201202538 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種根據申請專利範園第1項引文部分所述之 關門器。 【先前技術】 大多時候，彈簧-液壓操作之關門器用於控制門系統之關閉。 在手動開門操作時，關門器轴經—臂組件旋轉，而累積能量之彈 簧經由一關門器中之驅動器受到預力負載。 關閉操作時，累積能量之彈簧釋放，且經由關門器之驅動器 及臂組件，無需外加能量，將門推回其零點位置。 為使此操作不致突然且非常快速進行，於關門器中，整個能 量累積器之彈簧力幾乎全部被—液壓阻尼器吸收。關閉操作時， 作為活塞表面之一功能，與彈簧力對應之液壓於阻尼器壓力媒體 室内建立，此壓力使力系統幾乎保持平衡狀態。 一受控之低量液體回流由壓力室進入關門器之一儲液空間， 觉一調節閥調節。其間產生一微小之力量比例不平衡，使門在彈 簧力作用下’相對緩慢關閉。 僅使用一調節閥，就可能由任何門角度，對整個關門程序調 整出唯一不變之關門速度，直至門抵達關閉位置。使門抵達關閉 位置時，不會過於撞擊門框上之門座，整個關閉程序需於受控情 況下進行。 根據門系統之材質、結構與密封元件，若過於快速關閉，門 將由門框彈回，並局部打開。因而，可能發生擺動，直至門抵達 完全休止位置。 然而，為避免上述效應，將關閉速度調慢，則缺點係，由較 寬開門角度起算，全部關閉操作需時甚久，浪費時間。高度使用 201202538 之門，此時間設定非常重要，因為，經常門板不再完全回到零點 位置。此外，若室外低溫，關閉時間長有不利影響，因為損失較 多熱能。 特別係在电梯系統上，各樓層之門每增加一秒關閉時間，都 將導致各樓層使用者等待時間加長，係由於電梯車廂僅在門完全 關閉後才離開。特別在此應用例中，不可能單純提高關閉速度， 其技術理由為：電梯門配有限制開關，及關閉位置之自動門栓， 門板由於太過快速關閉而彈回，將極度干擾控制程序，且造成整 個系統作動不良。 唯有一第二關閉減速區可解決此問題，在此解決方案中，門 速在即將到達零點位置時，大幅減速，使門最終能緩慢關閉。此 第二關閉減速區可用其自身之調節閥調整。因而可將第一減速區 碉成相當快速，明確縮短全部關閉操作。 習知之關門器上，整個液壓關閉操作劃分成二或多個區，不 同速度區係藉由在阻尼活塞或煞車活塞，於其表面設置不同之排 油孔貫現。根據活塞位置對應一門角度，在壓力室之排放通道經 由活塞邊緣打開或關閉。在進一步作法中，排放通道設有不同設 定之調節閥，容許調節不同門速。 然而，此類習知關門器中，缺點在於，此極簡單之控制方法 僅適合阻尼活塞之流體位移容量夠大，因而僅適合較大關門器， 或較大驅動裝置。小型關門器，由於其工作位移低，以及其活塞 面較小，特別以凸輪技術，並不具有足夠位移容積。由於公差， 在缸體與阻尼活塞間無法避免存在或多或少之間隙，流體可能以 無法控制之方式洩漏。 条·於門之關閉操作中’壓力室中一排放通道關閉，或因操作， 在工作行程中被阻尼活塞打開，一定容積之洩漏液體以不受控制 6 201202538 之方式經由活塞及缸壁間之間隙排流。液壓液體始終試圖流向壓 力較低之關門器之儲液空間。此洩漏液體使液壓功能無法確定速 度區之開始與結束之角度。 大型關門器具有較高之單位門角度流體位移容積，此效應僅 有相對較小之影響，然而設計成極小型之關門器具有很小之液體 容積’若干液壓功能將由於上述問題而失效。 在缸壁上設置排油孔之控制方法另一缺點在於，大多時候， 在阻尼活塞上無密封環可用，此係由於密封環通過排油孔時，很 快就損壞。能允許通過排油孔之密封設計極少。然而，此類特殊 密封需要大組件尺寸，此於很小之關門器中並不存在。 另一習知之控制關門速度之方法在於，使用一或多個控制 閥，位於關門器缸室之螺合之密封塞。根據門角度，並因而對應 阻尼活塞之移動位置’該些控制閥因與活塞前面機械性接觸，而 被打開。於此情況，一排放通道開放，其藉由一位於下游之可調 節之調節閥，控制液壓液體回流至關門器之儲液空間。控制閥藉 由適當強度之彈簧或一電磁單元，於阻尼室中對抗液壓，而保持 關閉。控制閥僅於與阻尼活塞機械性接觸時才打開。阻尼活塞之 位置，及因此之切換點，分別對應一定之門開放角度。在阻尼活 塞之其餘行程中’控制閥必須隨行（come along as well)，由接觸 點開始’至門之零點位置，且對應鑽入螺合之密封塞。 然而，此類門關閉機構之缺點在於，門之速度僅能由慢調快。 當控制閥多打開一排油孔’即多產生一些節流開口，使關門速度 加快。由於控制閥進入螺合之密封塞，後者尺寸必須相對較寬， 配合活塞之其餘行程。此情況增加整個關門器構造長度。 此外，關門器設有一空心管，將排流控制於液壓保持打開之 功能。於此狀況，空心管殼體固定於側邊螺合之密封塞之一，位 201202538 於了定義之停止處’進人活塞之—旋轉密封環。液壓液體流經空 管至磁閥。當磁閥供能後，液壓液體無法流回關門器之儲 液2間’產生—保持打開之功能。 於門<打開操作中，空心管壓力較少進入活塞之旋轉密封 °，於打開操作結束後，累積能量之彈普才試圖釋放，液壓於 是建立。然而’此_門器之操作壓力相對較低，且具有相對較 高之流體容積。 、=括而言，必須注意，所述之已知關門器先前技術中之控制 方案皆不適合具有高工作壓力之很小關HU，係由於漏損嚴重， 而彈菁力太低’無法可靠保持控制閥關閉。 【發明内容】 因而，本發明之目的在於提出一種申請專利範圍第1項引文 所述類型之關門器，該關門器即使尺寸甚小，且工作壓力甚高， 亦可控制關門動作，由初始快速關閉，至-受控下之緩慢關^ 本發明之目的係藉由申請專利範圍第1項之特徵而達成。 、:關閉中之Η ’依其重量、門寬及關閉速度，具有相對甚高 之質量慣性，在即將把達關閉位置之前，必須完成重要之減速， 以降低門讀量。其間，阻尼器之壓力室巾之液壓上升，並迅速 卓升至甚高之壓力水準。 小型關HU ’由於活絲面小，其阻尼缸縣就基本處於高 壓力水準。此外，由於工作行程短，僅有極小之位移容積可用。 因而必須極為精確控制轉換至第二減速區，而不發生無法控 制之漏損。 … 。本發明之關門器完全符合該些功能要求，設於第一及快速減 速區之回流通道可以精密角度關閉，且絕對密合，在慢速關門運 動中，被阻尼活塞移動之液壓液體僅能經第二排放通道流回儲液 8 201202538 防止其 η因而產生足夠高之阻尼壓力，確保門充分被遲滞， 過於快速回到零點位置。 本發明之進—步有利發展說明於巾請專利侧附屬項。 特別係，將一延伸部，可為一桿，置於阻尼活塞，可造成一 切換點，該切換點取決於η角度，及取決於行程位置。 〃藉由肖④、封元件合作之延伸部，可在-特定位置實現完全 無淺漏之密封。因而，此配置同樣適合具有低液體位移（液ς容 積）之最小關門器系統。 快速閥區之立即與完全密封防止任何過衝及滑動。 έ、本發明之關門器完全無洩漏，此為在具有極少液體位移之系 統，’在阻尼巾快速建讀力之—主要先決條件。本發明之關 門器有利達成此條件，例如，容許於門系統接近零點位 力減速。 為達成由快至慢轉換中之速度遲滯，調節閥較佳設置為，二 凋節閥於速度區之切換點前平行打開，亦即於快速關閉速度區平 仃打開。而由切換點開始，液壓液體僅能經由慢速調節閥，由阻 尼缸之壓力室排出。 【實施方式】 圖1顯示本發明之關門器1，設有一殼體6。一驅動器20位 於殼體6内，該驅動器可經由一關門器軸19及一臂組件18與圖 中未詳細顯示之門聯結。驅動器20以設計成一凸輪驅動器為佳， 具有一凸輪盤29,以抗扭方式設於關門器軸19上，並具有兩滚子 30及31 ’滾子抵緊凸輪盤29。於此例中，滾子3〇被支持於阻尼 活塞24上’而滾子31位於一驅動活塞32，驅動活塞在操作上與 一能量蓄積彈簧21連接，彈簧則位於殼體6内。 此外’關門器1具一液壓阻尼器23。此阻尼器位於殼體6内， 201202538 包含被導引於—阻尼缸5内之阻尼活塞24。如上說明，阻尼活塞 24與驅動器2〇於操作上連接。 此外，阻尼器23具有一第一液體排放通道9，提供門之快速 關閉動作，及一第二液體排放通道14，提供門之慢速關閉動作。 根據本發明，由阻尼活塞24之移動方向R觀之，第一液體排放通 道9位於第二液體排放通道14後方。 在圖1及圖2所示之關門器！之實施例中，阻尼活塞24設有 一矛式延伸部2，其於阻尼活塞24關閉方向R延伸。在所示之實 施例中，延伸部2係透過一特殊安全閥單元3實施，該閥單元被 納入阻尼活塞24。然而，延伸部2之基本功能及基本構造可藉由 一位於阻尼活塞24之簡單直桿，或阻尼活塞之延伸，而達到: 在圖1與圖2所示之較佳實施例中，延伸部2設有—中心倒 角26。 一具有密封環8之密封元件7插入關門器殼體6内阻尼缸5 一螺合之街封塞4之空心室9’内。 啕不同$又彳万式，及由不同材料製成，且同樣可 實施成不同輪靡。在所示之實施例中，密封環8為—〇形卢 由另-較小之螺合之密封塞16，空心室9,被以液 $ ° ^ 1之外界環境隔絕。 由圖1及圖2可看出，液壓液體之排放通道9設於螺 封塞4,接續密封元件7，此通道通人—環狀通道⑺。。在 環狀通道U)通往—調節閥12，該調節射藉適當調 = 13通回關門器 通過調節閥12,在關門器殼體6中一回流通道 1之一低塾儲液空間17。 一調節閥15,該 排放通道14直接由阻尼缸5之壓力室通至另 201202538 閥可藉適當調節，使門慢速關閉。 此外，如圖1至圖3所示，在所示之實施例中，密封元件7 由二桶狀結構之半部41、42組成，兩半部可直接互相聯結。在所 示之實施例中，兩半部41及42互相螺合，且於圖2及圖3所示 之狀況下’兩半部限定出一内部容受室43。 一壓縮彈簧22位於内部容受室43内，抵住密封元件7，一端 指向殼體端部25。在另一端，壓縮彈簧22抵住一彈簧蓋33，該 彈簧蓋亦係位於容受室43内，且可於操作上與延伸部2連接。 另一壓縮彈簧27位於密封元件7外圍，此彈簧一端抵住螺合 之密封塞4，及抵住於其中之較小之螺合之密封塞16。另一端， 壓縮彈簧27抵住密封元件7之一定位肩部44。 在圖1至圖3所示之實施例中，壓縮彈簧22之彈簧係數大於 第二壓縮彈簧27之彈簧係數。 此外，一第二壓縮彈簧34位於阻尼活塞24與螺合之密封塞4 之間。 圖1至圖3進一步顯示，接續第二調節閥15，液體經由位於 關門器殼體6内之回流通道13，排流進入儲液空間17。 以下將說明上述關門器1之功能順序。 手動打開門時，一扭力經由臂組件18施加至關門器軸19。藉 驅動器2G之助，旋轉運動可產生—往復運動，使能量累積彈菁21 受到預力負載。 同時’阻尼活塞24連同延伸部2朝關門器轴19方向前進， 液壓液體可經由-孔及阻尼活塞中之—單向閥門流動，由關門器i 之儲液2間17進入壓力室，及阻尼知5。 當門被釋放後’能量累積彈簧21試圖放鬆，經由關門器β 驅動器2〇，將關門所需之扭力引入關門器轴19。為防止此操作摔 201202538 然發生’經由另-將關Η器軸19旋轉運動重新導向至阻尼活 之一往復運動，液壓反壓力於阻尼缸5中建立。 / 由於門之較寬打開角度，例如乃。，用ς達到舒適之出 件，-旦門被釋放，阻尼活塞24係位於接近關門器轴19處。位 於阻尼活塞24之延伸邵2完全離開密封元件7。 在關門操作中，阻尼活塞24再度接近於殼體端部Μ螺人之 密封塞4。阻尼活塞24之位置對應於延伸部2讀料件 觸點。密封元件7仍然打開。 # 在此例中，在關Π操作巾餘尼活塞24移動之祕液體可流 經於螺合之密封塞4中-傾斜孔28，進入螺合之密封塞4之办心 室 9,。 二 在與活塞延伸部2接觸前’密封元件7被壓縮彈菁27推壓， 離開較小之螺合之密封塞16之密封座，且被保持於—打開位置。 在關門操作巾，被阻尼活塞24推轉力室5之_，在密封 座打開情況下，不受阻擋地經由其他排油孔9、1〇及u，由空心 室9’流入殼體6。接著，液體流至快速調節之調節閥12。接^， 更多液體排流，經由回流孔13進入關門器丨儲液空間17。使門可 相對快速關閉。 在啟動第一關閉速度上，根據設計，位於阻尼活塞24之延伸 部2之長度配合所希望之切換點，亦即所希望之門角度。 當抵達此門角度，延伸部2起初壓緊位於密封元件7後側之 彈簧蓋33。彈簧蓋33本身被密封元件7内部之壓縮彈簧22墨迫， 抵緊密封元件7之一界緣，該壓縮彈簧之彈簧係數大於外圍彈簧 27之彈簧係數。 在阻尼活塞24繼續之關閉行程中，由於彈簧係數不同，位於 法、封元件7上之外圍彈簽27先被壓縮，整個密封元件7被推入内 12 201202538 部螺合之密封塞16之密封座8,。通往快速調節之調節閥12之排 放通道9被突然關閉，且毫無洩漏。 液壓液體因而僅能經由第二排放通道14，排放至慢速調節之 調節閥15，第二排放通道係額外設於阻尼活塞5中。因而，瞬間 建立非常高之壓力，門受到顯著減速，缓慢進入零點位置。 由於壓力增加’密封元件7更加被壓入密封座8,。密封座8, 代表密封元件7之一固定位置界限。 其係為何阻尼活塞24剩餘行程，由切換角度至門之零點位 置，被密封元件7内之壓縮彈簧22補償。在此情況中，密封座8, 保持連續關閉。 由於壓縮彈簧22之高彈簧係數，只有在抵達密封位置，才發 生明顯之彈簧壓縮。因而達到一種程序控制，首先密封座8，被密 封疋件7關閉，之後才允許補償活塞其餘行程長度。因此，長度 補償完全於密封元件7内，目而容許極為精簡之構造。 …以下將根據圖4說明本發明第二實施例。與圖1至圖3一致 之元件採用相同數字代表。因而，仍可參考上述說明。 在圖4所示之實施例中，延伸部2設計成一導引套筒％，與 、尼活塞24連接。在所示之實施例中，導引套筒％係螺入陳尼 活塞24。 在此實施例巾’料元件7位於導引套筒％之—内部容室 5。在此例中，密封元件7被壓縮彈簧乂施加預力，抵緊導幻套 筒35f接觸端40 ’該接觸端位於殼體末端25。 密封元^ 7具有—前端平面之料面*，可在殼體侧抵緊〆 h面】*所717之實施例中，密封面8,位絲小之螺合密封塞 16，該岔封塞螺入較大之螺合密封塞4。 卜圖4之顯示說明二個密封環％和％之配置位於 13 201202538 較大之螺合密封塞4與殼體6間，以及介於螺合之密封塞16與螺 合之密封塞4之間。 在此實施例中，密封元件7位於螺合之密封塞16，包含長度 補償之密封元件7可位於此例中之阻尼活塞24内，以及位於導引 套筒35中。 密封元件7被壓縮彈簧36壓緊在導引套筒35之接觸端4〇 上’壓縮彈簧係額外位於導引套筒35中，並在阻尼活塞24整個 工作行程中移動。 在此例中，納入之壓縮彈簧36之作用在於對阻尼活塞24剩 餘行程做長度補償’該剩餘行程係由滅速區之切換點至門之零 點。此外，壓縮彈簧36確保密封座8,始終受壓關閉，直至門抵達 Φ ®L gs 令那权置。 上述之所有實施例共同點在於，在一確定減速區之切換點， 密封元件7 —定進入一位於螺合之密封塞4或16中之密封座8,， 並關閉一緊隨之排油孔’及分別關閉一通往快速調節之調節閥12。 於此例中，密封座8,可直接位於主螺合之密封塞4中，或位 於其他較小之螺合之密封塞16中，後者位於前者之中。 當使用其他内邵分別較小之螺合之密封塞16時，密封座位 置，及因而減速區之切換點，變成可調。 f關閉密封座8’後，產生顯著壓力升高，t加推動密封元件7 進入密封座8’ ’並確保無麟條件。在後續之_操作上，液壓 液體需經慢速觸之調㈣15’流回儲液空間17，其造成慢速關 【圖式簡單說明】 所附圖式所作之說明中 本發明其他細節、特徵及優點於以下根據 將變得清楚，圖中所示為： 201202538 圖1 為本發明之關門器一縱向截面圖， 圖2 為圖1中關門器之一對應放大視圖，顯示阻尼器，為簡化圖示， 關門器殼體未繪出， ' 圖3 為與圖2對應之視圖，顯示門快速關閉時，排放通道關閉之情 形，及 圖4 為與圖3對應之視圖，為本發明關門器之一第二實施例。 【主要元件符號說明】 1 關門器 2 延伸部（桿） 3 安全閥單元 4 螺合之密封塞 5 阻尼缸 • 6 關門器殼體 7 密封元件 8 密封環（0形環） 8’ 密封座 9 排放通道，用於快速打開 9’ 空心室 10 環狀通道 11 孔 12 調節閥，用於快速打開 . 13 排放通道 14 排放通道，用於慢速打開 15 調節閥，用於慢速打開 16 第二較小之螺合之密封塞 17 儲液空間 15 201202538 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 臂組件 關門器軸 驅動器 能量蓄積彈簧 硬彈簧 阻尼器 阻尼活塞 殼體端部 倒角 壓縮彈簧 斜孔 凸輪盤 滚子 滚子 驅動活塞 彈簧蓋 第三壓縮彈簧，位於螺合之密封塞4與阻尼活 塞24之間 導引套筒 壓縮彈簧 密封環 密封環 密封環 接觸端 半部 半部 16 201202538201202538 VI. Description of the Invention: [Technical Field of the Invention] The present invention relates to a door closer according to the citation portion of the first application of the Patent Application. [Prior Art] Most of the time, a spring-hydraulic operated door closer is used to control the closing of the door system. In a manual door opening operation, the door closer shaft is rotated by the arm assembly, and the accumulated energy spring is subjected to a preload by a driver in a door closer. When the operation is turned off, the accumulated energy spring is released, and the actuator and arm assembly through the door closer push the door back to its zero position without additional energy. In order to prevent this operation from happening suddenly and very quickly, in the door closer, the spring force of the entire energy accumulator is almost completely absorbed by the hydraulic damper. When the operation is turned off, as a function of the piston surface, the hydraulic pressure corresponding to the spring force is established in the damper pressure medium chamber, and the pressure causes the force system to be almost balanced. A controlled low volume of liquid returning from the pressure chamber into one of the reservoirs of the door closer is sensed by a regulating valve. In the meantime, a slight imbalance in the force is produced, causing the door to close relatively slowly under the action of the spring force. With only one regulating valve, it is possible to adjust the entire closing speed of the entire closing procedure from any door angle until the door reaches the closed position. When the door is brought to the closed position, it does not hit the door seat on the door frame too much, and the entire closing procedure needs to be carried out under controlled conditions. According to the material, structure and sealing components of the door system, if it is closed too quickly, the door will be bounced back by the door frame and partially opened. Thus, a swing may occur until the door reaches the fully rest position. However, in order to avoid the above effects, the shutdown speed is slowed down, and the disadvantage is that from the wide opening angle, all the closing operations take a long time and waste time. The height is used at the gate of 201202538. This time setting is very important because the door panel is no longer fully returned to the zero position. In addition, if the outdoor temperature is low, the shutdown time has a long-term adverse effect because more heat is lost. In particular, in the elevator system, every one second of the closing time of each floor door will cause the waiting time of the users on each floor to be lengthened because the elevator car leaves only after the door is completely closed. Especially in this application example, it is impossible to simply increase the closing speed. The technical reason is that the elevator door is equipped with a limit switch and an automatic door latch in the closed position, and the door panel rebounds due to too fast closing, which will extremely interfere with the control program. And caused the entire system to malfunction. Only a second closing deceleration zone can solve this problem. In this solution, the door speed decelerates sharply when it reaches the zero position, so that the door can finally close slowly. This second closing deceleration zone can be adjusted with its own regulating valve. Thus, the first deceleration zone can be made relatively fast, and all closing operations are clearly shortened. In the conventional door closer, the entire hydraulic closing operation is divided into two or more zones, and different speed zones are formed by different damping holes on the surface of the damping piston or the brake piston. The discharge passage in the pressure chamber is opened or closed by the edge of the piston depending on the position of the piston corresponding to a door angle. In a further practice, the discharge passage is provided with differently arranged regulating valves allowing adjustment of different door speeds. However, a disadvantage of such conventional door closers is that this extremely simple control method is only suitable for damping pistons with a fluid displacement capacity that is large enough to be suitable only for larger door closers or larger drives. Small door closers do not have sufficient displacement volume due to their low working displacement and small piston surface, especially with cam technology. Due to tolerances, there is no more or less gap between the cylinder and the damping piston, and the fluid may leak in an uncontrollable manner. In the closing operation of the door, a discharge passage in the pressure chamber is closed, or due to the operation, the damping piston is opened during the working stroke, and a certain volume of leakage liquid is passed between the piston and the cylinder wall in a manner uncontrolled 6 201202538 The gap is drained. The hydraulic fluid always tries to flow to the reservoir space of the lower pressure gate closer. This leaking liquid prevents the hydraulic function from determining the angle of the start and end of the speed zone. Large door closers have a higher unit door angle fluid displacement volume, which has only a relatively small effect, whereas a very small door closer is designed with a small liquid volume. Several hydraulic functions will fail due to the above problems. Another disadvantage of the control method of providing the oil drain hole in the cylinder wall is that, most of the time, no seal ring is available on the damping piston, which is quickly damaged by the seal ring passing through the oil drain hole. There are very few seal designs that allow the passage through the drain hole. However, such special seals require large component sizes, which are not present in very small door closers. Another conventional method of controlling the closing speed is to use one or more control valves, a sealing plug located in the cylinder of the door closer. Depending on the angle of the door, and thus the position of the displacement of the damping piston, the control valves are opened by mechanical contact with the front of the piston. In this case, a discharge passage is opened, which controls the return of the hydraulic fluid to the liquid storage space of the door closer by means of an adjustable regulating valve located downstream. The control valve is held closed by a suitable strength spring or an electromagnetic unit against the hydraulic pressure in the damper chamber. The control valve opens only when it is in mechanical contact with the damping piston. The position of the damping piston, and hence the switching point, corresponds to a certain door opening angle. In the remaining strokes of the damping piston, the 'control valve must follow along well, starting from the point of contact' to the zero position of the door, and corresponding to the sealing plug that is screwed into the screw. However, a disadvantage of such door closing mechanisms is that the speed of the door can only be slowed down by slow speed. When the control valve opens more than one row of oil holes, more throttle openings are generated, which speeds up the closing speed. Since the control valve enters the screwed sealing plug, the latter must be relatively wide in size to match the rest of the piston. This condition increases the overall length of the door closer construction. In addition, the door closer is provided with a hollow tube that controls the discharge to maintain the hydraulic pressure. In this case, the hollow tube housing is fixed to one of the sealing plugs that are screwed to the side, and the position of the piston is rotated at the defined stop position 201202538. The hydraulic fluid flows through the air tube to the magnetic valve. When the magnetic valve is energized, the hydraulic fluid cannot flow back to the reservoir 2 of the door closer to produce a function that remains open. In the door opening operation, the hollow tube pressure is less likely to enter the rotary seal of the piston. After the opening operation, the accumulated energy is attempted to release, and the hydraulic pressure is established. However, the operating pressure of the door is relatively low and has a relatively high fluid volume. In addition, it must be noted that the known door closers of the prior art are not suitable for the HU with high working pressure, because the leakage is serious, and the elasticity is too low to be reliably maintained. The control valve is closed. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a door closer of the type described in the first application of the patent application. The door closer can control the door closing action even if the size is very small and the working pressure is very high. Shutdown, to - controlled slowdown ^ The object of the present invention is achieved by the features of claim 1 of the patent scope. ,: Close the middle Η Depending on its weight, door width and closing speed, it has a relatively high mass inertia. Before the closing position is reached, important deceleration must be completed to reduce the door reading. In the meantime, the hydraulic pressure of the pressure damper of the damper rises and rapidly rises to a very high pressure level. The small shut-off HU ’ is basically at a high pressure level due to its small live surface. In addition, due to the short working stroke, only a very small displacement volume is available. Therefore, it is necessary to control the conversion to the second deceleration zone with extremely precise control without uncontrollable leakage. ... . The door closer of the invention fully meets the functional requirements, and the return passages provided in the first and rapid deceleration zones can be closed at a precise angle and are absolutely close. In the slow closing movement, the hydraulic fluid moved by the damping piston can only pass through The second discharge channel flows back to the reservoir 8 201202538 to prevent its η from producing a sufficiently high damping pressure, ensuring that the door is fully retarded and returns to the zero position too quickly. The advantageous development of the present invention is described in the patent side attachment of the towel. In particular, an extension, which can be a rod, is placed in the damping piston to create a switching point that depends on the angle of the η and on the position of the stroke. 〃With the extension of the cooperation of the shovel 4 and the sealing element, a complete leak-free seal can be realized at a specific position. Thus, this configuration is equally suitable for a minimum door closer system with low liquid displacement (liquid helium volume). Immediate and complete sealing of the quick valve zone prevents any overshoot and slippage. έ, the door closer of the present invention is completely leak-free, which is a major prerequisite for a system with minimal liquid displacement, 'fast reading force on the damper towel. The door closer of the present invention advantageously achieves this condition, for example, allowing the door system to decelerate near zero. In order to achieve a speed lag in the fast-to-slow transition, the regulating valve is preferably arranged such that the two-way valve opens in parallel before the switching point of the speed zone, that is, in the fast closing speed zone. Starting from the switching point, the hydraulic fluid can only be discharged through the pressure chamber of the damper via the slow regulating valve. [Embodiment] FIG. 1 shows a door closer 1 of the present invention, which is provided with a casing 6. A driver 20 is located within the housing 6 and is coupled to a door (not shown in detail) via a door closer shaft 19 and an arm assembly 18. Preferably, the driver 20 is designed as a cam driver having a cam plate 29 that is disposed in a torque-proof manner on the door closer shaft 19 and has two rollers 30 and 31' rollers that abut the cam plate 29. In this example, the roller 3 is supported on the damper piston 24 and the roller 31 is located in a drive piston 32 which is operatively coupled to an energy accumulating spring 21 which is located within the housing 6. Further, the door closer 1 has a hydraulic damper 23. The damper is located within the housing 6, and 201202538 includes a damper piston 24 that is guided within the damper cylinder 5. As explained above, the damper piston 24 is operatively coupled to the driver 2. Further, the damper 23 has a first liquid discharge passage 9 which provides a quick closing action of the door, and a second liquid discharge passage 14 which provides a slow closing action of the door. According to the present invention, the first liquid discharge passage 9 is located behind the second liquid discharge passage 14 by the moving direction R of the damper piston 24. The door closer shown in Figures 1 and 2! In the embodiment, the damper piston 24 is provided with a spear-type extension 2 which extends in the closing direction R of the damper piston 24. In the illustrated embodiment, the extension 2 is implemented by a special safety valve unit 3 which is incorporated into the damping piston 24. However, the basic function and basic construction of the extension 2 can be achieved by a simple straight rod located in the damping piston 24, or an extension of the damping piston: In the preferred embodiment shown in Figures 1 and 2, the extension 2 has a center chamfer 26. A sealing element 7 having a sealing ring 8 is inserted into the hollow chamber 9' of the damper cylinder 5 in the door closer housing 6 which is screwed into the street plug 4.啕 Different from $ 10,000 and made of different materials, and can also be implemented as different rims. In the illustrated embodiment, the seal ring 8 is a 〇-shaped seal from the other-smaller-sealed seal plug 16, and the hollow chamber 9 is isolated from the environment of the liquid $ ° ^ 1 . As can be seen from Figures 1 and 2, the discharge passage 9 of the hydraulic fluid is provided in the screw plug 4, which is connected to the sealing member 7, which passage leads to the annular passage (7). . In the annular passage U), there is provided a control valve 12 which is adjusted to the appropriate position. 13 is passed back to the door closer. By means of the regulating valve 12, one of the return channels 1 in the door closer housing 6 is lowered below the reservoir space 17. A regulating valve 15, the discharge passage 14 is directly connected from the pressure chamber of the damper cylinder 5 to the other 201202538 valve, so that the door can be slowly closed. Further, as shown in Figs. 1 to 3, in the illustrated embodiment, the sealing member 7 is composed of the half portions 41, 42 of the two barrel structures, and the two halves can be directly coupled to each other. In the illustrated embodiment, the two halves 41 and 42 are screwed together and, in the condition shown in Figures 2 and 3, the two halves define an interior receiving chamber 43. A compression spring 22 is located within the interior receiving chamber 43 against the sealing member 7 with one end directed toward the housing end 25. At the other end, the compression spring 22 abuts against a spring cover 33 which is also located within the receiving chamber 43 and is operatively connectable to the extension 2. Another compression spring 27 is located on the periphery of the sealing member 7, one end of the spring against the screwed sealing plug 4, and a smaller screwed sealing plug 16 against it. At the other end, the compression spring 27 abuts against the positioning shoulder 44 of one of the sealing elements 7. In the embodiment shown in Figures 1 through 3, the spring rate of the compression spring 22 is greater than the spring rate of the second compression spring 27. Furthermore, a second compression spring 34 is located between the damping piston 24 and the screwed sealing plug 4. 1 to 3 further show that, following the second regulating valve 15, the liquid is discharged into the liquid storage space 17 via the return passage 13 located in the door closer housing 6. The functional sequence of the above-described door closer 1 will be described below. When the door is manually opened, a torque is applied to the door closer shaft 19 via the arm assembly 18. With the help of the driver 2G, the rotary motion produces a reciprocating motion that causes the energy accumulation of the elastomer 21 to be subjected to a preload. At the same time, the 'damper piston 24 along with the extension 2 is advanced toward the door closer axis 19, and the hydraulic fluid can flow through the - hole and the damping piston - the one-way valve, from the reservoir 17 of the door closer i into the pressure chamber, and the damping Know 5. When the door is released, the energy accumulating spring 21 attempts to relax, and the torque required to close the door is introduced into the closer shaft 19 via the door closer β driver 2〇. In order to prevent this operation from falling, 201202538, the hydraulic back pressure is established in the damper cylinder 5 by re-directing the rotary motion of the brake shaft 19 to the damper movement. / Due to the wide opening angle of the door, for example. To achieve a comfortable release, the damping piston 24 is located close to the door closer shaft 19 when the door is released. The extension 2 of the damping piston 24 completely leaves the sealing element 7. In the door closing operation, the damping piston 24 is again approached to the sealing plug 4 of the end of the housing. The position of the damping piston 24 corresponds to the extension 2 read material contact. The sealing element 7 is still open. # In this example, the liquid that moves in the operation of the towel, the piston 24, can flow through the screwed sealing plug 4, the inclined hole 28, into the chamber 9 of the screwed sealing plug 4. Second, before the contact with the piston extension 2, the sealing member 7 is pressed by the compressed elastomer 27 away from the sealing seat of the smaller screwed sealing plug 16 and held in the -open position. In the door closing operation wiper, the damper piston 24 is pushed by the damper chamber 5, and when the seal seat is opened, the casing 6 is flown from the hollow chamber 9' via the other oil drain holes 9, 1 〇 and u without being blocked. The liquid then flows to the rapidly regulated regulating valve 12. Then, more liquid is drained, and enters the door closer 丨 liquid storage space 17 through the return hole 13 . The door can be closed relatively quickly. At the start of the first closing speed, depending on the design, the length of the extension 2 at the damping piston 24 matches the desired switching point, i.e., the desired door angle. When this door angle is reached, the extension 2 initially compresses the spring cover 33 on the rear side of the sealing member 7. The spring cover 33 itself is forced by the compression spring 22 inside the sealing member 7 against a boundary edge of the sealing member 7, the spring coefficient of which is greater than the spring rate of the peripheral spring 27. During the closing stroke of the damping piston 24, due to the different spring coefficients, the peripheral latch 27 on the sealing element 7 is first compressed, and the entire sealing element 7 is pushed into the inner seal 12 201202538. Block 8,. The discharge passage 9 leading to the quick-adjustment regulating valve 12 is suddenly closed and there is no leakage. The hydraulic fluid can thus only be discharged via the second discharge passage 14 to the retarding regulating valve 15, which is additionally provided in the damping piston 5. As a result, a very high pressure is established instantaneously, and the door is significantly decelerated and slowly enters the zero position. The sealing member 7 is more pressed into the sealing seat 8 due to the pressure increase. The sealing seat 8, representing a fixed positional limit of one of the sealing elements 7. It is why the remaining stroke of the damping piston 24 is compensated by the compression spring 22 in the sealing member 7 from the switching angle to the zero position of the door. In this case, the sealing seat 8 is kept closed continuously. Due to the high spring rate of the compression spring 22, significant spring compression occurs only when the sealing position is reached. Thus, a program control is achieved in which the seat 8 is first sealed and closed by the sealing element 7, after which the remaining stroke length of the piston is allowed to be compensated. Therefore, the length compensation is completely within the sealing member 7, and the configuration is extremely simplified. The second embodiment of the present invention will be described below with reference to FIG. Elements consistent with Figures 1 through 3 are represented by the same numerals. Therefore, reference is still made to the above description. In the embodiment shown in Figure 4, the extension 2 is designed as a guide sleeve % for connection to the piston 212. In the illustrated embodiment, the guide sleeve % is threaded into the Chenni piston 24. In this embodiment, the material member 7 is located at the inner portion 5 of the guide sleeve. In this case, the sealing member 7 is biased by the compression spring , to abut the contact end 40' of the guide sleeve 35f. The contact end is located at the end 25 of the housing. The sealing element has a material plane* of the front end surface, which can be abutted on the side of the casing 】h surface*717, in the embodiment, the sealing surface 8, the small wire screw sealing plug 16, the tamping Screw into the larger screw seal plug 4. The display of Fig. 4 shows that the arrangement of the two sealing rings % and % is located between 13 201202538 between the larger screw sealing plug 4 and the housing 6, and between the screwed sealing plug 16 and the screwed sealing plug 4. . In this embodiment, the sealing element 7 is located in a threaded sealing plug 16, and the length-compensating sealing element 7 can be located within the damping piston 24 in this example, as well as in the guiding sleeve 35. The sealing element 7 is pressed by the compression spring 36 against the contact end 4 of the guiding sleeve 35. The compression spring is additionally located in the guiding sleeve 35 and moves over the entire working stroke of the damping piston 24. In this example, the incorporated compression spring 36 functions to compensate for the remaining stroke of the damping piston 24. The remaining stroke is from the switching point of the deceleration zone to the zero of the door. In addition, the compression spring 36 ensures that the sealing seat 8 is always closed by pressure until the door reaches Φ ® L gs to force that. Common to all of the above embodiments is that, at a switching point for determining the deceleration zone, the sealing member 7 is intended to enter a sealing seat 8 in the screwed sealing plug 4 or 16 and close the tight oil drain hole. 'And close a regulating valve 12 to the quick adjustment. In this case, the sealing seat 8 can be located directly in the main screwed sealing plug 4 or in other smaller screwed sealing plugs 16, the latter being located in the former. When other internally sealed plugs 16 of smaller inner shafts are used, the sealing seat, and thus the switching point of the deceleration zone, becomes adjustable. f After closing the sealing seat 8', a significant pressure rise is produced, t plus pushing the sealing element 7 into the sealing seat 8'' and ensuring no lining conditions. In the subsequent operation, the hydraulic fluid needs to be transferred to the liquid storage space 17 through the slow touch (4) 15', which causes the slow speed off. [Simple Description of the Drawings] Other details and features of the present invention in the description of the drawings And the advantages will be apparent from the following, which is shown in the figure: 201202538 Figure 1 is a longitudinal sectional view of the door closer of the present invention, and Figure 2 is a corresponding enlarged view of one of the door closing devices of Figure 1, showing the damper for simplification As shown in the figure, the door closer housing is not shown, 'Figure 3 is a view corresponding to Figure 2, showing the case where the discharge passage is closed when the door is quickly closed, and Figure 4 is a view corresponding to Figure 3, which is the door closer of the present invention. A second embodiment. [Main component symbol description] 1 Door closer 2 Extension (rod) 3 Safety valve unit 4 Screwed sealing plug 5 Damping cylinder • 6 Door closer housing 7 Sealing element 8 Sealing ring (0-ring) 8' Sealing seat 9 Drainage channel for quick opening 9' hollow chamber 10 annular channel 11 hole 12 regulating valve for quick opening. 13 drain channel 14 drain channel for slow opening 15 regulating valve for slow opening 16 second Small screw seal plug 17 Storage space 15 201202538 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 Arm assembly door closer shaft drive energy accumulating spring hard spring Damper damping piston housing end chamfer compression spring oblique hole cam disc roller roller drive piston spring cover third compression spring, between the screw seal plug 4 and the damping piston 24 guide sleeve compression spring seal ring Seal ring seal ring contact end half half 16 201202538
43 44 45 46 R 容受室 定位肩部 内部容室 密封面 運動方向 1743 44 45 46 R Receiving chamber Positioning shoulder Inner chamber Sealing surface Direction of movement 17