之速度+v方 向移動之情形時，如a所示，當鋸線3之捲繞角度於橫動輥 5之位置處為銳角時，則F2> F1，因此速度控制器η輸入 k號S1及彳§號S2並產生與F1 — F2 = -^F之變動相對應之 修正速度-AV，並自基準速度+v減去修正速度_△、，藉此 產生與速度指令{(+V)—(-Λν)} =+(ν+Λν)相對應之信 號S3 ’藉由該信號S3使橫動馬達6加速。相反，如圖4之 b所示，當鋸線3之捲繞角度於橫動輥5之位置處為鈍角 時，則F2<F1，因此速度控制器13產生與F1 —F2 = +Af 之變動相對應之修正速度+AV，並自基準速度+v減去修正 速度+AV，藉此產生與速度指令{(+ν)_(+Λν)} — △ V)相對應之信號S3 ’藉由該信號S3而使橫動馬達6減速。 又，如圖6所示，於橫動輥5朝往復移動之速度_v方向 移動之情形時，如a所示，當鋸線3之捲繞角度於橫動輥5 之位置處為銳角時，則F2>F1 ’因此速度控制器13輸入信 號S1及信號S2並產生與F1 — F2 = -AF之變動相對應之修 正速度-Δν ’並自基準速度-V減去修正速度_av，藉此產 生與速度指令{(-V)—(-Λν)} =·(ν—Λν)相對應之信號 S3 ’藉由該信號S3使橫動馬達6減速。相反，如圖5之匕 099104968 16 201036907 所示，當鋸線3之捲繞角度於橫動輥5之位置處為鈍角時， 則F2<F1，因此速度控制器13產生與pi —= 之變 動相對應之修正速度+AV，並自基準速度_v減去修正速度 +AV，藉此產生與速度指令{(_v)_(+AV)} =_(v+av) 相對應之信號S3，藉由該信號S3而使橫動馬達6加速。 再者，與上述例不同，當將橫動輥5接近張力輥14方向 之速度v設定為-符號，相反將橫動輥5離開張力輥14方向 Ο 之速度v設定為+符號時，修正速度土Δν係經常對基準速 度土V進行加法運算而非進行減法運算。 如上述，於橫動輥5之往復移動中，當鋸線3之位置因鑛 線3之捲繞間距變化等而偏離目標位置時，則速度控制器 I3對基準速度±v進行修正速度±Δν之加錢算，將橫動 親5之往復移動速度V朝加速或減速方向調節，藉此使鑛 線3之位置回到目標位 ο 置之方向，而使鋸線3之位置自動巧 隨目標位置。再者，於如知 目動追 、起動之初期，即便鋸線3之位置 目標位置，亦可藉由以μ ^ 夏偏離 之速度控制，而使鑛線3之位晉於 短時間内移動至目標位置，因此達到穩定。 ； 二速、控制除相於將橫_ 5之往復移動速度 固定而進行驅動時外介 保持 之經過逐漸增大速度ν 飞•間 而進打加速驅動時、及隨時 過逐漸減小速度V㈣行減速雜時之任—一間之經 如上述，橫動輥5 > + 月 "轴7相祕魅4之財向為直角 099104968 及巧 17 201036907 方向’因此橫動輥5之溝槽朝向係經常於捲盤4上與軸方向 鋸線3之位移方向一致。因此，鋸線3即便於捲盤4之軸方 向位移，鋸線3亦不會脫離横動輥5，而其斷線亦會減少。 又’板動輥5之輥軸7係藉由擺動臂9而保持，藉由相對 於捲盤4之軸方向為平行之擺動轴8可將擺動臂9相對於往 復移動用之滑件17而擺動自如地支持，因此即便捲盤4之 鑛線3捲徑發生變化’橫動輥5之溝槽方向會財與鑛線3 之方向保持—致，因此科實防止_線3之捲徑變化而引 起鋸線3之脫落。 於合力之檢測過程中，於橫動輥5與張力輥14之間，在 鑛線3之直線狀路徑之1區間内，鑛線3幾乎無張力變動， 而於檢測基準合力F1或變動合力打時，不會出現因各測 定位置處之張力值差異㈣起之誤差，因此速度控制之精度 變佳。 基準合力檢測HU之設置位置並不受限於張力輥“之位 其他位置。圖7例係於跳動糙15之位置處設 土準口力檢測器U，使跳動輥15兼用作張力輥14之功 張力輥14)^置麵衫準合力檢測 輥14)之間°^F1目此㈣粮5與跳動觀15(張力 曰之幸昆為單方向轉換用之導輥18。 於圖7之跳動輥15之設置位置處，張力 因鑛線3之彎曲$ @Λ '、有寺會 之考曲或麟雜中導輥18之存在，而與橫動輕 099104968 18 201036907 5位置處之張力T稍有不同。又，鋸線3對於跳動輥b之 捲繞角度例如為180°，其與橫動輥5位置處之鋸線3位於 目標位置時之捲繞角度9〇°不同。因此，基準合力之大 小亦與圖1中之基準合力F1不同。 因此，由跳動輥15位置之基準合力檢測器U所檢測之測 定值係無法直接作為信號S1而輸出至速度控制器13。此 時’如上所述’基準合力檢測器11之測定值係藉由對該值 〇 乘以適當係數、或者於輸出k遽之傳達路徑中插入換算5|， 就可與變動合力F2比較之位準之基準合力F1所對應的信 號S1進行運算，並發送至速度控制器13。 又，圖8例係將張力輥14處鋸線3之捲繞角度設為與橫 動輥5位置處鑛線3之捲繞角度9〇。不同之角度值。鑛線3 係例如以捲繞角度180。捲繞於張力輥14後，其視需要可經 由1個或2個以上之導輥18而被導引至跳動輥μ等之既定 〇 位置處。 然後，圖9例係繼橫動輥5後配置跳動輥15，使跳動輥 15兼用作張力輥14之功能，於跳動輥15(張力輥14)之位置 處由基準合力檢測器11檢測基準合力F1。圖9中之跳動輥 15(張力輥14)由旋轉賦勢手段21之水平方向的賦勢臂22 而可轉動自如地受支持，鑛線3於以捲繞角度為例如18〇。 捲繞於跳_ 15(張力輥14)後，其被導引至跳動棍15等之 既定位置處。賦勢臂22係以水平方向為基準位置而朝任_ 099104968 19 201036907 f向轉動，但該基準位置並不受限於水平方向，亦可設定為 相對於水平線為傾斜之方向。該例為圖7之變形例，"省 略圖7之導輥.就減少導輕18之設置數、降低旋轉負載 及減少零件數之觀點而言，較佳係省略導親18。 而且圖10例係由直動式賦勢手段26而非旋轉賦勢手段 21可位移自如地支持跳動幸昆15(張力幸昆14)。再者，直動式 賦勢手26主要藉由電系統、例如線性馬達、電動馬達與 走轉饋進螺桿’螺帽等直線運動變換手段之組合、彈菁或流 體壓力或者錘重而朝所需方向產生賦勢力。 由圖7至圖10例可知’於檢測基準合力fi日夺張力輕 14上鑛線3之捲制度並不受限於90。，可歧為適當之角 度，又，基準合力檢測器11之設置位置、即張力輥14之設 置位置並不受限於包含以橫動輥5為一端之1區間，經由可 比較位準信號S1(基準合力Fi)之運算處理而可選定位鑛線 3之任意路徑。 (產業上之可利用性） 由以上可知’本發明主要在將纏繞於送出側捲盤4之鋸線 3送出至線鑛機2情況時，鋸線3相對於捲盤4之整列捲繞 不完全時具有效果。 然而’本發明亦可利用於捲取侧。於捲取側，只要橫動輥 5正確進行往復移動’則鋸線3會成為整列捲繞在捲取側之 捲盤4的狀態’而當鋸線3因任一原因偏離目標位置時’捲 099104968 20 201036907 取側之橫動控制裝置10藉由調節橫動輥5之速度V而可使 鋸線3回到目標位置。 再者，捲盤4亦可設置為水平放置而非縱向放置。於捲盤 4水平放置之情形時，橫動輥5係於水平方向進行往復移動。 【圖式簡單說明】 圖1係作為本發明前提之線鋸機用橫動裝置之前視圖。 圖2係作為本發明前提之線鋸機用橫動裝置中橫動輥支 0 持部分之俯視圖。 圖3係本發明橫動控制裝置之方塊線圖。 圖4係鋸線目標位置處之控制原理說明圖。 圖5係鋸線於+方向移動時之控制原理說明圖。 圖6係鋸線於-方向移動時之控制原理說明圖。 圖7係基準合力另一測定例之說明圖。 圖8係基準合力另一測定例之說明圖。 〇 圖9係基準合力另一測定例之說明圖。 圖10係基準合力又一測定例之說明圖。 【主要元件符號說明】 1 橫動裝置 2 線鋸機 3 鋸線 4 捲盤 5 橫動輥 099104968 21 201036907 6 7 8 9 10 11 12 13 14 15 16 17 18 19 橫動馬達 輥軸 擺動軸 擺動臂 橫動控制裝置 基準合力檢測器 變動合力檢測器 速度控制器 張力親 跳動輥 旋轉·往復直線運動變換手段 滑件 導輥 支持軸 20 框架 21 旋轉賦勢手段 22 賦勢臂 23 輥軸 24 輥軸 25 基準速度設定器 26 直動式賦勢手段 a 橫動輥5位置處鋸線3之捲繞角度為銳角時 099104968 22 201036907 b 橫動輥5位置處鋸線3之捲繞角度為鈍角時 FI 基準合力 F2 變動合力 SI 、 S2 、 S3信號 T 張力 V 往復移動之速度 VI 基準速度 +v 橫動輥5接近張力輥14之方向之速度 -V 橫動輥5離開張力輥14之方向之速度 △ F 差 △ V 修正速度 099104968 23201036907 VI. Description of the Invention: [Technical Field of the Invention] The present invention relates to a method and apparatus for traversing a moving speed of a traversing device for a wire sawing machine. [Prior Art] It is difficult to include the state of the entire line on the sending side to supply the line to the line mining machine. The reel of the ore line from the delivery side is supplied to the cutting position of the wire saw by the traversing device on the delivery side, and the semiconductor is cut at the cutting position: The read-through _ is taken up to the reel on the take-up side. In this way, the detecting device is disposed on both the reel on the delivery side and the reel on the take-up side at the position of each of the money (four), so that the horizontal direction of the horizontal wheel is transverse to the direction of the mine, in other words, in the roll. The reciprocating movement of the disk in the axial direction allows the saw wire to be fed at a right angle to the axial direction of each reel, and the reel is fed from the delivery side to the wire saw machine, and the wire is fed from the wire. The saw wire of the saw is taken up to the reel on the take-up side. Especially in the reel of the delivery side, when the entire row of the saw wire is not wound correctly, the feeding position of the saw wire is shifted from the position of the traverse roller of the traverse numerical control, and thus - the saw wire on the delivery side reel is sent out The position deviates from the synchronization of the reciprocating movement of the traversing roller. Therefore, the speed correction control must be performed for the reciprocating movement of the traverse. Patent Document 1 and Patent Document 2 disclose a contact roll type traverse control 099104968 3 201036907. The control technology is configured to arrange a pair of contact rollers to insert a saw wire near the reel and correct the reciprocating movement speed of the traverse guide roller according to the contact of any contact roller with the saw wire, so that the position of the traverse guide roller follows The location of the silver line. In the conventional contact roller type traverse control, the correction control of the reduction speed of the saw line and any touch is caused by (4) the small deviation of the ore line on the reel, and the local position of the reel When the winding pitch of the mine line is increased incorrectly, the delay of the traverse guide roller cannot follow the change of the larger winding pitch due to the delay of the control system, and the mine self-guided drop or the mine wire breakage may occur. Happening. [PRIOR ART DOCUMENT] [Patent Document 1] [Patent Document 1] Japanese Patent Laid-Open Publication No. Hei. No. Hei. No. Hei. Therefore, an object of the present invention is to provide a transverse medullary technique which solves the shortcomings of the prior art, that is, can also trace the change of the larger volume _ the distance of the line, and can prevent the detachment or disconnection of the saw wire. (Means for Solving the Problem) According to the above problem, the traverse control method of the present invention is to wind the ore (3) of the reel (4) for the machine (7) around the traverse 及) and the tension 姊 4), and The process of reciprocating the traverse parent (5) in the axial direction of (4) (4) on the reel (the sentence 099104968 4 201036907 and the traverse roller (5) set the target position of the saw wire (3) relative to the reel ( 4) In the traverse device (丨) whose direction of the axis is a right angle, the reference resultant force (F1) of the wrong line (3) is detected at the position of the tension roller (14), and at the position of the traverse roller (5) - Detecting the change resultant force (F2) according to the displacement of the saw wire (3) from the target position, and controlling the reciprocation of the traverse roller (5) according to the variation of the difference between the reference resultant force (F1) and the fluctuating resultant force (F2) (Δ!?) Movement speed (V) (first invention). In the above-described traverse control method, the 'correction speed (AV) is obtained by the variation of the difference (AF) between the reference resultant force 0 (F1) and the combined force (F2). The reciprocating speed (V) of the moving roller (5) is calculated by adding or subtracting the correction speed (Δν) from the reference speed (VI) of the reciprocating movement of the traverse roller (5) (second invention). The traverse control device (10) for winding the saw wire (3) of the reel (4) for the wire saw machine (2) is wound around the traverse roller (5) and the tension roller (14), and is The traverse roller (5) sets the target position of the saw wire (3) relative to the reel between the reel (4) and the traverse roller (5) during the reciprocating movement of the reel (4) in the axial direction of the reel (4). (4) The traverse device (1) in which the direction of the axis 为 is a right angle includes a reference force detector (11) for detecting the reference resultant force (F1) of the saw wire (3) at the position of the tension 轺; Detecting the variation of the combined force (F2) at the position of the traverse roller (5) according to the displacement of the saw wire (3) from the target position (12); and the resultant force (F1) and the combined force according to the reference (F2) The speed (Δ) of the traverse roller (5) is obtained by the variation of the difference (ΔΡ), and the speed controller (13) of the traverse motor (6) speed command is given according to the obtained speed (V) ( According to a third aspect of the invention, in the traverse control device (10), the speed controller (13) sets the reference speed (V1) of the reciprocating 099104968 5 201036907 movement, and the difference between the reference resultant force (F1) and the fluctuating resultant force (F2). (10)) Change the correction speed (Λν), and the speed (V) of the reciprocating movement of the traverse roller (5) is calculated by adding and subtracting the speed (νν) of the reference speed (νι) (fourth invention). In the traverse (4) device (10), the linear path of the ore line (3) is set to one section, the tension roller (Μ) is disposed in the i section, and the reference resultant force detection 11 (11) is set to the tension 姊. At the position of 彳), the traverse sub-system is placed on the other end side of the above-mentioned one section, and the yaw force detector (12) is provided at the position of the traverse roller (5) (the fifth invention). In the above-mentioned traverse control difficulty (10), the line (3) at the position of the traverse roller (5) = the volume of the material (3) at the position of the volume (3) is set at an equal angle. Value (6th invention). In the traverse control device (10), the registration axis (7) of the traverse roller (5) is a direction perpendicular to the axial direction of the reel (4) (the seventh invention). == In the (4) device (10), the traverse of the town (7) is oscillated by the pendulum _, the lion f (9) system II is swayed by the axis of the axis (4) Support (Eighth (Invention Effect)) According to the traverse control method of the present invention, in the traverse device (1), the base soap & force is detected at the position of the tension roller (14) ?1), at the same time at the traverse roller according to the displacement of the tin wire (3) from the target position (F2), according to the reference resultant force 卬m force (the difference between the υ and the combined force (F2) (simple change and 099104968 201036907 The speed (V) of the reciprocating movement of the traverse roller (5) is controlled, so that the displacement of the saw wire (3) from the target position can be grasped by the continuous variation value of the resultant value at the position of the traverse roller (5). There is a large change in the pitch, and the traverse roller can follow. In addition to increasing the allowable range of the winding pitch of the saw wire (3), there is no disconnection of the saw wire (3), and the wire (3) is broken. If the problem is not good, the reliability of the movement of the saw wire (3) on the wire saw (2) can be improved (the first invention). The reference speed (vi) of the reciprocating movement of the loose 辕 (5) will be based on the reference force 〇 ( F1) The correction speed (ΔV) obtained by the variation of the difference (AF) of the combined force (F2) is added and subtracted as a fluctuation, and the speed (V) of the reciprocating movement of the traverse roller (5) is calculated. The fluctuation speed (Δ▽) of the fluctuation portion does not largely change, and the large fluctuation of the speed (V) can be suppressed, the speed control is stabilized, and the responsiveness is also improved (second invention). Further, the traverse according to the present invention The control device (1〇), the displacement of the saw wire (7) from the target position can be continuously controlled by changing the resultant force (F2), whereby the traverse roller (5) can follow even if there is a large change in the inter-winding distance. In addition to the increase in the allowable range of the winding spacing of the ore line (3), there are no problems such as the falling off of the sawing wire (3), the broken wire of the sawing wire (3), and the sawing wire (3) in the wire sawing machine (2) The reliability of the upper movement is improved, and the speed adjustment of the reciprocating movement of the traverse roller can be performed by the simple configuration of the reference resultant force detector (11), the variable force detector (12), and the speed controller (13), so that it is easy And optimal control is realized inexpensively (third invention). In the above-described traverse control device (1〇), the reciprocating movement The fixed reference speed (VI) is added and subtracted by the variable partial correction speed (^v), and the reciprocating moving speed (V) of the traverse 099104968 201036907 roller (5) is calculated, so that the modified portion correction speed (AV) does not largely change. It is possible to suppress a large fluctuation in the speed (V), the speed control of the speed (v) is stabilized, and the responsiveness of the control is also improved (fourth invention). In the above-described sway control device (10), the saw wire (3) a linear roller path (14) and a reference total force detector (11) are provided on one end of the linear path, and the traverse roller (5) and the variable force detector (12) are not disposed on the other end side of the first section. Therefore, the saw wire (3) has almost no tension change at both ends of the 1 section, and as a result, when the reference resultant force (F1) and the fluctuating resultant force (F2) are measured, the detection error caused by the difference in tension between the ends of the interval may occur. Therefore, the accuracy of the speed control is improved (the fifth invention). In the above traverse control setting (1〇), if the winding angle of the saw wire (3) at the position of the traverse light (7) and the tension roller (14) is set to an equal value, the reference resultant force detector (11) The output of the output and the variable force detector (12) does not need to be converted, and the material can be directly obtained by sampling the difference (the sixth invention). In the traverse control device (10), The axis _(5) is set to the direction perpendicular to the axis of the difficulty (4), and the direction of the groove of the city (7) is the same as the direction of displacement of the mystery (4). Even if the mine (3) has a financial displacement, the material (3) will fall off from the county _) and the broken line of the ore (3) can be reduced (the seventh invention). In the traverse control (10), the roller shaft (7)' of the traverse roller (5) is held by the shaft f (9) and is 099104968 which is parallel with respect to the axial direction of the reel (4). 201036907 The swing shaft (8) rotatably supports the swing arm (9) with respect to the reciprocating slider (17), and when the winding diameter of the saw wire (3) on the reel (4) changes ' By the swinging of the swing arm (9), the direction of the groove of the traversing roller (5) often coincides with the direction of the saw wire (3), so that the change of the winding diameter of the saw wire (3) can be reliably prevented. The saw wire (3) is detached (the eighth invention). [Embodiment] Fig. 1 shows the relationship between the traverse device 1 and the wire saw 2 as a target. The traverse device 1 is disposed on the winding side of the saw wire 3 with respect to the wire saw 2 except for the delivery side of the saw wire 3. In Fig. 1, the traverse device 1 on the delivery side is a reel 4 in which the saw wire 3 is wound and stored on the delivery side, and the saw wire 3 is taken out from the reel 4 and wound around the traverse with the groove. After the roller 5, it is guided in the direction of the line miner 2 via the grooved tension roller 14, the grooved dancer roller I5, and further one or more grooved guide rollers 18. The saw wire 3 is supplied to the wire saw 2 . The line recorder 2 cuts the workpiece by moving the saw wire 3. Then, the saw wire 3 is guided toward the take-up side from one or more guide rolls 18 with grooves, and is passed through a grooved bounce roller 15, a grooved tension roll 14, and a take-up The traverse roller 5 to which the side traverse device 1 is attached is taken up to the reel 4 on the take-up side. In the specific example shown in the figure, the traverse device 1 on the delivery side has the same configuration as the traverse device 1 on the winding side. Therefore, the same components as those of the traverse device 1 on the take-up side and the traverse device 1 on the delivery side are also described above, and in the following description, the traverse device 1 on the delivery side which is particularly important is described, and is appropriately omitted. 099104968 9 201036907 Description of the traversing device 1 on the take-up side. The reel 4 on the delivery side can be rotatably supported by the support wheel 19 of the frame 20. At the time of the delivery, the reel 4 is driven to rotate by the extraction of the saw wire 3, or the rotation of the saw wire 3 is maintained at a predetermined value by a drive motor (not shown), and the rotation is actively driven in the delivery direction. Further, the traverse roller 5 reciprocates in the lateral direction of the movement direction of the saw wire 3 by the traverse motor 6 and the reciprocating linear motion conversion means 16, in other words, in the axial direction of the reel 4, so as to reel 4 and The saw wire 3 is maintained at the target position between the moving rollers 5. Here, the position of the 'mine line 3' is set to a position where the position of the reel 4 does not interfere with the adjacent metal line 3 and does not rub against each other, that is, the direction with respect to the axis of the reel 4 is Right angle direction. (4) The reciprocating linear motion changing means 16 is actually carried by the feed screw type direct acting unit. (4) The traverse motor 6 changes the rotation speed of the feeding screw type linear motion unit which is the feeding/reducing linear motion conversion hand 916 via the rotation direction, and the rotational speed of the fixed rotation speed, and the slider 17 of the material driving object is set to reciprocate. mobile. . The rotary reciprocating linear motion changing means can also be constructed as a slider crank type. In the case of the above-described slider crank unit configuration, the traverse motor drives the crank in the same rotational direction, and the rotation of the crank imparts a predetermined linear reciprocating motion to the slider 17 via the link. Fig. 1 shows a support example of the traverse roller 5. The slider ρ is held by the county axis 8 which is parallel to the axis direction of the reel 4, and can be freely held by the counter. 099104968 201036907 One end of the boom 9 supports the traverse roller 5, and the other end of the swing arm 9 is opposite to The axial direction of the reel 4 is preferably a right angle direction and does not intersect the roller shaft 7 to rotatably support the traverse 5 . Further, the roller shaft 7 of the traverse 5 can be directly attached to the detecting portion of the yaw force detector 12 attached to the oscillating arm 9, or can be attached to the oscillating arm in a state in which it can be displaced in the direction of the resultant force of the saw wire 3. The other end of the 9 is abutted against the detecting portion of the variable force detector 12 to detect the resultant force. 〇 Next, the tension roller 14 is rotatably supported relative to the roller shaft 24. The roller shaft 24 of the tension roller 14 can be directly attached to the detecting portion of the reference resultant force detector 11 attached to the frame 20, or can be attached to the frame 20 in a state in which it can be displaced in the direction in which the combined force of the saw wire 3 is generated, and abuts against the reference. The detecting portion of the force detector 11 detects the resultant force. Further, the dancer roller 15 is rotatably supported in the circular arc direction by the biasing arm 22 of the biasing means 21 and the front end roller shaft 23 of the biasing arm 22.转动 The rotation imparting means 21 allows the oscillating roller 15 to oscillate in the direction of the circular arc, thereby absorbing the predetermined length of the saw wire 3 while absorbing the path length of the saw wire 3. Further, the dancer roller 15 may be constituted by a direct-acting orienting means instead of the rotary biasing means 21. For a specific example thereof, it will be described later with reference to Fig. 10. In the illustrated example, the traverse roller 5 is adjacent to the tension roller 14, and the saw wire 3 is stretched linearly between the two to form a section of the sawing path. The tension roller 14 is disposed on one end side of the one section, and the traverse roller 5 is disposed on the other end side of the section 099104968 11 201036907. Therefore, at the position of the traverse roller 5 and the position of the tension roller 14, the tension T of the saw wire 3 is equal. Further, regarding the winding angle of the saw wire 3 at the position of the traverse roller 5 and the winding angle of the saw wire 3 at the position of the tension roller 14, considering the convenience of measurement when detecting the resultant force at the respective positions, a preferred aspect The values are set to equal angle values, an example of which is a right angle. Moreover, Fig. 3 shows the traverse control device 10 of the present invention. The traverse control device 10 is based on the traverse device 1 and has a reference total force detector 11, a yaw force detector 12, and a speed controller 13 for correcting the reciprocating speed V of the traverse roller 5. The reference resultant force detector 11 is composed of a force-electric signal conversion sensor such as a load unit, a magnetic amplification sensor, and the like, which abuts on the tension T of the saw wire 3 at the position of the tension roller 14 The resultant force produces a directional displacement roller shaft 24, and the resultant force of the tension roller 14 is detected as the reference resultant force F1 of the saw wire 3, and the electrical signal S1 proportional to the reference resultant force F1 is sent to the speed controller 13. Here, since the reference resultant force F1 is the component of the tension T of the saw wire 3 with respect to the state in which the tension roller 14 is wound, the tension T of the saw wire 3 is obtained by using the winding angle of 1/2 of 90°. = F110545°. The tension T is controlled by the tension so that the movement of the saw wire 3 often becomes a target value, and therefore the reference resultant force F1 often becomes a fixed value during the movement of the saw wire 3. On the other hand, the variable resultant force detector 12 is constructed by the force-transport 099104968 12 201036907 conversion sensor as described above, and abuts at the position of the traverse roller 5 against the light shaft 7 which is displaceable in the direction of the resultant force generation. The resultant force of the mine line 3 with respect to the traverse 5 winding state is the actual fluctuating force F2 of the saw wire 3, and the electric signal S2 proportional to the fluctuating force F2 is sent to the speed controller 13. As described above, the tension τ of the field line 3 at the position of the traverse roller 5 is also equal to the tension τ at the tension position. Therefore, if the ore line 3 is at a right angle with respect to the target position, that is, the axial direction of the reel 4 between the traverse roller 5 and the reel C1 disc 4, the winding angle of the traverse roller 5 and the tension at the position of the tension view 14 Since the winding angle is the same angle value, even if the shifting roller 5 is laterally moved (moving in the direction of the reel* axis), the fluctuating resultant force F2 at this position is equal to the reference resultant force F1. ..., and the 'right ϋ line 3 is positioned from the target position between the traverse roller 5 and the reel 4.] The angle of rotation of the ore line 3 with respect to the (four) roller 5 deviates from a right angle and changes in a direction of a sharp or obtuse angle. Therefore, 'although the tension is not changed at the position of the traverse roller 5 ❹ 2' (4) The dynamic force F2 will produce a change larger than the reference human foot length 77 H at the acute angle of the winding angle' and the winding angle at the obtuse angle It will produce less than the change in the benchmark force. In the lateral movement of the & moving roller 5, the winding angle of the ore line 3 changes at the position of the transverse change ^, and thus the fluctuating force F2 will be compared with the winding angle "beyond your squatting", so it can be used as Detect the parameters of the mine. Line 3 from the target position. The speed control (rotation speed control) of the traverse motor 6 is focused on; the displacement (offset) of the ore line 3 from the target position is detected by the change of the winding angle of the ore line 3 at the position of the moving motor 5. 099104968 13 201036907 The speed controller 13 compares the reference resultant force F1 according to the signal S1 with the fluctuation resultant force F2 according to the signal S2, and obtains the reciprocating speed V of the traverse roller 5 based on the variation of the difference Δ] ρ, which is obtained based on the obtained The speed V is applied to the traverse motor 6 speed command signal S3. As shown in the figure, the speed controller 13 sets the reference speed vi of the reciprocating movement by the reference speed setter 25, and the speed controller 13 determines the acceleration or deceleration according to the sign of the difference AF, according to the difference. The absolute value is used to obtain the correction speed Δ▽, and the reference speed V1 is added or subtracted by the correction speed Δν to generate the speed command signal S3, and the traverse motor 6 is driven by the 5 HAI "fa? tiger S 3 . As described above, the winding angle of the misalignment line 3 at the position of the traverse light 5 and the winding angle of the ore line 3 at the position of the tension pro 14 are set to be equal. Therefore, the output signal S1 of the reference resultant force detector 11 and the output signal S2 of the variable resultant force detector 12 are in a state in which they can be directly compared. Thereby, signal processing can be easily performed. However, when the winding angle of the 3rd position at the 5th position and the 3rd winding degree at the position of the tension pro 14 are set equal to each other, the reference resultant force detector 11 or the variable resultant force detector 12 is used. The output is multiplied by a factor, or a converter is inserted in the transmission path of the signals Si, S2, thereby converting the signals Sb to S2 to a comparable level for comparison. Specific examples in which the winding angles are set to unequal angle values will be exemplified in Figs. 7 to 10 to be described later. The traverse control device 10 on the delivery side commands the traverse motor 6 to rotate the rotation direction at a predetermined speed of 099104968 14 201036907 degrees according to the command S3 of the speed command, and rotates by reciprocating linear motion. The means 16 reciprocally linearly moves the slider 17 in the axial direction of the reel 4, and the mineral line 3 is placed between the reel 4 and the traversing roller 5 by synchronizing the reciprocating motion of the slider 17 with the winding pitch. The position is maintained at a target position at a right angle to the axial direction of the reel 4. Further, the stroke of the reciprocating movement is set within the winding body of the reel 4. In the process of such traverse control, if the winding pitch of the saw wire 3 is erroneously increased by the reel 4 of the delivery side, the position of the saw wire 3 is offset between the reel 4 and the traverse roller 5 At the time of position, the speed controller 13 adjusts the reciprocating speed v in the direction in which the saw wire 3 is displaced from the target position, whereby the position of the saw wire 3 is returned to the target position between the reel 4 and the traverse 5. 4 to 6 show the positional change of the saw wire 3 between the reel 4 and the swaying roller 5 in the reciprocating movement stroke of the traverse roller 5, the resultant force F1 according to the signal S1 at this time, and the change according to the signal S2. The size of the joint force F2 is relatively close. In the drawings, as an example, the speed v of the traverse roller 5 in the direction of the tension roller 14 is set to a + sign, and the speed V of the traverse roller 5 in the direction of the tension roller 14 is set to a sign. As shown in FIG. 4, in the process of moving the traverse roller 5 in either direction, if the saw wire 3 is at the target position, the tension T is equal at the respective positions of the traverse roller 5 and the tension roller 14 and the saw wire 3 is Since the winding angle is the same value, the reference resultant force F1 is equal to the variable resultant force F2. Therefore, the difference between the reference resultant force fi and the variable resultant force F2 is zero, that is, F1 - F2 = AF = 〇. As long as the 3D 099104968 15 201036907 is held at the target position, the relationship of △? = 〇 will remain unchanged. At this time, it is not necessary to control the speed correction of the reciprocating speed v of the traverse roller 5. This state is an ideal control aspect. Next, as shown in FIG. 5, when the traverse roller 5 is moved in the speed + v direction of the reciprocating movement, as shown by a, when the winding angle of the saw wire 3 is an acute angle at the position of the traverse roller 5, , F2 > F1, so the speed controller η inputs k number S1 and 彳§ number S2 and generates a correction speed -AV corresponding to the change of F1 - F2 = -^F, and subtracts the correction speed from the reference speed + v _Δ, thereby generating a signal S3' corresponding to the speed command {(+V) - (-Λν)} = + (ν + Λν), by which the traverse motor 6 is accelerated. On the contrary, as shown in b of Fig. 4, when the winding angle of the saw wire 3 is an obtuse angle at the position of the traverse roller 5, then F2 < F1, so the speed controller 13 produces a change with F1 - F2 = + Af Corresponding correction speed +AV, and subtracting the correction speed +AV from the reference speed +v, thereby generating a signal S3' corresponding to the speed command {(+ν)_(+Λν)} - ΔV) This signal S3 decelerates the traverse motor 6. Further, as shown in FIG. 6, when the traverse roller 5 is moved in the speed_v direction of the reciprocating movement, as shown by a, when the winding angle of the saw wire 3 is an acute angle at the position of the traverse roller 5, , F2 > F1 'The speed controller 13 inputs the signal S1 and the signal S2 and generates a correction speed -Δν ' corresponding to the fluctuation of F1 - F2 = -AF and subtracts the correction speed _av from the reference speed -V. This generates a signal S3' corresponding to the speed command {(-V) - (-Λν)} = (ν - Λν), which decelerates the traverse motor 6 by the signal S3. On the contrary, as shown in Fig. 5, 099104968 16 201036907, when the winding angle of the saw wire 3 is an obtuse angle at the position of the traverse roller 5, then F2 < F1, and therefore the speed controller 13 produces a change with pi -= Corresponding to the correction speed +AV, and subtracting the correction speed +AV from the reference speed _v, thereby generating a signal S3 corresponding to the speed command {(_v)_(+AV)} = _(v+av), The traverse motor 6 is accelerated by the signal S3. Further, unlike the above example, when the speed v of the traverse roller 5 in the direction of the tension roller 14 is set to the - sign, and the speed v of the traverse roller 5 from the direction of the tension roller 14 is set to the + sign, the correction speed is set. The soil Δν system often adds the reference velocity soil V instead of subtracting it. As described above, in the reciprocating movement of the traverse roller 5, when the position of the saw wire 3 deviates from the target position due to the change in the winding pitch of the mine wire 3, etc., the speed controller I3 corrects the reference speed ±v by the speed ± Δν Adding money, the reciprocating moving speed V of the traverse pro 5 is adjusted in the direction of acceleration or deceleration, thereby returning the position of the mine 3 to the direction of the target position, and the position of the saw 3 is automatically matched with the target. position. Furthermore, in the initial stage of the tracking and starting, even if the position of the saw wire 3 is at the target position, the position of the mine 3 can be moved to a short time by the speed control of the μ ^ summer deviation. The target position is therefore stable. ; 2nd speed, control, and the phase is increased by the reciprocating movement speed of the horizontal _ 5, and the external medium is gradually increased by the speed ν. • When the acceleration is driven, and the speed is gradually reduced (V) Deceleration of the time - one as described above, the traverse roller 5 > + month " axis 7 phase secret charm 4 of the wealth is right angle 099104968 and clever 17 201036907 direction 'so the traverse roller 5 groove orientation It is often coincident with the direction of displacement of the axial direction saw wire 3 on the reel 4. Therefore, even if the saw wire 3 is displaced in the axial direction of the reel 4, the saw wire 3 does not come off the traverse roller 5, and the broken wire is also reduced. Further, the roller shaft 7 of the plate rolling roller 5 is held by the swing arm 9, and the swing arm 9 can be moved relative to the slider 17 for reciprocating movement by the swing shaft 8 which is parallel with respect to the axial direction of the reel 4. It is freely supported by the swing, so even if the diameter of the ore 3 of the reel 4 changes, the direction of the groove of the traverse roller 5 will be maintained in the direction of the mine 3, so the volume of the coil is prevented from changing. And causing the saw wire 3 to fall off. During the detection process of the resultant force, between the traverse roller 5 and the tension roller 14, in the interval of the linear path of the mine line 3, the mine line 3 has almost no tension fluctuation, and the joint force F1 or the variable force is detected. When the error due to the difference in the tension value at each measurement position (4) does not occur, the accuracy of the speed control becomes better. The setting position of the reference resultant force detecting HU is not limited to the other positions of the tension roller. The example of Fig. 7 is to set the grounding force detector U at the position of the bounce roughness 15 so that the dancer roller 15 also serves as the tension roller 14. The work tension roller 14) is placed between the face-to-face force detection roller 14) ° ^ F1 mesh (4) grain 5 and the beating view 15 (tension 曰 幸 幸 for the single direction conversion guide roller 18. At the set position of the roller 15, the tension is due to the bending of the mine line 3 @@', the presence of the temple test or the guide roller 18 of the lining, and the tension T at the position of the traverse light 099104968 18 201036907 5 In addition, the winding angle of the saw wire 3 to the dancer roller b is, for example, 180°, which is different from the winding angle 9〇° when the saw wire 3 at the position of the traverse roller 5 is at the target position. Therefore, the reference resultant force The magnitude is also different from the reference resultant force F1 in Fig. 1. Therefore, the measured value detected by the reference resultant force detector U at the position of the dancer roller 15 cannot be directly output to the speed controller 13 as the signal S1. The measured value of the 'reference force detector 11 is obtained by multiplying the value 适当 by an appropriate coefficient, or The conversion scale 5| is inserted into the transmission path of the output k遽, and the signal S1 corresponding to the reference resultant force F1 of the level of the comparison force F2 is calculated and sent to the speed controller 13. Further, Fig. 8 shows the tension The winding angle of the saw wire 3 at the roller 14 is set to be the winding angle 9 矿 of the mine wire 3 at the position of the traverse roller 5. The angle value is different. The mine wire 3 is, for example, wound at an angle of 180. After 14 , it may be guided to a predetermined 〇 position of the dancer roller μ or the like via one or more guide rollers 18 as needed. Then, in FIG. 9 , the pulsating roller 15 is disposed after the traverse roller 5 , The dancer roller 15 is also used as the function of the tension roller 14, and the reference resultant force F1 is detected by the reference resultant force detector 11 at the position of the dancer roller 15 (tension roller 14). The dancer roller 15 (tension roller 14) in Fig. 9 is rotated. The horizontally oriented arm 22 of the potential means 21 is rotatably supported, and the mine 3 is at a winding angle of, for example, 18 〇. After being wound around the hop 15 (tension roller 14), it is guided to At the predetermined position of the jumping stick 15, etc. The arm 22 is oriented in the horizontal direction and is oriented toward _ 099104968 19 201036907 f However, the reference position is not limited to the horizontal direction, and may be set to a direction inclined with respect to the horizontal line. This example is a modification of Fig. 7, " omitting the guide roller of Fig. 7 to reduce the guide light 18 From the viewpoint of setting the number, reducing the rotational load, and reducing the number of parts, it is preferable to omit the guide member 18. Moreover, the example of Fig. 10 is capable of displaceably supporting the jump by the direct acting type means 26 instead of the rotary orienting means 21. Kun 15 (Tension Xingkun 14). Furthermore, the direct-acting hand 26 is mainly composed of a combination of electric system, such as a linear motor, an electric motor, and a linear motion conversion means such as a screw feed nut. Or fluid pressure or hammer weight to create a force in the desired direction. It can be seen from the example of Fig. 7 to Fig. 10 that the system of measuring the joint force fi and the tension of the upper mine line 3 is not limited to 90. The position of the reference resultant force detector 11, that is, the position at which the tension roller 14 is disposed, is not limited to including one section with one end of the traverse roller 5, via the comparable level signal S1. The calculation of the (reference resultant force Fi) can optionally locate any path of the mine line 3. (Industrial Applicability) As apparent from the above, the present invention mainly winds the saw wire 3 with respect to the entire row of the reel 4 when the saw wire 3 wound around the delivery side reel 4 is sent to the wire miner 2 . It has an effect when it is complete. However, the present invention can also be utilized on the take-up side. On the take-up side, as long as the traverse roller 5 is correctly reciprocated, the saw wire 3 will be in a state of being wound around the reel 4 on the take-up side. When the saw wire 3 is deviated from the target position for any reason, the roll 099104968 20 201036907 The traverse control device 10 of the take-up side can return the saw wire 3 to the target position by adjusting the speed V of the traverse roller 5. Furthermore, the reel 4 can also be placed horizontally rather than vertically. When the reel 4 is horizontally placed, the traverse roller 5 reciprocates in the horizontal direction. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a front view of a traverse device for a wire saw machine as a premise of the present invention. Fig. 2 is a plan view showing a holding portion of a traverse roller in a traverse device for a wire saw machine which is a premise of the present invention. Figure 3 is a block diagram of the traverse control device of the present invention. Figure 4 is an explanatory diagram of the control principle at the target position of the saw line. Fig. 5 is an explanatory diagram of the control principle when the saw wire is moved in the + direction. Fig. 6 is an explanatory diagram of the control principle when the saw wire is moved in the - direction. Fig. 7 is an explanatory view showing another measurement example of the reference combined force. Fig. 8 is an explanatory view showing another measurement example of the reference combined force. 〇 Fig. 9 is an explanatory view showing another measurement example of the reference combined force. Fig. 10 is an explanatory view showing another measurement example of the reference resultant force. [Description of main component symbols] 1 traversing device 2 wire sawing machine 3 sawing wire 4 reel 5 traverse roller 099104968 21 201036907 6 7 8 9 10 11 12 13 14 15 16 17 18 19 traverse motor roller shaft oscillating shaft oscillating arm Traverse control device reference resultant force detector change force detector speed controller tension pro-bounce roller rotation reciprocating linear motion change means slider guide roller support shaft 20 frame 21 rotary orientation means 22 fusible arm 23 roller shaft 24 roller shaft 25 Reference speed setter 26 Direct-acting biasing means a When the winding angle of the sawing wire 3 is at an acute angle at the position of the traverse roller 5, 099104968 22 201036907 b When the winding angle of the sawing wire 3 at the position of the traverse roller 5 is an obtuse angle, the FI reference Force F2 Change resultant force SI, S2, S3 signal T Tension V Speed of reciprocating movement VI Reference speed + v Speed of traverse roller 5 in the direction of tension roller 14 -V Speed of traverse roller 5 away from tension roller 14 △ F Difference △ V correction speed 099104968 23