201202120 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種甲板起重機的油壓驅動裝置、起重 機裝置、油壓泵浦的控制裝置及船舶。 【先前技術】 甲板起重機係設置於貨船之甲板上，且用在輸運於海 上的貨物之裝載或卸載作業中。貨物係涉及到許多方面可 從雜貨類、穀物、煤炭等的散裝物至貨櫃且通過世界的港 口而運送。因而，在進行海上貨物之搬運時，甲板起重機 爲不可或缺的裝卸貨物機械。 在甲板起重機的驅動方式之中，一般可列舉電動油壓 式。此爲藉由電動馬達之動力來驅動被搭載於甲板起重機 的油壓泵浦，且藉由從油壓泵浦吐出的作動油使油壓致動 器驅動，進而藉由其動力來驅動油壓裝置的方法。 來自油壓泵浦的作動油之吐出流量Q(l/min)，係 當將油壓泵浦之每一旋轉的作動油之吐出容量設爲q( cc/rev)、將油壓泵浦的旋轉數設爲N(rpm)、將油壓泵 浦的容積效率設爲卩pv時，可以下式表示。 [數式1] Q=qXNX77pv/l 000 在此，作爲油壓泵浦的種類，可列舉固定容量型與可 變容量型。固定容量型的油壓栗浦，係每一旋轉的作動油 之吐出容量q爲一定。因此，即使油壓裝置於空轉（ -5- 201202120 idling )狀態下，固定容量型的油壓泵浦，也會吐出與驅 動時相同的容量之作動油。又，可變容量型的油壓泵浦， 係可將每一旋轉的作動油之吐出容量q設爲可變。然而， 可變容量型的油壓泵浦之控制方法，一般可採用固定馬力 控制’且在輕負載時或是油壓裝置於空轉狀態時，每一旋 轉的作動油之吐出容量q會變成最大吐出容量。 又，油壓泵浦的旋轉數N，雖然是成爲相應於電動馬 達之旋轉數的値，但是由於電動馬達的旋轉數爲固定，所 以即使在油壓裝置於空轉狀態下仍會以與驅動時相同的旋 轉數來旋轉。 (專利文獻1)日本特開2007-137641號公報 【發明內容】 (發明所欲解決之問題） 如此，先前技術供油壓裝置驅動用的油壓泵浦，係在 油壓裝置於空轉狀態時，對油壓致動器的作動油之供給就 無關於需不需要，均會吐出最大流量的作動油。因此，有 產生白白浪費掉的驅動能源及較大的噪音之問題。在對油 壓致動器供給作動油時，若來自油壓泵浦的作動油之吐出 流量越大，則油壓泵浦的驅動所造成的噪音、作動油通過 作動油供給管線時所產生的噪音、以及白白浪費掉的驅動 能源就會變得越大。 因此，本發明係有鑒於上述問題而開發完成者，本發 明之目的係在於提供一種在油壓裝置於空轉狀態下，能夠 -6 - 201202120 降低噪音之產生及白白浪費掉的驅動能源之既新穎又經改 良過的甲板起重機的油壓驅動裝置。 (解決問題之手段） 爲了解決上述課題，依據本發明之一態樣，可提供一 種甲板起重機的油壓驅動裝置，其具有：油壓致動器，其 係使油壓裝置動作；及油壓泵浦，其係透過作動油供給管 線將作動油供給至上述油壓致動器；以及控制部，其係按 照指示上述油壓裝置之動作的操作，來控制被供給至上述 油壓致動器的作動油之流量，並且當連接於上述油壓泵浦 的上述油壓致動器在一預定時間以上未動作時，便將來自 該油壓泵浦的作動油之吐出流量控制成大致最小。 依據如此的構成，可按照指示油壓裝置的動作之操作 而控制來自油壓泵浦的作動油之吐出流量。此時，當連接 於油壓泵浦的油壓致動器在一預定時間以上未動作的空轉 狀態之情況時，便將來自油壓泵浦的作動油之吐出流量設 在大致最小。因此，可將先前技術於空轉狀態下成爲最大 吐出流量的作動油設在最小吐出流量。因此，在油壓裝置 未動作的空轉狀態下，可降低因作動油通過作動油管線時 泰 所產生的噪音及白白浪費掉的驅動能源。 又，亦可復具備：電動馬達，其係驅動上述油壓栗浦 :以及變頻器，其係控制上述電動馬達的旋轉數，上述控 制部，係利用上述變頻器將上述電動馬達的旋轉數設在最 小，藉此將上述油壓栗浦的旋轉數設在最小，且將上述吐 201202120 出流量控制成大致最小。 又，亦可爲：上述油壓泵浦，爲可變容量型油壓泵浦 ，上述控制部，係將上述油壓泵浦之每一旋轉的作動油之 吐出容量設在最小，藉此將上述吐出流量控制成大致最小 〇 又，上述油壓驅動裝置，亦可包含複數個配置有上述 油壓致動器、上述作動油供給管線及上述油壓泵浦的油壓 供給系，複數個上述油壓泵浦’係連結於一個上述電動馬 達而被驅動，上述控制部，係將複數個上述油壓泵浦之中 、連接於上述油壓泵浦的上述油壓致動器在一預定時間以 上未動作的油壓泵浦之上述每一旋轉的作動油之吐出容量 控制成大致最小。 又，亦可復具備：電磁閥，其係透過控制油供給管線 而與上述油壓泵浦連接，並切換對上述油壓泵浦供給控制 油之有無，上述油壓泵浦，係可按照上述供給控制油之有 無來變更上述每一旋轉的作動油之吐出容量，上述控制部 ，係藉由控制上述電磁閥，將上述吐出流量控制成大致最 小。 又，上述油壓泵浦，亦可具有：活塞，其係吐出相應 於衝程量的上述作動油；以及調整部，其係利用上述控制 油之油壓來調整上述活塞的衝程量。 上述作動油，亦可從貯藏上述作動油的油槽被供給至 上述油壓泵浦，並且從上述油壓泵浦吐出的上述作動油係 被回收至上述油槽，該油壓驅動裝置復具備：送風機，其 -8- 201202120 係送出施加壓力後的空氣；及熱交換器，其係設置於從上 述油壓泵浦吐出的作動油被回收至上述油槽的路徑上，並 使從上述油壓泵浦吐出的作動油之熱朝向由上述送風機所 送出的空氣移動；以及第2變頻器，其係控制用以驅動上 述送風機的第2電動馬達之旋轉數，上述控制部，係當在 一預定時間以上的期間，偵測出沒有指示上述油壓裝置之 動作的操作時，就利用上述第2變頻器將上述第2電動馬 達的旋轉數控制成大致最小》 又，上述控制部，亦可檢測出於上述預定期間以內已 進行指示上述油壓裝置之動作的操作之期間，利用上述第 2變頻器，將上述第2馬達之旋轉數，控制成與從上述油 壓栗浦吐出的作動油之溫度成正比、或與進行指示上述油 壓裝置之動作的操作的操作部之傾斜成正比的旋轉數。 又，爲了解決上述課題，依據本發明之另一態樣，可 提供一種起重機裝置，其具有：油壓致動器，其係使油壓 裝置動作；及油壓泵浦，其係透過作動油供給管線將作動 油供給至上述油壓致動器；以及控制部，其係按照指示上 述油壓裝置之動作的操作，來控制被供給至上述油壓致動 器的作動油之流量，並且當連接於上述油壓栗浦的上述油 壓致動器在一預定時間以上未動作時，便將來自該油壓泵 浦的作動油之吐出流量控制成大致最小。 又，爲了解決上述課題，依據本發明之另一態樣，可 提供一種油壓泵浦的控制裝置，係將作動油供給至使油壓 裝置動作的油壓致動器，其具有：控制部，其係按照指示 -9- 201202120 上述油壓裝置之動作的操作，來控制被供給至上述油壓致 動器的作動油之流s，並且當連接於上述油壓泵浦的上述 油壓致動器在一預定時間以上未動作時，便將來自該油壓 泵浦的作動油之吐出流量控制成大致最小。 又，爲了解決上述課題，依據本發明之另一態樣，可 提供一種船舶，其具備1個或2個以上的起重機裝置，該 起重機裝置係具有：油壓致動器，其係使油壓裝置動作； 及油壓泵浦，其係透過作動油供給管線將作動油供給至上 述油壓致動器；以及控制部，其係按照指示上述油壓裝置 之動作的操作，來控制被供給至上述油壓致動器的作動油 之流量，並且當連接於上述油壓泵浦的上述油壓致動器在 一預定時間以上未動作時，便將來自該油壓泵浦的作動油 之吐出流量控制成大致最小。 (發明效果） 如以上說明依據本發明，則藉由減少在甲板起重機的 油壓裝置未動作時從油壓泵浦吐出的作動油之流量，即可 降低白白浪費掉的驅動能源及噪音》 【實施方式】 以下一邊參照所附圖式，一邊針對本發明的實施形態 加以詳細說明。另外，在本說明書及圖式中，有關實質上 具有同一功能構成的構成要素，係藉由附記同一元件符號 而省略重複說明。 -10- 201202120 首先，針對本發明之第1至第5實施形態的甲板起重 機之全體構成一邊參照第1圖一邊加以說明，之後，針對 各實施形態之甲板起重機的油壓驅動裝置加以說明。 [甲板起重機的全體構成] 甲板起重機10，係設置於船舶（未圖示）的甲板上 ，且用在輸運於海上的貨物之裝載或卸載作業中。甲板起 重機10，係具有：下部支柱（post) 20、旋轉支柱（起重 機操縱室（crane house) ) 30、旋轉軸承32、運轉室40 、懸臂（jib ) 50、懸臂支撐部52、掛鉤60、滑輪（操縱 室頂篩（house top sieve)群）62、滑輪（懸臂頂篩群） 64及鋼索66。在旋轉支柱（起重機操縱室）30，係配設 有之後詳述的甲板起重機之油壓驅動裝置1〇〇。旋轉支柱 30，係在下部支柱20之上部藉由設置於其下部的旋轉軸 承3 2，以該軸承的旋轉軸線爲中心能夠在甲板上水平地 迴旋。將藉由迴旋旋轉支柱3 0，使起重機的懸臂50迴旋 的動作，稱爲旋轉（slewing)。 在旋轉支柱30的前方側部，係設置有運轉室40。在 運轉室40，係設置有用以操作甲板起重機的手柄。在旋 轉支柱3 0，復設置有懸臂5 0。懸臂5 0，係藉由將其一端 設置於旋轉支柱下端的2處之懸臂支撐部52而能夠俯仰 地支撐。將爲了使懸臂50對準與貨物之間的距離，以懸 臂支撐部52爲中心使懸臂50進行俯仰（傾斜）的動作， 稱爲上下擺動（luffing)。旋轉及上下擺動，係分別包含 -11 - 201202120 於懸臂5 0之控制中。 在懸臂50的前端部，係能夠升降地懸吊有用以搬運 貨物的掛鉤60。貨物的裝載或卸載，係藉由通過設置於 旋轉支柱3 0之頂部的滑輪62之組、及設置於懸臂5 0之 前端部的滑輪64之組將鋼索66往上捲繞或往下捲繞而進 行。將藉由主要由掛鉤60、複數個滑輪62、64、鋼索66 構成的吊掛裝置將貨物進行裝載或卸載的動作，稱爲吊掛 (hoist)。 <第1實施形態> [甲板起重機的油壓驅動裝置之內部構成] 其次，針對本發明第1實施形態的甲板起重機的油壓 驅動裝置一邊參照第2圖一邊加以說明。第2圖係顯示第 1實施形態的甲板起重機之油壓驅動裝置100的內部構成 。油壓驅動裝置1〇〇，係具有用以進行吊掛之控制的第1 油壓供給系110、用以進行上下擺動及旋轉之控制的第2 油壓供給系1 50以及控制部250。例如該控制部2 50，亦 可爲序列控制用之作爲電腦的PLC( Programmable Logic Controller:可編程邏輯控制器）。 第1油壓供給系1 1 〇，係包含用以控制吊掛用滾筒 1 3 5的油壓供給管線，該吊掛用滾筒1 3 5係連結於作爲油 壓裝置之一例的吊掛裝置。第1油壓供給系11 〇，係具有 電動馬達1 1 5、吊掛用油壓泵浦1 20、電磁比例流量控制 閥125及油壓馬達130。另外，油壓馬達130，係使油壓 -12- 201202120 裝置動作的油壓致動器之一例。使用第1油壓供給系no 可控制貨物之往上懸吊、往下懸吊動作（吊掛動作）。 吊掛用油壓泵浦1 20及電磁比例流量控制閥1 25，係 按照電位計（.Potentiometer ) 46之檢測値而可.分別改變每 一旋轉的吐出容量與閥體的開啓度。電位計46，係被安 裝於配置在運轉室內之用以進行吊掛操作的手柄42，且 檢測手柄42之旋轉角。該檢測値被送至控制部25 0。控 制部250，係按照電位計46之檢測値而產生相應於手柄 42之旋轉角的電信號。所產生的電信號，係透過電氣管 線傳遞至電磁閥123及吊掛用放大器140，藉此可控制吊 掛用油壓泵浦120之每一旋轉的吐出容量及電磁比例流量 控制閥125的開啓度。吊掛用油壓泵浦120，係連接於電 動馬達115，當電動馬達115動作時，可藉由其動力從吊 掛用油壓泵浦120吐出作動油。 吊掛用油壓泵浦1 2 0，另透過電磁比例流量控制閥 125連結於被配置在油壓供給管線的油壓馬達130，並供 給作動油至油壓馬達1 3 0。藉此，油壓馬達1 3 0會動作， 且藉由其動力使吊掛用滾筒135旋轉。結果，可使吊掛裝 置進行升降。 當電磁比例流量控制閥1 25開啓時，從吊掛用油壓泵 浦1 20吐出的作動油，就會僅以相應於電磁比例流量控制 閥1 25之開啓度的流量供給至油壓馬達丨3 〇，且剩餘的流 量可利用電磁比例流量控制閥1 2 5旁通，而回到作動油槽 (在此未圖示）。吊掛用滾筒1 3 5會藉由依所供給的作動 -13- 201202120 油而被驅動的油壓馬達130來旋轉並開始或繼續進行吊掛 裝置之往上懸吊或往下懸吊動作。當電磁比例流量控制閥 125閉合時，從吊掛用油壓泵浦120吐出的作動油就不會 被供給至油壓馬達1 3 0，而吊掛用滾筒1 3 5之旋轉動作會 停止並停止吊掛裝置之往上懸吊或往下懸吊動作。 另外，吊掛用油壓泵浦120，爲可變容量型油壓泵浦 。在此，可變容量型油壓栗浦，爲可改變作動油之吐出容 量的泵浦，例如，可列舉斜板式可變容量型油壓泵浦作爲 一例。斜板式可變容量型油壓泵浦，係藉由控制對各活塞 提供軸向位移的斜板之傾斜角（稱爲傾轉角）就可連續地 變更壓油的吐出容量。 第2油壓供給系1 5 0，係包含控制連結於懸臂5 0的 上下擺動用滾筒175及連結於旋轉支柱30的旋轉裝置 1 90之與第1油壓供給系1 1 〇不同系統的油壓供給管線。 第2油壓供給系150，係具有電動馬達155、上下擺動/旋 轉用油壓泵浦160、電磁比例流量控制閥165、油壓馬達 1 7 〇、電磁比例流量控制閥1 8 0及油壓馬達1 8 5。使用第2 油壓供給系1 5 0可控制懸臂5 0的俯仰（上下擺動動作） ，並且可控制懸臂50的迴旋（旋轉動作）。 上下擺動/旋轉用油壓泵浦1 6 0，係按照電位計4 8之 檢測値而變更每一旋轉的吐出容量，且電磁比例流量控制 閥1 6 5、1 8 0，係按照電位計4 8之檢測値而可改變閥體的 開啓度。電位計48，係安裝於被配置在運轉室內之用以 進行懸臂操作的手柄44，並檢測手柄44的旋轉角。該檢 -14- 201202120 測値被送至控制部250。控制部250，係按照電位計48之 檢測値而產生相應於手柄44之旋轉角的電信號。所產生 的電信號，係透過電氣管線傳遞至電磁閥163、上下擺動 用放大器195及旋轉用放大器198，藉此可控制上下擺動/ 旋轉用油壓泵浦160之每一旋轉的吐出容量、電磁比例流 量控制閥1 65的開啓度及電磁比例流量控制閥1 80的開啓 度。上下擺動/旋轉用油壓泵浦160，係連接於電動馬達 155，當電動馬達155動作時，可藉由其動力從上下擺動/ 旋轉用油壓栗浦160吐出作動油。 上下擺動/旋轉用油壓泵浦160，另透過電磁比例流量 控制閥165連結於被配置在油壓供給管線的油壓馬達170 ，並供給作動油至油壓馬達1 70。藉此，旋轉用滾筒1 75 會旋轉。結果，可將懸臂5 0設在所期望的傾斜角。上下 擺動/旋轉用油壓泵浦160，另透過電磁比例流量控制閥 180連結於被配置在油壓供給管線的油壓馬達185，並供 給作動油至油壓馬達185。藉此，旋轉裝置190會旋轉達 。結果，可使旋轉支柱30旋轉，且使懸臂50旋轉。 當電磁比例流量控制閥1 65開啓時，從上下擺動/旋 轉用油壓泵浦160吐出的作動油就會供給至油壓馬達170 ，且上下擺動用滾筒175會旋轉並開始或繼續進行上下擺 動動作，且改變懸臂50的傾斜。當電磁比例流量控制閥 165閉合時，從上下擺動/旋轉用油壓泵浦160吐出的作動 油就不會被供給至油壓馬達170，而上下擺動用滾筒175 之旋轉動作會停止並停止上下擺動動作，而可固定懸臂 -15- 201202120 5 0的傾斜位置。 當電磁比例流量控制閥1 80開啓時，從上下擺動/旋 轉用油壓泵浦160吐出的作動油就會供給至油壓馬達185 ，且旋轉裝置1 90會旋轉並開始或繼續進行旋轉動作，且 開始或繼續進行懸臂5 0的迴旋。當電磁比例流量控制閥 180閉合時，從上下擺動/旋轉用油壓泵浦160吐出的作動 油就不會被供給至油壓馬達185，而旋轉裝置190之旋轉 動作會停止並停止旋轉動作。藉此，懸臂50的動作會停 止。另外，上下擺動/旋轉用油壓泵浦160，係與吊掛用油 壓泵浦120同樣爲可變容量型油壓泵浦。 在控制部250，例如內建有未圖示的CPU，且按照運 轉室的手柄操作來控制油壓。又更具體而言，控制部250 ，係按照指示吊掛裝置之往上捲繞、中立、往下捲繞之動 作的手柄42之操作將來自吊掛用油壓泵浦1 20的作動油 之吐出流量控制成最大，並且藉由控制電磁比例流量控制 閥1 2 5之開啓度而控制供給至油壓馬達1 3 0的作動油之流 量。當手柄42之操作未進行一預定時間以上時，便將來 自吊掛用油壓泵浦1 20的作動油之吐出流量控制成最小， 並且藉由控制電磁比例流量控制閥1 25之開啓度而中斷對 油壓馬達130供給作動油。之後，當再次進行手柄42之 操作時，控制部250，就會將來自吊掛用油壓泵浦120的 作動油之吐出流量控制成最大，並且藉由控制電磁比例流 量控制閥1 2 5之開啓度而再次開始對油壓馬達1 3 0供給作 動油。 -16- 201202120 又，控制部250，係按照指示懸臂50之動作的手柄 44之操作將來自上下擺動/旋轉用油壓泵浦160的作動油 之吐出流量控制成最大，並且藉由控制電磁比例流量控制 閥1 6 5及電磁比例流量控制閥1 8 0之開啓度而控制供給至 油壓馬達170及油壓馬達185的作動油之流量。然後，當 手柄44之操作未進行一預定時間以上時，便將來自上下 擺動/旋轉用油壓泵浦160的作動油之吐出流量控制成最 小。之後，當再次進行手柄44之操作時，控制部25 0， 就會將來自上下擺動/旋轉用油壓泵浦160的作動油之吐 出流量控制成最大。 亦即，控制部2 50，係判斷爲了驅動油壓裝置而用的 油壓馬達，該油壓裝置係按照相應於手柄42及手柄44之 操作的電位計46及電位計48之檢測値而動作。然後，在 分別連接於油壓泵浦的油壓馬達在一預定時間以上未動作 的情況下，就會以來自該油壓泵浦的作動油之吐出流量變 成最小的方式控制。 此時，控制部2 50，係藉由控制電磁閥123而變更吊 掛用油壓泵浦120之每一旋轉的吐出容量，並變更來自吊 掛用油壓泵浦1 2 0的作動油之吐出流量。又’同樣地，控 制部250，係藉由控制電磁閥163而變更上下擺動/旋轉用 油壓泵浦160之每一旋轉的吐出容量，並變更來自上下擺 動/旋轉用油壓泵浦160的作動油之吐出流量。 另外，控制部250，係控制吊掛用油壓泵浦1 20及上 下擺動/旋轉用油壓泵浦160的吐出流量，並且控制電磁 -17- 201202120 比例流量控制閥1 25、電磁比例流量控制閥1 65及電磁比 例流量控制閥1 80的開啓度。亦即，供給至油壓馬達1 3 0 、油壓馬達1 70及油壓馬達1 85的作動油之油量，最終可 藉由電磁比例流量控制閥1 2 5、電磁比例流量控制閥1 6 5 及電磁比例流量控制閥1 8 0來調整。例如，當不想使油壓 馬達130動作時，可藉由電磁比例流量控制閥125全部閉 合而停止對油壓馬達1 3 0供給作動油。因此，即使在不想 使油壓馬達1 3 0動作的情況，也沒有必要將來自吊掛用油 壓栗浦120的吐出流量設爲零。 [吐出流量的變更] 在此，針對藉由電磁閥之控制而變更每一旋轉的作動 油之吐出流量的構成之詳細，使用第3圖加以說明。另外 ，在此，雖然針對吊掛用油壓泵浦120之每一旋轉的作動 油之吐出容量之變更舉例加以說明，但是就連上下擺動/ 旋轉用油壓泵浦160的情況也是同樣的。又，作爲可變容 量型的油壓泵浦之種類，雖然主要可列舉斜板形與斜軸形 ，但是以下是以斜板形之可變容量型油壓泵浦爲例加以說 明。 第3圖係顯示可變容量型之吊掛用油壓泵浦120的構 成之一例的說明圖。吊掛用油壓泵浦120，係具有以從外 殼500突出的方式配置的驅動軸5 04，在外殼500內，係 於驅動軸504之周圍具有複數個活塞502。驅動軸504， 係與電動馬達115連接並伴隨電動馬達115之旋轉而旋轉 18- 201202120 。然後，複數個活塞502，係按照驅動軸504之旋轉而旋 轉。此時，活塞502，係藉由旋轉並且藉由被斜板5 06按 壓，而從最內部之容積較寬的活塞5 02-A之狀態至最內部 之容積較寬的活塞502-B之狀態之間進行往復運動。 此時，活塞502，係在從活塞502-A遷移至活塞502-B之狀態的狀態下，會與作動油出口 524連接，且僅以被 斜板506擠出的部分吐出活塞5 02內部的作動油。又，在 從活塞5 02-B遷移至活塞502-A之狀態的狀態下，活塞 5 02，係與作動油入口 522連接，且從作動油入口 522吸 入作動油至活塞502內部。亦即，處於活塞5 02-A之狀態 的活塞502之內部容積、與處於活塞502-B之狀態的活塞 5〇2之內部容積的差異，會成爲每一個活塞5 02之每一旋 轉的作動油之吐出容量。在此，作動油入口 522係與未圖 示的作動油槽連接，而作動油出口 524係透過電磁比例流 量控制閥125來與油壓馬達130連接。 可變容量型之吊掛用油壓泵浦120，係可變更與相對 於驅動軸5〇4的斜板506之角度相應的傾轉角α之大小。 當該傾轉角α爲零時，由於處於活塞502-Α之狀態的活塞 502之內部容積、與處於活塞502-Β之狀態的活塞502之 內部容積的差異會變成零，所以驅動軸5〇4之每一旋轉的 作動油之吐出容量會變成零。 吊掛用油壓泵浦120，係具有：控制油入口 5 26;及 第1調整用活塞508，其係藉由從控制油入口 526注入的 控制油之壓力，朝使斜板5 0 6之傾轉角α減少的方向推出 -19- 201202120 斜板506;以及彈簧510，其係當沒有控制油之壓力時， 朝使斜板506之傾轉角〇：增大的方向對斜板506施加壓力 。藉由控制油之壓力，爲彈簧5 1 0之強度以上，彈簧5 1 0 就會依控制油之壓力而縮緊，且斜板506之傾轉角會減少 。藉此’吊掛用油壓泵浦120的驅動軸504之每一旋轉的 作動油之吐出容量會減少。 例如’在彈簧510之強度爲5kg/cm2的情況下，當將 控制油之壓力設爲lOkg/cm2時，在控制油被注入的狀態 下，第1調整用活塞5 08是一邊推斜板506之一端，一邊 藉由控制油之壓力朝使傾轉角α減少的方向推出，而斜板 之另一端，係朝縮緊彈簧510的方向推出。然後，可調整 傾轉角α直至第2調整用活塞509碰到最小傾轉角調整止 動器5 3 1爲止。又，在控制油未被注入的狀態下，斜板 506可藉由彈簧510之力被推至使傾轉角α增大的方向， 且可調整傾轉角α直至第1調整用活塞508碰到最大傾轉 角調整止動器530爲止》如此，藉由調整彈簧510之強度 、或控制油之壓力暨最大傾轉角調整止動器530及最小傾 轉角調整止動器531之位置，就可控制傾轉角α成爲最小 傾轉角amin及最大傾轉角am ax中之其中一個。另外， 最大傾轉角調整止動器530之位置，係可藉由第1調整螺 桿5 40來調整。又，最小傾轉角調整止動器531之位置， 係可藉由第2調整螺桿541來調整。亦即，第1調整用活 塞508、第2調整用活塞509、斜板506、彈簧510、最小 傾轉角調整止動器531及最大傾轉角調整止動器530，爲 -20- 201202120 藉由控制油之壓力來調整活塞5 02之衝程（stroke)量的 調整部之一例。 另外，控制油入口 526，係透過控制油供給管線而與 電磁閥1 2 3連接。控制部2 5 0，係藉由控制該電磁閥1 2 3 ，而控制有無對吊掛用油壓泵浦1 20供給控制油並控制吊 掛用油壓泵浦120之斜板506的傾轉角α。例如，電磁閥 123，係按照來自控制部25 0的電信號之有無來切換有無 對吊掛用油壓泵浦1 20供給控制油。亦即，控制部250， 係當連接於吊掛用油壓泵浦120的油壓馬達在一預定時間 以上未動作時，會對電磁閥123輸入電信號。然後，按照 該電信號，電磁閥1 23會被切換成：控制油供給管線與吊 掛用油壓泵浦120之控制油入口 526連接，且對吊掛用油 壓泵浦120供給控制油的狀態。又，控制部250，係在連 接於吊掛用油壓泵浦120的油壓馬達再次動作的情況時， 會停止對電磁閥123輸入電信號，而電磁閥123會被切換 成：停止對吊掛用油壓泵浦120之控制油入口 5 26供給控 制油，且控制油入口 526可與油槽連接的狀態。 藉由如此構成，控制部250，係可藉由控制電磁閥 123，來控制吊掛用油壓泵浦120之驅動軸之每一旋轉的 吐出容量。 [控制部的處理] 其次，針對藉由控制本實施形態的油壓驅動裝置1 00 的控制部2 5 0而執行的油壓泵浦控制，一邊參照第4圖所 -21 - 201202120 示的流程圖一邊加以說明》 油壓泵浦控制處理，係當運轉者在運轉室40接通甲 板起重機1 〇之運轉開關時才開始。在步驟S 1 0 5中，控制 部2 50，係判斷連接於吊掛用油壓泵浦的油壓馬達是否在 一預定時間以上未動作。具體而言，可根據是否有用以使 連接於吊掛用油壓泵浦的油壓馬達130動作的手柄操作來 判斷》 在步驟S1 05藉由控制部250判斷出連接於吊掛用油 壓泵浦120的油壓馬達130在一預定時間以上未動作的情 況，就前進至步驟S110，且控制部250會將吊掛用油壓 泵浦120之每一旋轉的作動油之吐出容量控制成最小容量 。藉此，可從吊掛用油壓泵浦1 20吐出最小流量的作動油 。此時，電磁比例流量控制閥1 25會藉由控制部250之控 制而成爲全閉，且不對油壓馬達130供給作動油，而油壓 馬達130之動作停止的結果，會停止貨物之吊掛動作。 另一方面，在步驟S105藉由控制部250判斷出連接 於吊掛用油壓泵浦120的油壓馬達130在一預定時間以內 有動作的情況，就前進至步驟S 1 1 5，且控制部2 50會將 吊掛用油壓泵浦120之每一旋轉的作動油之吐出容量控制 成最大容量。藉此，可從吊掛用油壓泵浦120吐出最大流 量的作動油。此時，可對油壓馬達透過被控制成相 應於手柄42之操作的開啓度之電磁比例流量控制閥1 2 5 來供給作動油，且可藉由從油壓馬達130輸出的動力’來 執行貨物之吊掛動作。 -22- 201202120 然後，在步驟s 1 2 0，控制部2 5 0，係判斷連接於上下 擺動/旋轉用油壓泵浦160的油壓馬達是否在一預定時間 以上未動作。具體而言，可判斷用以使連接於上下擺動/ 旋轉用油壓泵浦的油壓馬達170及油壓馬達185中之至少 一個動作的手柄44之操作是否有在一預定時間以上。 在步驟S 1 20藉由控制部判斷出連接於上下擺動/旋轉 用油壓泵浦160的油壓馬達在一預定時間以上未動作的情 況，亦即，當油壓馬達1 70及油壓馬達1 85兩者均未動作 的時間已持續一預定時間以上時就前進至步驟S 1 25 »然 後，控制部25 0，係將上下擺動/旋轉用油壓泵浦160之每 一旋轉的作動油之吐出容量控制成最小容量。藉此，可從 上下擺動/旋轉用油壓栗浦160吐出最小流量的作動油。 此時，電磁比例流量控制閥1 65及電磁比例流量控制閥 180會藉由控制部25 0之控制而成爲全閉，且不對油壓馬 達170及油壓馬達185供給作動油，而油壓馬達170及油 壓馬達1 8 5之動作停止的結果，會停止懸臂5 0之動作。 另一方面，在步驟S1 20藉由控制部判斷出連接於上 下擺動/旋轉用油壓泵浦1 60的油壓馬達在一預定時間以 內有動作的情況，就前進至步驟S 1 3 0，且控制部2 5 0會 將上下擺動/旋轉用油壓泵浦160之每一旋轉的作動油之 吐出容量控制成最大容量。藉此，可從上下擺動/旋轉用 油壓泵浦160吐出最大流量的作動油。此時，可對油壓馬 達17〇及油壓馬達185，透過被控制成相應於手柄44之 操作的開啓度之電磁比例流量控制閥1 6 5或電磁比例流量 -23- 201202120 控制閥1 8 0而供給作動油，且懸臂5 0會動作。例如，在 手柄44之操作僅爲上下擺動操作的情況時，電磁比例流 量控制閥1 80就會全閉而中斷對連接於旋轉裝置的油壓馬 達1 8 5供給作動油。 其次，在步驟S135中，可判斷運轉者是否已將甲板 起重機10之運轉開關予以斷開。在藉由控制部250判斷 出運轉開關並未被斷開時，控制部250，就會回到步驟 S1 05，且再次判定連接於吊掛用油壓泵浦的油壓馬達是否 在一預定時間以上未動作》 如上所述，步驟S105至步驟S130之處理，係可在步 驟S135反覆至運轉開關被斷開爲止。當運轉者將運轉開 關予以斷開時，本處理就結束。另外，步驟S1 0.5至步驟 S115之處理、及步驟S120至步驟S130之處理，並不一 定要以圖示之順序完成，亦可並行地處理。 依據以上說明的第1實施形態，控制部25 0，係按照 顯示吊掛裝置之動作的手柄42之操作而將來自吊掛用油 壓泵浦120的作動油之每一旋轉的吐出容量控制成最大容 量。此時，在進行手柄42之操作的期間，既可將來自吊 掛用油壓泵浦1 2 0的作動油之吐出流量始終控制成最大， 又能夠可變地控制》藉此，在進行操作的期間，可從吊掛 用油壓泵浦1 2 0吐出大致最大吐出流量的作動油。結果， 油壓馬達130會動作，且可藉由其動力而執行吊掛裝置之 往上捲繞及往下捲繞。 另一方面，控制部250，係當手柄42之操作在一預 -24- 201202120 定時間以上未進行時’便將來自吊掛用油壓泵浦丨2〇的作 動油之吐出流量控制成最小。結果’僅能從吊掛用油壓泵 浦1 20吐出最小吐出容量的作動油，藉此可抑制噪音。又 ’也能降低在最大容量之作動油被吐出時所產生之白白浪 費掉的驅動能源。如前面所述，在進行了懸臂50的手柄 44之操作時也是同樣的。 另外’在第1實施形態中，已針對藉由控制油壓泵浦 之每一旋轉的吐出容量，來控制油壓泵浦之吐出流量的方 法加以說明。如上所述，油壓泵浦之吐出流量，係根據每 一旋轉的吐出容量、與旋轉數而決定。其次，在第2實施 形態中，係針對藉由控制油壓泵浦之旋轉數來控制吐出流 量的方法加以說明。 <第2實施形態> 其次，針對本發明第2實施形態的甲板起重機之油壓 驅動裝置100，一邊參照第5圖一邊加以說明。在本實施 形態的甲板起重機之油壓驅動裝置1 〇〇中，於藉由變頻器 控制電動馬達之旋轉數，來控制油壓栗浦的作動油之吐出 流量此點是與第1實施形態的甲板起重機之油壓驅動裝置 1 〇〇有所不同。因而，以以上的差異點爲中心進行第2實 施形態之說明，且有關與第1實施形態同樣之處的說明則 予以省略。 [甲板起重機的油壓驅動裝置之內部構成] -25- 201202120 第5圖係顯示第2實施形態的甲板起重機之油壓驅動 裝置1 00的內部構成。本實施形態的油壓驅動裝置1 〇〇， 復具備用以控制驅動吊掛用油壓泵浦120的電動馬達115 之旋轉數的吊掛用變頻器2 05、及用以控制驅動上下擺動/ 旋轉用油壓泵浦160的電動馬達155之旋轉數的上下擺動 /旋轉用變頻器2 1 0，以取代不具有第1實施形態的油壓驅 動裝置100爲了控制油壓泵浦之每一旋轉的吐出容量而所 具有的電磁閥123及電磁閥163。 吊掛用變頻器205，係設置在控制部250與電動馬達 1 1 5之間的電氣管線，且與電動馬達1 1 5連接。如前面所 述，電位計46 ’係檢測手柄42之旋轉角。該檢測値被送 至控制部250。控制部250，係按照檢測値產生相應於手 柄42之旋轉角的電信號。所產生的電信號，係從控制部 250輸入至吊掛用放大器140及吊掛用變頻器205。吊掛 用變頻器2 0 5，係按照來自控制部2 5 0之信號而控制電動 馬達115之旋轉數。電動馬達115係提供預定量的動力至 吊掛用油壓泵浦120。藉此，可控制來自吊掛用油壓泵浦 1 2 0的作動油之吐出流量。 上下擺動/旋轉用變頻器210，係設置在控制部250與 電動馬達155之間的電氣管線，且與電動馬達155連接。 如前面所述，電位計4 8，係檢測手柄44之旋轉角。該檢 測値被送至控制部2 5 0。控制部2 50，係按照檢測値產生 相應於手柄44之旋轉角的電信號。所產生的電信號，係 從控制部250輸入至上下擺動/旋轉用放大器198及上下 -26- 201202120 擺動/旋轉用變頻器210。上下擺動/旋轉用變頻器210, 係按照來自控制部250之信號而控制電動馬達1 55之旋轉 數。電動馬達155係提供預定量的動力至上下擺動/旋轉 用油壓栗浦Ϊ60。藉此，可控_制來自上下擺"動/旋轉用油壓 泵浦160的作動油之吐出流量。 [控制部的處理] 其次，針對藉由控制本實施形態的油壓驅動裝置1 〇〇 的控制部250而執行的油壓泵浦控制處理，一邊參照第6 圖所示的流程圖一邊加以說明。 另外，第2實施形態的油壓泵浦控制處理，與第1實 施形態的油壓泵浦控制處理相較，其差異點在於：步驟 S210、步驟 S215、步驟S225、步驟 S230中的控制，並 非爲每一旋轉的吐出容量，而是旋轉數。又，在油壓馬達 在一預定時間以內有動作的情況時，電動馬達之旋轉數’ 係藉由控制部250，控制成相應於電位計之檢測値的値。 如上所述，油壓泵浦的吐出流量，係可由平均移旋轉 的吐出容量與旋轉數來表示。在本實施形態中，係藉由控 制該旋轉數，來控制油壓泵浦的吐出流量。亦即，藉由吊 掛用變頻器205來控制電動馬達115之旋轉數，且控制藉 由電動馬達115而被驅動的吊掛用油壓泵浦120之旋轉數 。另外，有關上下擺動/旋轉用油壓泵浦也是同樣的。 依據以上說明的第2實施形態，藉由按照油壓馬達之 動作有無來控制用以驅動油壓泵浦的電動馬達之旋轉數’ -27- 201202120 且將來自油壓泵浦的吐出流量設爲可變，就可與第1實施 形態同樣地謀求噪音之降低。此外，依據第2實施形態， 由於可藉由變頻器來控制電動馬達之輸出，所以可抑制消 耗電力。 如上所述，在第1實施形態中，已針對控制電磁閥並 藉由對油壓泵浦供給控制油之有無來變更油壓泵浦之每一 旋轉的作動油之吐出容量，以控制油壓泵浦之吐出容量的 方法加以說明；而在第2實施形態中，已針對藉由變頻器 控制來控制用以驅動油壓泵浦的電動馬達之旋轉數，藉此 控制油壓泵浦之旋轉數並控制油壓泵浦的作動油之吐出流 量的方法加以說明。 該2個方法，均可組合使用。因此，在第3實施形態 中，係針對控制每一旋轉的吐出容量與旋轉數之雙方的方 法加以說明。 <第3實施形態〉 [甲板起重機的油壓驅動裝置之內部構成] 第7圖係顯示第3實施形態的甲板起重機之油壓驅動 裝置100的內部構成。本實施形態的油壓驅動裝置100, 係除了第1實施形態的油壓驅動裝置1 〇〇之構成以外，還 具有已在第2實施形態說明過的吊掛用變頻器2 05及上下 擺動/旋轉用變頻器210。有關各自的構成要素之功能，由 於是與第1實施形態或第2實施形態的油壓驅動裝置1 00 相同，所以在此省略說明。 •28- 201202120 [控制部的處理] 其次’針對藉由控制本實施形態的油壓驅動裝置丨0 0 的控制部250而執行的油壓泵浦控制處理，—邊參照第8 圖所不的流程圖一邊加以說明。 另外’在本實施形態中，基本的動作是與第1實施形 態或第2實施形態相同，而差異點在於每一旋轉的吐出容 量之控制與旋轉數之控制是被組合進行，作爲在基於步驟 S30 5及步驟S3 30之判斷的各情況下完成的處理。但是， 有關各處理的內容，由於是與第1或第2實施形態相同， 所以在此省略說明。 如上所述，在第1至第3實施形態中，已針對吊掛用 油壓泵浦120與上下擺動/旋轉用油壓泵浦160可分別藉 由不同的電動馬達來驅動的情況加以說明。但是，也有吊 掛用油壓泵浦120與上下擺動/旋轉用油壓泵浦160可藉 由相同的電動馬達來驅動作爲單軸雙連式泵浦者。在如此 的油壓驅動裝置中，係針對本發明之適用油壓泵浦的吐出 流量之控制的情況，當作第4及第5實施形態說明如下。 <第4實施形態> [甲板起重機的油壓驅動裝置之內部構成] 第9圖係顯示第4實施形態的甲板起重機之油壓驅動 裝置100的內部構成。油壓驅動裝置1〇〇’與第3實施形 態相較，差異點在於：吊掛用油壓泵浦、與上下擺動/旋 -29- 201202120 轉用油壓泵浦可藉由相同的電動馬達105來驅動。該電動 馬達1 05之旋轉數，係可藉由吊掛/上下擺動/旋轉兼用的 變頻器200來控制。 亦即，吊掛用油壓泵浦120與上下擺動/旋轉用油壓 泵浦160可相互地連結其驅動軸，且按照依電動馬達105 之旋轉而旋轉的吊掛用油壓泵浦120之驅動軸的旋轉，使 上下擺動/旋轉用油壓泵浦160之驅動軸旋轉。 藉由如此構成的差異，第4實施形態的油壓驅動裝置 100，最大的差異點在於：電動馬達105之旋轉數，是設 爲吊掛用油壓泵浦120所需的旋轉數、與上下擺動/旋轉 用油壓泵浦160所需的旋轉數中之最大旋轉數。換句話說 ，即使是在並未進行上下擺動/旋轉操作時，在吊掛操作 被進行的情況，由於有必要使吊掛用油壓泵浦1 20驅動， 所以未被使用的上下擺動/旋轉用油壓泵浦也會成爲相同 的旋轉數。 [控制部的處理] 其次，針對藉由控制本實施形態的油壓驅動裝置1 〇〇 的控制部250而執行的油壓泵浦控制處理，一邊參照第 1 0圖所示的流程圖一邊加以說明。 首先，在步驟S405中，控制部2 5 0，係判斷全部的 油壓馬達是否在一預定時間以上未動作。如上所述，本實 施形態的油壓驅動裝置1 〇〇，係有必要以連接於電動馬達 105的油壓泵浦各自所需的旋轉數之中提供最大的旋轉數 -30- 201202120 之方式來驅動。亦即，只有在連接於電動馬達105的油壓 泵浦所驅動的油壓馬達之全部並未動作的情況時才能將旋 轉數設爲最小値。 因此，首先在步驟S405中，控制部250，係根據與 手柄42及手柄44之操作相應的電位計之檢測値來判斷全 部的油壓馬達是否在預定時間並未動作。然後，在藉由連 接於電動馬達105的油壓泵浦而被驅動的油壓馬達之全部 均在一預定時間以上未動作的情況時，就會前進至步驟 S410，而控制部25 0會藉由變頻器將電動馬達之旋轉數控 制成最小値。 另一方面，在步驟S405中，在藉由控制部250，判 斷出其中一個油壓馬達在一預定時間以內有動作的情況時 ，控制部250，會藉由變頻器將電動馬達之旋轉數控制成 相應於電位計之檢測値的値。 以下，有關步驟S420至步驟S445之處理，由於與例 如第4圖的步驟S105至步驟S135之處理相同所以省略說 明。 如以上說明，本發明第4實施形態的油壓驅動裝置， 係可藉由相同的電動馬達105來驅動吊掛用油壓泵浦120 與上下擺動/旋轉用油壓泵浦160作爲單軸雙連式泵浦。 因此’僅在變頻器控制中，僅有在全部的油壓馬達未動作 的情況時才能降低旋轉數而限制油壓泵浦的吐出流量。因 此’藉由一倂具有在第1實施形態中已說明之使用電磁閥 來控制油壓泵浦之每一旋轉的吐出容量之構成，則在吊掛 -31 - 201202120 或上下擺動/旋轉中之任一個處於並未動作 ，就可藉由每一旋轉的吐出容量之控制，來 吐出流量，且可降低噪音。更且，在全部的 動作的情況時，除了每一旋轉的吐出容量之 可藉由控制旋轉數，進而抑制作動油之吐出 消耗電力。 又，在單軸雙連式泵浦之構成中，亦可 ，而僅控制每一旋轉的吐出容量之構成。有 將當作第5實施形態並說明如下。 <第5實施形態> [甲板起重機的油壓驅動裝置之內部構成] 第1 1圖係顯示第5實施形態的甲板起 動裝置100的內部構成。油壓驅動裝置100 形態比較，差異點在於不具有控制電動馬達 的變頻器。 [控制部的處理] 有關第5實施形態的油壓泵浦控制處理 在第4圖中說明的第1實施形態相同，所以 〇 另外，雖未圖示，但是即使在單軸雙連 中，並不具有控制每一旋轉的作動油之吐出 亦可藉由變頻器控制來僅控制旋轉數。但是 的空轉狀態時 減少作動油之 油壓馬達並未 控制以外，還 流量，且降低 不使用變頻器 關如此的構成 重機之油壓驅 ，與第4實施 1 05之旋轉數 ，由於是與已 在此省略說明 式泵浦之構成 容量的構成， ，如上所述， -32- 201202120 僅在藉由變頻器控制進行旋轉數之控制的情況下，僅有在 全部的油壓馬達未動作時才可降低作動油之吐出流量，且 其噪音降低效果低。因此，在單軸雙連式泵浦之構成中使 用變頻器控制時，配合進行每一旋轉的吐出容量之控制是 極爲有效的。 在上述第1至第5實施形態中，各部的動作係相互地 關聯，且可一邊考慮相互的關聯，一邊置換作爲一系列的 動作。藉此，可將甲板起重機的油壓驅動裝置之實施形態 ，當作甲板起重機的油壓驅動方法之實施形態。 <風扇的旋轉數控制> [槪要] 如以上說明般，在電動油壓式的起重機中，係藉由電 動馬達之動力來驅動油壓泵浦，且藉由從油壓泵浦吐出的 作動油來驅動油壓致動器，然後藉由其動力驅動油壓裝置 。此時，上述第1至第5實施形態之甲板起重機的油壓驅 動裝置，係使用電磁閥將油壓泵浦之每一旋轉的吐出容量 控制成大致最小、或藉由變頻器將驅動油壓泵浦的電動馬 達之旋轉數控制成大致最小，藉此控制從油壓泵浦吐出的 作動油之吐出流量。 在第2圖、第5圖、第7圖、第9圖及第11圖中’ 雖然爲了簡化而未圖示，但是作動油’係可從貯藏作動油 的油槽供給至油壓泵浦，並且從油壓泵浦吐出的作動油可 回收至油槽。被回收後的作動油’係反覆供給至油壓泵浦 -33- 201202120 ，且在甲板起重機之內部循環。從油 係透過油壓馬達等的致動器，進行往 捲繞/往下捲繞、上下擺動裝置中的n 裝置中的右迴旋/左迴旋等的工作。】 被拉伸的動作、往上捲繞裝置中的往 置中的往下、及迴旋裝置中的往下動 負載一邊安全地下降的機構。在油壓 配衡（counter balance)閥等，且藉 效應調節作動油進行該工作並吸收所 工作結果全部會被當作能量由作動油 壓泵浦而施加壓力的作動油，係可藉 的管之內壁的摩擦（配管阻抗）等而 重機的油壓驅動裝置1〇〇，係具有用 將被加熱過的作動油進行冷卻的構成 述，但是作爲作動油冷卻用的構成之 的熱交換器。 依據上述第1至第5實施形態的 如上所述，可在甲板起重機之空轉狀 出的作動油之吐出流量控制成大致最 ，當例如作動油之吐出流量已控制成 某程度時，與始終以最大吐出流量吐 ，作動油的溫度上升會較低。然而， 熱交換器之送風機，係藉由電動馬達 動。該情況下，有可能不必要地進行 壓泵浦吐出的作動油 上捲繞裝置中的往上 臂往上/往下、迴旋 比時，在藉由負載而 下捲繞、上下擺動裝 作中，需要一邊保持 系統中，一般是使用 由以孔口（orifice) 需要的能量。此等的 所吸收。又，藉由油 由與作動油供給管線 加熱。因此，甲板起 以在回到油槽之前， 。雖然其詳細將於後 代表，有使用氣冷式 油壓驅動裝置100， 態下將從油壓泵浦吐 小。在如此的構成中 大致最小的狀態持續 出作動油的情況相較 將空氣送入氣冷式的 以固定的旋轉數被驅 作動油的冷卻。又， -34- 201202120 在藉由作動油的吐出流量之減少來使噪音降低化的上述第 1至第5實施形態的油壓驅動裝置100中，有時冷卻用風 扇的聲音會被感覺是噪音。因此，以下針對藉由控制用以 驅動該冷卻風扇的電動馬達之旋轉數而使噪音降低化的方 法，一邊參照第12圖至第14圖一邊說明其詳細。 [構成] 第12圖係槪略地顯示油壓驅動裝置100的油壓供給 系構成之一例的說明圖。第13圖係槪略地顯示油壓驅動 裝置100的油壓供給系構成之另一例的說明圖。第14圖 係顯示油壓驅動裝置1 〇〇的作動油冷卻風扇之控制處理流 程之一例的流程圖。 首先，當參照第12圖時，槪略地顯示單軸雙連式泵 浦之構成中的油壓系統。如上所述，油壓驅動裝置100, 係具有油槽350，且從油槽350對吊掛用油壓泵浦120及 上下擺動/旋轉用油壓泵浦1 60供給作動油。供給至吊掛 用油壓泵浦120的作動油，係藉由吊掛用油壓泵浦120施 加壓力而被吐出。然後，被吐出的作動油，係透過電磁比 例流量控制閥1 25，供給至驅動吊掛用滾筒1 3 5的油壓馬 達130。藉由油壓馬達130進行工作後的作動油、與藉由 電磁比例流量控制閥1 2 5進行流量控制而未供給至油壓馬 達1 3 0的作動油，係通過作動油回收管線1 1 3，且透過散 熱器（radiator) 330及濾油器（oil filter) 340回收至油 槽 3 5 0。 -35- 201202120 另一方面，供給至上下擺動/旋轉用油壓泵浦160的 作動油，係藉由上下擺動/旋轉用油壓泵浦1 60施加壓力 而被吐出。然後，被吐出的作動油，係透過電磁比例流量 控制閥1 65及電磁比例流量控制閥1 80，供給至驅動上下 擺動用滾筒175的油壓馬達170及驅動旋轉裝置190的油 壓馬達185。在油壓馬達170及油壓馬達185中進行工作 後的作動油、與藉由電磁比例流量控制閥1 65及電磁比例 流量控制閥1 80進行流量控制而未供給至油壓馬達1 70及 油壓馬達1 85的作動油，係通過作動油回收管線1 53，且 透過散熱器330及濾油器340回收至油槽350。 風扇320，係對空氣等的氣體施加壓力而送出的送風 機之一種。風扇3 20，係具有對後述的散熱器330，送出 供熱交換用的空氣之功能。 散熱器3 3 0,也被稱爲放熱器的熱交換器之一種。散 熱器330，係例如氣冷式的熱交換器，且具有：當從藉由 電動馬達3 05而被驅動的風扇3 20送出施加有壓力的空氣 時，使作動油之熱移動至從風扇320供給來的空氣之功能 。因此，經由散熱器3 3 0後的作動油，係使本身具有的熱 透過作爲油路的管而移動至空氣中，藉此可降低作動油的 溫度。該散熱器330，係設置在從各油壓泵浦吐出的作動 油被回收至油槽的路徑上。更詳言之，較佳是被設置在： 通過散熱器330後的作動油之後不會被用於工作的位置。 又，濾油器340，係用以清除混入於作動油之混入物的過 濾器。 -36- 201202120 然後，在本實施形態中，油壓驅動裝 控制電動馬達305之旋轉數的風扇用變頻 馬達3 05係用以驅動冷卻用風扇320。 3〇〇，係按照控制部250之指示控制電動J 數。電動馬達3 05之旋轉數、即風扇320 音就越大，風扇320之旋轉數越低噪音就 ，在作動油之吐出流量以成爲適當的方式 1至第5實施形態的油壓驅動裝置1 00中 作動油是否被用於工作，當與始終吐出最 動油的油壓驅動裝置相較時，於空轉狀態 度上升就會特別低。因此，藉由按照作動 適切地控制風扇3 20之旋轉數，就可降低 源消耗與無益的噪音。另外，有關該控制 1 4圖並說明如後。 另外，與以上說明的油壓裝置之驅動 有透過電磁閥123及電磁閥163而供給至 120與上下擺動/旋轉用油壓泵浦160的控 。該控制油，例如既可從與作動油相同的 亦可從不同的油槽供給。雖然在第1 2圖 設置有：透過電磁閥123及電磁閥163而 壓泵浦120與上下擺動/旋轉用油壓泵浦 會再次回收至油槽35〇用的回收管線。 當參照第13圖時，槪略地顯示雙泵 油壓驅動裝置1 〇〇中的油壓系統。該情況 置100，係具有 器300，該電動 該風扇用變頻器 馬達305之旋轉 之旋轉數越高噪 越小。如上所述 來控制的上述第 ，無論被吐出的 大吐出流量之作 下的作動油之溫 油之溫度上升而 白白浪費掉的能 方法，係使用第 系統不同，存在 吊掛用油壓泵浦 制油之供給管線 油槽3 5 0供給， 中未圖示，但是 供給至吊掛用油 1 6 0的控制油也 浦雙電動機型之 也是由於各構成 -37- 201202120 要素之功能與第1 2圖之例相同所以省略詳細 外，使用第1 2圖針對以下之形態加以說明： 連式泵浦之構成的油壓驅動裝置，且爲控制變 油壓泵浦之旋轉數控制與電磁閥所爲的油壓泵 轉的吐出量之雙方的構成中，加上控制用以驅 的馬達之旋轉數的構成之形態；且使用第13 之形態加以說明：即在雙泵浦雙電動機型之構 動裝置，且爲控制變頻器所爲的油壓泵浦之旋 電磁閥所爲的油壓泵浦之每一旋轉的吐出量之 中，加上控制用以驅動冷卻風扇的馬達之旋轉 形態。但是，本發明並非被限定於如此構成。 在僅具有變頻器所爲的油壓泵浦之旋轉數控制 爲的油壓泵浦之每一旋轉的吐出量控制中之任 油壓驅動裝置中，加上控制用以驅動冷卻風扇 之旋轉數的構成。亦即，在此說明之控制用以 扇的電動馬達之旋轉數的構成，係可適用於上 第5實施形態的油壓驅動裝置1 00中之任一個 [控制處理] 當參照第1 4圖時，顯示驅動冷卻用風扇 馬達3 05之旋轉數的控制處理。另外，雖然在 第13圖中並未圖示，但是油壓驅動裝置1〇〇 測作動油之溫度的溫度計測部。使用該溫度計 結果，控制部2 5 0，係判斷作動油溫度是否爲 的說明。另 即在單軸雙 頻器所爲的 浦之每一旋 動冷卻風扇 圖針對以下 成的油壓驅 轉數控制與 雙方的構成 數的構成之 例如，亦可 與電磁閥所 一種構成的 的電動馬達 驅動冷卻風 述之第1至 3 20的電動 第12圖及 ，係具有計 測部的計測 40°C以上（ -38- 201202120 S505 )。在作動油溫度爲40°C以上時，爲了要驅動冷卻 用風扇320，電動馬達305會開始旋轉。然後，控制部 250，係將驅動風扇320的馬達305之旋轉數控制成與作 動油溫度或手柄42及手柄44之傾倒角度成正比的旋轉數 (S 5 1 0 )。例如，在與作動油之溫度成正比而控制電動馬 達3 05之旋轉數時，就以作動油溫度爲40 °C，電動馬達 305之旋轉數會從600RPM開始旋轉，而作動油溫度爲 7〇°C，電動馬達3 05之旋轉數會到達最大旋轉數1 800RPM ，成爲與作動油溫度成正比的旋轉數，藉此控制部250可 藉由風扇用變頻器300來控制電動馬達305之旋轉數。另 —方面，在與手柄傾倒角度成正比而控制電動馬達3 05之 旋轉數時，控制部25 0，係按照由電位計46檢測出的手 柄42之操作角及由電位計48檢測出的手柄44之操作角 而控制電動馬達3 05之旋轉數。 又，雖然步驟S 5 1 0之控制係持續地進行，但是控制 部250會與此並行，判斷作動油溫度是否爲40 °C以下（ S515)。該判斷，爲驅動風扇的電動馬達305之停止條件 的判斷。然後，藉由步驟S515之判斷在作動油溫度爲 40°C以上時，控制部250 ’就會判斷在一預定時間以上之 期間，是否沒有手柄操作（S 5 20)。步驟S520之判斷， 係可根據電位計4 6及電位計4 8之檢測値來判斷。然後， 在一預定時間以內被檢測出有某個手柄操作時，會再次持 續步驟S 5 1 0之控制。另一方面，在被檢測出預定時間以 上沒有手柄操作時，會將風扇驅動用的電動馬達305之旋 -39- 201202120 轉數控制成最小旋轉數（S 52 5 )。步驟S 52 5之控制，係 持續至手柄操作被檢測出爲止。 另外，在步驟S 5 05之判斷中，在被判斷出作動油溫 度並非爲40 °C以上時，可判斷出下次運轉開關是否被甲板 起重機之運轉者斷開（S 5 3 5 )。在運轉開關被斷開時，本 控制處理就結束。另一方面，在運轉開關未被斷開時，就 會持續以上說明的控制並重複動作。 如以上所述，雖然一邊參照附圖一邊針對本發明的較 佳實施形態詳細地說明，但是本發明並未被限定於如此例 子。只要是本發明所屬技術領域中具有通常知識者，可明 白在申請專利範圍所述的技術思想之範圍內，皆能思及各 種的變更例或修正例，有關此等也當然可了解是屬於本發 明之技術範圍。 例如，在上述第1至第5實施形態中，雖然已就使用 油壓馬達作爲使油壓裝置動作的油壓致動器之甲板起重機 加以說明，但是本發明並未被限定於如此例子。例如，亦 可爲使用油壓氣缸的甲板起重機來取代油壓馬達。 例如，在第1及第2實施形態中，當手柄操作進行一 預定時間以上時，控制部2 5 0，就會將來自油壓泵浦的作 動油之吐出容量控制成最小。然而，本發明並未被限於此 ，亦可當手柄操作進行一預定時間以上時，將來自油壓泵 浦的作動油之吐出容量控制得比之前的作動油之吐出容量 還少。 又，在第1至第5實施形態中，當手柄操作已進行時 -40- 201202120 ，控制部2 5 0，會將來自油壓泵浦的作動油之吐出容量控 制成最大。然而’本發明並未被限於此’亦可當手柄操作 已進行時，將來自油壓泵浦的作動油之吐出容量控制得比 之前的作動油之吐出容量還多。 又，第1至第5實施形態的油壓驅動裝置100，雖然 具有第1油壓供給系1 1 0及第2油壓供給系1 5 0，但是本 發明並未被限於此。本發明的油壓驅動裝置100，只要具 有第1油壓供給系110及第2油壓供給系150中之至少一 個即可。又，在第1及第2實施形態的油壓驅動裝置1〇〇 中，雖然上下擺動動作與旋轉動作，係利用同一系統的第 2油壓供給系1 50來統一處理，但是本發明並未被限定於 此，亦可利用不同系統的油壓管線來個別地處理上下擺動 動作與旋轉動作。 本發明的油壓驅動裝置100，較佳爲適用於船舶。本 發明的油壓驅動裝置1〇〇，係可配設I個或複數個於船舶 之甲板。 又，在上述實施形態中，雖然是以被用於船舶的甲板 起重機爲例加以說明，但是本發明並未被限定於如此例子 。並不限於甲板起重機，還可適用於路上使用的起重機裝 置。又，本發明並未被限定於對起重機裝置之適用，還可 在電動油壓式的油壓裝置中，廣泛適用作爲油壓泵浦的控 制裝置。 【圖式簡單說明】 •41 - 201202120 第1圖係本發明之第1至第5實施形態的甲扳起重機 之全體構成圖。 第2圖係第1實施形態的甲板起重機之油壓驅動裝置 的內部構成圖。 第3圖係第1至第5實施形態的可變容量型油壓泵浦 之內部構成圖。 第4圖係顯示第1至第5實施形態的油壓泵浦控制處 理之流程圖。 第5圖係第2實施形態的甲板起重機之油壓驅動裝置 的內部構成圖。 第6圖係顯示第2實施形態的油壓泵浦控制處理之流 程圖。 第7圖係第3實施形態的甲板起重機之油壓驅動裝置 的內部構成圖。 第8圖係顯示第3實施形態的油壓泵浦控制處理之流 程圖。 第9圖係第4實施形態的甲板起重機之油壓驅動裝置 的內部構成圖。 第1 〇圖係顯示第4實施形態的油壓泵浦控制處理之 流程圖。 第π圖係第5實施形態的甲板起重機之油壓驅動裝 置的內部構成圖。 第12圖係顯示單軸雙連式泵浦型油壓驅動裝置的油 壓供給系統之一例的說明圖。 -42- 201202120 第13圖係顯示2泵浦2電動機型油壓驅動裝置的油 壓供給系統之一例的說明圖。 第14圖係顯示驅動冷卻用風扇的電動馬達之旋轉數 的控制動作之流程圖。 【主要元件符號說明】 10 :甲板起重機 20 :下部支柱 3 〇 :旋轉支柱 40 :運轉室 42、44 :手柄（操作部） 4 6、4 8 :電位計 5 0 :懸臂 52 :懸臂支撐部 6 0 :掛鉤 6 2、6 4 :滑輪 66 :鋼索 1 0 〇 :油壓驅動裝置 1 1 〇 :第1油壓供給系 105、 115、 155:電動馬達 1 2 0 :吊掛用油壓泵浦 123、163 :電磁閥（螺線管閥） 1 2 5、1 6 5、1 8 0 :電磁比例流量控制閥 130、 170、 185:油壓馬達 -43- 201202120 1 3 5 :吊掛用捲筒 140 :吊掛用放大器 1 5 0 :第2油壓供給系 160:上下擺動/旋轉用油壓泵浦 175:上下擺動用捲筒 190 :旋轉裝置 195:上下擺動用放大器 198 :旋轉用放大器 2 00 :變頻器（吊掛、上下擺動、旋轉兼用） 205 :吊掛用變頻器 210:上下擺動/旋轉用變頻器 2 5 0 :控制部 3 00 :風扇用變頻器 3 05 :電動馬達 320 :風扇 3 3 0 :散熱器（熱交換器） 3 4 0 :濾油器 3 5 0 :油槽 500 :外殼 502 :活塞 5 0 4 :驅動軸 5 0 6 :斜板 5 0 8 :第1調整用活塞 5 09 :第2調整用活塞 • 44- 201202120 5 1 0 :彈簧 522 :作動油入口 524 :作動油出口 526 :控制油入口 530:最大傾轉角調整止動器 5 3 1 __最小傾轉角調整止動器 540 :第1調整螺桿 541 :第2調整螺桿 -45 -201202120 VI. Description of the Invention: TECHNICAL FIELD The present invention relates to a hydraulic drive device for a deck crane, a crane device, a hydraulic pump control device, and a ship. [Prior Art] Deck cranes are installed on the deck of a cargo ship and used for loading or unloading of cargo transported to the sea. The goods are involved in many aspects from bulk cargoes such as groceries, grains, coal, etc. to containers and are transported through the world's ports. Therefore, deck cranes are an indispensable loading and unloading machine for handling cargo at sea. Among the driving methods of the deck crane, an electric hydraulic type is generally cited. This is driven by the power of the electric motor to drive the hydraulic pump mounted on the deck crane, and the hydraulic actuator is driven by the hydraulic oil discharged from the hydraulic pump, thereby driving the oil pressure by its power. The method of the device. The discharge flow rate Q (l/min) of the hydraulic oil from the hydraulic pump is set to q (cc/rev) when the hydraulic oil is pumped, and the hydraulic pressure is pumped. When the number of rotations is N (rpm) and the volumetric efficiency of the hydraulic pumping is 卩pv, it can be expressed by the following formula. [Expression 1] Q = qXNX77pv / l 000 Here, as the type of the hydraulic pump, a fixed capacity type and a variable capacity type are exemplified. The fixed-capacity hydraulic pump has a constant discharge capacity q for each rotating hydraulic oil. Therefore, even if the hydraulic unit is idling (-5-201202120 idling), the fixed-capacity hydraulic pump will discharge the same amount of oil as the drive. Further, the variable displacement type hydraulic pumping can change the discharge capacity q of each rotating working oil. However, the control method of the variable-capacity hydraulic pump can generally be controlled by a fixed horsepower', and when the light load is applied or the hydraulic device is in the idling state, the discharge capacity q of each rotating hydraulic oil becomes maximum. Spit the capacity. Further, although the number N of rotations of the hydraulic pump is 値 corresponding to the number of rotations of the electric motor, since the number of rotations of the electric motor is fixed, even when the hydraulic device is idling, it is still driven. Rotate with the same number of rotations. (Patent Document 1) JP-A-2007-137641 SUMMARY OF INVENTION (Problems to be Solved by the Invention) As described above, the hydraulic pump for driving the hydraulic device of the prior art is in the idling state of the hydraulic device. The supply of the hydraulic oil to the hydraulic actuator is irrelevant, and the maximum flow of the operating oil is spit out. Therefore, there is a problem that the generated driving energy and the loud noise are wasted. When the hydraulic oil is supplied to the hydraulic actuator, if the discharge flow rate of the hydraulic oil from the hydraulic pump is increased, the noise caused by the driving of the hydraulic pump and the generated oil when the operating oil is supplied through the hydraulic oil supply line are generated. The noise, as well as the wasted energy, will become bigger. Therefore, the present invention has been developed in view of the above problems, and an object of the present invention is to provide a novel energy source capable of reducing noise generation and being wasted in the idling state of the hydraulic device. A hydraulic drive unit for a modified deck crane. Means for Solving the Problems In order to solve the above problems, according to an aspect of the present invention, a hydraulic drive device for a deck crane having: an oil pressure actuator that operates an oil pressure device; and a hydraulic pressure can be provided. Pumping the hydraulic oil to the hydraulic actuator through a hydraulic oil supply line; and a control unit that controls the supply to the hydraulic actuator in accordance with an operation indicating the operation of the hydraulic device The flow rate of the operating oil is controlled, and when the hydraulic actuator connected to the hydraulic pump is not operated for a predetermined time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump is controlled to be substantially minimum. According to such a configuration, the discharge flow rate of the hydraulic oil from the hydraulic pump can be controlled in accordance with the operation of instructing the operation of the hydraulic device. At this time, when the hydraulic actuator connected to the hydraulic pump is in an idling state in which the hydraulic pump is not operated for a predetermined period of time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump is set to be substantially minimum. Therefore, the operating oil which has been the maximum discharge flow rate in the idling state in the prior art can be set at the minimum discharge flow rate. Therefore, in the idling state in which the hydraulic device is not operated, the noise generated by the action of the oil as it passes through the operating oil line and the driving energy that is wasted is reduced. Further, an electric motor may be further provided that drives the hydraulic pump and the inverter to control the number of rotations of the electric motor, and the control unit sets the number of rotations of the electric motor by the inverter. At the minimum, the number of rotations of the hydraulic pump is set to a minimum, and the discharge rate of the above-mentioned spout 201202120 is controlled to be substantially minimum. Further, the hydraulic pump may be a variable displacement hydraulic pump, and the control unit may set a discharge capacity of each of the rotating hydraulic oils of the hydraulic pump to a minimum. The hydraulic drive device may include a plurality of hydraulic pressure supply systems in which the hydraulic actuator, the actuating oil supply line, and the hydraulic pump are disposed, and the plurality of the above-mentioned discharge flow rates are controlled to be substantially minimum. The hydraulic pump is driven by being coupled to one of the electric motors, and the control unit is configured to connect the hydraulic actuators of the plurality of hydraulic pumps to the hydraulic pump for a predetermined time. The discharge capacity of each of the above-described rotary oils of the above-described unoperated hydraulic pump is controlled to be substantially minimum. Further, a solenoid valve may be further provided, which is connected to the hydraulic pump through a control oil supply line, and switches whether or not the hydraulic pump is supplied with the control oil, and the hydraulic pump may be as described above. The control unit controls the discharge valve to control the discharge capacity of each of the rotating hydraulic oils by controlling the presence or absence of the control oil, and the control unit controls the discharge valve to substantially reduce the discharge flow rate. Further, the hydraulic pump may have a piston that discharges the operating oil corresponding to the stroke amount, and an adjustment unit that adjusts the stroke amount of the piston by the hydraulic pressure of the control oil. The actuating oil may be supplied to the hydraulic pump from an oil sump storing the actuating oil, and the actuating oil discharged from the hydraulic pump may be recovered to the oil sump, the hydraulic drive device having: a blower -8-201202120 is the air after the pressure is applied; and the heat exchanger is disposed on the path of the hydraulic oil discharged from the hydraulic pump to the oil tank, and is pumped from the hydraulic pump The heat of the discharged working oil moves toward the air sent by the blower, and the second inverter controls the number of rotations of the second electric motor for driving the blower, and the control unit is for a predetermined time or longer During the period of time, when it is detected that there is no operation for instructing the operation of the hydraulic device, the rotation of the second electric motor is substantially minimized by the second inverter. Further, the control unit may detect that During the period in which the operation of instructing the operation of the hydraulic device is performed within the predetermined period, the number of rotations of the second motor is controlled by the second inverter. The temperature of the oil from the pump discharge pressure chestnut oil actuation of proportional, proportional to the number of revolutions performed or an operation of indicating an operation of the oil pressure of the operation means of the inclined portion. Further, in order to solve the above problems, according to another aspect of the present invention, a crane apparatus having: a hydraulic actuator that operates an oil pressure device; and a hydraulic pump that transmits oil a supply line supplies the operating oil to the hydraulic actuator; and a control unit that controls the flow of the operating oil supplied to the hydraulic actuator in accordance with an operation instructing the operation of the hydraulic device, and When the hydraulic actuator connected to the hydraulic pump is not operated for a predetermined time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump is controlled to be substantially minimum. Moreover, in order to solve the above problems, according to another aspect of the present invention, a hydraulic pump control device for supplying hydraulic oil to a hydraulic actuator for operating a hydraulic device may be provided, comprising: a control unit And controlling the flow of the hydraulic oil supplied to the hydraulic actuator according to the operation of the above-mentioned hydraulic device of the instruction -9-201202120, and when the above-mentioned oil pressure is connected to the hydraulic pump When the actuator is not operated for a predetermined period of time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump is controlled to be substantially minimum. Moreover, in order to solve the above problems, according to another aspect of the present invention, a ship including one or more crane devices having a hydraulic actuator that is hydraulically pressurized may be provided. The device operates; and the hydraulic pump supplies the hydraulic oil to the hydraulic actuator through the operating oil supply line; and the control unit controls the supply to the operation according to the operation indicating the operation of the hydraulic device a flow rate of the hydraulic oil of the hydraulic actuator, and when the hydraulic actuator connected to the hydraulic pump is not operated for a predetermined time or longer, the hydraulic oil from the hydraulic pump is discharged. The flow control is approximately minimal. (Effect of the Invention) As described above, according to the present invention, by reducing the flow rate of the hydraulic oil discharged from the hydraulic pump when the hydraulic device of the deck crane is not operating, the driving energy and noise that is wasted can be reduced. Embodiments Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the present specification and the drawings, the components that have substantially the same functional configuration are denoted by the same reference numerals, and the description thereof will not be repeated. -10-201202120 First, the overall configuration of the deck crane according to the first to fifth embodiments of the present invention will be described with reference to Fig. 1, and then the hydraulic drive system for the deck crane of each embodiment will be described. [Entire Configuration of Deck Crane] The deck crane 10 is installed on a deck of a ship (not shown) and used for loading or unloading of cargo transported at sea. The deck crane 10 has a lower post 20, a rotating strut (crane house) 30, a rotary bearing 32, a running chamber 40, a cantilever (jib) 50, a cantilever support portion 52, a hook 60, and a pulley (house top sieve group) 62, pulley (cantilever top screen group) 64 and steel cable 66. In the rotary strut (crane control room) 30, a hydraulic drive unit 1 of a deck crane which will be described later is disposed. The rotating strut 30 is attached to the upper portion of the lower strut 20 by a rotating bearing 32 disposed at a lower portion thereof, and is horizontally rotatable on the deck centering on the rotational axis of the bearing. The operation of rotating the boom 50 of the crane by rotating the strut 30 is referred to as slewing. An operation room 40 is provided on the front side portion of the rotating strut 30. In the operating room 40, a handle for operating the deck crane is provided. In the rotation of the strut 30, a cantilever 50 is repeatedly provided. The boom 50 is supported by the cantilever support portion 52 provided at one end of the lower end of the rotating strut. In order to align the cantilever 50 with the cargo, the operation of tilting (tilting) the cantilever 50 around the cantilever support portion 52 is referred to as up and down swinging. Rotation and up and down swing, respectively, contain -11 - 201202120 in the control of the cantilever 50. At the front end portion of the boom 50, a hook 60 for carrying goods can be suspended and lowered. The loading or unloading of the cargo is performed by winding the cable 66 upward or downward by a group of pulleys 62 disposed at the top of the rotating strut 30 and a pulley 64 disposed at the end of the cantilever 50. And proceed. The operation of loading or unloading goods by a hanging device mainly composed of a hook 60, a plurality of pulleys 62, 64, and a cable 66 is called a hoist. <First Embodiment> [Internal Configuration of Hydraulic Drive Device of Deck Crane] Next, a hydraulic drive device for a deck crane according to the first embodiment of the present invention will be described with reference to Fig. 2 . Fig. 2 is a view showing the internal configuration of the hydraulic drive unit 100 for a deck crane according to the first embodiment. The hydraulic drive system 1A includes a first hydraulic pressure supply system 110 for controlling the suspension, a second hydraulic pressure supply system 150 for controlling the vertical swing and the rotation, and a control unit 250. For example, the control unit 205 may be a PLC (Programmable Logic Controller) that is used as a computer for sequence control. The first hydraulic pressure supply system 1 1 〇 includes a hydraulic pressure supply line for controlling the hanging drum 135, and the hanging roller 135 is coupled to a hanging device as an example of a hydraulic device. The first hydraulic pressure supply system 11 includes an electric motor 1 15, a hydraulic pump 1 20 for suspension, an electromagnetic proportional flow control valve 125, and a hydraulic motor 130. Further, the hydraulic motor 130 is an example of a hydraulic actuator that operates the oil pressure -12-201202120 device. The first hydraulic pressure supply system no can control the upward suspension of the cargo and the downward suspension operation (hanging operation). Suspension hydraulic pump 1 20 and electromagnetic proportional flow control valve 1 25, according to the potentiometer (.Potentiometer) 46 detection . can change the discharge capacity of each rotation and the opening degree of the valve body. The potentiometer 46 is mounted to a handle 42 for performing a hanging operation disposed in the operating chamber, and detects the rotation angle of the handle 42. This detection 値 is sent to the control unit 25 0. The control unit 250 generates an electrical signal corresponding to the rotation angle of the handle 42 in accordance with the detection of the potentiometer 46. The generated electric signal is transmitted to the electromagnetic valve 123 and the suspension amplifier 140 through the electric line, whereby the discharge capacity of each rotation of the hydraulic pump 120 for suspension and the opening of the electromagnetic proportional flow control valve 125 can be controlled. degree. The hydraulic pump 120 for suspension is connected to the electric motor 115. When the electric motor 115 operates, the hydraulic oil can be discharged from the hydraulic pump 120 for suspension by its power. The hydraulic pump for hoisting is 120, and is connected to the hydraulic motor 130 disposed in the hydraulic pressure supply line through the electromagnetic proportional flow control valve 125, and supplies the hydraulic oil to the hydraulic motor 1130. Thereby, the hydraulic motor 1300 operates, and the suspension drum 135 is rotated by the power thereof. As a result, the hanging device can be raised and lowered. When the electromagnetic proportional flow control valve 156 is opened, the operating oil discharged from the sling hydraulic pump 126 is supplied to the hydraulic motor only at a flow rate corresponding to the opening degree of the electromagnetic proportional flow control valve 125. 3 〇, and the remaining flow can be bypassed by the electromagnetic proportional flow control valve 1 2 5 and returned to the actuating oil sump (not shown here). The hanging roller 1 3 5 is rotated by the hydraulic motor 130 driven by the supplied actuation -13-201202120 oil and starts or continues to suspend or hang the suspension device. When the electromagnetic proportional flow control valve 125 is closed, the hydraulic oil discharged from the suspension hydraulic pump 120 is not supplied to the hydraulic motor 130, and the rotation of the suspension roller 135 is stopped. Stop the hanging device from hanging up or hanging down. In addition, the hydraulic pump 120 for suspension is a variable displacement hydraulic pump. Here, the variable displacement oil pressure pump is a pump that can change the discharge capacity of the hydraulic oil. For example, a swash plate type variable displacement hydraulic pump can be cited as an example. The swash plate type variable displacement type hydraulic pump continuously changes the discharge capacity of the pressure oil by controlling the inclination angle of the swash plate which is axially displaced to each piston (referred to as the tilt angle). The second hydraulic pressure supply system 150 includes oil that is different from the first hydraulic pressure supply system 1 1 控制 that controls the vertical swing drum 175 connected to the boom 50 and the rotary device 190 connected to the rotary column 30 . Pressure supply line. The second hydraulic pressure supply system 150 includes an electric motor 155, an up-and-down swing/rotation hydraulic pump 160, an electromagnetic proportional flow control valve 165, a hydraulic motor 1 7 〇, an electromagnetic proportional flow control valve 1880, and a hydraulic pressure. Motor 1 8 5. The pitch (up and down swing operation) of the boom 50 can be controlled by the second hydraulic pressure supply system 150, and the swing (rotation motion) of the boom 50 can be controlled. The upper and lower swing/rotation hydraulic pump 160 is used to change the discharge capacity of each rotation according to the detection of the potentiometer 48, and the electromagnetic proportional flow control valve 1 6 5, 1 8 0 is based on the potentiometer 4 The detection of 8 can change the opening degree of the valve body. The potentiometer 48 is attached to a handle 44 disposed in the operating chamber for cantilever operation, and detects the rotation angle of the handle 44. The test - 14 - 201202120 is sent to the control unit 250. The control unit 250 generates an electric signal corresponding to the rotation angle of the handle 44 in accordance with the detection of the potentiometer 48. The generated electric signal is transmitted to the electromagnetic valve 163, the up-and-down swing amplifier 195, and the rotary amplifier 198 through the electric line, whereby the discharge capacity and electromagnetic of each rotation of the up-and-down swing/rotation hydraulic pump 160 can be controlled. The opening degree of the proportional flow control valve 1 65 and the opening degree of the electromagnetic proportional flow control valve 180. The up-and-down swing/rotation hydraulic pump 160 is connected to the electric motor 155, and when the electric motor 155 is operated, the hydraulic oil can be discharged from the up-and-down swing/rotation hydraulic pump 160 by the power thereof. The hydraulic pump 160 for swinging/rotating up and down is connected to the hydraulic motor 170 disposed in the hydraulic pressure supply line via the electromagnetic proportional flow control valve 165, and the hydraulic oil is supplied to the hydraulic motor 170. Thereby, the rotating drum 1 75 rotates. As a result, the cantilever 50 can be set at a desired tilt angle. The hydraulic pump 160 for swinging/rotating up and down is connected to the hydraulic motor 185 disposed in the hydraulic pressure supply line via the electromagnetic proportional flow control valve 180, and the hydraulic oil is supplied to the hydraulic motor 185. Thereby, the rotating device 190 will rotate up to . As a result, the rotating strut 30 can be rotated and the cantilever 50 can be rotated. When the electromagnetic proportional flow control valve 165 is opened, the hydraulic oil discharged from the vertical swing/rotation hydraulic pump 160 is supplied to the hydraulic motor 170, and the upper and lower swing rollers 175 are rotated and start or continue to swing up and down. Act and change the tilt of the cantilever 50. When the electromagnetic proportional flow rate control valve 165 is closed, the hydraulic oil discharged from the up-and-down swing/rotation hydraulic pump 160 is not supplied to the hydraulic motor 170, and the rotation of the up-and-down swing drum 175 is stopped and stopped. Swing motion, and can fix the tilt position of the cantilever -15- 201202120 5 0. When the electromagnetic proportional flow control valve 180 is opened, the hydraulic oil discharged from the up-and-down swing/rotation hydraulic pump 160 is supplied to the hydraulic motor 185, and the rotating device 90 rotates and starts or continues to rotate. And the rotation of the cantilever 50 is started or continued. When the electromagnetic proportional flow rate control valve 180 is closed, the hydraulic oil discharged from the vertical swing/rotation hydraulic pump 160 is not supplied to the hydraulic motor 185, and the rotation of the rotating device 190 is stopped and the rotation operation is stopped. Thereby, the action of the boom 50 is stopped. Further, the hydraulic pump 160 for swinging up and down/rotating is a variable displacement hydraulic pump similarly to the hydraulic pump 120 for suspension. For example, a CPU (not shown) is built in the control unit 250, and the hydraulic pressure is controlled in accordance with the operation of the handle of the operating room. More specifically, the control unit 250 drives the hydraulic oil from the hydraulic pump for hoisting 1 20 in accordance with the operation of the handle 42 for instructing the upward winding, neutral, and downward winding of the hanging device. The discharge flow rate is controlled to the maximum, and the flow rate of the hydraulic oil supplied to the hydraulic motor 130 is controlled by controlling the opening degree of the electromagnetic proportional flow control valve 12.5. When the operation of the handle 42 is not performed for a predetermined time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump 1 20 for suspension is controlled to a minimum, and by controlling the opening degree of the electromagnetic proportional flow control valve 125 The supply of the hydraulic oil to the hydraulic motor 130 is interrupted. Thereafter, when the operation of the handle 42 is performed again, the control unit 250 controls the discharge flow rate of the hydraulic oil from the hydraulic pump 120 for suspension to be maximized, and controls the electromagnetic proportional flow control valve 1 2 5 The opening degree is again started to supply the hydraulic oil to the hydraulic motor 130. -16-201202120 Further, the control unit 250 controls the discharge flow rate of the hydraulic oil from the up-and-down swing/rotation hydraulic pump 160 to be maximized in accordance with the operation of the handle 44 indicating the operation of the boom 50, and by controlling the electromagnetic ratio The flow rate of the operating oil supplied to the hydraulic motor 170 and the hydraulic motor 185 is controlled by the flow control valve 165 and the opening degree of the electromagnetic proportional flow control valve 180. Then, when the operation of the handle 44 is not performed for a predetermined time or longer, the discharge flow rate of the operating oil from the upper and lower swing/rotation hydraulic pump 160 is controlled to the minimum. Thereafter, when the operation of the handle 44 is performed again, the control unit 25 0 controls the discharge flow rate of the hydraulic oil from the vertical swing/rotation hydraulic pump 160 to be maximized. That is, the control unit 205 determines a hydraulic motor for driving the hydraulic device, and the hydraulic device operates in accordance with the detection of the potentiometer 46 and the potentiometer 48 corresponding to the operation of the handle 42 and the handle 44. . Then, when the hydraulic motor connected to the hydraulic pump is not operated for a predetermined time or longer, the discharge flow rate of the hydraulic oil from the hydraulic pump is minimized. At this time, the control unit 205 changes the discharge capacity of each rotation of the hydraulic pump 120 for suspension by controlling the electromagnetic valve 123, and changes the hydraulic oil from the hydraulic pump for suspension 1120. Spit traffic. In the same manner, the control unit 250 changes the discharge capacity of each rotation of the vertical swing/rotation hydraulic pump 160 by controlling the electromagnetic valve 163, and changes the hydraulic pump 160 from the vertical swing/rotation hydraulic pump 160. Actuating the flow of oil. Further, the control unit 250 controls the discharge flow rate of the hydraulic pump 1 20 for suspension and the hydraulic pump 160 for up-and-down swing/rotation, and controls the electromagnetic -17-201202120 proportional flow control valve 125, electromagnetic proportional flow control The opening degree of the valve 1 65 and the electromagnetic proportional flow control valve 180. That is, the amount of oil supplied to the hydraulic motor 1 3 0 , the hydraulic motor 1 70 , and the hydraulic motor 1 85 can be finally controlled by the electromagnetic proportional flow control valve 1 2 5 and the electromagnetic proportional flow control valve 16 5 and the electromagnetic proportional flow control valve 1 800 to adjust. For example, when it is not desired to operate the hydraulic motor 130, the hydraulic motor 1130 can be stopped from supplying the hydraulic oil by the electromagnetic proportional flow control valve 125 being fully closed. Therefore, even when the hydraulic motor 1 300 is not required to be operated, it is not necessary to set the discharge flow rate from the hydraulic pressure pump 120 to zero. [Change of discharge flow rate] Here, the details of the configuration of the discharge flow rate of the hydraulic oil for each rotation by the control of the electromagnetic valve will be described with reference to Fig. 3 . In addition, although the example of changing the discharge capacity of the hydraulic oil for each rotation of the hydraulic pump 120 for suspension is described here, the same applies to the case of the hydraulic pump 160 for up-and-down swing/rotation. Further, the type of the hydraulic pump of the variable capacity type is mainly a slanted plate shape and an oblique axis shape, but the following description will be made by taking a swash plate type variable displacement hydraulic pump as an example. Fig. 3 is an explanatory view showing an example of a configuration of a variable displacement type hydraulic pump 120 for suspension. The hydraulic pump 120 for suspension has a drive shaft 504 that is disposed to protrude from the outer casing 500. In the outer casing 500, a plurality of pistons 502 are provided around the drive shaft 504. The drive shaft 504 is coupled to the electric motor 115 and rotates with the rotation of the electric motor 115 18-201202120. Then, a plurality of pistons 502 are rotated in accordance with the rotation of the drive shaft 504. At this time, the piston 502 is rotated and pressed by the swash plate 506, from the state of the innermost wide piston 520-A to the state of the innermost wide piston 502-B. Reciprocating between them. At this time, the piston 502 is connected to the hydraulic oil outlet 524 in a state of being displaced from the piston 502-A to the piston 502-B, and only the portion extruded by the swash plate 506 is discharged from the inside of the piston 052. Actuate the oil. Further, in a state where the piston 502-B is moved to the state of the piston 502-A, the piston 502 is connected to the hydraulic oil inlet 522, and the hydraulic oil is sucked from the hydraulic oil inlet 522 to the inside of the piston 502. That is, the difference between the internal volume of the piston 502 in the state of the piston 502-A and the internal volume of the piston 5〇2 in the state of the piston 502-B becomes the actuation of each rotation of each piston 052. The discharge capacity of the oil. Here, the hydraulic oil inlet 522 is connected to a hydraulic oil reservoir (not shown), and the hydraulic oil outlet 524 is connected to the hydraulic motor 130 via an electromagnetic proportional flow control valve 125. The variable displacement type hydraulic pump 120 can change the tilt angle α corresponding to the angle of the swash plate 506 with respect to the drive shaft 5〇4. When the tilt angle α is zero, since the difference between the internal volume of the piston 502 in the state of the piston 502-Α and the internal volume of the piston 502 in the state of the piston 502-Β becomes zero, the drive shaft 5〇4 The discharge capacity of each rotating oil will become zero. The hydraulic pump 120 for hanging has a control oil inlet 5 26 and a first adjusting piston 508 which is driven by the pressure of the control oil injected from the control oil inlet 526 toward the swash plate 5 0 6 The direction in which the tilt angle α decreases is pushed out of the -19-201202120 swash plate 506; and the spring 510, when the pressure of the oil is not controlled, applies pressure to the swash plate 506 toward the tilting angle 使 of the swash plate 506: the increasing direction. By controlling the pressure of the oil, above the strength of the spring 5 10 , the spring 5 10 will be tightened according to the pressure of the control oil, and the tilt angle of the swash plate 506 will be reduced. Thereby, the discharge capacity of the hydraulic oil for each rotation of the drive shaft 504 of the hydraulic pump 120 for suspension is reduced. For example, when the strength of the spring 510 is 5 kg/cm 2 , when the pressure of the control oil is set to 10 kg/cm 2 , the first adjustment piston 508 is the one side swash plate 506 in a state where the control oil is injected. One end is pushed out by the pressure of the control oil toward the direction in which the tilt angle α is decreased, and the other end of the swash plate is pushed out toward the tightening spring 510. Then, the tilt angle α can be adjusted until the second adjustment piston 509 hits the minimum tilt angle adjustment stopper 513. Further, in a state where the control oil is not injected, the swash plate 506 can be pushed to a direction in which the tilt angle α is increased by the force of the spring 510, and the tilt angle α can be adjusted until the first adjustment piston 508 hits the maximum. The tilt angle adjustment stopper 530 is as follows. By adjusting the strength of the spring 510, or controlling the pressure of the oil and the maximum tilt angle adjustment stopper 530 and the minimum tilt angle adjustment stopper 531, the tilt angle can be controlled. α becomes one of the minimum tilt angle amin and the maximum tilt angle am ax. Further, the position of the maximum tilt angle adjustment stopper 530 can be adjusted by the first adjustment screw 540. Further, the position of the minimum tilt angle adjustment stopper 531 can be adjusted by the second adjustment screw 541. That is, the first adjustment piston 508, the second adjustment piston 509, the swash plate 506, the spring 510, the minimum tilt angle adjustment stopper 531, and the maximum tilt angle adjustment stopper 530 are controlled by -20-201202120 by An example of an adjustment portion for adjusting the stroke amount of the piston 052 by the pressure of the oil. Further, the control oil inlet 526 is connected to the solenoid valve 1 2 3 through the control oil supply line. The control unit 250 controls the presence or absence of the supply of the control oil to the hydraulic pump 1 20 for suspension and controls the tilt angle of the swash plate 506 of the hydraulic pump 120 for suspension by controlling the solenoid valve 1 2 3 . α. For example, the solenoid valve 123 switches whether or not the control oil is supplied to the hydraulic pump 1 20 for suspension in accordance with the presence or absence of an electric signal from the control unit 25 0 . In other words, the control unit 250 inputs an electric signal to the electromagnetic valve 123 when the hydraulic motor connected to the hydraulic pump 120 for suspension is not operated for a predetermined period of time or longer. Then, according to the electrical signal, the solenoid valve 1 23 is switched such that the control oil supply line is connected to the control oil inlet 526 of the hydraulic pump 120 for suspension, and the control oil is supplied to the hydraulic pump 120 for suspension. status. Further, when the hydraulic motor connected to the hydraulic pump for suspension 120 is operated again, the control unit 250 stops inputting an electric signal to the electromagnetic valve 123, and the solenoid valve 123 is switched to stop the suspension. The control oil inlet 526 of the hydraulic pump 120 is supplied with control oil, and the control oil inlet 526 is connected to the oil sump. According to this configuration, the control unit 250 can control the discharge capacity of each rotation of the drive shaft of the hydraulic pump 120 for suspension by controlling the solenoid valve 123. [Processing by Control Unit] Next, the hydraulic pump control executed by the control unit 250 of the hydraulic drive unit 100 of the present embodiment is referred to the flow shown in Fig. 4 - 201202120 The hydraulic pumping control process is started when the operator turns on the operation switch of the deck crane 1 in the operation room 40. In step S1 0 5, the control unit 205 determines whether or not the hydraulic motor connected to the hydraulic pump for suspension has not operated for a predetermined time or longer. Specifically, it can be determined according to whether or not it is useful to operate the handle of the hydraulic motor 130 connected to the hydraulic pump for suspension. In step S1 05, the control unit 250 determines that the hydraulic pump is connected to the suspension. When the hydraulic motor 130 of the pump 120 does not operate for a predetermined time or longer, the process proceeds to step S110, and the control unit 250 controls the discharge capacity of the rotary oil for each of the suspension hydraulic pumps 120 to be minimized. capacity. Thereby, the minimum flow of the hydraulic oil can be discharged from the hydraulic pump 1 20 for suspension. At this time, the electromagnetic proportional flow control valve 125 is fully closed by the control of the control unit 250, and the hydraulic motor 130 is not supplied with the operating oil, and the operation of the hydraulic motor 130 is stopped, and the hanging of the cargo is stopped. action. On the other hand, if the control unit 250 determines in step S105 that the hydraulic motor 130 connected to the hydraulic pump 120 for suspension is operated within a predetermined time, the process proceeds to step S1 15 and is controlled. The portion 2 50 controls the discharge capacity of each of the rotating hydraulic oils for the suspension hydraulic pump 120 to the maximum capacity. Thereby, the maximum flow of the hydraulic oil can be discharged from the hydraulic pump 120 for suspension. At this time, the hydraulic motor can be supplied with the hydraulic oil through the electromagnetic proportional flow control valve 1 2 5 controlled to correspond to the opening degree of the operation of the handle 42, and can be executed by the power 'output from the hydraulic motor 130' The hanging action of the goods. -22-201202120 Then, in step s 1 2 0, the control unit 205 determines whether or not the hydraulic motor connected to the vertical swing/rotation hydraulic pump 160 has not operated for a predetermined time or longer. Specifically, it is possible to determine whether or not the operation of the handle 44 for operating at least one of the hydraulic motor 170 and the hydraulic motor 185 connected to the hydraulic pump for vertical swing/rotation is operated for a predetermined time or longer. In step S1 20, the control unit determines that the hydraulic motor connected to the vertical swing/rotation hydraulic pump 160 has not operated for a predetermined time or longer, that is, when the hydraulic motor 170 and the hydraulic motor When the time when both of the two have not been operated has continued for a predetermined time or longer, the process proceeds to step S1 25 » Then, the control unit 25 0 is a rotary oil that rotates each of the up and down swing/rotation hydraulic pumps 160 The spit capacity is controlled to a minimum capacity. Thereby, the hydraulic oil of the minimum flow rate can be discharged from the hydraulic pump 160 for swinging up/down. At this time, the electromagnetic proportional flow rate control valve 165 and the electromagnetic proportional flow rate control valve 180 are fully closed by the control of the control unit 25 0, and the hydraulic motor 170 and the hydraulic motor 185 are not supplied with the operating oil, and the hydraulic motor is not provided. When the operation of 170 and the hydraulic motor 1 8 5 is stopped, the operation of the boom 50 is stopped. On the other hand, if the control unit determines in step S1 20 that the hydraulic motor connected to the vertical swing/rotation hydraulic pump 1 60 is operated within a predetermined time, the process proceeds to step S 1 3 0. Further, the control unit 250 controls the discharge capacity of the engine oil for each rotation of the vertical swing/rotation hydraulic pump 160 to the maximum capacity. Thereby, the maximum flow rate of the hydraulic oil can be discharged from the up-and-down swing/rotation hydraulic pump 160. At this time, the hydraulic motor 17 〇 and the hydraulic motor 185 can be transmitted through the electromagnetic proportional flow control valve 1 6 5 or the electromagnetic proportional flow -23 - 201202120 controlled by the opening degree corresponding to the operation of the handle 44. The operating oil is supplied with 0, and the boom 50 operates. For example, when the operation of the handle 44 is only for the up and down swing operation, the electromagnetic proportional flow control valve 180 is fully closed to interrupt the supply of the hydraulic oil to the hydraulic unit connected to the rotary unit. Next, in step S135, it can be determined whether or not the operator has turned off the operation switch of the deck crane 10. When the control unit 250 determines that the operation switch has not been turned off, the control unit 250 returns to step S105 and again determines whether the hydraulic motor connected to the hydraulic pump for suspension is at a predetermined time. As described above, the processing of steps S105 to S130 may be repeated until the operation switch is turned off in step S135. This process ends when the operator disconnects the operation switch. Further, the processing of steps S1 to S115 and the processing of steps S120 to S130 are not necessarily performed in the order illustrated, and may be processed in parallel. According to the first embodiment described above, the control unit 25 0 controls the discharge capacity of each rotation of the hydraulic oil from the hydraulic pump 120 for suspension in accordance with the operation of the handle 42 that displays the operation of the suspension device. Maximum capacity. At this time, during the operation of the handle 42, the discharge flow rate of the hydraulic oil from the hydraulic pump for suspension 1 0 0 can be always controlled to be the maximum, and can be variably controlled. During the period of time, the hydraulic oil pumping 1 2 0 can be used to discharge the operating oil of the maximum discharge flow rate. As a result, the hydraulic motor 130 operates, and the upward winding and the downward winding of the hanging device can be performed by the power thereof. On the other hand, the control unit 250 controls the discharge flow rate of the hydraulic oil from the hydraulic pump for slamming to a minimum when the operation of the handle 42 is not performed for a predetermined period of time -24 - 201202120. . As a result, only the operating oil of the minimum discharge capacity can be discharged from the hydraulic pump 1 20 for suspension, whereby noise can be suppressed. In addition, it can also reduce the driving energy that is lost when the maximum capacity of the operating oil is discharged. As before, the same is true when the operation of the handle 44 of the boom 50 is performed. Further, in the first embodiment, a method of controlling the discharge flow rate of the hydraulic pump by controlling the discharge capacity of each rotation of the hydraulic pump is described. As described above, the discharge flow rate of the hydraulic pump is determined based on the discharge capacity per rotation and the number of rotations. Next, in the second embodiment, a method of controlling the discharge flow rate by controlling the number of rotations of the hydraulic pump will be described. <Second Embodiment> Next, the hydraulic drive device 100 for a deck crane according to the second embodiment of the present invention will be described with reference to Fig. 5 . In the hydraulic drive unit 1 of the deck crane of the present embodiment, the discharge flow rate of the hydraulic oil of the hydraulic pump is controlled by the inverter controlling the number of rotations of the electric motor. This is the same as the first embodiment. The hydraulic drive unit 1 of the deck crane is different. Therefore, the second embodiment will be described with reference to the above differences, and the description of the same points as those of the first embodiment will be omitted. [Internal configuration of the hydraulic drive unit of the deck crane] -25-201202120 Fig. 5 is a view showing the internal configuration of the hydraulic drive unit 100 of the deck crane according to the second embodiment. The hydraulic drive device 1 of the present embodiment further includes a suspension inverter 205 for controlling the number of rotations of the electric motor 115 for driving the hydraulic pump 120 for suspension, and a control for driving up and down swing/ In place of the hydraulic drive device 100 of the first embodiment, in order to control the rotation of the hydraulic pump, the inverter for rotating the upper and lower swing/rotation of the electric motor 155 of the hydraulic pump for hydraulic rotation 155 is replaced by the inverter 2 1 0. The solenoid valve 123 and the solenoid valve 163 are provided to discharge the capacity. The suspension inverter 205 is an electric line provided between the control unit 250 and the electric motor 1 15 and is connected to the electric motor 1 15 . As previously described, the potentiometer 46' detects the angle of rotation of the handle 42. This detection 値 is sent to the control unit 250. The control unit 250 generates an electric signal corresponding to the rotation angle of the handle 42 in accordance with the detection 値. The generated electric signal is input from the control unit 250 to the suspension amplifier 140 and the suspension inverter 205. Suspension Using the inverter 205, the number of rotations of the electric motor 115 is controlled in accordance with a signal from the control unit 250. The electric motor 115 supplies a predetermined amount of power to the hydraulic pump 120 for suspension. Thereby, the discharge flow rate of the operating oil from the hydraulic pump for suspension 1 2 0 can be controlled. The up-and-down swing/rotation inverter 210 is an electric line provided between the control unit 250 and the electric motor 155, and is connected to the electric motor 155. As described earlier, the potentiometer 48 detects the angle of rotation of the handle 44. This detection 値 is sent to the control unit 250. The control unit 2 50 generates an electric signal corresponding to the rotation angle of the handle 44 in accordance with the detection 値. The generated electric signal is input from the control unit 250 to the up-and-down swing/rotation amplifier 198 and the up-and-down -26-201202120 swing/rotation inverter 210. The up-and-down swing/rotation inverter 210 controls the number of revolutions of the electric motor 1 55 in accordance with a signal from the control unit 250. The electric motor 155 is supplied with a predetermined amount of power to the upper and lower swing/rotation hydraulic pressure pump 60. Thereby, it is possible to control the discharge flow rate of the operating oil from the hydraulic pump 160 of the upper and lower pendulums. [Processing of Control Unit] Next, the hydraulic pump control process executed by the control unit 250 that controls the hydraulic drive device 1A of the present embodiment will be described with reference to the flowchart shown in FIG. . In addition, the hydraulic pump control process of the second embodiment differs from the hydraulic pump control process of the first embodiment in that the control in steps S210, S215, S225, and S230 is not For each rotation of the spit capacity, but the number of rotations. Further, when the hydraulic motor is operated within a predetermined time, the number of revolutions of the electric motor is controlled by the control unit 250 to correspond to the detection 値 of the potentiometer. As described above, the discharge flow rate of the hydraulic pump can be expressed by the discharge capacity and the number of rotations of the average rotation. In the present embodiment, the discharge flow rate of the hydraulic pump is controlled by controlling the number of revolutions. That is, the number of rotations of the electric motor 115 is controlled by the suspension inverter 205, and the number of rotations of the hydraulic pump 120 for suspension driven by the electric motor 115 is controlled. In addition, the same applies to hydraulic pumping for up and down swing/rotation. According to the second embodiment described above, the number of rotations of the electric motor for driving the hydraulic pumping is controlled by the presence or absence of the operation of the hydraulic motor '-27-201202120, and the discharge flow rate from the hydraulic pump is set to In the same manner as in the first embodiment, the noise can be reduced in the same manner as in the first embodiment. Further, according to the second embodiment, since the output of the electric motor can be controlled by the inverter, power consumption can be suppressed. As described above, in the first embodiment, the discharge capacity of the hydraulic oil for each rotation of the hydraulic pump is changed to control the oil pressure by controlling the solenoid valve and supplying the control oil to the hydraulic pump. The method of pumping the discharge capacity will be described. In the second embodiment, the number of rotations of the electric motor for driving the hydraulic pump is controlled by the inverter control, thereby controlling the rotation of the hydraulic pump. The method of controlling the discharge flow rate of the hydraulic oil by the hydraulic pump is described. The two methods can be used in combination. Therefore, in the third embodiment, a method of controlling both the discharge capacity and the number of rotations for each rotation will be described. <Third Embodiment> [Internal Configuration of Hydraulic Drive Device for Deck Crane] Fig. 7 is a view showing the internal configuration of a hydraulic drive device 100 for a deck crane according to a third embodiment. In addition to the configuration of the hydraulic drive device 1 of the first embodiment, the hydraulic drive device 100 of the first embodiment has the suspension inverter 205 described in the second embodiment and swings up and down/ The inverter 210 for rotation. Since the functions of the respective constituent elements are the same as those of the hydraulic drive unit 100 according to the first embodiment or the second embodiment, the description thereof will be omitted. • 28-201202120 [Processing by Control Unit] Next, the hydraulic pump control process executed by the control unit 250 that controls the hydraulic drive unit 丨0 0 of the present embodiment is referred to the eighth figure. The flow chart will be explained. Further, in the present embodiment, the basic operation is the same as that of the first embodiment or the second embodiment, and the difference is that the control of the discharge capacity per rotation and the control of the number of rotations are combined, and the steps are based on the steps. The processing completed in each case of the judgment of S30 5 and step S3 30. However, since the content of each process is the same as that of the first or second embodiment, the description thereof is omitted here. As described above, in the first to third embodiments, the case where the hydraulic pump 120 for suspension and the hydraulic pump 160 for vertical swing/rotation can be driven by different electric motors will be described. However, the hydraulic pump 120 for suspension and the hydraulic pump 160 for up and down swing/rotation can be driven by the same electric motor as a single-shaft double-connected pump. In the above-described hydraulic drive device, the control of the discharge flow rate of the hydraulic pump to which the present invention is applied will be described as the fourth and fifth embodiments as follows. <Fourth Embodiment> [Internal Configuration of Hydraulic Drive Device for Deck Crane] Fig. 9 is a view showing the internal configuration of the hydraulic drive device 100 for a deck crane according to the fourth embodiment. The hydraulic drive unit 1〇〇' is different from the third embodiment in that the hydraulic pump for suspension and the up-and-down swing/rotation -29-201202120 hydraulic pump can be driven by the same electric motor. 105 to drive. The number of revolutions of the electric motor 156 can be controlled by the inverter 200 which is used for hanging/up and down swing/rotation. In other words, the hydraulic pump 120 for suspension and the hydraulic pump 160 for up-and-down swing/rotation can mutually connect the drive shaft thereof, and the hydraulic pump 120 for suspension according to the rotation of the electric motor 105 can be used. The rotation of the drive shaft rotates the drive shaft of the hydraulic pump 160 for up-and-down swing/rotation. According to the difference in the configuration of the hydraulic drive device 100 of the fourth embodiment, the maximum difference is that the number of rotations of the electric motor 105 is the number of rotations required for the hydraulic pump 120 for suspension, and The maximum number of rotations required for the swing/rotation hydraulic pump 160. In other words, even in the case where the hoisting operation is not performed when the swaying/rotating operation is not performed, since it is necessary to drive the sling hydraulic pump 1 20, the unused up and down swing/rotation is performed. Pumping with hydraulic pressure will also be the same number of revolutions. [Processing by the Control Unit] Next, the hydraulic pump control process executed by the control unit 250 that controls the hydraulic drive device 1A of the present embodiment is described with reference to the flowchart shown in FIG. Description. First, in step S405, the control unit 250 determines whether or not all of the hydraulic motors have not been operated for a predetermined time or longer. As described above, in the hydraulic drive device 1 of the present embodiment, it is necessary to provide the maximum number of rotations -30 - 201202120 among the number of rotations required for the hydraulic pump connected to the electric motor 105. drive. That is, the number of rotations can be set to a minimum 只有 only when all of the hydraulic motors driven by the hydraulic pump connected to the electric motor 105 are not operated. Therefore, first, in step S405, the control unit 250 determines whether or not all of the hydraulic motors have not operated for a predetermined time based on the detection 电位 of the potentiometer corresponding to the operation of the handle 42 and the handle 44. Then, when all of the hydraulic motors driven by the hydraulic pump connected to the electric motor 105 are not operated for a predetermined time or longer, the process proceeds to step S410, and the control unit 25 0 The rotary motor of the electric motor is made into a minimum by the frequency converter. On the other hand, in step S405, when it is determined by the control unit 250 that one of the hydraulic motors is operated within a predetermined time, the control unit 250 controls the number of revolutions of the electric motor by the inverter. The enthalpy corresponding to the detection of the potentiometer. Hereinafter, the processing of steps S420 to S445 is omitted since it is the same as the processing of steps S105 to S135 of Fig. 4, for example. As described above, in the hydraulic drive system according to the fourth embodiment of the present invention, the hydraulic pump 120 for suspension and the hydraulic pump 160 for up and down swing/rotation can be driven by the same electric motor 105 as a single-axis double. Continuous pumping. Therefore, only in the inverter control, the number of revolutions can be reduced and the discharge flow rate of the hydraulic pump can be limited only when all the hydraulic motors are not operating. Therefore, the configuration of the discharge capacity for controlling each rotation of the hydraulic pump using the solenoid valve described in the first embodiment is performed in the suspension -31 - 201202120 or the up and down swing/rotation. When any one is not operating, the flow rate can be spit out by the control of the discharge capacity of each rotation, and the noise can be reduced. Further, in the case of all the operations, the discharge capacity of each rotation can be controlled by controlling the number of rotations, thereby suppressing the power consumption of the discharge of the engine oil. Further, in the configuration of the single-shaft double-connected pump, only the configuration of the discharge capacity per rotation may be controlled. The following will be described as the fifth embodiment. <Fifth Embodiment> [Internal Configuration of Hydraulic Drive Device for Deck Crane] Fig. 1 shows the internal configuration of the deck starter 100 according to the fifth embodiment. The hydraulic drive unit 100 has a different form and is different in that it does not have an inverter that controls the electric motor. [Processing by the Control Unit] The hydraulic pump control process according to the fifth embodiment is the same as the first embodiment described in the fourth embodiment. Therefore, although not shown, even in the single-axis double connection, The discharge of the operating oil having control of each rotation can also be controlled by the frequency converter to control only the number of rotations. However, in the idling state, the hydraulic motor that reduces the operating oil is not controlled, but also the flow rate, and the hydraulic drive that constitutes the heavy machine without using the inverter is turned off, and the number of rotations of the fourth embodiment 105 is due to Here, the configuration of the constituent capacity of the illustrative pump is omitted. As described above, -32-201202120 is only controlled by the inverter, and only when all the hydraulic motors are not operating. The discharge flow rate of the operating oil can be reduced, and the noise reduction effect is low. Therefore, when the inverter control is used in the configuration of the single-shaft double-connected pump, it is extremely effective to control the discharge capacity for each rotation. In the first to fifth embodiments described above, the operations of the respective units are associated with each other, and the series of operations can be replaced while considering the mutual relationship. Thereby, the embodiment of the hydraulic drive device for the deck crane can be regarded as an embodiment of the hydraulic drive method of the deck crane. <Control of the number of rotations of the fan> [Mains] As described above, in the electric hydraulic type crane, the hydraulic pump is driven by the power of the electric motor, and is discharged by hydraulic pumping. The oil is actuated to drive the hydraulic actuator and then the hydraulic device is driven by its power. In this case, in the hydraulic drive system for the deck crane according to the first to fifth embodiments, the discharge capacity of each rotation of the hydraulic pump is controlled to be substantially minimum by using a solenoid valve, or the driving oil pressure is driven by the inverter. The rotary digital control of the pumped electric motor is made substantially minimum, thereby controlling the discharge flow rate of the hydraulic oil discharged from the hydraulic pump. In the second, fifth, seventh, ninth and eleventh illustrations, although not shown for the sake of simplicity, the actuating oil can be supplied from the oil tank for storing the oil to the hydraulic pump, and The hydraulic oil discharged from the hydraulic pump can be recovered to the oil sump. The recovered operating oil is supplied back to the hydraulic pump -33- 201202120 and circulated inside the deck crane. The oil is driven by an actuator such as a hydraulic motor to perform a right-handed/left-turning operation in the n-device in the winding/down winding and the up-and-down swinging device. The mechanism that is pulled down, the downward direction in the upward direction of the winding device, and the downward movement of the turning device are safely lowered. In the oil balance counter valve, etc., and by adjusting the actuating oil to perform the work and absorb the work results, all of them will be regarded as the actuating oil whose energy is pumped by the hydraulic pumping, and the pipe can be borrowed. The hydraulic drive unit 1 of the heavy machine, such as the friction of the inner wall (the pipe impedance), has a configuration in which the heated oil is cooled, but the heat exchanger is configured to cool the working oil. . According to the above-described first to fifth embodiments, as described above, the discharge flow rate of the hydraulic oil that is idling in the deck crane can be controlled to be substantially the maximum, and when, for example, the discharge flow rate of the hydraulic oil is controlled to a certain extent, The maximum discharge flow rate is spit, and the temperature rise of the operating oil will be lower. However, the blower of the heat exchanger is driven by an electric motor. In this case, there is a possibility that when the upper arm is moved up and down and the turning ratio in the winding device of the actuating oil in the forced oil discharge device is unnecessarily performed, the winding is performed by the load and the upper and lower swings are mounted. It is necessary to maintain the system while generally using the energy required by the orifice. These are absorbed. Further, it is heated by the oil supply line and the operating oil supply line. Therefore, the deck is brought back to the oil tank. Although the details will be represented later, there is an air-cooled hydraulic drive unit 100, which will spit out from the hydraulic pump. In such a configuration, the case where the oil is substantially discharged in a substantially minimum state is driven by the cooling of the moving oil at a fixed number of rotations than when the air is sent to the air-cooled type. In the hydraulic drive device 100 according to the first to fifth embodiments of the first to fifth embodiments in which the noise is reduced by the decrease in the discharge flow rate of the hydraulic oil, the sound of the cooling fan may be perceived as noise. . Therefore, the method of reducing the noise by controlling the number of rotations of the electric motor for driving the cooling fan will be described below with reference to Figs. 12 to 14 . [Configuration] Fig. 12 is an explanatory view showing an example of the configuration of the hydraulic pressure supply system of the hydraulic drive device 100. Fig. 13 is an explanatory view showing another example of the configuration of the hydraulic pressure supply system of the hydraulic drive device 100. Fig. 14 is a flow chart showing an example of a control processing flow of the hydraulic oil cooling fan of the hydraulic drive unit 1 . First, when referring to Fig. 12, the hydraulic system in the configuration of the single-shaft double-connected pump is schematically shown. As described above, the hydraulic drive device 100 has the oil groove 350, and the hydraulic oil is supplied from the oil groove 350 to the hydraulic pump 120 for suspension and the hydraulic pump 160 for vertical swing/rotation. The operating oil supplied to the hydraulic pump 120 for sling is discharged by applying pressure to the hydraulic pump 120 for suspension. Then, the discharged hydraulic oil is supplied to the hydraulic motor 130 for driving the suspension roller 135 through the electromagnetic proportional flow control valve 125. The operating oil that has been operated by the hydraulic motor 130 and the operating oil that has not been supplied to the hydraulic motor 130 by the flow rate control by the electromagnetic proportional flow control valve 1 25 are passed through the operating oil recovery line 1 1 3 And recovered to the oil tank 350 by a radiator 330 and an oil filter 340. -35-201202120 On the other hand, the operating oil supplied to the hydraulic pump 160 for the vertical swing/rotation is discharged by the upper and lower swing/rotation hydraulic pump 146. Then, the hydraulic oil to be discharged is supplied to the hydraulic motor 170 that drives the vertical swinging drum 175 and the hydraulic motor 185 that drives the rotating device 190 through the electromagnetic proportional flow control valve 165 and the electromagnetic proportional flow control valve 180. The operating oil after the hydraulic motor 170 and the hydraulic motor 185 is operated, and the flow rate control by the electromagnetic proportional flow control valve 165 and the electromagnetic proportional flow control valve 180 is not supplied to the hydraulic motor 1 70 and the oil. The operating oil of the press motor 1 85 is recovered to the oil sump 350 through the actuating oil recovery line 1 53, and through the radiator 330 and the oil filter 340. The fan 320 is one of air blowers that apply pressure to a gas such as air. The fan 3 20 has a function of supplying air for heat exchange to a heat sink 330 which will be described later. The heat sink 320 is also a type of heat exchanger called a radiator. The heat sink 330 is, for example, an air-cooled heat exchanger, and has a function of moving the heat of the operating oil to the slave fan 320 when the air is applied from the fan 3 20 driven by the electric motor 305. The function of the supplied air. Therefore, the operating oil after the radiator 300 is moved into the air by transmitting the heat itself as a pipe of the oil passage, whereby the temperature of the operating oil can be lowered. The radiator 330 is provided in a path in which the hydraulic oil discharged from each hydraulic pump is recovered to the oil groove. More specifically, it is preferably disposed at a position where the oil after passing through the radiator 330 is not used for work. Further, the oil filter 340 is for removing a filter mixed with the mixed oil of the operating oil. -36-201202120 In the present embodiment, the fan drive motor for controlling the number of revolutions of the electric motor 305 is used to drive the cooling fan 320. 3〇〇, the electric motor J number is controlled in accordance with the instruction of the control unit 250. The number of rotations of the electric motor 3 05, that is, the sound of the fan 320 is larger, the lower the number of rotations of the fan 320 is, the noise is discharged, and the discharge flow rate of the hydraulic oil is appropriately adjusted to the hydraulic drive device 100 of the fifth embodiment. Whether or not the middle oil is used for work, when it is compared with the hydraulic drive device that always spits out the most dynamic oil, the rise in the idling state is particularly low. Therefore, by appropriately controlling the number of rotations of the fan 3 20 in accordance with the operation, the source consumption and the unhelpful noise can be reduced. In addition, the picture of this control is described below. Further, the driving of the hydraulic device described above is controlled by the solenoid valve 123 and the solenoid valve 163, and is supplied to the upper and lower swing/rotation hydraulic pump 160. The control oil can be supplied, for example, from the same oil or from different oil grooves. In Fig. 12, it is provided that the pressure pump 120 and the up-and-down swing/rotation hydraulic pump are again recovered to the recovery line for the oil tank 35 through the solenoid valve 123 and the solenoid valve 163. When referring to Fig. 13, the hydraulic system in the dual-pump hydraulic drive unit 1 is schematically shown. In this case, the device 300 is provided with the motor 300, and the motor has a lower rotation number of the rotation of the inverter motor 305. In the above-described first control, the energy of the warm oil of the operating oil, which is discharged by the large discharge flow rate due to the discharge, is wasted, and the hydraulic system for the suspension is used. The supply line for the oil supply line is supplied to the oil tank 350, which is not shown in the figure. However, the control oil supplied to the suspension oil 160 is also the type of the double-motor type. The function of each component is -37-201202120 and the first 2 The example of the figure is the same, and the detailed description is omitted. The following description will be given with reference to Fig. 2: The hydraulic drive device of the continuous pump configuration is controlled by the number of revolutions of the variable oil pump and the solenoid valve. In the configuration of both the discharge amount of the hydraulic pump, the configuration of the number of rotations of the motor for driving is added, and the configuration of the thirteenth embodiment is described: that is, the configuration of the dual-pump double-motor type The device is controlled to rotate the motor for driving the cooling fan by controlling the amount of discharge of each of the hydraulic pumps for the hydraulic pump of the hydraulic pump. However, the present invention is not limited to such a configuration. In any hydraulic drive device that controls the rotation amount of each rotation of the hydraulic pump to which the number of revolutions of the hydraulic pump is controlled by the inverter, the number of rotations for controlling the cooling fan is added. Composition. In other words, the configuration of controlling the number of rotations of the electric motor for the fan described above can be applied to any of the hydraulic drive devices 100 of the fifth embodiment. [Control processing] Referring to FIG. At the time, the control processing for driving the number of rotations of the cooling fan motor 305 is displayed. Further, although not shown in Fig. 13, the hydraulic drive device 1 measures the temperature measuring portion that is the temperature of the moving oil. Using the thermometer, the control unit 250 determines whether or not the temperature of the operating oil is . In other words, in the singular cooling fan diagram of the uniaxial dual-frequency device, the following is a configuration of the hydraulic drive number control and the number of the two components. The electric motor drives the first to third electric motors in the first to third embodiments, and the measurement is performed at 40 ° C or higher ( -38 - 201202120 S505 ). When the operating oil temperature is 40 °C or higher, the electric motor 305 starts to rotate in order to drive the cooling fan 320. Then, the control unit 250 numerically controls the rotation of the motor 305 that drives the fan 320 to a rotation number (S 5 1 0 ) proportional to the operating oil temperature or the tilting angle of the handle 42 and the handle 44. For example, when the number of revolutions of the electric motor 305 is controlled in proportion to the temperature of the operating oil, the operating oil temperature is 40 ° C, the number of revolutions of the electric motor 305 is rotated from 600 RPM, and the operating oil temperature is 7 〇. °C, the number of rotations of the electric motor 3 05 reaches the maximum number of rotations of 1 800 RPM, and becomes the number of rotations proportional to the temperature of the operating oil, whereby the control unit 250 can control the number of rotations of the electric motor 305 by the inverter 300 for the fan. . On the other hand, when the number of rotations of the electric motor 305 is controlled in proportion to the handle tilt angle, the control unit 25 0 follows the operation angle of the handle 42 detected by the potentiometer 46 and the handle detected by the potentiometer 48. The operating angle of 44 controls the number of revolutions of the electric motor 3 05. Further, although the control of step S 5 10 is continuously performed, the control unit 250 determines in parallel with this whether or not the temperature of the operating oil is 40 ° C or lower ( S515 ). This determination is a determination of the stop condition of the electric motor 305 that drives the fan. Then, when the operating oil temperature is 40 °C or higher by the judgment of step S515, the control unit 250' determines whether or not there is no handle operation for a predetermined period of time or longer (S 5 20). The judgment of step S520 can be judged based on the detection 电位 of the potentiometer 46 and the potentiometer 48. Then, when a certain handle operation is detected within a predetermined time, the control of step S 5 10 is continued again. On the other hand, when no handle operation is detected for a predetermined time or longer, the motor-driven electric motor 305 is rotated to a minimum number of rotations (S 52 5 ). The control of step S52 5 continues until the handle operation is detected. Further, in the judgment of step S505, when it is judged that the operating oil temperature is not 40 °C or higher, it can be determined whether or not the next operation switch is disconnected by the operator of the deck crane (S 5 3 5 ). This control process ends when the operation switch is turned off. On the other hand, when the operation switch is not turned off, the above-described control is continued and the operation is repeated. As described above, the preferred embodiments of the present invention have been described in detail with reference to the drawings, but the present invention is not limited to such examples. As long as it is a person having ordinary knowledge in the technical field to which the present invention pertains, it is to be understood that various modifications and alterations can be made within the scope of the technical idea described in the claims. The technical scope of the invention. For example, in the above-described first to fifth embodiments, a hydraulic motor is used as a deck crane for a hydraulic actuator that operates a hydraulic device, but the present invention is not limited to such an example. For example, it is also possible to replace a hydraulic motor with a deck crane using a hydraulic cylinder. For example, in the first and second embodiments, when the handle is operated for a predetermined time or longer, the control unit 250 controls the discharge capacity of the hydraulic oil from the hydraulic pump to be minimized. However, the present invention is not limited thereto, and when the handle is operated for a predetermined time or longer, the discharge capacity of the hydraulic oil from the hydraulic pump is controlled to be smaller than the discharge capacity of the previous hydraulic oil. Further, in the first to fifth embodiments, when the handle operation has been performed -40 - 201202120, the control unit 250 will control the discharge capacity of the hydraulic oil from the hydraulic pump to the maximum. However, the present invention is not limited to this. When the handle operation has been performed, the discharge capacity of the hydraulic oil from the hydraulic pump is controlled to be larger than the discharge capacity of the previous hydraulic oil. Further, the hydraulic drive system 100 of the first to fifth embodiments has the first hydraulic pressure supply system 110 and the second hydraulic pressure supply system 150, but the present invention is not limited thereto. The hydraulic drive device 100 of the present invention may have at least one of the first hydraulic pressure supply system 110 and the second hydraulic pressure supply system 150. Further, in the hydraulic drive system 1 of the first and second embodiments, the vertical swing operation and the rotation operation are collectively processed by the second hydraulic pressure supply system 150 of the same system, but the present invention does not. In addition to this, it is also possible to individually handle the up and down swing motion and the rotation motion using hydraulic lines of different systems. The hydraulic drive device 100 of the present invention is preferably applied to a ship. The hydraulic drive unit 1 of the present invention may be provided with one or a plurality of decks on a ship. Further, in the above embodiment, the deck crane used in the ship is described as an example, but the present invention is not limited to such an example. It is not limited to deck cranes and can also be applied to crane equipment used on the road. Further, the present invention is not limited to the application to the crane apparatus, and can be widely applied as a hydraulic pump control device in an electric hydraulic type hydraulic device. [Brief Description of the Drawings] - 41 - 201202120 Fig. 1 is a view showing the overall configuration of a swing crane according to the first to fifth embodiments of the present invention. Fig. 2 is a view showing the internal configuration of a hydraulic drive system for a deck crane according to the first embodiment. Fig. 3 is a view showing the internal configuration of a variable displacement hydraulic pump of the first to fifth embodiments. Fig. 4 is a flow chart showing the hydraulic pump control process of the first to fifth embodiments. Fig. 5 is a view showing the internal configuration of a hydraulic drive system for a deck crane according to a second embodiment. Fig. 6 is a flow chart showing the hydraulic pump control process of the second embodiment. Fig. 7 is a view showing the internal configuration of a hydraulic drive system for a deck crane according to a third embodiment. Fig. 8 is a flow chart showing the hydraulic pump control process of the third embodiment. Fig. 9 is a view showing the internal configuration of a hydraulic drive system for a deck crane according to a fourth embodiment. Fig. 1 is a flow chart showing the hydraulic pump control process of the fourth embodiment. Fig. pi is a diagram showing the internal structure of a hydraulic drive unit for a deck crane according to a fifth embodiment. Fig. 12 is an explanatory view showing an example of a hydraulic pressure supply system of a single-shaft double-connected pump type hydraulic drive system. -42- 201202120 Fig. 13 is an explanatory view showing an example of a hydraulic pressure supply system of a 2-pump 2 electric motor type hydraulic drive system. Fig. 14 is a flow chart showing the control operation of the number of rotations of the electric motor for driving the cooling fan. [Description of main component symbols] 10 : Deck crane 20 : Lower pillar 3 〇: Rotating strut 40 : Operating room 42 , 44 : Handle (operation part) 4 6 , 4 8 : Potentiometer 5 0 : Cantilever 52 : Cantilever support 6 0: Hook 6 2, 6 4 : Pulley 66 : Cable 1 0 〇: Hydraulic drive unit 1 1 〇: 1st hydraulic supply system 105, 115, 155: Electric motor 1 2 0 : Hydraulic pump for suspension 123, 163: Solenoid valve (solenoid valve) 1 2 5, 1 6 5, 1 8 0 : Electromagnetic proportional flow control valve 130, 170, 185: Hydraulic motor -43- 201202120 1 3 5 : Hanging roll Cylinder 140: Suspension amplifier 1 50: Second hydraulic pressure supply system 160: Up and down swing/rotation hydraulic pump 175: Up and down swing reel 190: Rotary device 195: Up and down swing amplifier 198: Rotary amplifier 2 00 : Inverter (hanging, swinging up and down, rotating) 205 : Inverter for hanging 210: Inverter for up and down swing/rotation 2 5 0 : Control unit 3 00 : Inverter for fan 3 05 : Electric motor 320 : Fan 3 3 0 : Radiator (heat exchanger) 3 4 0 : Oil filter 3 5 0 : Oil tank 500 : Housing 502 : Piston 5 0 4 : Drive shaft 5 0 6 : Oblique 5 0 8 : 1st adjustment piston 5 09 : 2nd adjustment piston • 44- 201202120 5 1 0 : Spring 522 : Actuating oil inlet 524 : Actuating oil outlet 526 : Control oil inlet 530 : Maximum tilt angle adjustment stopper 5 3 1 __ Minimum tilt angle adjustment stopper 540: 1st adjustment screw 541: 2nd adjustment screw - 45 -