200415290 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、槁樑、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11-336366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。 馨 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 200415290 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D!。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 7-4 5 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CΙΏ a X，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 1 η之後，開閉控制閥再度閉合而可獲得第丨阻尼係數亦 200415290 即最大値C m a x。 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 1及流量調整閥1 0 200415290 以獲得第1阻尼係數亦即最大値Cm a χ。 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1 1及流量調整閥丨〇再度 閉合以回復至桌1阻尼係數亦即最大値Cmax。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。 200415290 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 〇 )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32係不作動，維持 開閉操作閥1 1和流量調整閥丨〇爲閉合狀態，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和流量 調整閥1 0係暫時開啓，然後，開閉操作閥丨丨和流量調整閥 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32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30’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11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C m i η。此時，右側之流量調整閥1 〇 (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 C m a X。在右側之最大振幅點也進行同樣的作動，以上的動作 -10- 200415290 係被反覆。此外，在此場合，流量不大時，流量調整閥l 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Cinax,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 - 1 1 - 200415290 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40以例如由蓄 積壓力的緩衝器42、以及將此緩衝器42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4 2的 壓力爲大時輸出響導壓之切換閥4 3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 〇係成閉合狀 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F R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F R以上時，開閉控制閥不動作，而在較釋壓負載 -12- 200415290 FR還低的壓力，開閉控制閥會動作，以作成實現第1 5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圖所示，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51，藉由將放洩閥5 1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5 0之動作開始壓力以下時切換閥4 3會開啓，開閉操作 閥1 1會開啓，且流量調整閥1 0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 0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 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， - 13- 200415290 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。 此第丨丨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 〇 )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 作閥丨丨且中央之流量調整閥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 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 0 ,使負載卸除 以獲得第2阻尼係數亦即最小値C m 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^ -14- 200415290 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（流量調整閥丨〇 )係2個雙閥型 且使用2個油壓式驅動手段4 0之場合，乃使用與第5圖同 樣的油壓式驅動手段4 0 ,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n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 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4 0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Cm 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 0則會回復至第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 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 0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- 200415290 第l 〇圖所示，開閉控制閥（流量調整閥1 〇)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4 0，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 〇暫時開啓，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40係會作動，因開閉操作閥1丨再度閉合，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- 200415290 以下，依圖示本發明之實施形態加以說明。此實施形態例 #，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、 胃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丨〇開閉之開閉操作 閥（響導閥）1 1。開閉操作閥1 i係具有開位置和閉位置之 二路切換閥。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1 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，油壓減震器丨的阻尼係數係成爲最 大値Cm a X ° 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，流量調整閥丨〇係開啓，左側之油壓室4的 -17- 200415290 壓油係通過左側之止回閥12和流出用流路13、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Cm 1 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3 1作動以開閉開閉操作閥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 i , 事先設定爲朝B方向後傾。在此狀態，開閉操作閥1丨的埠 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 200415290 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，開閉操作閥丨丨係保持閉合狀態。 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n的閥體丨丨a被頂上， 且琿係一致，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 雲力杆3 5係與前述相同樣地在直線齒輪3丨上滑動，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丨_ i， 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i 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，開閉操作閥丨丨係開啓，依此，流 重S周整閥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 200415290 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Η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Cmax。 (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D()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。 以上雖然例示了使用流量調整閥1 〇的場合，但是在流量 不大的場合，係省略流量調整閥1 〇，僅開閉操作閥n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 200415290 32’所構成。連桿機構32,係由第1連桿33和第2連桿34, 構成。 第1連桿3 3爲與第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i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32,係與第1圖同樣地，第1連桿33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1 1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n、 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π的閥體u 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丨係被保持在閉 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- 200415290 A方向移動時，藉連桿機構3 2 ’不在直線齒輪3 1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1 0也維持閉合狀態，阻尼係數係成爲最大値C m a X，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 η。 (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1 1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，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1 1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40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- 200415290 此油壓式驅動手段4 0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43係與流量調整閥10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1 1，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43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1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42的壓力還低，切換閥43係開啓，來自切 換閥43之出口埠的壓油係作爲響導壓以對開閉操作閥i 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43 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 〇也維持閉合狀態，阻尼係 數係成最大値Cm a X，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 -23- 200415290 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，中央之流量調整閥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4 2、切換 閥4 3、開閉操作閥1 1係與前述同樣地動作，因爲中央之流 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，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 〇這點上與第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 - 200415290 係如前述般地被閉合，所以左側之開閉操作閥π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 數係成最大値C γώ a X，而以此阻尼係數C Hi a X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11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Cnn 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、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40的實施形態。其他之構成係與第5 圖相同。 200415290 如以上構成之油壓式的阻尼係數切換型油壓減震器1 - 5 係，僅在各自使用了 1個流量調整閥1 〇和1個油壓式驅動 手段4 0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 〇也開啓，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C m i 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 〇會 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，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- 200415290 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FR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 0圖所示，除了主放洩閥5 0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5 1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_ 200415290 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5 1，藉由將放洩閥 51之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1 0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 0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5 0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。 - 2 8 - 200415290 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：表不在第7圖的第5貫施形態設置有放拽閥之 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。 - 2 9 - 200415290 「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 1 0 · · ·流量調整閥 11· ••開閉操作閥 12 · · ·止回閥 1 3 · · ·流出用流路 1 4 · · ·入側旁路流路 1 5 · · ·出側旁路流路 1 6 · · ·止回閥 1 7 · · ·流入用通路 1 1 a · · ·閥體 30、30’ · · ·機械式驅動手段 3 1· · •直線齒輪（齒條） 3 2· ••曲柄機構 3 2 ’ · · ·連桿機構 3 3· · •第1連桿 34、34’· · ·第 2 連桿 -30- 200415290 3 5 · · ·滑動杆 3 6 · · ·彈簧 40 · · •油壓式驅動手段 41 . · ·節流閥 42 · · ·緩衝器 4 3 · · ·切換閥 5 0 · · ·主放洩閥 5 1· · •放洩閥200415290 发明 Description of the invention (The description of the invention should state: the technical field, prior art, content, implementation, and drawings of the invention.) (1) The technical field to which the invention belongs: The present invention relates to reducing earthquakes or wind. Hydraulic shock absorbers that shake structures (buildings, beams, roofs, etc.) caused by external vibration. (II) Prior technology: In the vibration damping device in the form of a shock absorber for reducing the structure shake, it is a φ variable damping device with a two-stage control that makes the opening and closing control valve to be fully open and fully closed (for example, , Japanese Patent Laid-Open No. 11-336366) and so on. 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. The hydraulic shock absorber 1 of Xin is as 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. The longitudinal L 200415290 shaft hydraulic shock absorber load L in Figure 14 and the horizontal axis deflection between layers (Deformation at the end of Maxwell mode). The dashed line damping coefficient is a conventional shock absorber D0. Wire system damping coefficient switching type shock absorber D !. Also, only the two-step 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. 7-4 5 7 8 1 In comparison, 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. Then, the first damping coefficient, that is, the maximum 値 CΙΏ a X, can be obtained. 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 Cm 1 η, and the opening and closing control valve is closed again and The first damping coefficient obtained is 200415290, which is the maximum 値 C max. 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 11 and the flow adjustment valve 1 200415290 to obtain the first damping coefficient, that is, the maximum 値 Cm a χ. 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 11 and the flow adjustment valve 丨 〇 are closed again by the mechanical driving means 30 to return to the table 1 damping coefficient, which is the maximum 値 Cmax. 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. 200415290 The fourth aspect of the damping coefficient switching type hydraulic shock absorber is shown in Fig. 1 when the on-off control valve (flow adjustment valve 1 0) is a single valve type. Relative to the movement in the A direction of the piston 3, the crank mechanism 32 is inactive, and the opening and closing operation valve 11 and the flow adjustment valve are kept closed. When starting to move in the B direction, the crank mechanism 32 is activated and first opens and closes. Operate the valve! 1 and the flow regulating valve 10 are temporarily opened, and then the opening and closing operation valve 丨 丨 and the flow regulating 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, and the closed state is closed. maintain. 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 driving means 3 0 ′ which 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 driving means 30 ′ is not actuated, and the operation valve 1 1 is opened and closed. Close and close the left side flow regulating valve 10 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, it is obtained by temporarily opening and closing the operation valve 11 with the mechanical driving means 30 'and temporarily opening the flow regulating valve 10 on the left side to remove the load. The second damping coefficient is the minimum 値 C mi η. At this time, the right-side flow regulating valve 10 (opening and closing control valve) 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 C ma X, can be obtained by moving in the B direction. . The same action is performed at the maximum amplitude point on the right. The above action is repeated. In addition, in this case, 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 opening and closing 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 Cinax, and the opening and closing control is performed when the movement of the piston is reversed to reduce the oil pressure. 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. The cylinder buffer chamber communicates with the buffer to accumulate pressure, and a switching valve that operates based on the pressure of the buffer and the pressure difference between the cylinder cylinder pressure chamber and the pressure cylinder-1 1-200415290. As shown in FIG. 5, FIG. 6, or FIG. 7, the seventh embodiment of the damping coefficient switching type hydraulic shock absorber uses a hydraulic drive means 40 such as a buffer 42 that accumulates pressure, and Compare the pressure of this buffer 42 with the actual pressure of the flow path after the hydraulic cylinder chamber is directly combined. Only when the pressure of the buffer 42 is large is the switching valve 43 that outputs the pilot pressure. The buffer 4 2 and the switching valve 4 3 on the left side increase the pressure caused by the movement of the piston 3 in the A direction. The opening and closing operation valve 11 and the flow adjustment valve 10 0 are maintained closed, and the movement caused by the movement in the B direction is closed. When the pressure drops, the opening and closing operation valve 11 and the flow adjustment valve 10 are temporarily opened, and then, via the right buffer 42 and the switching valve 43, the opening and closing operation valve 11 and the flow adjustment valve 10 are closed 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 -12-200415290 FR, the opening and closing control valve will operate to create a load deformation relationship as 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 includes: each of which limits the pressure of the hydraulic chamber on both sides of the piston A relief valve that restricts the pressure of the buffer. When the actuation pressure of the relief valve is higher than the hydraulic pressure driving means for driving the opening and closing control valve, the opening and closing control valve remains closed and The pressure of the shock absorber is equal to or lower than the operation start pressure of the relief valve. The 10th aspect of the damping coefficient switching type hydraulic shock absorber is shown in Fig. 8 to Fig. 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 pressures 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 side bypass flow path 15 are provided. The set pressure of 51 is set to be lower than the operating start pressure of the main relief valve 50, so that the switching valve 4 3 will open only when the operating start pressure of the main relief valve 50 is below the opening and closing operation valve 1 1 will open , 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 bypass flow path 15, a relief valve 50 and a flow adjustment valve 10 are arranged in parallel. In the eleventh aspect of the present invention, the damping coefficient switching type hydraulic shock absorber is a damping coefficient switching type hydraulic shock absorber such as the sixth, seventh, eighth, ninth, or tenth aspect, in which two groups of oil The hydraulic pressure driving means are hydraulic chambers provided on both sides of the piston.-13- 200415290 This hydraulic pressure driving means is used to drive an on-off control valve for the hydraulic pressure chambers provided on both sides of the piston in common. . As shown in Figures 5 and 8, the damping coefficient switching type hydraulic shock absorber in this aspect is shown in Figures 5 and 8. The opening and closing control valve (flow adjustment valve 1 〇) is a single valve type and uses two hydraulic 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 which operates 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 driving means 40 is not activated, and the left-side opening and closing operation valve 丨 丨 is closed, and the central flow regulating valve 10 (opening and closing control valve) is closed in advance to obtain the first damping coefficient, that is, 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 10 is used to remove the load to obtain the second damping coefficient, which is the minimum 値 C mi 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. 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 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 hydraulic driving means are hydraulic chambers respectively provided on both sides of the piston. The hydraulic driving means is used to drive the opening and closing control of the hydraulic chambers that are commonly provided on both sides of the living chamber. valve. 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 adjustment valve 丨 〇) 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 of A, although the oil pressure in the oil pressure chamber 4 on the left will rise, The hydraulic drive means 40 is not operated, and the left-side opening and closing operation valve n 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 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 the flow rate adjustment The valve 1 〇 removes the load to obtain the second damping coefficient, that is, the minimum 値 Cm i η. When the piston 3 moves in the direction B again, the oil pressure in the oil pressure chamber 4 on the right will rise, so the oil pressure driving means 40 on the right will act, and the right-hand opening and closing operation valve 11 and the flow adjustment valve 10 will be closed. Will return to the first damping coefficient, which is the 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 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. The thirteenth aspect of the present invention has a damping coefficient switching type hydraulic shock absorber such as the sixth, seventh, eighth'9 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 Fig. 7 '-15- 200415290 Fig. 10, and the on-off control valve (flow adjustment valve 1 〇) is a single valve type and When using one hydraulic drive means 40, the same hydraulic drive means 40 as in Fig. 5 is used. While the piston 3 is moving in the direction of A, although the hydraulic pressure of the hydraulic chamber 4 on the left increases, However, because the hydraulic drive means 40 does not operate, 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, and the opening and closing operation valve 1 1 is temporarily opened and the flow rate adjustment valve 1 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 because the opening and closing operation valve 1 丨 is closed again, the flow adjustment valve 10 is closed again. 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 -16-200415290 The following describes the embodiment of the present invention as shown in the drawings. In the example # of this embodiment, a flow regulating valve is used in the hydraulic circuit of the hydraulic shock absorber to allow high-pressure hydraulic oil to pass at high speed and to be instantaneously blocked. 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. FIG. 5, FIG. 6 and FIG. 7 show the third embodiment, the fourth embodiment, and the fifth embodiment in which the switching of the damping coefficient is performed by oil pressure. 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. The opening / closing control valve 6 is a flow regulating valve (poppet valve) 10 for large flow in this embodiment, and is connected to an opening / closing operation valve (sound pilot valve) 11 which controls the opening and closing of the flow regulating valve. The open / close operation valve 1 i is a two-way switching valve having 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 1 2 on the left side and the outflow flow path 13 and has The inlet side of the throttle valve bypasses the flow path 14 and acts on the back 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 becomes the maximum 値 Cm a X °. Then, when the on-off operation valve 11 is opened at the maximum amplitude point, the back pressure of the flow adjustment valve 10 is reduced, and the flow adjustment valve 丨 〇 The system is open, and the pressure of the oil pressure chamber 4 on the left side is -17- 200415290. The oil pressure is passed through the left check valve 12 and the outflow flow path 13, and the open flow control valve 1 〇, the outlet bypass flow path 1 5, And the check valve 16 on the right side and the inflow passage 17 flow into the hydraulic chamber 4 on the right side, so the load is removed and the damping coefficient of the hydraulic shock absorber 1 becomes the minimum 値 Cm 1 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, a mechanical drive means 30 is used, and the hydraulic shock absorber 1-1 only depends on an external force. 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 driving means 30 is constituted by, for example, a linear gear (rack) 31 fixed to the piston rod 8 and a crank mechanism 32 by which the linear gear 31 operates to open and close the operation valve 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 33 is set to tilt backward in the B direction with respect to the linear gear 3 i in advance. In this state, the port system of the opening / closing operation valve 1 丨 deviates, and the valve body 1 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 of the linear gear 31. The front 200415290 end rod only moves forward and backward and slides on the linear gear 31. The first link 3 3 maintains Lean back posture, the opening and closing operation valve 丨 丨 is kept closed. At the point of maximum amplitude, when the piston rod 8 changes its direction of movement and moves to the B direction, the front rod of the sliding rod 35 is pressed by the spring 36 to engage the tooth flanks of the linear gear 31, and the first link 3 to 3 Tilt in the A direction, the first link 33 and the second link 34 are linear, and the valve body 丨 a of the opening and closing operation valve n is topped, and the system is the same, so the opening and closing operation valve 11 is opened. status. 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 gliding lever 35 is slid on the linear gear 3, as described above, so the closed state of the open / close operation valve 11 is maintained. After the mechanical damping coefficient switching type hydraulic shock absorber 丨 _ i constituted above is assembled into a column beam structure of a building through a bracket as shown in FIG. 12, the next operation is performed. (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 i 〇 is also maintained in the closed state, and the damping coefficient is set to the maximum 値 Cmax, so that the damping coefficient Cm ax is used for damping. (2) At the point of maximum amplitude on the left side, when the moving direction of the piston rod 8 is changed to the direction b, 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 is opened. Accordingly, the flow control valve 10 also becomes open. Because the pressure of 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 The system 200415290 is the minimum 値 Cm i η. (3) When the piston rod 8 moves in the direction B again, the crank mechanism 32 moves in the opposite direction and tilts in the direction A, so the opening and closing operation valve Η is closed again, and accordingly, the flow adjustment valve 10 is closed again. The damping coefficient is returned 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 is maintained in a closed state. With respect to the movement in the B direction, the The damping coefficient is set to the maximum 値 Cmax. (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 D () with a constant damping coefficient, The energy absorption capacity 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 has exemplified the case where the flow regulating valve 10 is used, when the flow rate is not large, the flow regulating valve 10 is omitted, and the damping coefficient can be switched only by opening and closing the operation valve n. Π · Double-valve type mechanical damping coefficient switching type hydraulic shock absorber 1 _ 2 As shown in Fig. 3, flow regulating valves (poppet valves) are respectively provided for the left and right hydraulic chambers 4 and 1 0 And the embodiment of the on-off operation valve (sound pilot valve) 11 opens and closes the on-off operation valve 11 and the flow rate adjustment valve 10 connected to the hydraulic chambers 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) 31 and a link mechanism 200415290 32 ′. The link mechanism 32 is composed of a first link 33 and a second link 34. The first link 33 has the same structure as in the first figure, but the second link 34 is connected to the front end of the i-th link 33 through a pin or the like, and is connected through the pin or the like at both ends. The valve body 1 1 a of the right-handed and left-handed operating valve 1 1 ° This kind of link mechanism 32 is the same as the first figure, and the first link 33 is in the direction B relative to the linear gear 3 1 Set backwards. 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 of A, the slide lever 35 slides on the linear gear 31 in the same manner as in the first figure, and the first link 3 3 maintains a backward leaning posture, for right-handed and left-handed use. The opening and closing operation valves n 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 ua of the opening / closing operation valve π moves horizontally together, the opening / closing operation valve 11 on the left side is in an open state, and the opening / closing operation valve 11 on the right side is in a closed state. Even if the piston rod 8 moves in the B direction again, 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 1 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. -200415290 When moving in the A direction, the link mechanism 3 2 'does not slide on the linear gear 3 1 and the left opening and closing operation valve 1 1 is maintained closed, whereby the left flow regulating valve 10 is also maintained closed and damped. The coefficient system becomes the maximum 値 C ma X, and the damping coefficient Cm a X is used for damping. (2) When the moving direction of the piston rod 8 is changed 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 flow regulating valve on the left side 10 is also turned on. Since the hydraulic oil in the hydraulic chamber 4 on the left side flows out to the hydraulic chamber 4 on the right side, the load is temporarily removed, and the damping coefficient becomes the minimum 値 Cm i η. (3) At this time, the opening and closing operation valve 1 on the right side is in a closed state. Even if the piston rod 8 moves in the direction B, the link mechanism 3 2 'does not slide on the linear gear 3 1 and the opening and closing operation valve 1 on the right side. The 1 series is maintained closed, so that the right-side flow adjustment valve 10 is also maintained closed, and the damping coefficient is restored to the maximum 値 Cm a X ° (4) by repeating the above actions on both sides of the hydraulic cylinder, as described in section 丨As shown in Fig. 4, compared with the usual hydraulic shock absorber with a certain 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 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 11. 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 The 40 is assembled into the hydraulic circuit of FIG. 1, and the change of the damping coefficient is performed by the change of the hydraulic pressure. -22- 200415290 This hydraulic drive means 40 is an inflow passage 1 7 and 17 connected to each of the hydraulic chambers 4 and 4 through a throttle valve 41 and a buffer for accumulating oil. 42 and a switching valve (pop-up valve) 43 connected to the buffer 42 for opening and closing the control valve 11 for opening and closing. The switching valve 43 is a poppet valve type similar to the flow regulating valve 10. The buffer port 4 2 is connected to the inlet port, and the back pressure port and the inflow passage 17 are communicated. The pressure oil from the outlet port is used as a pilot pressure to supply. The operation valve 11 is opened and closed, and a valve body such as a spool of the 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 43 through the inflow passage 17, the switching valve 4 3 is closed. From 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 1 remains closed. When the pressure in the oil pressure chamber 4 starts to decrease, the back pressure of the switching valve 43 is lower than the pressure of the buffer 42. The switching valve 43 is opened. The pressure oil from the outlet port of the switching valve 43 is used as the pilot pressure. Acts on the on-off operation valve i 1 to open the on-off operation valve 11. 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 of the hydraulic chamber 4 on the left will rise. Since the switching valve 43 on the left is closed as described above, the opening and closing operation valve 1 1 on the left remains closed, whereby the central flow regulating valve 1 〇 also remains closed. State, the damping coefficient is set to the maximum 値 Cm a X, and the damping coefficient Cm a X is used to dampen the vibration. (2) At the point of maximum amplitude on the left side, when the direction of movement of the piston rod 8 is changed, and -23-200415290 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 as described above It opens normally, so the opening and closing operation valve 1 1 on the left is opened. Accordingly, the central flow regulating valve 10 is also opened. Since the pressure of the oil pressure chamber 4 on the left passes the flow regulating valve 10, the pressure on the right 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 right side buffer 4 2, the switching valve 4 3, and the opening and closing operation valve 1 1 act in the same manner as above, because the central flow regulating valve 10 will close, so damp The coefficient is returned to the maximum 値 Cm a X. (4) By repeating the above actions on both sides of the hydraulic cylinder, as shown in Fig. 14, compared with a normal hydraulic damper 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 type hydraulic damping coefficient switching type hydraulic shock absorber 1-4 As shown in FIG. 6, the flow control valve 1 is provided 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 only two flow adjustment valves 1 are used, and is the same as that in FIG. 5 The operation is as follows: (1) From the state shown in Figure 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- 200415290 is closed as described above, so the opening and closing operation valve π on the left side is maintained closed, whereby the flow adjustment valve 10 on the left side is also maintained closed, and the damping coefficient is set to the maximum 値 C γώ a X, and this damping coefficient C Hi a X 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 hydraulic chamber 4 on the left begins to decrease, and the switching valve 4 3 on the left is opened as described above, so the opening and closing operation valve 11 on the left The system is opened, and the left side flow regulating valve 10 is also opened. Since the pressure of the left oil pressure chamber 4 flows into the right side oil pressure chamber 4 through the left side flow regulating valve 10, the load is temporarily removed. , The damping coefficient system becomes the minimum 値 Cnn 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 and closing operation valve 1 1 on the right operate in the same manner as described above, because the flow regulating valve 10 on the right will close, so The damping coefficient is restored 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, it is similar to the ordinary hydraulic shock absorber with a constant damping coefficient. By comparison, 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 single valve type hydraulic circuit is provided in Fig. 5 An embodiment of the pressure driving means 40. The other components are the same as those in FIG. 5. 200415290 The hydraulic damping coefficient switching type hydraulic shock absorber 1-5 series configured as above is only the same as the first in that a flow regulating valve 1 0 and a hydraulic driving means 4 0 are used respectively. Figure 5 is different and acts the same as in the case of Figure 5: (1) From the state of Figure 7, when the piston rod 8 moves in the direction of A in response to an earthquake or the like, the pressure of the oil pressure chamber 4 on the left will be Ascending, because 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, and the This 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 oil from 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 the minimum 値 C mi η. (3) When the piston rod 8 moves in 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 1 0 is closed, the damping coefficient is restored to Maximum 値 Cm a X. (4) By repeating the above actions on both sides of the hydraulic cylinder, as shown in Fig. 14, compared with a normal hydraulic damper 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- 200415290 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 FR to achieve the first Figure 15 shows the load deformation relationship. Specifically, as shown in FIG. 8 to FIG. 10, in addition to the main relief valve 50, a relief valve 5 1 for limiting the pressure of the buffer 42 is provided, and this relief valve 5 1 is provided. The operating start pressure is set to be lower than the operating pressure of the main relief valve 50 to achieve the load-deformation relationship of FIG. 15. In the single valve and double drive type damping coefficient switching type hydraulic shock absorber of Fig. 8-27_ 200415290 1-3, two flow paths connecting the left and right oil pressure chambers 4 and 4 are provided, and on each flow path A main relief valve 50 is provided to relieve the pressure in each of the hydraulic chambers 4, and each of the left and right buffers 42 is provided with a bypass flow path 1 5 for discharging the pressure between the buffer 42 and the flow adjustment valve 10 to the outlet side. By setting the set pressure of the bleed valve 51 to be lower than the operation start pressure of the main bleed valve 51, the bleed valve 51 is set to a pressure lower than the operation start pressure of the main bleed 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 driving type damping coefficient switching type hydraulic shock absorber 1 to 4 in FIG. 9, the single valve to single driving type • single driving type damping coefficient switching type hydraulic shock absorber 1 to 5 In this case, the main bleed valve 50 and the bleed valve 5 1 are provided in the same manner, and they operate in the same manner as described above. In addition, in the case where there are one flow control valve 10 in FIGS. 8 and 10, two main relief valves 50 are provided on the flow path that connects the left and right oil pressure chambers 4, 4. However, it is also possible to arrange one relief valve 50 and the flow adjustment valve 10 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. -2 8-200415290 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 manner. 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 manner. 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 of Fig. 6; Fig. 10 is a hydraulic circuit diagram showing an embodiment in which a drag 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. Figure 14 shows the relationship between the load and deformation of the shock absorber hydraulic shock absorber. Fig. 15: A graph showing the relationship between the load and deformation of a shock absorber hydraulic shock absorber provided with a relief valve. -2 9-200415290 「Explanation of Representative Symbols of Main Parts」: 1-1 ~ 1-5 ··· Hydraulic shock absorber 2 · · · Hydraulic cylinder 3 · ·. Piston 4 · · · Oil pressure chamber 5 · · · Flow path 6 · · · On-off control valve 8 · · · Piston rod 9 · · • Accumulator 1 0 · · · Flow regulating valve 11 · • • On-off operating valve 12 · · · Check valve 1 3 · · · Outflow flow path 1 4 · · · Inflow bypass flow path 1 5 · · · Outflow bypass flow path 1 6 · · · Check valve 1 7 · · · Inflow passage 1 1 a · · · Valve body 30, 30 '· · · Mechanical drive means 3 1 · · • Linear gear (rack) 3 2 · • • Crank mechanism 3 2' · · · Link mechanism 3 3 · · • 1st link 34, 34 '· · · 2nd link -30- 200415290 3 5 · · · Slider 3 6 · · · Spring 40 · · • Hydraulic drive 41. · · Throttle valve 42 · · · Buffer 4 3 · · · Switching valve 5 0 · · · Main drain valve 5 1 · · • Drain valve
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