593861 玖、發明說明 ^ ^ ^ ^ “ , (發明說明應敘明：發明所屬之技術領域、先前技術、內容、實施方式及圖式簡單說明） (一） 發明所屬技術領域： 本發明係有關用以減低由地震或風等之振動外力所造成 結構物（建築物、橋樑、屋頂等）搖晃之油壓減震器者。 (二） 先前技術： 在用以減低結構物搖晃之減震器形式的制震裝置中，係具 有使開閉控制閥之開度成爲全開和全閉之2階段控制的可 φ 變阻尼裝置（例如，日本專利特開平1 1 - 3 3 6 3 6 6號）等。 . 此種油壓減震器的基本構造係如第1 1圖所示，係由油壓 缸2、在油壓缸2內往復動之兩杆型的活塞3、和設置在活 塞3之兩側的油壓室4、4、以及設置在連接此兩油壓室的 流路5上之開閉控制閥6等等所構成，藉由來自控制器7之 控制電流的供給，使開閉控制閥（電磁閥）6作全閉和全開 之2段階開閉動作，可將油壓減震器1的阻尼係數2段階地 切換成最大値Cmax和最小値Cmin。 · 此種油壓減震器1係如第1 2圖所示，乃透過支架等之構 成造要素而被安裝在構造物之層間，所以包含有支架之裝置 部的力學特性係如第1 3圖所示之彈簧和緩衝筒爲串列結合 的Maxwell型模式所表示。 第1 1圖之裝置中，藉由將裝置的阻尼係數亦即將開閉控 制閥6的閥開度在振動之最大振幅點作切換，以執行如第1 4 圖所示之大能量吸收，可減低結構物之振動。第1 4圖的縱 一 6 - 軸係油壓減震器之負載L,橫軸係層間變形（Maxwell型模 式端部間變形）·，虛線係阻尼係數爲一定之習知型減震器 D0，實線係阻尼係數切換型減震器Di。又因爲僅以所謂的閥 開度C爲全閉或全開之兩端的2階段控制就可以，因此和使 閥開度連續可變控制的裝置（例如，日本專利特公平7 -45 7 8 1號）相較之下，係可使裝置的構造簡單。 然而，在前述之先前的裝置中，必然地，由於使用感測器或 控制器或電磁閥等等之電氣零件，所以不斷電電源裝置和特 別的電源配線係有其必要。又，電氣零件的一部分由於具有 必需定期地交換的物件，所以也會產生維護費用。 本發明係爲解決此種課題而成者，其目的爲提供一阻尼係 數切換型油壓減震器，係於可變阻尼型之油壓減震器中，在 不需要一切來自外部的能量供給下可將阻尼係數自動地切 換，可經常確實地發揮超越一般的油壓減震器之能量吸收能 力。 (三）發明內容： 本發明之第1樣態之阻尼係數切換型油壓減震器係具備 有，油壓缸、在此油壓缸內往復動之活塞、設置在此活塞的 兩側之油壓室、以及設置在接合此兩油壓室的流路且依開 閉以變化阻尼係數之開閉控制閥，其特徵係構成爲，相對於 活塞在一方向之移動，開閉控制閥係維持閉合狀態而可獲得 第1阻尼係數亦即最大値Cmax，當活塞之移動逆向變換時， 開閉控制閥係暫時開啓而獲得第2阻尼係數亦即最小値 Cm i η之後，開閉控制閥再度閉合而可獲得第1阻尼係數亦 -7- 593861 即最大値Cmax。 此第1樣態之阻尼係數切換型油壓減震器係本發明之基 本的構成，係使用藉油壓減震器之活塞的移動而作動之機械 式驅動手段（參照第1圖〜第4圖）或油壓式驅動手段（第 5圖〜第7圖參照）等方式以控制開閉控制閥，乃作成在不 需要一切來自外部的能量供給下可將油壓減震器的阻尼係 數以機械式手段或油壓予以直接切換者。開閉控制閥係使 用有例如第1圖所示之以開閉操作閥1 1作動之流量調整閥 1 0或單獨的開閉操作閥1 1等等。 本發明之第2樣態之阻尼係數切換型油壓減震器係係具 備有油壓缸、在此油壓缸內往復動之活塞、設置在此活塞 的兩側之油壓室、以及設置在接合此兩油壓室的流路且依 開閉以變化阻尼係數之開閉控制閥，其特徵爲，機械式驅動 手段係設置在活塞杆和開閉控制閥之間且構成爲，相對於活 塞之一方向的移動，開閉控制閥係維持閉合狀態以獲得第1 阻尼係數亦即最大値Cm a X ,而在活塞之移動逆向變換時，開 閉控制閥係暫時開啓而獲得第2阻尼係數亦即最小値Cm i η 之後，開閉控制閥再度閉合而可獲得第1阻尼係數亦即最大 値 C m a X 〇 此第2樣態之阻尼係數切換型油壓減震器係，使用如第2 圖或第4圖所示之機械式驅動手段之場合。例如在第2圖 中，使用僅在活塞3的移動方向變換時才藉活塞3作動之機 械式驅動手段3 0，在活塞3往A方向移動中，使機械式驅動 手段3 0不作動，事先閉合開閉操作閥1丨及流量調整閥！ 〇 一 8 - 以獲得第1阻尼係數亦即最大値Cmax。 在左側之最大振幅點當活塞3的移動方向往B方向變換 時，機械式驅動手段3 0係作動且藉由暫時開啓開閉操作閥 1 1使流量調整閥1 0係暫時開啓而使負載被卸除，以獲得第 2阻尼係數亦即最小値Cm i η。活塞3再往B方向移動時，以 機械式驅動手段3 0將開閉操作閥i 1及流量調整閥1 〇再度 閉合以回復至桌1阻尼係數亦即最大値C m a X。在右側之最 大振幅點也執行與前述同樣的作動，以上的動作係被反覆。 此外，流量調整閥1 0係使用在作動油的流量爲大之場合者， 在流量不大之場合，流量調整閥1 〇之開閉操作閥1 1可作爲 開閉控制閥單獨使用。 本發明之第3樣態之阻尼係數切換型油壓減震器係如第 2樣態之阻尼係數切換型油壓減震器，其中驅動開閉控制閥 之機械式驅動手段係由設置在油壓缸之活塞杆的直線齒 輪、及依此直線齒輪而作動以將開閉控制閥開閉之曲柄機 構所構成。 此第3樣態之阻尼係數切換型油壓減震器係，將機械式驅 動手段限定在第2圖、第4圖所示之構造的場合。若事先 使曲柄機構之前端側的第1連桿設定爲對直線齒輪後傾，則 對直線齒輪之一方向的移動係維持後傾姿勢，在直線齒輪變 換移動方向時，第1連桿係成直立狀態。 本發明之第4樣態之阻尼係數切換型油壓減震器係在第 2或第3樣態之阻尼係數切換型油壓減震器中，構成爲活塞 兩側之油壓室的壓力以1個開閉控制閥加以控制。 -9 - 此第4樣態之阻尼係數切換型油壓減震器係如第1圖所 示，開閉控制閥（流量調整閥1 0 )爲1個單閥型之場合。 相對於活塞3之A方向的移動，曲柄機構3 2係不作動，維持 開閉操作閥1 1和流量調整閥1 〇爲閉合狀態，在開始往B方 向移動時，曲柄機構3 2係作動且首先開閉操作閥1 1和流量 調整閥1 0係暫時開啓，然後，開閉操作閥1 1和流量調整閥 1 〇係再度回復至閉合狀態，相對於B方向的移動，由於曲柄 機構3 2不作動，此閉合狀態係被維持。 本發明之第5樣態之阻尼係數切換型油壓減震器係如第 2或第3樣態之阻尼係數切換型油壓減震器，其中構成爲以 各自獨立之開閉控制閥來控制活塞兩側之油壓室的壓力。 此第5樣態之阻尼係數切換型油壓減震器係如第3圖所 示，開閉控制閥（流量調整閥1 0 )爲2個雙閥型之場合。 乃使用僅在活塞3之移動方向變換時依活塞3作動的機械 式驅動手段3 0 ’，在活塞3往A方向移動中，因不使機械式 驅動手段3 0 ’作動，將開閉操作閥1 1閉合，且事先閉合左側 之流量調整閥10,以獲得第1阻尼係數亦即最大値Cmax。 在左側的最大振幅點當活塞3之移動方向往B方向變換時， 藉由以機械式驅動手段30’暫時開啓開閉操作閥1 1而暫時 開啓左側之流量調整閥1 0，使負載卸除而獲得第2阻尼係 數亦即最小値Cm i η。此時，右側之流量調整閥1 0 (開閉控 制閥）係由開啓狀態切換成閉合狀態，由於此閉合狀態被維 持，所以對Β方向之移動可獲得第1阻尼係數亦即最大値 Cm ax。在右側之最大振幅點也進行同樣的作動，以上的動作 -10- 593861 係被反覆。此外，在此場合，流量不大時，流量調整閥1 〇之 開閉操作閥1 1可作爲開閉控制閥單獨使用。 又，在具備了具有如以之機械式驅動手段的開閉控制閥之 阻尼係數切換型油壓減震器中，爲了避免不預期的大負載作 用在裝置上造成裝置破壞，例如有時係設置限制左右油壓室 的壓力之放洩閥。 本發明之第6樣態之阻尼係數切換型油壓減震器係具備 有油壓缸、在此油壓缸內往復動之活塞、設置在此活塞的 兩側之油壓室、以及設置在接合此兩油壓室的流路且依開 閉以變化阻尼係數之開閉控制閥，其特徵爲，油壓式驅動手 段係設置在油壓缸之油壓回路且構成爲依活塞之一方向的 移動而一側之油壓室的油壓上昇時，開閉控制閥係維持閉合 狀態而可獲得第1阻尼係數亦即最大値Cmax，且在活塞之 移動成逆向變換使該油壓下降時，開閉控制閥係暫時開啓而 獲得第2阻尼係數亦即最小値Cm i η之後，依另一側之油壓 室的油壓上昇，開閉控制閥係再度閉合而可獲得第1阻尼係 數亦即最大値Cmax。 此第6樣態之阻尼係數切換型油壓減震器係使用如第5 圖、第6圖或第7圖所示之油壓式驅動手段的場合。係利 用在活塞的移動方向變換時之油壓變化者。 本發明之第7樣態之阻尼係數切換型油壓減震器係如第 6樣態之阻尼係數切換型油壓減震器，其中驅動開閉控制閥 之油壓式驅動手段係由與油壓缸油壓室連通而蓄積壓力的 緩衝器、以及依此緩衝器之壓力和油壓缸油壓室之壓力差 -11- 593861 而作動之切換閥所構成。 _ 此第7樣態之阻尼係數切換型油壓減震器係如第5圖、 第6圖或第7圖所示，係將油壓式驅動手段4 0以例如由蓄 積壓力的緩衝器4 2、以及將此緩衝器4 2的壓力與油壓缸 室直接結合後之流路的實際壓力作比較，僅在緩衝器42的 壓力爲大時輸出響導壓之切換閥43所構成之場合，藉由左 側之緩衝器4 2和切換閥4 3，對活塞3在A方向移動所造成 之壓力上昇，開閉操作閥1 1和流量調整閥1 0係維持閉合狀 態，而對於在B方向之移動所造成之壓力下降，開閉操作閥 1 1和流量調整閥1 0係暫時開啓，接著，藉由右側之緩衝器42 和切換閥4 3，開閉操作閥1 1和流量調整閥1 0係成閉合狀 態且此狀態被維持。 本發明之第8、9樣態之阻尼係數切換型油壓減震器係具 備有各自限制活塞兩側之油壓室的壓力之放洩閥，且構成爲 在該放洩閥之作動開始壓力以上時，驅動開閉控制閥之油 壓式驅動手段係不動作而維持開閉控制閥爲閉合狀態。 此第8、9樣態之阻尼係數切換型油壓減震器係，在如第 6或第7樣態所記載之具備有油壓式驅動手段之開閉控制 閥的阻尼係數切換型油壓減震器中，例如在設置有限制左右 之油壓室的壓力之放洩閥的場合，如第1 5圖所示，以釋壓負 載FR以上而言，在最大振幅點並不一定是負載最大，例如在 P點所示之負載（油壓）的極大點，開閉控制閥係動作終了， 因第1 5圖的負載變形關係不能實現，所以構成爲在第1 5圖 之釋壓負載FR以上時，開閉控制閥不動作，而在較釋壓負載 -12- 593861 fr還低的壓力，開閉控制閥會動作，以作成實現第15圖之負 載變形關係者。 本發明之第1 0樣態之阻尼係數切換型油壓減震器係如第 7樣態之阻尼係數切換型油壓減震器，其中具備有··各自限 制活塞兩側之油壓室的壓力之放洩閥；限制緩衝器的壓力 之放洩閥，其係使在該放洩閥之作動開始壓力以上時，驅動 開閉控制閥之油壓式驅動手段不動作，開閉控制閥維持閉合 狀態且緩衝器的壓力係成爲該放洩閥之作動開始壓力以 下。 此第1 0樣態之阻尼係數切換型油壓減震器係如第8圖〜 第1 0圖所不，油壓式驅動手段係由緩衝器和切換閥構成之 場合的具體構成，係設置釋放各油壓室4之壓力的主放洩閥 50,在左右之緩衝器42各自設置將緩衝器之壓力往出側旁 路流路1 5釋放的放洩閥5 1，藉由將放洩閥51的設定壓力 設定爲較主放洩閥5 0的動作開始壓力還低，使得僅在主放 洩閥50之動作開始壓力以下時切換閥43會開啓，開閉操作 閥1 1會開啓，且流量調整閥1 〇會開啓。 此外，在第8圖、第10圖中，雖然在連通左右之油壓室4、 4的流路上設置2個主放洩閥5 0，但是也可以在經過止回閥 的流出用流路1 3和出側旁路流路1 5之間，將1個放洩閥5 0 和流量調整閥1 〇並列設置。 本發明之第1 1樣態之阻尼係數切換型油壓減震器係如第 6、7、8、9或第1 〇樣態之阻尼係數切換型油壓減震器，其 中2組的油壓式驅動手段係各自設置在活塞兩側的油壓室， - 1 3 - 593861 構成爲藉此等油壓式驅動手段來驅動以共通地設置在活塞 兩側之油壓室的1個開閉控制閥。 此第1 1樣態之阻尼係數切換型油壓減震器係如第5圖、 第8圖所示，開閉控制閥（流量調整閥1 0 )係1個單閥型 且使用2個油壓式驅動手段40的場合。使用在油壓上昇時 不作動，而在油壓下降時作動的油壓式驅動手段40，在活塞 3往A方向移動中，雖然左側之油壓室4的油壓會上昇，但 是因左側之油壓式驅動手段40不作動，閉合左側之開閉操 作閥1 1且中央之流量調整閥1 0 (開閉控制閥）事先閉合， 以獲得第1阻尼係數亦即最大値Cm a X。在左側之最大振幅 點當活塞3的移動方向往B方向變換時，由於油壓開始下降， 左側之油壓式驅動手段40係作動，藉由暫時開啓左側之開 閉操作閥1 1且暫時開啓中央之流量調整閥1 〇，使負載卸除 以獲得第2阻尼係數亦即最小値Cm i η。活塞3再往B方向 移動時，因爲右側之油壓室4的油壓會上昇，右側之油壓式 驅動手段40係作動，將流量調整閥1 0再度閉合而回復至第 1阻尼係數亦即最大値Cm a X。在右側之最大振幅點也進行 同樣的作動，以上的動作係被反覆。此外，在此油壓式的場 合，流量不大時，流量調整閥1 0之開閉操作閥1 1可作爲開 閉控制閥單獨使用。 本發明之第1 2樣態之阻尼係數切換型油壓減震器係如第 6、7、8、9或第1 0樣態之阻尼係數切換型油壓減震器，其 中2組的油壓式驅動手段係各自設置在活塞兩側的油壓室， 構成爲藉此等油壓式驅動手段來驅動以共通地設置在活塞 -14 一 兩側之油壓室的1個開閉控制閥。 此第1 2樣態之阻尼係數切換型油壓減震器係如第6圖、 第9圖所示，開閉控制閥（流量調整閥1 0 )係2個雙閥型 且使用2個油壓式驅動手段40之場合，乃使用與第5圖同 樣的油壓式驅動手段40，在活塞3往A方向移動中，雖然左 側之油壓室4的油壓會上昇，但是因爲左側之油壓式驅動手 段40不作動，將左側之開閉操作閥1 1及流量調整閥1 〇 (開 閉控制閥）事先閉合以獲得第1阻尼係數亦即最大値Cm ax。 在左側之最大振幅點當活塞3的移動方向往B方向變換時， 由於油壓開始下降，左側之油壓式驅動手段40係作動，藉由 暫時開啓左側之開閉操作閥1 1及流量調整閥1 〇，使負載卸 除以獲得第2阻尼係數亦即最小値C m i η。 當活塞3再往Β方向移動時，因右側之油壓室4的油壓會 上昇，所以右側之油壓式驅動手段40係作動，而閉合右側的 開閉操作閥1 1及流量調整閥1 〇則會回復至第1阻尼係數 亦即最大値Cmax。在右側之最大振幅點也進行同樣的作動， 以上的動作係被反覆。此外，在此油壓式的場合，流量不大 時，流量調整閥1 0之開閉操作閥Π可作爲開閉控制閥單獨 使用。 本發明之第1 3樣態之阻尼係數切換型油壓減震器係如第 6、7、8、9或第1 〇項樣態之阻尼係數切換型油壓減震器， 其中1組的開閉控制閥及油壓式驅動手段係相對於活塞兩 側的油壓室成共通地設置。 此第1 3樣態之阻尼係數切換型油壓減震器係如第7圖、 -15 - 593861 第1 0圖所示，開閉控制閥（流量調整閥1 ο )係1個單閥型 且使用1個油壓式驅動手段40的場合，乃使用與第5圖同 樣的油壓式驅動手段40 ,在活塞3往A方向移動中，雖然左 側之油壓室4的油壓會上昇，但是因爲油壓式驅動手段40 不作動，將開閉操作閥1 1及流量調整閥1 0 (開閉控制閥） 事先閉合以獲得第1阻尼係數亦即最大値Cm ax。在左側之 最大振幅點當活塞3的移動方向往B方向變換時，由於油壓 開始下降，油壓式驅動手段40係作動，藉由將開閉操作閥1 1 暫時開啓且將流量調整閥1 0暫時開啓，而使負載卸除以獲 得第2阻尼係數亦即最小値Cm i η。當活塞3再往B方向移 動時，因右側之油壓室4的油壓會上昇，所以油壓式驅動手 段4 0係會作動，因開閉操作閥1 1再度閉合，使得流量調整 閥10再度閉合而回復至第1阻尼係數亦即最大値Cmax。 在右側之最大振幅點也進行同樣的作動，以上的動作係被反 覆。此外，在此油壓式的場合，流量不大時，流量調整閥1 〇 之開閉操作閥1 1可作爲開閉控制閥單獨使用。 在如以上之構成中，把由地震或風等之振動外力所引起之 油壓減震器的活塞移動或壓力變化，藉由機械式或油壓式的 驅動手段作變換以直接切換控制油壓減震器之開閉控制閥， 所以可在不需要一切來自外部之能量供給下自動地切換阻 尼係數，使得感測器、控制器、電磁閥等等以及不斷電電源 裝置和特別的電源配線等係不需要，可經常確實地發揮超越 一般的油壓減震器之能量吸收能力。 (四）實施方式 -16- 593861 以下，依圖示本發明之實施形態加以說明。此實施形態例 係，在油壓減震器之油壓回路使用了使大流量的壓油高速通 過且可瞬時遮斷之流量調整閥。第1圖、第2圖係表示以 機械式執行油壓減震器之阻尼係數切換的第1實施形態，第 3圖、第4圖係表示機械式之第2實施形態者。第5圖、 第6圖、第7圖係表示以油壓式執行阻尼係數切換之第3 實施形態、第4實施形態及第5實施形態者。 I · 單閥型機械式阻尼係數切換型油壓減震器1 - 1 如第1圖所示，油壓減震器1 - 1係與習知相同，乃由油壓 缸2、雙杆型之活塞3、活塞3兩側之油壓室4、4、以及 設置在連接兩油壓室的流路5上之開閉控制閥6等所構成。 開閉控制閥6在此實施形態中係大流量用之流量調整閥（提 動閥）1 0，係連接有控制此流量調整閥1 〇開閉之開閉操作 閥（響導閥）1 1。開閉操作閥丨丨係具有開位置和閉位置之 一路切換閥。且在油壓回路上設置有用以補償依作動油之 壓縮或溫度變化所造成容積變化等之蓄壓器9。 在開閉操作閥1 1爲閉合狀態下，當活塞3往A方向（左 側）移動時，左側之油壓室4的壓油係透過左側之止回閥！ 2 和流出用流路1 3及具有節流閥的入側旁路流路1 4而對流 量調整閥1 0的閥體背面作用，由於此背壓昇高，所以流量調 整閥1 0閉合。藉此，油壓減震器1 - 1的阻尼係數係成爲最 大値Cmax ° 然後，於最大振幅點當開閉操作閥1 1開啓時，流量調整閥 1 0的背壓降低，流量調整閥1 0係開啓，左側之油壓室4的 -17- 壓油係通過左側之止回閥1 2和流出用流路1 3、及開啓狀 態的流量調整閥1 〇、出側旁路流路1 5、以及右側之止回閥 1 6和流入用通路1 7而流入右側之油壓室4，所以負載被卸 除，油壓減震器1的阻尼係數係成爲最小値C m i η。 即使活塞3往Β方向（右側）移動之場合，該動作也是對 稱地被執行，以上之動作係被反覆以行制震（參照第1 4圖 之實線D i )。 在此種構成之油壓減震器1 - 1中，以第1實施形態而言， 如第2圖所示，係使用機械式驅動手段30，僅依外力的油壓 減震器1 - 1之作動，將油壓減震器1 - 1之阻尼係數作成可兩 階段地切換成最大値C m a X和最小値C m i η。 機械式驅動手段3 0例如係由固定在活塞杆8的直線齒輪 (齒條）31和藉此直線齒輪31作動以開閉開閉操作閥1 1 的曲柄機構3 2所構成。曲柄機構3 2係將第1連桿3 3的基 部透過銷等而固定在油壓缸側且設定爲在活塞移動方向可 搖動，將第2連桿3 4的前端透過銷等而連接在開閉操作閥 1 1之閥柱等之閥體1 1 a。且，第1連桿3 3的基部係設置朝 直線齒輪3 1突出的滑動杆3 5。此滑動杆3 5係前端杆相對 於基部杆爲在軸方向進退自如地被收納的二重杆，藉由彈簧 3 6，前端杆係朝直線齒輪3 1推壓。 此種曲柄機構3 2係，第1連桿3 3乃相對於直線齒輪3 1， 事先設定爲朝B方向後傾。在此狀態，開閉操作閥1 1的埠 係偏離，閥體1 1 a係保持在閉合位置。在此狀態當活塞杆8 往A方向移動時，滑動杆3 5係對應直線齒輪3 1之凹凸、前 - 1 8 - 593861 端杆僅進退移動而在直線齒輪3 1上滑動，第1連桿3 3係維 持後傾姿勢，開閉操作閥1 1係保持閉合狀態。 在最大振幅點當活塞杆8變換移動方向往b方向移動時， 滑動杆3 5的前端杆係被彈簧3 6按住而與直線齒輪3 1的齒 側面係合，第1連桿3 3係在A方向傾動，第1連桿3 3和第 2連桿3 4係呈直線狀，開閉操作閥1 1的閥體1丨a被頂上， 且埠係一致，所以開閉操作閥1 1係呈開啓狀態。 此外，活塞杆8在B方向移動時，第1連桿3 3係在A方向 傾動，開閉操作閥1 1係成爲再度閉合之狀態。在此狀態，滑 動杆3 5係與前述相同樣地在直線齒輪3 1上滑動，所以開閉 操作閥1 1之閉合狀態係被保持。 將以上之構成的機械式阻尼係數切換型油壓減震器1- !， 如第1 2圖所示，透過支架組裝進建物的柱樑架構內之後，則 進行如次之動作。 (1 )由第1圖和第2圖的狀態，活塞杆8依地震等因素而 往A方向移動時，藉由曲柄機構3 2不在直線齒輪3 1上滑動 作動，開閉操作閥1 1係維持閉合狀態，依此，流量調整閥1 〇 也維持閉合狀態，阻尼係數係成最大値Cmax，以此阻尼係數 Cm ax來制震。 (2 )在左側之最大振幅點當活塞杆8的移動方向變換往B 方向開始移動時，曲柄機構3 2係作動而成直線狀且將開閉 操作閥1 1之閥體1 1 a頂上，開閉操作閥1 1係開啓，依此，流 量調整閥1 0也成爲開啓狀態，由於左側之油壓室4的壓油 流入右側之油壓室4，所以負載暫時被卸除，阻尼係數係成 - 1 9- 593861 爲最小値Cm i η。 (3 )活塞杆8再往Β方向移動時，由於曲柄機構3 2係往逆 方向作動且在Α方向傾動，所以開閉操作閥1 !係再度閉合， 依此，流量調整閥1 0也再度閉合，阻尼係數係回復至最大値 Cmax ° (4 )在此狀態，藉由曲柄機構3 2不在直線齒輪3 1上滑動 作動，開閉操作閥1 1係維持閉合狀態，相對於B方向的移動， 可將阻尼係數設定爲最大値C m a X。 (5 )藉由在油壓缸的兩側反覆以上的動作，如第1 4圖之實 線D!所示，與通常之阻尼係數爲一定的油壓減震器dq相比 較下，能量吸收能力係大幅地提升。且，僅依地震等之振動 外力所導致的活塞移動就可自動地切換阻尼係數。 以上雖然例不了使用流量調整閥1 0的場合，但是在流量 不大的場合，係省略流量調整閥1 0，僅開閉操作閥1 1就可 執行阻尼係數之切換。 Π . 雙閥型機械式阻尼係數切換型油壓減震器1 - 2 如第3圖所示，係對左右之油壓室4、4各別地設置流量 調整閥（提動閥）1 0及開閉操作閥（響導閥）1 1的實施形 態，使連接至各油壓室4的開閉操作閥1 1和流量調整閥1 〇 予以個別地開閉。 與第1圖同樣地，藉開閉操作閥1 1來開閉控制流量調整 閥1 0。開閉操作閥1 1係使用右手用和左手用各一，藉與第 1圖同樣的機械式驅動手段3 0以行開閉。 機械式驅動手段3 0 ’係由直線齒輪（齒條）3 1和連桿機構 -20 - 593861 3 2’所構成。連桿機構32,係由第1連桿33和第2連桿34, 構成。 桌1連彳干3 3爲與弟1圖相同的構成，但是第2連桿3 4 ’係 透過銷等將中間部安裝在第1連桿3 3的前端，且在兩端透 過銷等而連接在右手用和左手用之開閉操作閥1 1的閥體 1 1 a ° 此種連桿機構3 2 ’係與第1圖同樣地，第1連桿3 3係相 對於直線齒輪3 1，朝B方向後傾般地設置。在此狀態，左側 之開閉操作閥1 1係在閉合位置，右側之開閉操作閥11係保 持在開啓位置。由此狀態，即使活塞杆8朝A方向移動，也 與第1圖同樣地，滑動杆3 5係在直線齒輪31上滑動，第1 連桿3 3係維持後傾姿勢，右手用·左手用之開閉操作閥u、 11係保持其狀態。 在最大振幅點當活塞杆8變換移動方向往B方向移動時， 係與第1圖同樣地藉直線齒輪3 1的齒側面，第1連桿3 3係 在A方向傾動，右手用·左手用之開閉操作閥1 1的閥體i } a 係一起水平移動，左側之開閉操作閥1 1係開啓狀態，右側之 開閉操作閥1 1係呈閉合狀態。即使活塞杆8再往B方向移 動，由於滑動杆3 5在直線齒輪3 1上滑動，所以左側之開閉 操作閥1 1係開啓狀態，右側之開閉操作閥1 1係被保持在閉 合狀態。 如以上之構成之機械式的阻尼係數切換型油壓減震器1 -2係作動如次： (1 )由第3圖和第4圖之狀態，當活塞杆8依地震等而往 -21- 593861 A方向移動時，藉連桿機構3 2，不在直線齒輪3丨上滑動作動， 左側之開閉操作閥1 1係維持閉合狀態，藉此左側之流量調 整閥10也維持閉合狀態，阻尼係數係成爲最大値Cmax，而 以此阻尼係數Cm a X來制震。 (2 )在左側之最大振幅點當活塞杆8之移動方向變換，開 始往B方向移動時，連桿機構3 2，係作動，左側之開閉操作 閥1 1開啓，藉此左側之流量調整閥1 〇也成爲開啓狀態，由 於左側之油壓室4的壓油會朝右側之油壓室4流出，所以負 載暫時被卸除，阻尼係數成爲最小値Cm i n。 (3 )此時，右側之開閉操作閥1 1係閉合狀態，即使活塞杆 8再往B方向移動，藉由連桿機構3 2，不在直線齒輪3 1上滑 動作動，右側之開閉操作閥丨丨係維持閉合狀態，藉此右側之 流量調整閥1 0也維持閉合狀態，阻尼係數回復至最大値 Cm a X ° (4 )藉由在油壓缸之兩側反覆以上的動作，如第1 4圖所示， 與通吊之阻尼係數爲一疋的油壓減震器相比較下，能量吸收 能力係大幅地提升。且，光是地震等之振動外力所致之活塞 的移動就可自動地切換阻尼係數。 此外，在此第2實施形態的場合，流量不大時係將流量調 整閥1 0省略，僅開閉操作閥丨丨就可執行阻尼係數之切換。 瓜·單閥•雙驅動型油壓式阻尼係數切換型油壓減震器1 一 3 如第5圖所示，取代第1圖之機械式驅動手段3 0，改成將 油壓式驅動手段4 0組裝入第1圖的油壓回路，以油壓的變 化來執行阻尼係數的切換。 -22- 593861 此油壓式驅動手段40係各自透過節流閥4 1而被連接至 各油壓室4、4的流入用通路1 7、1 7 ,且係由蓄積壓油之緩 衝器42，以及連接至此緩衝器42之用以開閉控制開閉操作 閥1 1之切換閥（提動閥）4 3所構成。 切換閥4 3係與流量調整閥1 〇同爲提動閥型，在入口埠連 接緩衝器4 2，且使背壓埠和流入用通路1 7連通，將來自出 口埠之壓油作爲響導壓以供給開閉操作閥i丨，使開閉操作 閥1 1的閥柱等閥體驅動。 因此，油壓室4的壓力上昇時，在緩衝器4 2雖然被蓄積有 壓油，由於也透過流入用通路1 7對切換閥4 3作用有大的背 壓，所以切換閥4 3係被閉合，由切換閥4 3之出口埠，壓油係 對開閉操作閥1 1不作爲響導壓作用，開閉操作閥i丨係保持 閉合狀態。油壓室4之壓力開始下降時，切換閥4 3之背壓 係變得較緩衝器4 2的壓力還低，切換閥4 3係開啓，來自切 換閥4 3之出口埠的壓油係作爲響導壓以對開閉操作閥1 1 作用，使開閉操作閥1 1開啓。 如以上之構成之油壓式的阻尼係數切換型油壓減震器1 -3係作動如次： (1 )由第5圖之狀態，當活塞杆8依地震等而往A方向移 動時，左側之油壓室4的壓力會上昇，由於左側之切換閥4 3 係如前述般地被閉合，所以左側之開閉操作閥1 1係維持閉 合狀態，藉此中央之流量調整閥1 0也維持閉合狀態，阻尼係 數係成最大値Cm ax，而以此阻尼係數Cm ax來制震。 (2 )在左側之最大振幅點當活塞杆8之移動方向變換，開 -23- 593861 始往B方向移動時，左側之油壓室4的壓力開始下降，左側 之切換閥4 3係如前述般地開啓，所以左側之開閉操作閥} i 係開啓，依此，中央之流量調整閥丨〇也開啓，由於左側之油 廳室4的壓油係通過流量調整閥1 〇朝右側之油壓室4流入， 所以負載係暫時被卸除，阻尼係數係成爲最小値Cm i η。 (3 )活塞杆8再往Β方向移動時，右側之緩衝器42、切換 閥4 3、開閉操作閥丨1係與前述同樣地動作，因爲中央之流 量調整閥10會閉合，所以阻尼係數係回復至最大値Cmax。 (4 )藉由在油壓缸之兩側反覆以上的動作，如第丨4圖所示， 與通常之阻尼係數爲一定的油壓減震器相比較下，能量吸收 能力係大幅地提升。且，光是地震等之振動外力所致之活塞 的移動就可自動地切換阻尼係數。 此外，開閉操作閥1 1雖然被設置2個，但是1個也可以。 在此第3實施形態之場合也在流量不大時，可省略流量調整 閥1 0，僅以開閉操作閥1 1就可執行阻尼係數之切換。 IV . 雙閥•雙驅動型油壓式阻尼係數切換型油壓減震器1 - 4 如第6圖所示，爲在第5圖之油壓回路中將流量調整閥1〇 配設右手用和左手用各一之實施形態。其他的構成係與第 5圖相同。 如以上構成之油壓式的阻尼係數切換型油壓減震器1-4 係，僅在使用了 2個流量調整閥1 0這點上與第5圖不同，與 第5圖之場合同樣地係作動如次： (1 )由第6圖之狀態，當活塞杆8依地震等而往A方向移 動時，左側之油壓室4的壓力會上昇，由於左側之切換閥4 3 -24- 593861 係如前述般地被閉合，所以左側之開閉操作閥11係維持閉 合狀態，藉此左側之流量調整閥1 〇也維持閉合狀態，阻尼係 數係成最大値Cm ax,而以此阻尼係數Cm ax來制震。 (2)當活塞杆8之移動方向變換，開始往B方向移動時，左 側之油壓室4的壓力開始下降，左側之切換閥4 3係如前述 般地開啓，所以左側之開閉操作閥1 1係開啓，依此左側之流 量調整閥1 0也開啓，由於左側之油壓室4的壓油係通過左 側之流量調整閥1 0朝右側之油壓室4流入，所以負載係暫 時被卸除，阻尼係數係成爲最小値Cm i η。 (3 )活塞杆8再往Β方向移動時，右側之緩衝器42、切換 閥43、右側之開閉操作閥1 1係與前述同樣地動作，因爲右 側之流量調整閥1 0會閉合，所以阻尼係數係回復至最大値 Cm a X ° (4 )藉由在油壓缸之兩側反覆以上的動作，如第1 4圖所示， 與通常之阻尼係數爲一定的油壓減震器相比較下，能量吸收 能力係大幅地提升。且，光是地震等之振動外力所致之活塞 的移動就可自動地切換阻尼係數。 此外，在此第4實施形態之場合，當流量不大時係將流量 調整閥1 0省略，僅以開閉操作閥1 1就可執行阻尼係數之切 換。 V . 單閥•單驅動型油壓式阻尼係數切換型油壓減震器1 - 5 如第7圖所示，係在第5圖之單閥型的油壓回路中配設了 1個油壓式驅動手段4 0的實施形態。其他之構成係與第5 圖相同。 -25- 593861 如以上構成之油壓式的阻尼係數切換型油壓減震器丨-5 係，僅在各自使用了 1個流量調整閥1 0和1個油壓式驅動 手段40這點上與第5圖不同，且與第5圖之場合同樣地作 動如次： (1 )由第7圖之狀態，當活塞杆8依地震等而往A方向移 動時，左側之油壓室4的壓力會上昇，由於左側之切換閥4 3 係如前述般地被閉合，所以開閉操作閥1 1係維持閉合狀態， 藉此流量調整閥1 0也維持閉合狀態，阻尼係數係成最大値 Cmax，而以此阻尼係數Cmax來制震。 (2 )當活塞杆8之移動方向變換往B方向移動時，左側之 油壓室4的壓力開始下降，切換閥43係如前述般地開啓，所 以開閉操作閥1 1係開啓，依此流量調整閥1 0也開啓，藉由 油壓室4的壓油通過流量調整閥1 〇朝右側之油壓室4流入， 所以負載係暫時被卸除，阻尼係數係成爲最小値Cnn η。 (3 )活塞杆8再往Β方向移動時，緩衝器4 2和切換閥4 3、 開閉操作閥1 1係與前述同樣地動作，因爲流量調整閥1 0會 閉合，所以阻尼係數係回復至最大値Cmax。 (4 )藉由在油壓缸之兩側反覆以上的動作，如第丨4圖所示， 與通常之阻尼係數爲一定的油壓減震器相比較下，能量吸收 能力係大幅地提升。且，光是地震等之振動外力所致之活塞 的移動就可自動地切換阻尼係數。 、 此外，開閉操作閥1 1雖然被設置2個，但是1個也可以。. 在此第3實施形態之場合也在流量不大時，可省略流量調整 閥1 〇，僅以開閉操作閥1 1就可執行阻尼係數之切換。 -26 - 593861 此外，在此第5實施形態之場合，流量不大時係將流量調 整閥1 0省略，僅以開閉操作閥1 1就可執行阻尼係數之切 換。 VI . 附放洩閥之阻尼係數切換型油壓減震器 爲了避免在裝置中產生不預期的大負載而破壞裝置，例如 有時設置用以限制左右之油壓室的壓力之放洩閥。在具備 擁有機械式驅動手段的開閉控制閥之阻尼係數切換型油壓 減震器上設置有放洩閥之場合的負載變形關係成爲第1 5圖 所示之圖表。在第1 5圖中，於釋壓負載FR，壓力係約略成一 定。在機械式之場合，與壓力無關地在活塞之衝程終點係不 使開閉控制閥作動，所以不會產生問題。 一方面，在具備擁有油壓式驅動手段的開閉控制閥之阻尼 係數切換型油壓減震器中設置有放洩閥之場合，如第1 5圖 所示，在釋壓負載FR以上時，不一定在最大振幅點爲負載最 大，例如在P點所示之油壓負載的極大點，開閉控制閥係動 作結束，所以第1 5圖之負載變形關係不能實現。 於是，在油壓式之場合，藉由在第1 5圖之釋壓負載FR以上 時，開閉控制閥不動作，在較釋壓負載h還低的壓力，開閉 控制閥係動作，以實現第1 5圖之負載變形關係。 具體言之，如第8圖〜第1〇圖所示，除了主放洩閥50以 外，係設置限制緩衝器4 2之壓力的放洩閥5 1，藉由將此放 洩閥51之動作開始壓力設定爲主放洩閥5 0之動作壓力以 下，以實現第1 5圖之負載變形關係。 在第8圖之單閥•雙驅動型阻尼係數切換型油壓減震器 - 27- 593861 1 - 3中，設置2個將左右之油壓室4、4連通的流路，在此各 流路上設置使各油壓室4之壓力放洩的主放洩閥50 ,在左 右之各緩衝器42設置有將緩衝器42和流量調整閥1 0之間 的壓力朝出側旁路流路1 5放洩的放洩閥51，藉由將放洩閥 5 1之設定壓力設定爲較主放洩閥50的動作開始壓力還低， 使得僅在主放洩閥50之動作開始壓力以下時，切換閥43開 啓、開閉操作閥1 1開啓、流量調整閥1 0開啓。 在第9圖之雙閥•雙驅動型阻尼係數切換型油壓減震器 1-4之場合，第10圖之單閥•單驅動型阻尼係數切換型油壓 減震器1 - 5之場合也同樣地設置有主放洩閥50和放洩閥5 1， 且與前述同樣地動作。 此外，在第8圖、第1 0圖的流量調整閥1 〇爲1個之場合 中，雖然在將左右之油壓室4、4予以連通的流路上設置2 個主放洩閥5 0，但是也可以在經過止回閥的流出用流路1 3 和出側旁路流路1 5之間，將1個放洩閥50和流量調整閥1 0 並列設置。 (五）圖式簡單說明 第1圖：以機械式執行本發明之阻尼係數切換型油壓減 震器的阻尼係數切換之第1實施形態的油壓回 路圖。 第2圖：表示第1實施形態之閥的驅動機構之側面圖。 第3圖：以機械式執行本發明之阻尼係數切換型油壓減 震器的阻尼係數切換之第2實施形態的油壓回 路圖。 593861 第4圖：表示第2實施形態之閥的驅動機構之側面圖。 第5圖：以油壓式執行本發明之阻尼係數切換型油壓減 震器的阻尼係數切換之第3實施形態的油壓回 路圖。 第6圖：以油壓式執行本發明之阻尼係數切換型油壓減 震器的阻尼係數切換之第4實施形態的油壓回 路圖。 第7圖：以油壓式執行本發明之阻尼係數切換型油壓減 震器的阻尼係數切換之第5實施形態的油壓回 路圖。 第8圖：表示在第5圖的第3實施形態設置有放洩閥之 實施形態的油壓回路圖。 第9圖··表示在第6圖的第4實施形態設置有放洩閥之 實施形態的油壓回路圖。 第1 0圖：表示在第7圖的第5實施形態設置有放洩閥之 實施形態的油壓回路圖。 第1 1圖：表示阻尼係數切換型油壓減震器之基本構造的 槪要圖。 第1 2圖：表示制震用油壓減震器之設置例的前視圖。 第1 3圖：制震用油壓減震器之力學模式圖。 第1 4圖：表示制震用油壓減震器之負載和變形的關係圖 形。 第1 5圖：表示設置有放洩閥的制震用油壓減震器之負載 和變形的關係圖形。 -29- 593861 主要部分之代表符號說明」 1 - 1〜1 - 5 ···油壓減震器 2 . ••油壓缸 3 · ••活塞 4 · ••油壓室 5 · ••流路 6 · ••開閉控制閥 8 · ••活塞杆 9 · ••蓄壓器 10 · • •流量調整閥 11· • •開閉操作閥 12 · • •止回閥 13 · • •流出用流路 14 · • •入側旁路流路 15 · ••出側旁路流路 16 · • •止回閥 17 · • •流入用通路 11a • · ·閥體 30、 3 0’· · ·機械式驅動弓 31 · • •直線齒輪（齒條） 32 · ••曲柄機構 32’ • · •連桿機構 33 · • •第1連桿 34、 3 4’· · ·第2連桿 - 30593861 发明, description of the invention ^ ^ ^ ^ ", (the description of the invention should state: the technical field, prior art, content, embodiments, and drawings of the invention briefly) (1) the technical field to which the invention belongs: the present invention is related Hydraulic shock absorbers to reduce the vibration of structures (buildings, bridges, roofs, etc.) caused by external forces such as earthquakes or wind. (2) Prior technology: In the form of shock absorbers used to reduce the vibration of structures The vibration damping device has a φ variable damping device (for example, Japanese Patent Laid-Open No. 1 1-3 3 6 3 6 6) and the like, which have a two-stage control of the opening and closing control valve opening and closing in two stages. . The basic structure of this type of hydraulic shock absorber is shown in Figure 11. It consists of a hydraulic cylinder 2, a two-rod type piston 3 reciprocating in the hydraulic cylinder 2, and two sides of the piston 3. The hydraulic pressure chambers 4 and 4 and the opening and closing control valve 6 provided on the flow path 5 connecting the two hydraulic pressure chambers are configured to open and close the control valve (electromagnetic) by supplying a control current from the controller 7. The valve) 6 performs two-stage opening and closing actions of full-closing and full-opening. The damping coefficient of the hydraulic shock absorber 1 can be switched to the maximum 値 Cmax and the minimum 値 Cmin in two steps. · This type of hydraulic shock absorber 1 is shown in Figure 12 and is installed between the layers of the structure through components such as brackets. Therefore, the mechanical characteristics of the device part including the bracket are as shown in Figure 1 and 3. The spring and buffer tube shown in the figure are represented by a Maxwell-type mode combined in series. In the device of FIG. 11, by switching the damping coefficient of the device, that is, the valve opening degree of the opening and closing control valve 6 is switched at the point of the maximum amplitude of vibration, so that the large energy absorption shown in FIG. 14 can be reduced. Structural vibration. Fig. 1 Vertical 4-Load L of the shaft hydraulic shock absorber, inter-layer deformation of the horizontal axis (deformation at the ends of the Maxwell-type mode), and the dashed line damping coefficient is a conventional shock absorber D0 , The solid line is a damping coefficient switching type shock absorber Di. Also, only the two-stage control with the so-called valve opening degree C as the fully closed or fully open ends is possible, so it is a device that continuously controls the valve opening degree (for example, Japanese Patent No. 7-45 7 8 No. 1) ) In contrast, the structure of the device can be simplified. However, in the foregoing prior devices, it is inevitable that since electric components such as sensors or controllers or solenoid valves are used, uninterruptible power supply devices and special power supply wiring are necessary. In addition, a part of electrical parts has items that need to be exchanged regularly, so maintenance costs are incurred. The present invention has been made to solve such a problem, and an object thereof is to provide a damping coefficient switching type hydraulic shock absorber which is connected to a variable damping type hydraulic shock absorber and does not require all external energy supply. The damping coefficient can be switched automatically, and the energy absorption capacity of ordinary hydraulic shock absorbers can be surely exerted. (3) Summary of the Invention: The first aspect of the present invention is a damping coefficient switching type hydraulic shock absorber provided with a hydraulic cylinder, a piston reciprocating in the hydraulic cylinder, and two pistons provided on both sides of the piston. The oil pressure chamber and the opening and closing control valve provided in the flow path connecting the two oil pressure chambers and changing the damping coefficient according to opening and closing are characterized in that the opening and closing control valve system is maintained in a closed state relative to the movement of the piston in one direction. The first damping coefficient, that is, the maximum 値 Cmax, can be obtained. When the piston movement is reversed, the opening and closing control valve system is temporarily opened to obtain the second damping coefficient, that is, the minimum 値 Cm i η, and the opening and closing control valve is closed again to obtain The first damping coefficient is also -7-593861, which is the maximum 値 Cmax. This first aspect of the damping coefficient switching type hydraulic shock absorber is the basic structure of the present invention, and it is a mechanical driving means that is operated by the movement of the piston of the hydraulic shock absorber (refer to FIGS. 1 to 4). (Figure) or hydraulic drive means (refer to Figures 5 to 7) to control the opening and closing control valve, so that the damping coefficient of the hydraulic shock absorber can be mechanically changed without the need for all external energy supply. Direct switching by means of hydraulic or hydraulic pressure. The on-off control valve is, for example, a flow regulating valve 10 operated by an on-off operation valve 11 as shown in FIG. 1 or a separate on-off operation valve 11 and the like. The second aspect of the present invention is a damping coefficient switching type hydraulic shock absorber provided with a hydraulic cylinder, a piston reciprocating in the hydraulic cylinder, hydraulic chambers provided on both sides of the piston, and The opening and closing control valve that connects the flow paths of the two oil pressure chambers and changes the damping coefficient according to opening and closing is characterized in that a mechanical driving means is provided between the piston rod and the opening and closing control valve and is configured to be one of the pistons. In the direction of movement, the opening and closing control valve system is kept closed to obtain the first damping coefficient, which is the maximum 値 Cm a X, and when the movement of the piston is reversed, the opening and closing control valve system is temporarily opened to obtain the second damping coefficient, which is the minimum 値. After Cm i η, the opening and closing control valve is closed again to obtain the first damping coefficient, which is the maximum value 値 C ma X 〇 This second aspect of the damping coefficient switching type hydraulic shock absorber system is used as shown in Figure 2 or 4 In the case of the mechanical driving means shown in the figure. For example, in FIG. 2, the mechanical driving means 30 that is actuated by the piston 3 only when the moving direction of the piston 3 is changed is used. When the piston 3 is moved in the A direction, the mechanical driving means 30 is not activated. Close the opening and closing operation valve 1 丨 and the flow adjustment valve! 〇 8-to obtain the first damping coefficient, which is the maximum 値 Cmax. At the maximum amplitude point on the left, when the moving direction of the piston 3 is changed to the B direction, the mechanical driving means 30 is actuated and the flow regulating valve 10 is temporarily opened by opening and closing the operation valve 1 1 to temporarily unload the load. Divide to obtain the second damping coefficient, which is the minimum 値 Cm i η. When the piston 3 moves in the B direction again, the opening and closing operation valve i 1 and the flow adjustment valve 1 0 are closed again by mechanical driving means 30 to return to the table 1 damping coefficient, which is the maximum 値 C m a X. The same operation as described above is performed at the maximum amplitude point on the right, and the above operations are repeated. In addition, the flow regulating valve 10 is used when the flow rate of the hydraulic oil is large. When the flow rate is not large, the opening and closing operation valve 11 of the flow regulating valve 10 can be used alone as an on-off control valve. In the third aspect of the present invention, the damping coefficient switching type hydraulic shock absorber is the same as the second aspect of the damping coefficient switching type hydraulic shock absorber, in which the mechanical driving means for driving the opening and closing control valve is provided at the hydraulic pressure. A linear gear of a piston rod of the cylinder and a crank mechanism that operates in response to the linear gear to open and close the opening and closing control valve. In this third aspect, the damping coefficient switching type hydraulic shock absorber system limits the mechanical driving means to the case of the structure shown in Figs. 2 and 4. If the first link on the front end side of the crank mechanism is set to tilt back to the spur gear in advance, a backward tilting posture is maintained for the movement of one direction of the spur gear. When the spur gear changes the direction of movement, the first link is turned into Upright. In the fourth aspect of the present invention, the damping coefficient switching type hydraulic shock absorber is formed in the second or third aspect of the damping coefficient switching type hydraulic shock absorber. 1 open / close control valve to control. -9-The fourth aspect of the damping coefficient switching type hydraulic shock absorber is shown in Figure 1 when the on-off control valve (flow control valve 1 0) is a single valve type. Relative to the movement in the A direction of the piston 3, the crank mechanism 3 and 2 are inactive, and the opening and closing operation valve 11 and the flow adjustment valve 10 are maintained in a closed state. When starting to move in the B direction, the crank mechanism 3 and 2 are activated and first The on-off operation valve 11 and the flow adjustment valve 10 are temporarily opened. Then, the on-off operation valve 11 and the flow adjustment valve 10 are restored to the closed state again. With respect to the movement in the B direction, the crank mechanism 32 does not operate. This closed state is maintained. The fifth aspect of the present invention has a damping coefficient switching type hydraulic shock absorber, such as the second or third aspect of the damping coefficient switching type hydraulic shock absorber, which is configured to control the piston with its own independent opening and closing control valve. Pressure in the oil pressure chambers on both sides. As shown in Fig. 3, the fifth aspect of the damping coefficient switching type hydraulic shock absorber is a case where the on-off control valve (flow regulating valve 1 0) is a two-valve type. The mechanical drive means 3 0 ′ that is actuated by the piston 3 only when the moving direction of the piston 3 is changed. When the piston 3 is moved in the direction A, the mechanical drive means 3 0 ′ is not activated, and the operation valve 1 is opened and closed. 1 is closed, and the left side flow regulating valve 10 is closed in advance to obtain the first damping coefficient, that is, the maximum 値 Cmax. At the maximum amplitude point on the left side, when the moving direction of the piston 3 is changed to the B direction, the opening and closing operation valve 1 1 is temporarily opened by the mechanical driving means 30 ′, and the flow regulating valve 10 on the left side is temporarily opened to remove the load. A second damping coefficient, that is, the minimum 値 Cm i η is obtained. At this time, the flow control valve 10 (opening and closing control valve) on the right is switched from the open state to the closed state. Since this closed state is maintained, the first damping coefficient, which is the maximum 値 Cm ax, can be obtained by moving in the B direction. The same operation is performed at the maximum amplitude point on the right. The above action is repeated -10- 593861. In addition, in this case, when the flow rate is not large, the opening / closing operation valve 11 of the flow regulating valve 10 can be used alone as an on-off control valve. In addition, in a damping coefficient switching type hydraulic shock absorber provided with an on-off control valve having a mechanical driving means, in order to avoid an unexpected large load acting on the device and causing damage to the device, for example, restrictions may be set. Relief valves for pressure in the left and right hydraulic chambers. The sixth aspect of the present invention provides a damping coefficient switching type hydraulic shock absorber including a hydraulic cylinder, a piston reciprocating in the hydraulic cylinder, hydraulic chambers provided on both sides of the piston, and The opening and closing control valve that connects the flow paths of the two hydraulic chambers and changes the damping coefficient according to opening and closing characteristics is characterized in that the hydraulic driving means is provided in the hydraulic circuit of the hydraulic cylinder and is configured to move in one direction of the piston When the oil pressure in the oil pressure chamber on one side rises, the opening and closing control valve system is kept closed to obtain the first damping coefficient, which is the maximum 値 Cmax, and when the movement of the piston is reversed to reduce the oil pressure, the opening and closing control is performed. After the valve system is temporarily opened to obtain the second damping coefficient, which is the minimum 値 Cm i η, the oil pressure in the oil pressure chamber on the other side rises, and the opening and closing control valve system is closed again to obtain the first damping coefficient, which is the maximum 値 Cmax. . The sixth aspect of the damping coefficient switching type hydraulic shock absorber is the one using the hydraulic drive means as shown in Figure 5, Figure 6, or Figure 7. It is used when the oil pressure changes when the direction of movement of the piston is changed. In the seventh aspect of the present invention, the damping coefficient switching type hydraulic shock absorber is the same as the sixth aspect of the damping coefficient switching type hydraulic shock absorber, in which the hydraulic driving means for driving the opening and closing control valve is connected with the hydraulic pressure. Cylinder oil pressure chamber communicates and accumulates a buffer, and a switching valve that operates based on the pressure difference between the buffer and the pressure difference between the oil cylinder pressure chamber and the hydraulic cylinder. _ The damping coefficient switching type hydraulic shock absorber of the seventh aspect is shown in FIG. 5, FIG. 6 or FIG. 7, and the hydraulic drive means 40 is, for example, a buffer 4 that accumulates pressure. 2. And compare the pressure of the buffer 42 with the actual pressure of the flow path after the hydraulic cylinder chamber is directly combined, and only when the pressure of the buffer 42 is large, the switching valve 43 which outputs the pilot pressure is used. With the buffer 4 2 and the switching valve 4 3 on the left, the pressure caused by the movement of the piston 3 in the A direction is increased. The opening and closing operation valve 11 and the flow adjustment valve 10 are maintained in a closed state, and for the movement in the B direction The resulting pressure drop, the opening and closing operation valve 11 and the flow adjustment valve 10 are temporarily opened, and then, by the right buffer 42 and the switching valve 4 3, the opening and closing operation valve 11 and the flow adjustment valve 10 are closed. State and this state is maintained. In the eighth and ninth aspects of the present invention, the damping coefficient switching type hydraulic shock absorber is provided with a relief valve which restricts the pressure of the oil pressure chamber on both sides of the piston, and is configured to start the pressure at the actuation of the relief valve. In the above case, the hydraulic driving means for driving the opening and closing control valve does not operate and maintains the opening and closing control valve in a closed state. In the eighth and ninth aspects of the damping coefficient switching type hydraulic shock absorber, as described in the sixth or seventh aspect, the damping coefficient switching type hydraulic pressure reduction of the on-off control valve provided with the hydraulic drive means is described. For example, when a relief valve is provided in the vibrator to limit the pressure of the left and right hydraulic chambers, as shown in FIG. 15, the maximum amplitude point may not necessarily be the maximum load at the maximum amplitude point, as shown in FIG. 15. For example, at the maximum point of the load (hydraulic pressure) shown at point P, the opening and closing control valve system has ended. Because the load deformation relationship in FIG. 15 cannot be realized, it is configured to be above the pressure relief load FR in FIG. 15 At this time, the opening and closing control valve does not operate, but at a pressure lower than the pressure relief load -12-593861 fr, the opening and closing control valve will operate to create the load deformation relationship shown in Figure 15. The damping coefficient switching type hydraulic shock absorber of the tenth aspect of the present invention is the damping coefficient switching type hydraulic shock absorber of the seventh aspect, which is provided with an oil pressure chamber each limiting the hydraulic chambers on both sides of the piston. Pressure relief valve; pressure relief valve to limit the pressure of the buffer, which prevents the hydraulic drive means that drives the opening and closing control valve from operating when the operating pressure of the relief valve is above the opening and closing control valve to maintain a closed state The pressure of the shock absorber is equal to or lower than the operation start pressure of the relief valve. This 10th aspect of the damping coefficient switching type hydraulic shock absorber is as shown in Figures 8 to 10, and the hydraulic driving means is a specific structure in the case of a buffer and a switching valve. The main relief valves 50 for releasing the pressure in each of the hydraulic chambers 4 are provided at the left and right buffers 42 respectively, and the relief valves 51 for releasing the pressure of the buffers to the outlet bypass flow path 15 are provided to release the pressure. The setting pressure of the valve 51 is set to be lower than the operation start pressure of the main relief valve 50, so that the switching valve 43 is opened only when the operation start pressure of the main relief valve 50 is below, and the opening and closing operation valve 11 is opened, and The flow adjustment valve 10 will open. In addition, in Figs. 8 and 10, although two main relief valves 50 are provided on the flow path connecting the left and right oil pressure chambers 4, 4, the outflow flow path 1 passing through the check valve may also be used. Between 3 and the outlet bypass flow path 15, a relief valve 50 and a flow adjustment valve 10 are arranged in parallel. The 11th aspect of the present invention has a damping coefficient switching type hydraulic shock absorber such as the 6, 7, 8, 9, or 10th aspect of the damping coefficient switching type hydraulic shock absorber, of which 2 groups of oil The hydraulic driving means are hydraulic chambers provided on both sides of the piston.-1 3-593861 This hydraulic driving means is used to drive one opening and closing control of the hydraulic chambers provided on both sides of the piston in common. valve. As shown in Fig. 5 and Fig. 8, the damping coefficient switching type hydraulic shock absorber of the first aspect is a single-valve type and uses two oil pressures. In the case of the driving means 40. When the hydraulic pressure driving means 40 which does not operate when the oil pressure rises and is operated when the oil pressure drops is used, the piston 3 moves in the direction A. Although the oil pressure in the oil pressure chamber 4 on the left increases, The hydraulic drive means 40 is not activated, and the left-side opening and closing operation valve 11 is closed and the central flow regulating valve 10 (opening and closing control valve) is closed in advance to obtain the first damping coefficient, which is the maximum 値 Cm a X. At the maximum amplitude point on the left side, when the moving direction of the piston 3 is changed to the B direction, the hydraulic pressure driving means 40 on the left side is actuated because the hydraulic pressure starts to decrease. By temporarily opening the opening and closing operation valve 11 on the left side and temporarily opening the center The flow adjustment valve 1 〇 removes the load to obtain the second damping coefficient, which is the minimum 値 Cm i η. When the piston 3 moves in the B direction, the oil pressure in the oil pressure chamber 4 on the right will rise, and the oil pressure driving means 40 on the right will act, closing the flow adjustment valve 10 again and returning to the first damping coefficient. Maximum 値 Cm a X. The same operation is performed at the maximum amplitude point on the right, and the above operations are repeated. In addition, in this hydraulic type, when the flow is not large, the opening and closing operation valve 11 of the flow regulating valve 10 can be used alone as an on-off control valve. The 12th aspect of the present invention has a damping coefficient switching type hydraulic shock absorber such as the 6, 7, 8, 9, or 10th aspect of the damping coefficient switching type hydraulic shock absorber, of which 2 groups of oil The pressure driving means are oil pressure chambers respectively provided on both sides of the piston, and are configured to drive one opening and closing control valve of the oil pressure chambers provided on one side of the piston-14 in common by the oil pressure driving means. As shown in Fig. 6 and Fig. 9, the damping coefficient switching type hydraulic shock absorber of the 12th aspect is an open / close control valve (flow control valve 1 0) of two double valve types and uses two hydraulic pressures. In the case of the type driving means 40, the same hydraulic driving means 40 as in Fig. 5 is used. While the piston 3 is moving in the direction A, although the hydraulic pressure of the hydraulic chamber 4 on the left increases, the hydraulic pressure on the left is increased. The type driving means 40 is not operated, and the left opening and closing operation valve 11 and the flow adjustment valve 10 (opening and closing control valve) are closed in advance to obtain a first damping coefficient, that is, maximum 値 Cm ax. When the moving direction of the piston 3 is shifted to the B direction at the maximum amplitude point on the left side, the hydraulic pressure driving means 40 on the left side is actuated because the hydraulic pressure starts to decrease. By temporarily opening the opening and closing operation valve 11 and the flow adjustment valve on the left side 10, the load is removed to obtain the second damping coefficient, which is the minimum 値 C mi η. When the piston 3 moves in the direction of B again, the oil pressure in the oil pressure chamber 4 on the right side will rise, so the oil pressure driving means 40 on the right side will act, and the opening and closing operation valve 11 and the flow rate adjustment valve 1 on the right side will be closed. Will return to the first damping coefficient, which is the maximum 値 Cmax. The same operation is performed at the maximum amplitude point on the right, and the above operations are repeated. In addition, in this hydraulic type, when the flow rate is not large, the opening / closing operation valve Π of the flow regulating valve 10 can be used alone as an on-off control valve. In the thirteenth aspect of the present invention, the damping coefficient switching type hydraulic shock absorber is such as the sixth, seventh, eighth, nine, or tenth aspect of the damping coefficient switching type hydraulic shock absorber, of which one group of The on-off control valve and the hydraulic driving means are provided in common with respect to the hydraulic chambers on both sides of the piston. This 13th aspect of the damping coefficient switching type hydraulic shock absorber is shown in Figure 7 and -15-593861 Figure 10, the opening and closing control valve (flow adjustment valve 1 ο) is a single valve type and When a single hydraulic drive means 40 is used, the same hydraulic drive means 40 as in Fig. 5 is used. When the piston 3 moves in the direction A, the hydraulic pressure of the hydraulic chamber 4 on the left increases, but Since the hydraulic driving means 40 is not activated, the opening and closing operation valve 11 and the flow adjustment valve 10 (opening and closing control valve) are closed in advance to obtain the first damping coefficient, which is the maximum 値 Cm ax. At the maximum amplitude point on the left, when the moving direction of the piston 3 is changed to the B direction, the hydraulic pressure driving means 40 is actuated because the hydraulic pressure starts to decrease. The opening and closing operation valve 1 1 is temporarily opened and the flow regulating valve 1 0 is opened. Temporarily turn on and remove the load to obtain the second damping coefficient, which is the minimum 値 Cm i η. When the piston 3 moves in the B direction again, the oil pressure in the oil pressure chamber 4 on the right will rise, so the hydraulic drive means 40 will actuate, and the opening and closing operation valve 11 will be closed again, so that the flow adjustment valve 10 will be again Close and return to the first damping coefficient, which is the maximum 値 Cmax. The same operation is performed at the maximum amplitude point on the right, and the above operations are repeated. In addition, in this hydraulic type, when the flow rate is not large, the opening and closing operation valve 11 of the flow regulating valve 10 can be used alone as an on-off control valve. In the above structure, the piston movement or pressure change of the hydraulic shock absorber caused by an external force such as an earthquake or wind is changed by a mechanical or hydraulic driving means to directly switch and control the hydraulic pressure. The damper's opening and closing control valve can automatically switch the damping coefficient without requiring all external energy supply, so that sensors, controllers, solenoid valves, etc., as well as uninterruptible power supply devices and special power wiring, etc. It is not necessary, and it can often exert the energy absorption ability beyond ordinary hydraulic shock absorbers. (IV) Embodiment -16-593861 Hereinafter, the embodiment of the present invention will be described with reference to the drawings. In this embodiment, the hydraulic circuit of the hydraulic shock absorber uses a flow rate adjustment valve that allows a large amount of pressure oil to pass at high speed and can be shut off instantaneously. Figures 1 and 2 show the first embodiment in which the damping coefficient switching of the hydraulic shock absorber is performed mechanically, and Figures 3 and 4 show the second embodiment in the mechanical type. Figures 5, 6, and 7 show the third embodiment, the fourth embodiment, and the fifth embodiment in which the switching of the damping coefficient is performed by a hydraulic method. I · Single-valve type mechanical damping coefficient switching type hydraulic shock absorber 1-1 As shown in the first figure, the hydraulic shock absorber 1-1 is the same as the conventional one, which is composed of hydraulic cylinder 2 and double rod type The piston 3, the oil pressure chambers 4, 4 on both sides of the piston 3, and the opening and closing control valve 6 provided on the flow path 5 connecting the two oil pressure chambers are formed. In this embodiment, the opening and closing control valve 6 is a flow regulating valve (poppet valve) 10 for large flow, and is connected to an opening and closing operation valve (sound pilot valve) 11 that controls the opening and closing of the flow regulating valve 10. The opening and closing operation valve is a one-way switching valve with an open position and a closed position. A pressure accumulator 9 is provided on the hydraulic circuit to compensate for the volume change caused by the compression or temperature change of the hydraulic oil. When the opening and closing operation valve 11 is closed, when the piston 3 moves in the direction A (left side), the hydraulic pressure of the hydraulic chamber 4 on the left side passes through the check valve on the left side! 2 and the outflow flow path 13 and the inlet-side bypass flow path 14 with a throttle valve act on the back side of the valve body of the flow adjustment valve 10. Since this back pressure rises, the flow adjustment valve 10 is closed. Thereby, the damping coefficient of the hydraulic shock absorber 1-1 becomes the maximum 値 Cmax °. Then, when the on-off operation valve 11 is opened at the maximum amplitude point, the back pressure of the flow regulating valve 10 is reduced, and the flow regulating valve 1 0 The -17- pressure of the oil pressure chamber 4 on the left side passes through the check valve 12 on the left side and the outflow flow path 1 3, and the flow regulating valve 1 in the open state, and the bypass flow path 1 5 And the check valve 16 on the right side and the inflow passage 17 flow into the oil pressure chamber 4 on the right side, the load is removed and the damping coefficient of the hydraulic shock absorber 1 becomes the minimum 値 C mi η. When the piston 3 moves in the direction B (right side), this action is performed symmetrically, and the above actions are repeated to suppress the vibration (refer to the solid line D i in FIG. 14). In the hydraulic shock absorber 1-1 having such a configuration, in the first embodiment, as shown in FIG. 2, the hydraulic shock absorber 1-1 is a mechanical drive means 30, and only an external force is used. The damping coefficient of the hydraulic shock absorber 1-1 can be switched to the maximum 切换 C ma X and the minimum 値 C mi η in two stages. The mechanical drive means 30 is constituted by, for example, a linear gear (rack) 31 fixed to the piston rod 8 and a crank mechanism 32 which operates by the linear gear 31 to open and close the operation valve 1 1. The crank mechanism 3 2 fixes the base of the first link 33 to the hydraulic cylinder through a pin and the like, and is set to be swingable in the piston moving direction. The front end of the second link 34 is connected to the opening and closing through the pin and so on. Operate the valve body 1 1 a of the valve stem and the like of the valve 1 1. The base of the first link 33 is provided with a slide bar 35 that protrudes toward the linear gear 31. The front end rod of the sliding rod 35 is a double rod which is freely accommodated in the axial direction with respect to the base rod. The front rod rod is pushed toward the linear gear 31 by a spring 36. In such a crank mechanism 3 2 series, the first link 3 3 is set to tilt backward in the B direction with respect to the linear gear 3 1 in advance. In this state, the port system of the opening and closing operation valve 1 1 deviates, and the valve body 1 a is maintained in the closed position. In this state, when the piston rod 8 moves in the direction A, the sliding rod 3 5 corresponds to the unevenness and front of the linear gear 3 1-1 8-593861. The end rod only moves forward and backward and slides on the linear gear 31. The first link 3 The 3 series maintains a backward tilt posture, and the opening and closing operation valve 1 1 series remains closed. At the point of maximum amplitude, when the piston rod 8 changes its direction of movement and moves in the direction b, the front rod of the sliding rod 35 is held by the spring 36 to engage the tooth flanks of the linear gear 31 and the first connecting rod 3 3 Tilt in the A direction, the first link 33 and the second link 3 4 are linear, the valve body 1a of the opening and closing operation valve 11 is topped, and the port system is the same, so the opening and closing operation valve 11 is On. When the piston rod 8 is moved in the B direction, the first link 33 is tilted in the A direction, and the opening and closing operation valve 11 is closed again. In this state, the slide lever 35 is slid on the linear gear 31 in the same manner as described above, so the closed state of the open / close operation valve 11 is maintained. The mechanical damping coefficient switching type hydraulic shock absorber 1-! Constructed as described above, as shown in FIG. 12, is assembled into the column beam structure of the building through the bracket, and then performs the next operation. (1) From the state shown in Figures 1 and 2, when the piston rod 8 moves in the direction A due to factors such as earthquakes, the crank mechanism 32 does not slide on the linear gear 31, and the opening and closing operation valve 11 is maintained. In the closed state, the flow adjustment valve 10 is also maintained in the closed state, and the damping coefficient is set to a maximum 値 Cmax, so that the damping coefficient Cm ax is used to dampen. (2) At the point of maximum amplitude on the left side, when the moving direction of the piston rod 8 is changed to the B direction, the crank mechanism 3 2 is actuated into a straight line, and the valve body 1 1 a of the opening and closing operation valve 1 1 is opened and closed. The operation valve 11 is opened, and accordingly, the flow adjustment valve 10 is also opened. Since the pressure oil in the oil pressure chamber 4 on the left flows into the oil pressure chamber 4 on the right, the load is temporarily removed and the damping coefficient becomes − 1 9- 593861 is the minimum 値 Cm i η. (3) When the piston rod 8 moves in the direction B, the crank mechanism 32 moves in the reverse direction and tilts in the direction A, so the opening and closing operation valve 1 is closed again, and accordingly, the flow adjustment valve 10 is closed again. The damping coefficient is restored to the maximum 値 Cmax ° (4). In this state, the crank mechanism 3 2 does not slide on the linear gear 3 1, and the opening and closing operation valve 1 1 maintains a closed state. Relative to the movement in the B direction, Set the damping coefficient to the maximum 値 C ma X. (5) By repeating the above actions on both sides of the hydraulic cylinder, as shown by the solid line D! In Fig. 14, compared with the ordinary hydraulic shock absorber dq with a constant damping coefficient, energy absorption The ability is greatly improved. Moreover, the damping coefficient can be automatically switched only by the piston movement caused by the external force of vibration such as an earthquake. Although the above does not exemplify the case where the flow regulating valve 10 is used, when the flow is not large, the flow regulating valve 10 is omitted, and the damping coefficient can be switched only by opening and closing the operating valve 11. Π. Double-valve type mechanical damping coefficient switching type hydraulic shock absorber 1-2 As shown in Fig. 3, flow control valves (poppet valves) 1 0 and opening and closing are respectively provided for the left and right oil pressure chambers 4, 4 An embodiment of the operation valve (sound pilot valve) 11 opens and closes the on-off operation valve 11 and the flow rate adjustment valve 10 connected to each hydraulic chamber 4 individually. As in the first figure, the control flow rate adjustment valve 10 is opened and closed by opening and closing the operation valve 11. The opening / closing operation valve 1 1 is opened and closed by a right-handed and a left-handed valve, and is mechanically driven by the same method as in FIG. 1. The mechanical driving means 3 0 ′ is composed of a linear gear (rack) 3 1 and a link mechanism -20-593861 3 2 '. The link mechanism 32 is composed of a first link 33 and a second link 34. Table 1 flail 3 3 has the same structure as that of Figure 1. However, the second link 3 4 ′ is attached to the front end of the first link 3 3 through a pin or the like, and the pins and the like are passed through at both ends. The valve body 1 1 a ° connected to the right-handed and left-handed opening and closing operation valve 1 1 This kind of link mechanism 3 2 ′ is the same as the first figure, and the first link 3 3 is opposite to the linear gear 3 1, Set backwards in the B direction. In this state, the left opening and closing operation valve 11 is in the closed position, and the right opening and closing operation valve 11 is maintained in the open position. In this state, even if the piston rod 8 moves in the direction A, the slide lever 35 slides on the linear gear 31 as in the first figure, and the first link 3 3 maintains a backward leaning posture, for right and left hands. The opening and closing operation valves u and 11 maintain their states. At the point of maximum amplitude, when the piston rod 8 changes its direction of movement and moves to the B direction, the same as in the first figure, the tooth flanks of the linear gear 3 1 are used, and the first link 3 3 is tilted in the A direction. For right and left hands The valve body i} a of the opening and closing operation valve 1 1 moves horizontally together, the opening and closing operation valve 11 on the left is in an open state, and the opening and closing operation valve 11 on the right is in a closed state. Even if the piston rod 8 moves further in the direction B, the slide lever 35 slides on the linear gear 31, so the opening and closing operation valve 11 on the left side is opened, and the opening and closing operation valve 11 on the right side is kept closed. The mechanical damping coefficient switching type hydraulic shock absorber 1-2 constituted as described above operates as follows: (1) From the state of Figs. 3 and 4, when the piston rod 8 goes to -21 in accordance with an earthquake, etc. -593861 When moving in the direction of A, the link mechanism 3 2 is not used to slide the linear gear 3 丨. The left-side opening and closing operation valve 1 1 is kept closed, and the left-side flow regulating valve 10 is also kept closed. The damping coefficient The system becomes the maximum 値 Cmax, and the damping coefficient Cm a X is used for damping. (2) When the moving direction of the piston rod 8 changes at the maximum amplitude point on the left side and starts to move in the B direction, the link mechanism 3 2 is actuated, and the opening and closing operation valve 11 on the left side is opened, thereby the left side flow adjustment valve 10 is also turned on. Since the hydraulic oil in the oil pressure chamber 4 on the left side flows out to the oil pressure chamber 4 on the right side, the load is temporarily removed and the damping coefficient becomes the minimum 値 Cmin. (3) At this time, the opening and closing operation valve 1 1 on the right side is in a closed state. Even if the piston rod 8 moves to the B direction again, the link mechanism 3 2 does not slide on the linear gear 3 1, and the opening and closing operation valve on the right side 丨丨 Keep the closed state, so that the right-side flow adjustment valve 10 also maintains the closed state, and the damping coefficient returns to the maximum 値 Cm a X ° (4) By repeating the above actions on both sides of the hydraulic cylinder, as in the first As shown in Figure 4, compared with a hydraulic shock absorber with a damping coefficient of one ton, the energy absorption capacity is greatly improved. In addition, the damping coefficient can be automatically switched only by the movement of the piston caused by a vibrational external force such as an earthquake. In addition, in the case of the second embodiment, when the flow rate is not large, the flow rate adjustment valve 10 is omitted, and the damping coefficient can be switched only by opening and closing the operation valve 丨 丨. Melon · Single valve · Dual drive type Hydraulic damping coefficient switching type hydraulic shock absorber 1-3 As shown in Fig. 5, replace the mechanical drive means 30 of Fig. 1 and change to the hydraulic drive means 40 is assembled into the hydraulic circuit in Figure 1, and the damping coefficient is switched by changing the hydraulic pressure. -22- 593861 This hydraulic drive means 40 is connected to the inflow passages 1 7 and 17 of the hydraulic chambers 4 and 4 through the throttle valve 41, respectively, and is a buffer 42 for accumulating oil. And a switching valve (pop-up valve) 43 which is connected to this buffer 42 to open and close the control valve for opening and closing operation 1 1. Switching valve 4 3 is the same as the flow regulating valve 1 〇 It is a poppet valve type. The buffer port 4 is connected to the inlet port, and the back pressure port and the inflow passage 17 are connected. The pressure oil from the outlet port is used as the pilot pressure. By supplying the opening-closing operation valve i 丨, a valve body such as a spool of the opening-closing operation valve 11 is driven. Therefore, when the pressure in the oil pressure chamber 4 rises, although pressure oil is accumulated in the buffer 42, since the large back pressure acts on the switching valve 4 3 through the inflow passage 17, the switching valve 4 3 is Closed by the outlet port of the switching valve 43, the oil pressure system does not act as a pilot pressure for the opening and closing operation valve 11 and the opening and closing operation valve i 丨 remains closed. When the pressure in the oil pressure chamber 4 starts to decrease, the back pressure system of the switching valve 43 becomes lower than the pressure of the buffer 42, the switching valve 4 3 is opened, and the pressure oil system from the outlet port of the switching valve 43 is used as The pilot pressure is sounded to act on the on-off operation valve 1 1, and the on-off operation valve 11 is opened. The hydraulic damping coefficient switching type hydraulic shock absorber 1-3 of the above structure operates as follows: (1) From the state of FIG. 5, when the piston rod 8 moves in the direction A according to an earthquake, etc., The pressure in the hydraulic chamber 4 on the left will rise. Since the switching valve 4 3 on the left is closed as described above, the opening and closing operation valve 1 1 on the left is maintained closed, whereby the central flow regulating valve 10 is also maintained. In the closed state, the damping coefficient is set to the maximum 値 Cm ax, and the damping coefficient Cm ax is used to dampen the vibration. (2) When the moving direction of the piston rod 8 is changed at the maximum amplitude point on the left side, and the opening direction is from 23 to 593861, the pressure in the oil pressure chamber 4 on the left side starts to decrease. The switching valve 4 on the left side is as described above. It opens normally, so the opening and closing operation valve} i on the left side is opened, and accordingly, the central flow adjustment valve 丨 〇 is also opened. Since the pressure of the oil chamber 4 on the left side passes through the flow adjustment valve 1 〇, the oil pressure on the right side is opened. Since the chamber 4 flows in, the load system is temporarily removed, and the damping coefficient system becomes the minimum 値 Cm i η. (3) When the piston rod 8 moves to the direction B again, the buffer 42 on the right, the switching valve 4 3, and the opening / closing operation valve 1 act in the same manner as above, because the central flow regulating valve 10 is closed, so the damping coefficient is Return to the maximum 値 Cmax. (4) By repeating the above actions on both sides of the hydraulic cylinder, as shown in Fig. 4 and 4, compared with the ordinary hydraulic shock absorber with a constant damping coefficient, the energy absorption capacity is greatly improved. In addition, the damping coefficient can be automatically switched only by the movement of the piston caused by a vibrational external force such as an earthquake. In addition, although two opening / closing operation valves 11 are provided, one may be sufficient. In the case of the third embodiment, when the flow rate is not large, the flow rate adjustment valve 10 can be omitted, and the damping coefficient can be switched only by operating the valve 11 by opening and closing. IV. Double-valve and double-drive hydraulic damping coefficient switching type hydraulic shock absorbers 1-4 As shown in Fig. 6, the right-hand and left-hand flow control valves 10 are arranged in the hydraulic circuit of Fig. 5 Use one for each embodiment. The other components are the same as those in FIG. 5. The hydraulic damping coefficient switching type hydraulic shock absorber 1-4 system configured as above is different from FIG. 5 in that two flow regulating valves 10 are used, and is the same as that in FIG. 5 The operation is as follows: (1) From the state of Fig. 6, when the piston rod 8 moves in the direction A according to an earthquake, the pressure of the oil pressure chamber 4 on the left will rise. Because of the left switching valve 4 3 -24- 593861 is closed as described above, so the left-side opening and closing operation valve 11 is kept closed, whereby the left-side flow regulating valve 1 〇 is also kept closed, and the damping coefficient is set to the maximum 値 Cm ax, and the damping coefficient Cm ax to dampen. (2) When the moving direction of the piston rod 8 changes and starts to move in the B direction, the pressure of the oil pressure chamber 4 on the left begins to decrease, and the switching valve 4 3 on the left is opened as described above, so the left opening and closing operation valve 1 Series 1 is opened, and the left side flow regulating valve 10 is also opened. Since the pressure of the hydraulic chamber 4 on the left side flows into the hydraulic chamber 4 on the right side through the flow regulating valve 10 on the left side, the load is temporarily unloaded. In addition, the damping coefficient system becomes the minimum 値 Cm i η. (3) When the piston rod 8 moves in the direction B again, the buffer 42 on the right, the switching valve 43, and the opening and closing operation valve 11 on the right operate in the same manner as described above, because the flow regulating valve 10 on the right will close, so damping The coefficient is returned to the maximum 値 Cm a X ° (4). By repeating the above action on both sides of the hydraulic cylinder, as shown in Figure 14, compared with the ordinary hydraulic shock absorber with a constant damping coefficient. The energy absorption capacity is greatly improved. In addition, the damping coefficient can be automatically switched only by the movement of the piston caused by a vibrational external force such as an earthquake. In addition, in the case of this fourth embodiment, when the flow rate is not large, the flow rate adjustment valve 10 is omitted, and the damping coefficient can be switched only by opening and closing the operation of the valve 11. V. Single valve / single drive type hydraulic damping coefficient switching type hydraulic shock absorber 1-5 As shown in Fig. 7, a hydraulic type is installed in the hydraulic circuit of the single valve type of Fig. 5 Embodiment of the driving means 40. The other components are the same as those in FIG. 5. -25- 593861 The hydraulic damping coefficient switching type hydraulic shock absorber constructed as above 丨 -5 series only uses one flow regulating valve 10 and one hydraulic driving means 40 respectively. Different from Fig. 5 and acting the same as the occasion of Fig. 5: (1) From the state of Fig. 7, when the piston rod 8 moves in the direction of A according to an earthquake, etc., the left side of the oil pressure chamber 4 The pressure will rise. Since the switching valve 4 3 on the left is closed as described above, the opening and closing operation valve 11 is maintained closed, whereby the flow adjustment valve 10 is also maintained closed, and the damping coefficient is maximized 値 Cmax, The damping coefficient Cmax is used for damping. (2) When the moving direction of the piston rod 8 is changed to the B direction, the pressure of the oil pressure chamber 4 on the left side starts to decrease, and the switching valve 43 is opened as described above, so the opening and closing operation valve 11 is opened, and the flow rate is accordingly. The adjustment valve 10 is also opened, and the pressure of the oil pressure chamber 4 flows into the oil pressure chamber 4 on the right through the flow adjustment valve 10, so the load is temporarily removed and the damping coefficient becomes minimum 値 Cnn η. (3) When the piston rod 8 moves to the direction B again, the buffer 4 2 and the switching valve 4 3, and the opening and closing operation valve 1 1 operate in the same manner as described above, because the flow adjustment valve 10 will close, so the damping coefficient is restored to The maximum 値 Cmax. (4) By repeating the above actions on both sides of the hydraulic cylinder, as shown in Fig. 4 and 4, compared with the ordinary hydraulic shock absorber with a constant damping coefficient, the energy absorption capacity is greatly improved. In addition, the damping coefficient can be automatically switched only by the movement of the piston caused by a vibrational external force such as an earthquake. In addition, although two opening / closing operation valves 11 are provided, one may be used. . In the case of this third embodiment, even when the flow rate is not large, the flow rate adjustment valve 10 can be omitted, and the damping coefficient can be switched only by opening and closing the operation of the valve 11. -26-593861 In addition, in the case of this fifth embodiment, the flow adjustment valve 10 is omitted when the flow rate is not large, and the damping coefficient can be switched only by opening and closing the operation valve 11. VI. Damping coefficient switching type hydraulic shock absorber with bleed valve In order to avoid undesired large load in the device and damage the device, for example, bleed valves are sometimes provided to limit the pressure of the left and right oil pressure chambers. The load-deformation relationship when a relief valve is provided in a damping coefficient switching type hydraulic shock absorber having an on-off control valve with a mechanical drive means is shown in the graph in FIG. 15. In Figure 15, the pressure is approximately constant at the pressure release load FR. In the case of the mechanical type, since the opening and closing control valve is not operated at the end of the stroke of the piston regardless of the pressure, no problem occurs. On the other hand, when a relief valve is provided in a damping coefficient switching type hydraulic shock absorber having an on-off control valve having a hydraulic drive means, as shown in FIG. 15, when the pressure relief load FR or more, The maximum load is not necessarily at the maximum amplitude point. For example, at the maximum point of the hydraulic pressure load shown at point P, the operation of the opening and closing control valve system is completed, so the load deformation relationship of FIG. 15 cannot be realized. Therefore, in the case of the hydraulic type, the opening and closing control valve does not operate when the pressure relief load FR in FIG. 15 or more is exceeded, and the opening and closing control valve system operates at a pressure lower than the pressure relief load h to achieve Figure 15 shows the load deformation relationship. Specifically, as shown in FIGS. 8 to 10, in addition to the main relief valve 50, a relief valve 51 is provided to limit the pressure of the buffer 42, and the relief valve 51 is operated by this. The starting pressure is set below the operating pressure of the main relief valve 50 to achieve the load-deformation relationship of Fig. 15. In the single valve / double drive type damping coefficient switching type hydraulic shock absorber-27-593861 1-3 in FIG. 8, two flow paths connecting the left and right oil pressure chambers 4 and 4 are provided. On the road, a main relief valve 50 for releasing the pressure of each hydraulic chamber 4 is provided, and the left and right buffers 42 are provided with a bypass flow path 1 for discharging the pressure between the buffer 42 and the flow adjustment valve 10 toward the outlet side. 5 The bleeder relief valve 51 is set to a pressure lower than the operation start pressure of the main bleeder valve 50 by setting the set pressure of the bleeder valve 51 to be lower than the operation start pressure of the main bleeder valve 50 only. The switching valve 43 is opened, the opening and closing operation valve 11 is opened, and the flow adjustment valve 10 is opened. In the case of the double valve / double drive type damping coefficient switching type hydraulic shock absorber 1-4 in FIG. 9, and in the case of the single valve • single driving type damping coefficient switching type hydraulic shock absorber 1-4 in FIG. 9 The main bleed valve 50 and the bleed valve 51 are also provided in the same manner, and operate in the same manner as described above. In addition, in the case where there are one flow regulating valve 10 in FIGS. 8 and 10, two main relief valves 50 are provided on the flow path that connects the left and right hydraulic chambers 4, 4. However, one relief valve 50 and the flow regulating valve 10 may be arranged in parallel between the outflow flow path 13 and the outflow bypass flow path 15 passing through the check valve. (V) Brief description of the drawing Figure 1: The hydraulic circuit diagram of the first embodiment of mechanically performing the damping coefficient switching of the damping coefficient switching type hydraulic shock absorber of the present invention. Fig. 2 is a side view showing the valve driving mechanism of the first embodiment. Fig. 3 is a hydraulic circuit diagram of the second embodiment in which the damping coefficient switching of the damping coefficient switching type hydraulic shock absorber of the present invention is performed mechanically. 593861 Fig. 4: A side view showing a valve driving mechanism of the second embodiment. Fig. 5 is a hydraulic circuit diagram of a third embodiment in which the damping coefficient switching of the damping coefficient switching type hydraulic shock absorber of the present invention is performed by a hydraulic method. Fig. 6 is a hydraulic circuit diagram of a fourth embodiment in which the damping coefficient switching of the damping coefficient switching type hydraulic shock absorber of the present invention is performed in a hydraulic type. Fig. 7 is a hydraulic circuit diagram of a fifth embodiment in which the damping coefficient switching of the damping coefficient switching type hydraulic shock absorber of the present invention is performed in a hydraulic type. Fig. 8 is a hydraulic circuit diagram showing an embodiment in which a drain valve is provided in the third embodiment of Fig. 5; Fig. 9 is a hydraulic circuit diagram showing an embodiment in which a drain valve is provided in the fourth embodiment in Fig. 6. Fig. 10: A hydraulic circuit diagram showing an embodiment in which a drain valve is provided in the fifth embodiment of Fig. 7. Figure 11: Essential diagram showing the basic structure of a damping coefficient switching type hydraulic shock absorber. Fig. 12: A front view showing an example of installation of a hydraulic damper for vibration damping. Fig. 13: Mechanical model diagram of the hydraulic damper for vibration damping. Fig. 14: A graph showing the relationship between the load and deformation of a hydraulic damper for vibration damping. Fig. 15: A graph showing the relationship between the load and deformation of a shock absorber hydraulic shock absorber provided with a relief valve. -29- 593861 Description of representative symbols of main parts '' 1-1 ~ 1-5 ... Hydraulic shock absorber 2. •• Hydraulic cylinder 3 • •• Piston 4 • •• Hydraulic chamber 5 • •• Flow path 6 • •• Open / close control valve 8 • •• Piston rod 9 • •• Accumulator 10 • • • Flow adjustment valve 11 · • • Open / close operation valve 12 · • • Check valve 13 · • • Outflow flow path 14 · • • Inflow bypass flow path 15 · • • Outflow bypass flow path 16 · • • Check valve 17 • • • Inflow passage 11a • • • Valve bodies 30, 3 0 '• • Mechanical drive bow 31 • • • Linear gear (rack) 32 • • • Crank mechanism 32' • • • Link mechanism 33 · • • 1st link 34, 3 4 '· · · 2nd link-30
593861 35 · · •滑動杆 36 · · •彈簧 40 · · •油壓式驅動手段 41 · · •節流閥 42 · · •緩衝器 43 · · •切換閥 50 ·. •主放洩閥 51 · · •放洩閥593861 35 · · · Slide 36 · · · Spring 40 · · · Hydraulic drive 41 · · · Throttle valve 42 · · · • Shock absorber 43 · · • Switching valve 50 ·. • Main relief valve 51 · · • Drain valve
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