201200758 六、發明說明： 【發明所屬之技術領域】 本發明係關於適用於流體壓緩衝器等之衰減閥。 【先前技術】 曰本特許廳在2002年發行之jP2〇〇2-349629A揭示有 設於單流式之複筒型油壓緩衝器之衰減閥。 早流式之複筒型油壓緩衝器具備汽缸、收裝於汽缸之 活塞、結合於活塞並從汽缸突出之活塞桿，設於保障汽缸 内之作動油量之變動之貯藏槽之外側。 ;/又紅之内側係藉由活塞分隔為活塞桿側之油室、活 塞杯之相反側之油室。衰減間係設於從活塞桿側之油室往 貯藏槽之作動油之流出路。 2壓緩衝益係不論活塞桿之伸長與收縮皆從活塞桿側 之:由至透過衰減閥使作動油流出，藉由衰減閥之 乍動方向使伸側农減力與縮側衰減力產生。 【發明内容】 著座=間具備藉由線圈彈簧往閉側彈塵之間體與使間體 重而、·卜^ °衰減閥之開㈣係依存於線圏彈簧之初期荷 疋。開閥後之衰減閥之衰減特性係依存 之彈簧當奴 廿义深圏5早簧 巧〜山r 定。因此，藉由事先設定此等值，可任意 °又疋/壓緩衝器之發生衰減力。 右油壓緩衝器以高速重複伸縮，活塞桿側之油室之壓 4 201200758 力會對應激烈變動。此麼力變動誘起衰減 間體之振動，結果有使衰減間之衰減力特性不安=彈脊或 性。 < 可能 本發明之目的’因此，係使衰減閥之衰減力特性… 為了達成以上之目的，本發明之衰減閥 .”。 於間室開口之流入開口；於流入開口周圍設置C; 座；收裝於間室之間體；將間體往閥座彈壓之收：狀之闕 之線圈彈簧；從與線圈彈簧之伸縮方向大致正'於間室 閥至開口之流出開口。衰減閥另具備位於流 ：向於 彈簧之間並覆蓋線圈彈簧之轴環。 與線圈 本發明之詳細及其他特徵或優點在說明書之 载中說明且於附加之圖面顯示。 之°己 【實施方式】 若參照圖面之圖丨，單流式之複筒型油壓緩衝器D且 同軸設於汽缸20之外側之外管2卜汽缸2〇與外管2丨^ 一 =係藉由與眼構件25a 一體之蓋體25㈤定。於汽缸外 官21之另—端係固定桿狀導引部2。於汽缸2〇係填充作動 油。此外，於汽缸20與外管21之間係設置封入有作動油 與氣體之貯藏槽尺。 / 對汽紅20係可滑動地支持於桿狀導引部2之活塞桿 從輛方向侵入。於汽缸2〇内之活塞桿23之侵入端 土 22。活塞22係滑接於汽缸20之内周面，將汽缸2〇内 乃&為活塞桿側之油室R1與相反側之油室R2。 201200758 相反側之油ϋ： R2之與活s 22才目反側之端部係藉由固 定於 >丄缸20之栓部24密閉。於栓部24係設置盔 許從汽缸2。之外側之貯藏…相反側之油室= 油之流入並遮斷反向之作動油之流動之止回閥29。 於活塞22係設置無抵抗地容許從相反側之油室R2往 活塞柃側之油至R 1之作動油之流入並遮斷反向之作動油之 流動之止回閥2 7。 ' 刀別密閉貯藏槽 忏狀導引部 R1且具有可滑動地支持活塞桿23之功能 “干狀導引2係形成面對活塞桿23之凹部2a。對 部2a係滑接於活塞椁 十 邱2係、鱼止 之抗封構件30欲合。於桿狀導 〇卜2係進一步§番·^ t 側支持.¾宾π ;匕密封構件30更活塞桿側之油室 側支待活塞彳干2 3之輪？ R1之間，於桿狀 °於軸承31與活塞桿側之油 3丨大之外徑之if狀、g。"與陶23之間係形成比軸 心衣狀通路2b。 於面對此環狀通 明之衰減閥丨。 b且桿狀導引部2之内側設置本 衰減間丨係在既定少 室R1往聍藏櫓D ^通抵抗下容許從活塞桿側之 K <作動油夕..ώ山ea 於活塞桿2 3 之峨出之閥0 周之外罩39固著基端係眼構件26a '嵌合於外管2 1之 部係被橡膠套外罩39之外周與外管21之外周之嵌 ^ 安38覆蓋。 於油壓緩％势 衝益D妆始。士 室R2經過止 ％時，作動油從縮小之相反側之 間27户λ、土 μ入居塞桿側之油室R1。活塞桿 6 201200758 之往汽缸20之侵入體積相當之作動油從活塞桿側之油室 R1經過衰減閥1往貯藏槽r流出。 於油壓緩衝器D伸長時，作動油從貯藏槽R經過止回 閥29無抵抗地流入擴大之相反側之油室R2。反之縮小之 活塞杯側之油室R丨之作動油經過衰減閥1往貯藏槽尺流 出。 盘 ’^，早々IL式之複筒型油壓緩衝器D係於伸長動作 與收縮動作之任—者皆經過衰減閥1使作動油從活塞桿側 之油室R1往貯藏槽R流出。 參照圖2針對衰減閥1說明。 與環=係:成圓筒形狀之閥室3 b '將閥室3 b 係形成於與…。之中心轴正二閥至儿與流入開 入開口 軸正乂之相同中心軸上。包圍流 於 住間室3b之開口部而形成環狀之闕座4。 開口 ：：二:b之内周面係連通於貯藏槽R之流出開口 U 力*·出開口 1 1之中心軸係 3a之令心軸。 係正又於閥室3b及流入開口 衰減閥1具備著座於閥 4彈壓之線圈强I < 之閥體5、將閥體5往閥座 、圈弹簣6、配置為覆蓋飨圃2路垃 螺合於閥 复盍線圈彈簧6且將基端7b 叫至3b之内周之軸環7、 轴環7之内田 克持線圈彈普ό之螺合於 疋内周之彈簧座10。 閥體5係由著座於閥座4之 流入開口 3a肉#山 圓盤邛5a、從圓盤部5a往 a内大出之前端部5b、张 端部5b相拓加 $成於與圓盤部5a之前 相反側之圓筒狀之基端部5c構成。. 201200758 5b係形成為嵌合於流入開口 3a之圓柱狀 前端部 。於前 端部几係形成大致U字形剖面之槽部5d。槽部5d係於前 端部5b之前端與外周面分別開口。前端部5b之外周面之 槽部5d之開口部係藉由於閥體5從閥座4上升而連通於閥 室3b。 前端部5b具有對應於閥體5之上升距離而使環狀通路 2b與閥室3b之流通剖面變化之機能、在著座位置與最大上 升位置之間將閥體5之變位往閥室3b之中心軸方向導引之 導引機能。 於圓盤部5a係於往閥座4之著座部之外側之2處以^ 度間隔形成於徑向延伸之缺口 5f。缺口 5f係於闊室扑^ 中心軸方向，換言之圖之左右方向貫通圓盤部h形成。: 口 5f係形成為在閥體5從閥座4上升之狀態不會妨礙從》 入開口 3a往閥室313之作動油之流入。於圓盤部5 係線圈彈蒉6之一端抵接。 基端部5c係位於線圈彈簧6之内側。於基端部5c係汚 成於閥室3 b開口之中空部5 g 〇於„触c〆， g 、閥體5係开> 成連接槽奇 5d與中工5g之孔口 5e。基端部5c具有將線圈彈簧“ 變形限定於線圏彈簣6之伸縮方向即間室3b之中心轴以 之機能。如上述，藉由將線圈强暮< 圈弹黃6之變形限定於線圈謂 簧…申縮方向即闊室3b之中心細方向，可防止線圈彈笼 6與轴環7之干涉並抑制線圈彈簧6之與闕室3b之令； 正交之方向之振動。 於彈箸座1〇亦形成往線圈彈簧6之内側突出而發揮同 8 201200758 ::機能之前端部10a。另外，螺合於軸環7之内周 尹、座㈣、將背面漏出於桿狀導引部2之外周= 係對應於從桿狀導引部2之外側施加於彈菁座1〇之背10 钿作孔之旋動操作使閥室3b中 之 此操作，可…定後… 向之位置變化。藉 j任思》又疋線圈彈簧6之初期荷重。 "之=菁6係於閥室3,之中心轴方向伸縮。流出開口 汗口之方向係因此大致正交於線 於流出開口 η之内周係管9螺合。管9係::方:。 油面之下方開口。亦可代替使…、合於流出 1丨而改以壓入或溶接將管9固定於流出開口"。 广環7係對來自閥室儿内之往流出開"之 =!揮保護線圈彈菁6之功能。亦即，覆蓋線圈彈*6 以使…開口 33經過閥"往流出開口 U之作動:不 形成橫斷線圈彈簧6之流動。藉由設置轴環7，= = 内側在流出開口 U之作動油之 達流出開口丨丨。 、軸％ 7之刖端而到 較理想係關於閥室3b之中、、缸士人 之前端7a之位置八〜軸方向將間體5之軸環7 下線圈彈簧6^二°T°亦即’在間體5著座之狀態 於流出開口 u之開？圓盤部5a之背面位置υ與相當 設置軸環7之前之最接近閥座4之端部之位置X之間 之開口部全置A。11此設定，流出開口" I1生地面野車由環 出開口 11之作動油… 從閥室3b到達流 …内周面形成之〉:動會全部經由轴環7之外周面與間 /成之環狀間隙。 201200758 '由壓緩衝器D之活塞桿23側之油室 %狀通路2 b對@ ς & 内之壓力係經 耵間體5之前端部5b做為 ，深圈彈蒉6對闊體5作用之 b 閥體5保持著应 力以下之場合， 者庋於閥座4之狀態。在閥體 之狀態下，样邱s Η τ 係者座於閥座4 槽。卩5d不於閥室3b内具有開口部。 另外，孔口 5e係將槽部5d與閥室讣 在活塞桿側夕4 Λ 隨時連通。因此， ，至R1之壓力上升較小之人 油室η丨之作^^ a # Λ s，活塞桿側之 又作動油係經環狀通路2b與孔 〈 流入閥室3b，你4山μ 兴孔口 5e與中空部5 b從流出開口 1 1經管9往貯銥桃〇 過程，從軸瑗7 + & 仕％减槽R流出。在此 衣7之内側往外側形成橫切線 :之流動。然而，從…流出之作動之作動 動不：於線圈彈簧6引起振動。 小’此流 右因活塞桿側之油室R1 2b作用於前端部5b之門門^ 坚力上升而經環狀通路 之m 4力超㈣圈彈簧6對閥體5你ra 之閉閥力，閥體5從閥座4上升 f閥體5作用 經槽部5d-入. 升將槽部“連通於閥室讣。 丨5d-入閥室3b之流體經缺σ 5 間之環狀間隙而到達流出 ^室3 b201200758 VI. Description of the Invention: [Technical Field] The present invention relates to a damping valve suitable for use in a fluid pressure damper or the like. [Prior Art] JP2〇〇2-349629A issued by the Office of the Patent Office in 2002 discloses a damping valve provided in a single-flow type tubular hydraulic buffer. The early-flow type multi-cylinder type oil pressure damper is provided with a cylinder, a piston housed in the cylinder, a piston rod coupled to the piston and protruding from the cylinder, and is disposed outside the storage tank for protecting the amount of oil in the cylinder. The inner side of the red is separated by the piston into the oil chamber on the piston rod side and the oil chamber on the opposite side of the piston cup. The attenuation is provided in the outflow path of the moving oil from the oil chamber on the side of the piston rod to the storage tank. 2 pressure buffer benefits regardless of the expansion and contraction of the piston rod from the piston rod side: from the through the damping valve to make the working oil out, by the damping valve's sway direction to make the extension side of the agricultural reduction and contraction side damping force. SUMMARY OF THE INVENTION In the seating = between the coil spring and the closing side, the body and the body are heavy, and the opening of the damping valve (4) depends on the initial load of the coil spring. The attenuation characteristics of the damping valve after opening the valve are dependent on the spring as a slave, and the squats are deep and early. Therefore, by setting this value in advance, the damping force of the buffer can be arbitrarily/depressed. The right oil pressure damper repeats the expansion and contraction at a high speed, and the pressure of the oil chamber on the piston rod side 4 201200758 The force will change drastically. This force variation induces the vibration of the attenuating body, and as a result, the damping force characteristic between the attenuations is disturbed = ridge or sex. <Possible for the purpose of the present invention. Therefore, the damping force characteristic of the damping valve is... In order to achieve the above object, the damping valve of the present invention is provided in the opening of the opening of the chamber; C is disposed around the inflow opening; Included in the compartment between the compartments; the coil spring that presses the compartment to the valve seat: the coil spring of the shape of the coil; from the direction of the expansion and contraction of the coil spring, the outlet valve is substantially positive from the compartment valve to the opening. The flow is: a collar that is between the springs and covers the coil spring. The details and other features or advantages of the present invention are described in the specification and are shown in the accompanying drawings. Figure 丨, single-flow multi-cylinder type oil pressure buffer D and coaxially disposed outside the cylinder 20, tube 2, cylinder 2, and outer tube 2丨^ = by integral with eye member 25a The cover body 25 (five) is fixed to the other end of the cylinder outer portion 21, and the rod-shaped guide portion 2 is fixed. The cylinder 2 is filled with hydraulic oil. Further, the cylinder 20 and the outer tube 21 are sealed with operating oil. Storage tank with gas. / For steam red 20 series The piston rod that is movably supported by the rod-shaped guide 2 intrudes from the direction of the vehicle. The piston rod 23 in the cylinder 2 is invaded into the end soil 22. The piston 22 is slidably connected to the inner circumference of the cylinder 20, and the cylinder 2 is closed. The inner chamber & is the oil chamber R1 on the piston rod side and the oil chamber R2 on the opposite side. 201200758 The oil side on the opposite side: the end portion of the opposite side of the R2 and the live side is fixed by the > The plug portion 24 is sealed. The plug portion 24 is provided with a helmet from the cylinder 2. The outer side is stored... the opposite side of the oil chamber = the inflow of oil and the check valve 29 for interrupting the flow of the reverse acting oil. The 22 series is provided with a non-resisting check valve 27 that allows the flow of the oil from the opposite side of the oil chamber R2 to the piston side to the oil of R1 and interrupts the flow of the reverse oil. The groove-shaped guide portion R1 has a function of slidably supporting the piston rod 23 "the dry guide 2 is formed to form the recess 2a facing the piston rod 23. The opposing portion 2a is slidably attached to the piston 椁 10 邱 2, and the fish sealing member 30 is closed. In the rod-shaped guide 2 2 2 further § 番 · ^ t side support. 3⁄4 π; 匕 sealing member 30 more on the piston rod side of the oil chamber side support piston to dry 2 3 wheel? Between R1, in the shape of a rod, the oil of the bearing 31 and the piston rod side is larger than the outer diameter of the if, g. " and the ceramic 23 form a specific axis-like passage 2b. Attenuating the valve for this ring-shaped opening. b, and the inner side of the rod-shaped guiding portion 2 is provided with the fascia between the predetermined small chamber R1 and the D 通 抵抗 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 容许 ea ea ea ea ea ea ea ea ea ea ea ea ea ea ea ea 2 3, the valve is closed, the cover 39 is fixed to the base end eye member 26a', and the portion fitted to the outer tube 2 1 is covered by the outer periphery of the rubber cover outer cover 39 and the outer circumference of the outer tube 21 . In the oil pressure, the potential is reduced. When the chamber R2 passes through the stop %, the oil is moved from the opposite side of the narrowed side to 27 chambers λ and soil μ into the oil chamber R1 on the side of the plug rod. Piston rod 6 201200758 The intrusion volume of the cylinder 20 is equivalent to that of the oil flowing from the oil chamber R1 on the piston rod side through the damping valve 1 to the storage tank r. When the hydraulic damper D is extended, the operating oil flows from the storage tank R through the check valve 29 into the oil chamber R2 on the opposite side of the expansion without resistance. Conversely, the oil in the oil chamber R of the piston cup side is discharged through the damping valve 1 to the storage tank. The disc ’^, the IL-type double-cylinder type hydraulic damper D is used for both the expansion operation and the contraction operation, and the actuation oil passes through the damping valve 1 to flow the hydraulic oil from the oil chamber R1 on the piston rod side to the storage tank R. Description will be made with respect to the damping valve 1 with reference to FIG. And the ring = system: a valve chamber 3b' having a cylindrical shape is formed in the valve chamber 3b. The center axis of the positive two valve is on the same central axis as the inflow opening shaft. The annular sill 4 is formed by surrounding the opening of the living room 3b. Opening: ::2: The inner surface of b is the outflow opening that communicates with the storage tank R. U Force*·Outlet 1 1 The central axis of the shaft 3a. The valve chamber 3b and the inflow opening damping valve 1 are provided with a valve body 5 that is placed on the coil 4 of the valve 4, and the valve body 5 is placed on the valve seat and the ring magazine 6 to cover the 飨圃2. The shaft is screwed to the valve rewinding coil spring 6 and the base end 7b is called to the inner circumference of the collar 3 of the 3b, and the inner ring of the collar 7 is screwed to the spring seat 10 of the inner circumference of the crucible. The valve body 5 is formed by the inflow opening 3a of the valve seat 4, the meat disc #5a, the front end portion 5b extending from the disc portion 5a into the a, and the end portion 5b. The cylindrical base end portion 5c on the opposite side of the disk portion 5a is formed. 201200758 5b is formed to be fitted to the cylindrical front end portion of the inflow opening 3a. The groove portion 5d having a substantially U-shaped cross section is formed in the front end portion. The groove portion 5d is opened at the front end and the outer peripheral surface of the front end portion 5b, respectively. The opening of the groove portion 5d on the outer peripheral surface of the distal end portion 5b is communicated with the valve chamber 3b by the valve body 5 rising from the valve seat 4. The distal end portion 5b has a function of changing the flow cross section of the annular passage 2b and the valve chamber 3b in accordance with the rising distance of the valve body 5, and displacing the valve body 5 toward the valve chamber 3b between the seating position and the maximum rising position. The guidance function of the central axis direction guide. The disk portion 5a is formed at a distance from the outer side of the seat portion of the valve seat 4 at intervals of 5 to the radially extending notch 5f. The notch 5f is formed in the direction of the center axis of the wide chamber, in other words, the disk portion h is formed in the left-right direction. The port 5f is formed so as not to impede the flow of the hydraulic oil from the inlet opening 3a into the valve chamber 313 in a state where the valve body 5 is raised from the valve seat 4. One end of the coil magazine 5 is abutted on the disk portion 5. The base end portion 5c is located inside the coil spring 6. The base portion 5c is smeared into the hollow portion 5g of the opening of the valve chamber 3b. The contact is closed, and the valve body 5 is opened. The connection port 5d and the 5g hole 5e. The end portion 5c has a function of "deformation of the coil spring" to the center axis of the space 3b, which is the direction in which the wire magazine 6 is stretched. As described above, by limiting the deformation of the coil to the coil spring 6, the direction of the coil is the center direction of the wide chamber 3b, and the interference between the coil cage 6 and the collar 7 can be prevented and the coil can be suppressed. The spring 6 and the chamber 3b; the vibration in the direction of the orthogonal. The magazine 1 is also formed to protrude toward the inner side of the coil spring 6 to function as the front end portion 10a of the 201200758::function. Further, the inner circumference of the collar 7 is screwed into the inner circumference of the collar 7, and the seat (4) is leaked from the outer side of the rod-shaped guide portion 2 to the outer side of the rod-shaped guide portion 2. 10 The rotation operation of the boring hole allows the operation in the valve chamber 3b to be determined... to change its position. By j Ren Si" and the initial load of the coil spring 6. " = Jing 6 is in the valve chamber 3, the central axis of the expansion and contraction. Outflow opening The direction of the sweat opening is thus substantially orthogonal to the inner circumference of the outflow opening η. Tube 9 Series:: Party:. Open below the oil level. Alternatively, the tube 9 may be fixed to the outflow opening by pressing or melting. The wide ring 7 series functions from the inside of the valve room to the outflow of the ring. That is, the coil bomb *6 is covered so that the opening 33 passes through the valve " to the outflow opening U: the flow of the transverse coil spring 6 is not formed. By providing the collar 7, = = the inside of the outlet opening U is made to flow out of the opening 丨丨. , the end of the shaft % 7 to the ideal system about the valve chamber 3b, the position of the front end 7a of the cylinder man, the axis of the shaft 5, the collar of the body 5, the lower coil spring 6 ^ 2 °T ° That is, in the state in which the intervening body 5 is seated, the opening of the outflow opening u is opened. The opening portion υ between the rear surface position 圆盘 of the disk portion 5a and the position X closest to the end portion of the valve seat 4 before the collar 7 is provided is completely set A. 11This setting, the outflow opening " I1 raw ground vehicle is driven by the ring opening 11... From the valve chamber 3b to the flow... The inner peripheral surface is formed: the movement is all via the outer circumference of the collar 7 The annular gap. 201200758 'The pressure in the oil chamber %-shaped passage 2 b on the piston rod 23 side of the pressure damper D is opposite to the front end portion 5b of the inter-turn body 5, and the deep loop magazine 6 pairs of wide bodies 5 When the valve body 5 of the action b is kept below the stress, it is in the state of the valve seat 4. In the state of the valve body, the sample s Η τ τ is seated in the seat of the valve seat 4. The 卩5d does not have an opening in the valve chamber 3b. Further, the orifice 5e communicates with the valve chamber 随时 on the side of the piston rod at any time. Therefore, the pressure rise to the R1 is small, the oil chamber η 丨 ^ ^ a Λ s, the piston rod side of the operating oil through the annular passage 2b and the hole < into the valve chamber 3b, you 4 mountain μ The opening 5e and the hollow portion 5b are discharged from the outflow opening 1 1 through the tube 9 to the peach tree, and flow out from the shaft 瑗 7 + & A transverse line is formed on the inner side of the garment 7 to the outside: the flow. However, the action of the action from the outflow does not: the coil spring 6 causes vibration. Small 'this flow right due to the oil chamber R1 2b on the piston rod side acts on the door of the front end portion 5b ^ The strength rises and the m 4 force exceeds the (4) circle spring 6 through the annular passage to the closing force of the valve body 5 The valve body 5 rises from the valve seat 4, and the valve body 5 acts through the groove portion 5d-in. The liter portion "connects to the valve chamber 讣. 丨5d-the fluid entering the valve chamber 3b passes through the annular gap between the σ and the σ And arrive at the outflow ^ room 3 b
流出。 違L出開口 U，通過管9往貯藏槽R :時’線圏彈“之大部分位於轴環7之内側， 内之作動油之流動不會 問至3b之中心軸 圓评貢〇不會使與 外，線圈彈“之二：之荷重作用於線圈彈菁6。此 黃6之中漏出至細 方向之變位。 與闕至3b之中心軸正交之 10 201200758 因此，即使油壓緩衝器D以高速伸縮，通過衰減閥i 之作動油之流量増大，閥室3b内之作動油之流動亦不會於 線圈彈箐6引起與閥室3b之中心軸正交之方向，換言之線 圈彈簧6之橫斷方向之振動。 因此’閥體5亦不會引起同方向之振動，衰減閥！即 使在油壓緩衝器D以高速作動之場合亦可使安定之衰減力 發生。 在此’ a兒明將軸環7之前端7a之位置A設定於相當於 抓出開口 1 1之開口之最接近閥座4之端部之位置X與在閥 體5著座之狀態下線圈彈簧6之一端抵接之圓盤部5a之背 面位置Y之間之意義。 —將位置A設定於離位置γ比離位置χ近係因為為了使 閥至3b内之作動油之流動不會橫切線圈彈簧6，防止同方 向之作動油直接流入流出開口丨丨較理想。 此外’將位置A設定於離位置χ比離位置γ近係 於閥體5之上升時確保轴環7之内側與外側之連通。若 體5之上升使轴環7之内側之容積縮小，會有從轴環^ 内：往外側之作動油之移動產生。此時，若形成於軸 之⑨"而部7a與閥體5之圓盤部5a之間之環狀間隙之面 足¥狀間隙會成為從軸環7之内側往外側之作動 動之抵抗而有衰減力產±。 ^之移 右將位置A超過位置γ設定於閥座4側，從閥體 上升開始之時點便與轴環7之前端部7a與間體5 之 5a於閥室3b之中心細太6 晶 圓盤部 之中〜軸方向重疊。若形成於此等構件„ τ閘之環 201200758 狀間隙之流通抵抗大’環狀間隙之 力之主體，無法獲得基於槽部 ^ -二‘、’、 一 d與閥至3 b之流通剖面積 =厂閥1之本來之农減力特性。為了獲得基於槽部^與 ::室3b之流通剖面積之衰減閥1之本來之衰減力特性，必 須將位S A設定於離位£ χ比離位置γ近。 參照圖3-6說明在關於軸環7之前端部7a之位置a之 以上之條件之令更詳細之設定。 若參照圖3,在此係以閥體5之最大上升位置之圓盤部 5a之背面位置為Y1。此衰減閱1係將軸環7之前端部7a 之位置A設定於位置γ與位置γ 1之間。 參照圖4說明此設定之衰減間】之衰減力特性。 活塞22以低速作動之場合係環狀通路2b之壓力上升 小，闊體5維持著座於間座4之狀態。在此狀態係衰減間丨 僅經孔口 5e使作動油流通。因此，衰減閥丨之發生衰減力 係基於孔口特性而與活塞速度一起急增。 若因活塞速度之上升而環狀通路2b之壓力更加上升， 閥體5從閥座4上升。之後係藉由槽部兄連通於閥室讣， 衰減閥丨之以後之發生衰減力依存於槽部5d與閥室3b之 流通剖面積’相對於活塞速度衰減力呈現線性且緩慢之辦 加。 曰 於衰減閥1 ’在軸環7之前端部7a之位置A設定於位 置Y與位置Y1之間之場合，在閥體5開始上升之時點係於 閥體5之圓盤部5a與軸環7之前端部7a之間有充分之環狀 間隙存在。因此，此環狀間隙不對伴隨閥體5之上升而從 12 201200758 軸環7之内側往外側移動之作動油給予實質之抵抗。 另-方面，若活塞速度更加上升，圓盤部二背面位 置接近最大上升相當之位置Y1，圓盤部5a與軸環7之前端 部〜重疊，此等之間之環狀間隙顯著變小。此活塞速度相 當於圖6之速度α。 活塞速度超過速度4，圓盤部53與轴環7之前端部 h之環狀間隙對從轴環7之内側往外側流出之作動油產生 大流通抵抗。因此，在速度 1 以上相對於活塞速度，衰 減閥1係使相對於活塞速度之發 疋及炙發生农減力之增加率再增大。 亦即’如圖3所示，若脾以供7 ‘山Flow out. Violation of the L out of the opening U, through the tube 9 to the storage tank R: the majority of the 'line bombs' are located inside the collar 7, the flow of oil inside does not ask the central axis of 3b rounds Gongga will not With the outer and outer coils, the second one: the load acts on the coil. This yellow 6 leaks out into the fine direction. 10 201200758 orthogonal to the central axis of 阙3b Therefore, even if the hydraulic damper D is expanded at a high speed, the flow rate of the kinetic oil passing through the damping valve i is large, and the flow of the moving oil in the valve chamber 3b is not in the coil The crucible 6 causes a direction orthogonal to the central axis of the valve chamber 3b, in other words, a vibration of the coil spring 6 in the transverse direction. Therefore, the valve body 5 will not cause vibration in the same direction, and the damping valve! Even in the case where the hydraulic damper D is operated at a high speed, the damping force of the stability can be generated. Here, the position A of the front end 7a of the collar 7 is set to a position X corresponding to the end of the opening of the grip opening 1 1 closest to the valve seat 4 and a coil in a state where the valve body 5 is seated. The meaning of the position between the back side of the disc portion 5a at which one end of the spring 6 abuts. - Setting the position A to the position γ is closer to the position than because the flow of the oil in the valve 3b does not cross the coil spring 6, and it is preferable to prevent the oil in the same direction from flowing directly into the outflow opening. Further, the position A is set to be in a position away from the position χ to ensure the communication between the inner side and the outer side of the collar 7 when the position of the valve body 5 is increased. If the rise of the body 5 causes the volume of the inner side of the collar 7 to be reduced, there is a movement from the inside of the collar ^ to the outside of the moving oil. At this time, if the surface of the annular gap between the portion 9' and the disc portion 5a of the valve body 5 is formed, the foot-like gap becomes a resistance against the movement from the inner side of the collar 7 to the outer side. There is a damping force ±. When the position is shifted to the right, the position A is set to the valve seat 4 side, and the point from the rise of the valve body is the same as the front end portion 7a of the collar 7 and the 5a of the intermediate body 5 at the center of the valve chamber 3b. The direction of the axis in the disk overlaps. If the main body of the force of the loop of the 201200758 gap of the τ gate ring is resisted by the large ring gap, the flow cross-sectional area based on the groove portion ^ - two ', ', a d and the valve to 3 b cannot be obtained. = The original damping force characteristic of the factory valve 1. In order to obtain the original damping force characteristic of the damping valve 1 based on the flow section area of the groove portion and the: chamber 3b, the position SA must be set to the off position. The position γ is closer. A more detailed setting of the condition above the position a of the end portion 7a of the collar 7 will be described with reference to Figs. 3-6. Referring to Fig. 3, the maximum rising position of the valve body 5 is used here. The position of the back surface of the disk portion 5a is Y1. This attenuation reading 1 sets the position A of the front end portion 7a of the collar 7 between the position γ and the position γ 1. The damping force of the set attenuation is explained with reference to Fig. 4 . When the piston 22 is operated at a low speed, the pressure rise of the annular passage 2b is small, and the wide body 5 is maintained in the state of the seat 4. In this state, the damper is only circulated through the orifice 5e. The damping force of the damping valve is increased sharply along with the piston speed based on the orifice characteristics. If the pressure of the annular passage 2b rises further due to the increase in the piston speed, the valve body 5 rises from the valve seat 4. After that, the groove portion is connected to the valve chamber 讣, and the damping force after the damping valve 依 is dependent on The flow cross-sectional area of the groove portion 5d and the valve chamber 3b is linear and slow with respect to the piston speed damping force. The position A of the damping valve 1' at the front end portion 7a of the collar 7 is set at the position Y and the position Y1. In the case where the valve body 5 starts to rise, a sufficient annular gap exists between the disk portion 5a of the valve body 5 and the front end portion 7a of the collar 7. Therefore, the annular gap is not matched to the valve. When the body 5 rises, the moving oil moving from the inner side of the 12 201200758 collar 7 to the outside gives a substantial resistance. On the other hand, if the piston speed is increased, the rear position of the disc portion is close to the maximum rise position Y1, the disc The portion 5a overlaps with the front end portion of the collar 7, and the annular gap between them is remarkably small. This piston speed corresponds to the speed α of Fig. 6. The piston speed exceeds the speed 4, and the disc portion 53 and the collar 7 The annular gap of the front end portion h is within the collar 7 The flow oil flowing out to the outside generates a large flow resistance. Therefore, at a speed of 1 or more with respect to the piston speed, the damping valve 1 increases the rate of increase of the agricultural reduction force with respect to the piston speed and the enthalpy. As shown in Figure 3, if the spleen is for the 7' mountain
右將軸％ 7之前端部7a之位置A 設定於位置Y與位置γ 1之間，.、壬耷冻麻 > 在活塞速度之增加途中發 生衰減力之增加率增大。 若參照圖5,顯示於此圖之衰減閥1係將轴環7之前端 部7a之位置A設定於位置γι與位置X之間。 在此場合，即使於閥體5之最大上升位置，閥體5之 圓盤部5a與軸環7之前端部7a亦不會重疊。 若參照圖6，將將· ， _ 〇將將軸裱7之前端部7a之位置a 外 定之衰減闊1係閥體s 〇x 4體5上升後於所有之活塞速度呈現線性 且緩慢之增加特性。亦g 吁『 亦即，使發生衰減力之増加率增 速度α不存在。 如上述，衰減間！係因轴環7之前端部〜 設定而發揮不同之衰減力特性。 之 卜根據要求之衰減力特性，亦可省略孔口 5e。 ’、’、、、圖7說明關於軸環7與彈簧座10之構成之本 13 201200758 發明之第2實施例。 在此實施例係將細環7 據此構成，雖不能獨立調整軸枣7座10事先一體形成。根 圈彈簧6之初期荷重，但可減：:之前端部7a之位置與線 造簡化。 減閥1之零件數而將構 參照圖8說明關於輪環 之第3實施例。 Θ座1 0之構成之本發明 在此實施例係將軸環7形 藉由嵌合於軸環7之内‘，、有底筒狀。彈簧座10係 線圈彈簣ό作用於彈簧座1〇之」釉衣7之底部7d來支持 與彈簣座1G雖為個別構件何重。根據此構成’軸環7 軸環7之内周攻螺紋，可省略^於彈·^座W之外周與 -方面，於彈簧座1G與轴環 構件之加卫之麻煩。另 複數塾片，可獨立設定關於闊室3二之間夹持單數或 之位置與線圈彈簧6之初期荷重。 、軸方向之軸環7 參照圖9說明本發明之第4實施例。 於此實施例之衰減閥】係軸環7之前 於閥座4之閥體5之圓盤部&之外周之 3到達者座 前端部7a與閥室3b之中心轴方向之_ °但轴環7之 RB m Μ Air ^ C ί· * 3C之間係設定不 阻礙、·!缺口 5f之作動油之流通之充 其他實施例不同，不於閥室3b之中心輪方^言缺口 5f係與 而係以形成於圓盤…闕座4側之面之::通成圓。盤部5a 於軸環7之前端部7a與圓盤部5a y卜周之間倍<5·定ρ 狀間隙P。藉由使軸環7之前端部7a之 一衣 k為一定，不受 14 201200758 間體5之上升位置影響地於 之外周.之間確保一定之产灿长7之前端部〜與圓盤部5a 衣狀間隙p。 根據此實施例，若因環 從閥座4上升，伴隨轴環7 2b之壓力上升而閥體5 從軸環7之内側通過環狀之内谷積減少’作動油會 環7之内側之壓力上升。此/力；；:7之外側流出，轴 ^ ^丄 刀係對閥體5做為背壓作用 因此，错由於將閥體5往 ^[作用。 4弹壓之線圈彈簧 用力加上此背壓，強化閥體 反作 1閉間力，對間艘S L , 升後之活塞速度之上升 f閥體5開始上 生农減力之增加率之斜率 圖6顯示之特性更大。 竹手比於 根據此實施例，可使衰減％ !之 活塞速度之增加率增加。 衣減力之相對於 另外，若使軸環7之前端部 a马住基女而7b將内徑縮小 之圓錐形狀，可使衰減閥丨之 I生衣減力之增加率相對於 活塞速度之上升加速度地增加。 作用於閥體5之閥室3b之中、、紅士 &』 < ng至之中〜軸方向之按壓力強化係 對閥體5之振盪防止亦產生理想之作用。此作用與軸環7 產生之線圈彈簧6之振盡抑制作用相輔相成，衰減閥！即 使對油壓緩衝器D之激烈伸縮亦維持安定之發生衰減力。 參照圖10說明關於圓盤部5a之構成之本發明之第4 實施例之變形例。 *…、圖1 0 ’圓盤部5 a與其他實施例同樣地於閥室3 b 之中〜軸方向具備貫通圓盤部5a之缺口 5f。與其他實施例 不同，圓盤部5a並不將背面直接抵接於線圈彈簧6而是隔 15 201200758 著墊片32抵接於線圈彈菁6。 之閥體5之圓盤部5a之 7之間形成既定之環狀 3 2亦可谷易調整環狀間 藉由使用墊片32,即使在既存 外徑尺寸小之場合’亦可於與轴環 間隙ρ。ϋ由使用外徑不同 隙Ρ之大小。 个發明之第5實施例 食 • 一 \Ύ'\ 〇 於此實施例之衰減閥丨係軸 山 之圓盤部5a之外月. "刖鸲部7a通過閥負Right, the position A of the front end portion 7a of the axis %7 is set between the position Y and the position γ1, and the rate of increase in the damping force increases as the piston speed increases. Referring to Fig. 5, the damping valve 1 shown in this figure sets the position A of the front end portion 7a of the collar 7 between the position γι and the position X. In this case, even at the maximum rising position of the valve body 5, the disk portion 5a of the valve body 5 and the front end portion 7a of the collar 7 do not overlap. Referring to Fig. 6, the position of a front end portion 7a of the shaft yoke 7 will be attenuated, and the position of the front end portion 7a of the shaft yoke 7 will be attenuated. The first valve body s 〇x 4 body 5 rises and then linearly and slowly increases at all piston speeds. characteristic. It is also called "that is, the rate of increase α of the damping force does not exist. As mentioned above, the attenuation! The damping force characteristics are different due to the setting of the front end of the collar 7 to the setting. The aperture 5e may also be omitted depending on the required damping force characteristics. Fig. 7 illustrates a second embodiment of the invention relating to the configuration of the collar 7 and the spring seat 10. In this embodiment, the thin ring 7 is constructed in accordance with this, and it is not possible to independently adjust the shaft 7 to be integrally formed in advance. The initial load of the root spring 6 can be reduced: the position and the line of the front end portion 7a are simplified. The third embodiment of the wheel ring will be described with reference to Fig. 8 by reducing the number of parts of the valve 1. The present invention having the structure of the sley 10 is in this embodiment, the collar 7 is shaped to be fitted into the collar 7, and has a bottomed cylindrical shape. The spring seat 10 is attached to the bottom 7d of the glaze 7 of the spring seat 1 to support the weight of the magazine 1G as an individual member. According to this configuration, the inner circumferential tapping of the collar 7 of the collar 7 can omit the trouble of the spring seat 1G and the collar member in terms of the outer circumference of the spring and the seat W. In addition, the plurality of cymbals can independently set the position of the singular or the singularity between the wide chambers 3 and the initial load of the coil spring 6. Axle ring 7 in the axial direction A fourth embodiment of the present invention will be described with reference to Fig. 9 . The damping valve of this embodiment is the shaft of the valve body 5 before the collar 7 and the outer circumference of the third portion of the front end portion 7a of the valve body 4 and the valve chamber 3b. The RB m Μ Air ^ C ί ** of the ring 7 is not blocked, and the flow of the oil flowing through the notch 5f is different from the other embodiments, and the center wheel of the valve chamber 3b is not limited to 5f. And the surface formed on the side of the disc...the sley 4:: is made into a circle. The disk portion 5a is doubled <5<5> between the front end portion 7a of the collar 7 and the disk portion 5a y. By making the garment k of the front end portion 7a of the collar 7 constant, it is not affected by the rising position of the 14 201200758 body 5, and the outer circumference is ensured between the ends of the collar 7 and the disc portion. 5a Clothing gap p. According to this embodiment, if the ring rises from the valve seat 4, the pressure of the collar 7 2b rises and the valve body 5 decreases from the inner side of the collar 7 through the inner valley of the ring to reduce the pressure inside the ring 7 of the oil. rise. This / force;;: 7 outflow from the outside, the shaft ^ ^ 刀 knife system acts as a back pressure on the valve body 5 Therefore, the fault is due to the valve body 5 to ^ [acting. 4 The spring of the coil spring force is added to this back pressure to strengthen the valve body to make a closing force. For the SL, the piston speed rises after the rise, and the slope of the increase rate of the valve body 5 starts to decrease. Figure 6 shows that the characteristics are greater. According to this embodiment, the increase rate of the piston speed of the attenuation %! can be increased. In contrast, if the front end portion a of the collar 7 is caused to bear the base and the 7b has a conical shape with a reduced inner diameter, the rate of increase of the damping force of the damping valve can be made relative to the speed of the piston. The acceleration increases. The pressing force acting on the valve chamber 3 in the valve chamber 3b of the valve body 5, the red and the ng to the middle to the axial direction, also has an ideal effect on the oscillation prevention of the valve body 5. This action complements the vibration suppression of the coil spring 6 produced by the collar 7 and attenuates the valve! Even if the hydraulic shock absorber D is strongly stretched, the damping force of the stability is maintained. A modification of the fourth embodiment of the present invention relating to the configuration of the disk portion 5a will be described with reference to Fig. 10 . In the valve chamber 3b, the notch 5f penetrating the disk portion 5a is provided in the axial direction of the valve chamber 3b in the same manner as the other embodiments. Unlike the other embodiments, the disk portion 5a does not directly abut the coil spring 6 but the spacer 32 abuts against the coil spring 6 . The predetermined annular shape is formed between the disc portions 5a of the valve body 5, and the valleys can be adjusted. By using the spacer 32, even when the existing outer diameter is small, the shaft can be used. Ring gap ρ. ϋ The size of the gap is different by using the outer diameter. The fifth embodiment of the invention is a food; a \Ύ'\ 衰减 the damping valve of the embodiment is a shaft of the shaft 5a outside the moon. "刖鸲7a passes the valve negative
► C 二之外周’到達闊室3b之中心轴方向之，. 係以丨80度間隔於2處形成絞孔8 於此實施例軸環7之内相丨 ,^ _ 之内側之作動油雖不能繞過軸環 之則端部7“主轴環7之外 油係改經絞孔8往轴環……Μ 7之内側之㈣ _ , 軸％ 7之外側流出。於此實施例係藉由 閥體5之從閥座4之上升，從於pq —。k βΒ 上开從於閥至^開口之槽部5d往 闊至3 b流入之作動油、福文丨 c . 通過孔口 5e流入閥室3b之作動由 一起流入軸環7之内側，通過絞孔8到達流出開口丨^。 絞孔8係對從軸環7之内側往外側流出之作動油之流 動給予一定之抵抗，於絞孔8之上下流產生壓力差。因此机 於此實施例亦藉由閥體5從閥座4上升而於軸環7之内側 有背壓產生。 因此，根據此實施例亦與第3實施例同樣地，強化將 閥體5往閥座4按壓之閥室3b之中心軸方向之按壓力。因 此’與軸環7產生之線圈彈簧6之振盪抑制作用相輔相成， 即使對油壓緩衝器D之激烈伸縮衰減閥1亦維持安定之發 生衰減力。 16 201200758 。。〃如上述，根據本發明，藉由將彈性支持閥體5之線圈 =* 6以軸環7覆蓋’彳阻止橫斷線圈彈簧6之作動油之 流動之生A ’抑帝】橫斷線圈料6之作動油之流動對閱體5 造成之振動。因此，即使在油壓緩衝器D以高速伸縮之場 合衰減閥1亦產生安定之衰減力。 本發明僅於線圈彈簧6之周圍設置軸環7即可實施。 因此’對既存之衰減閥亦可容易且低成本地適用本發明。 關於以上之說明皆係將以2〇1〇年〇6月3〇曰為申請曰 之日本特願2009-148535號、日本特願2〇〇9_148536號日 本特願2〇〇9-148538號之内容藉由於此引用而組合。 以上’雖通過數個特定之實施例說明本發明，但本發 明並不限於上述之各實施例。對當業者而t，可以申請專 利範圍之技術範圍對此等實施例施加各種修正或變更。 例如，於以上之各實施例油壓緩衝器D雖係以單流式 之複筒型油壓緩衝器構成’ 本發明之衰減閥不問單筒式 與複筒式’且不問單流型與雙流型皆可適用…卜，在本 發明之衰減閥流動之流體不限於作動油。本發明之衰減閥 、用於以氣體纟、水溶液、電氣黏性流體、磁氣黏性 流體等各種流體為對象之衰減閥。 以上各實施例中，流入開口 3a係形成於與閱室扑同轴 上，但流入開口 3a之位置非與閥室扑同軸上亦可。本發明 亦可適用於線圈彈簧6之伸縮方向與流出開口 ^】之開口部 之方向大致正交之各種衰減閥。 本發明之實施例所包含之排他性質或特長係請求如 201200758 下。 【圖式簡單說明】 圖1為適用本發明之衰減闕之單向流式之複筒型油壓 緩衝器之縱剖面圖。 圖2為农減閥之擴大縱剖面圖。 圖3雖類似於圖2，但係顯示關於軸環之尺寸之變化。 圖4為顯示圖3之衰減閥之衰減力特性之圖。 圖5雖類似於圖2 ’但係顯示關於軸環之尺寸之另一變 化。 圖6為顯示圖5之衰減閥之衰減力特性之圖。 圖7雖類似於圖2，但係顯示本發明之第2實施例。 圖8雖類似於圖2 ,但係顯示本發明之第3實施例。 圖9雖類似於圖2，但係顯示本發明之第*實施例。 圖1 0雖類似於圖9，但係顯示關於圓盤部之構成之變 化。 圖11雖類似於圖2，但係顯示本發明之第5實施例。 【主要元件符號說明】 1 衰減閥 2 桿狀導引部 2a 凹部 2b 環狀通路 9 管 18 201200758 20 汽缸 2 1 外管 22 活塞 23 活塞桿 24 栓部 25 蓋體 25a 眼構件 26a 眼構件 27 · 止回閥 29 止回閥 30 密封構件 3 1 軸承 38 橡膠套 39 外罩 D 油壓緩衝器 R 貯藏槽 R1 活塞桿側之油室 R2 相反側之油室 19►C2 outer circumference 'reaches the central axis direction of the wide chamber 3b. The reaming hole 8 is formed at two places at intervals of 丨80 degrees. In this embodiment, the inner side of the collar 7 is 丨, and the inner side of the ^ _ The end portion 7 of the collar cannot be bypassed. "The oil system outside the spindle ring 7 is changed by the reaming hole 8 to the inner side of the collar ... Μ 7 , and the outer side of the shaft % 7 flows out. This embodiment is by way of The rise of the valve body 5 from the valve seat 4, from the pq -.k β 上 open from the valve to the opening groove portion 5d to the 3 b into the moving oil, Fu Wen 丨 c. Flow through the orifice 5e The operation of the valve chamber 3b flows into the inner side of the collar 7 together, and reaches the outflow opening 通过 through the reaming hole 8. The reaming hole 8 gives a certain resistance to the flow of the moving oil flowing out from the inner side of the collar 7 to the outside, and is twisted. The downward flow above the hole 8 creates a pressure difference. Therefore, the embodiment also generates a back pressure on the inner side of the collar 7 by the valve body 5 rising from the valve seat 4. Therefore, according to this embodiment and the third embodiment, Similarly, the pressing force in the direction of the central axis of the valve chamber 3b that presses the valve body 5 toward the valve seat 4 is reinforced. Therefore, the oscillation of the coil spring 6 generated by the collar 7 is suppressed. The action complements each other, even if the elastic expansion and damping valve 1 of the oil pressure buffer D maintains the damping force of the stability. 16 201200758. As described above, according to the present invention, the coil of the elastic support valve body 5 = * 6 The collar 7 covers the '彳 to prevent the flow of the moving oil of the transverse coil spring 6'. A 'Suppressor' traverses the vibration caused by the flow of the moving oil of the coil material 6 to the reading body 5. Therefore, even in the oil pressure In the case where the damper D is stretched at a high speed, the damping valve 1 also generates a stable damping force. The present invention can be implemented only by providing the collar 7 around the coil spring 6. Therefore, the existing damping valve can be easily and inexpensively applied. The present invention is based on the Japanese Patent Application No. 2009-148535, which is based on the application of the Japanese 〇 〇 〇 〇 〇 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 2009 The contents of 148538 are combined by this reference. The above description has been described by way of several specific embodiments, but the invention is not limited to the embodiments described above. For the practitioner, t can apply for the technical scope of the patent scope. Applying to these embodiments For example, in the above embodiments, the oil pressure buffer D is constituted by a single-flow type double-cylinder type oil pressure buffer. The damping valve of the present invention does not require a single cylinder type and a double cylinder type and does not ask. Both the single flow type and the double flow type are applicable. The fluid flowing in the damping valve of the present invention is not limited to the operating oil. The damping valve of the present invention is used for gas enthalpy, aqueous solution, electric viscous fluid, magnetic viscous fluid In the above embodiments, the inflow opening 3a is formed coaxially with the reading chamber, but the position of the inflow opening 3a is not coaxial with the valve chamber. The present invention is also applicable. The various damping valves are substantially orthogonal to the direction in which the coil spring 6 is expanded and contracted in the direction of the opening of the opening. The exclusive nature or feature contained in the embodiments of the present invention is as set forth in 201200758. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view showing a one-way flow type double-cylinder type oil pressure buffer to which the attenuating crucible of the present invention is applied. Figure 2 is an enlarged longitudinal sectional view of the agricultural reduction valve. Figure 3, although similar to Figure 2, shows changes in the dimensions of the collar. Fig. 4 is a graph showing the damping force characteristics of the damping valve of Fig. 3. Figure 5 is similar to Figure 2' but shows another variation regarding the size of the collar. Figure 6 is a graph showing the damping force characteristics of the damping valve of Figure 5. Fig. 7 is a view similar to Fig. 2 showing a second embodiment of the present invention. Fig. 8 is a view similar to Fig. 2 showing a third embodiment of the present invention. Fig. 9 is a view similar to Fig. 2 showing a fourth embodiment of the present invention. Although Fig. 10 is similar to Fig. 9, it shows a change with respect to the constitution of the disk portion. Fig. 11 is a view similar to Fig. 2 showing a fifth embodiment of the present invention. [Description of main components] 1 damping valve 2 rod guide 2a recess 2b annular passage 9 tube 18 201200758 20 cylinder 2 1 outer tube 22 piston 23 piston rod 24 bolt portion 25 cover 25a eye member 26a eye member 27 Check valve 29 Check valve 30 Sealing member 3 1 Bearing 38 Rubber sleeve 39 Housing D Oil pressure damper R Storage tank R1 Oil chamber R2 on the piston rod side Oil chamber 19 on the opposite side