1354741 四、指定代表圓 (一) 本案指定代表圖為：第（2)圖。 (二) 本代表圖之元件符號簡單說明： 1 活塞缸 11 主活塞 12 主活塞桿 2 主缸體 21 固接管 3 阻尼靜子 4 主缸體頂端蓋 41 主缸體底端蓋 5 外力 61 底油室 62 下油室 63 上油室 64 頂油室 五、化學式 六、發明說明 【發明所屬之技術領域】 本創作揭示一種阻尼自動調郎避震器，其可依受力速度而自動調 整其阻尼係數，在受力速度達第一值以下時可自動鎖定，在受力 速度達第一值以上時可自動解除鎖定，在受力速度達第二值以上 時可進行高速洩壓，而介於第一值與第二值之間時可連續自動改 變其阻尼係數，且係數調整之過程中，不需要額外之驅動能源者。 2 1354741 【先前技術】 一般習知之阻尼器，如圖1所示’其主要原理為，在運作過程中， 流體穿過節流孔時’因流體黏滯特性造成阻尼效應，構成阻尼器 整體的剛性特質。其優點是構造簡單’但缺點是在運作過程中， 由於節流孔之截面積固定，故其阻尼係數無法即時依受力特性而 自動調變，此特性會讓缸組傾向於將尖峰能量直接導入泊接於其 上的機械結構，造成機械結構受到高頻震動而較易損壞。 • 中華民國專利第431390號揭示一種可快速調整阻尼係數之阻尼器 設計，然而其未具有依據受力條件自動調整阻尼係數之功效；中 華民國專利第M253544號揭示一種易控制暨可鎖定之阻尼器，利 於使用者透過簡單的按壓動作即可達成阻尼係數切換的功能，阻 * . 尼係數切換至極大狀態時，可提供幾近鎖固的功能，以利人力車 輛在進行加速動作時，減省人力之損耗，但仍未具有阻尼係數自 動調整之功能；中華民國專利第458229號揭示一種可依據受力速 度自動調整阻尼係數之阻尼器，然而其自動調整的範圍必須在設 计或製造時期予以決定，無法根據實際使用時的操作狀況即時調 變，中華民國專利第]VI299798號揭示一種可調變係數自調阻尼 器’其主要構造為在活塞上設置可與壓力相關之流口，當活塞受 到雙方面較大壓力差時，會移動至距離平衡點較遠處，因此可將 《口開啟至較大截面處，造成活塞前後之流率增加、阻尼係數下 降’然而此設計之活塞體積龐大質量較重，故極易受到流體壓力 t動之影響’且不觀行高速之往復運動。 3 1354741 電子式阻尼係數器可克服部分問題，其主要原理為，以電子的手 段取得運作過財之受力大小、速度等參數，崎運算得到輸出 訊號’用以控舰動H ’以充放流體之流量多寡、或改變節流孔 之有效截面積、或流體之黏滯係數（如電黏性流體、磁性流體） 等特性，以達到控制阻尼係數的效果。然而電子式阻尼器，通常 需要較為魔大而昂貴的電力驅動系統’以驅動其⑽致動器作 動，在重貞載與高頻作動的場合中，致動器需消耗較高功率；再 者’電子電路驅動祕需要良好祕護，在高溫、潮濕、辦 污、電力供應不足的環境下難保其可靠性及可用性，因此其應用 場合有其限制。 【發明内容】 有鏗於以上習知之阻尼H與電子式阻尼器設計與顧上之缺點， 吾人提出一種可不需供給額外致動能量，即可自行依受力速度或 大小，而自動改變阻尼係數之阻尼器，其流口之控制單元質量更 小，因此可達成更高之反應速度，並更可供使用者依據操作條件 隨時手動改變並增大阻尼調魏圍，其運作過財*需驅動電 力’尤其_於重貞載與高頻作動、卫作環麟電子祕不合適、 或無法提供驅動能源等場合設置。 而本創作機體兼具低頻與高頻之能i過濾特性，其可在震盈剛發 生時的尖峰_ ’自動降低阻尼係數，讓高頻能量盡可能被濾除； 在尖峰震麟段猶，阻尼係數可以自動調升，儘速衰減持續震 盪之能量，使結構在較短時間内趨於靜穩；而所提供之使用者調 4 135*4741 變功能’可供使用者依照操作條件隨時手動改變阻尼係數之自動 調變範圍’並猶時歡雜尼器，令之無法伸長驗，達成完 全鎖固之功效，此魏_有觀人力車輛之制，可減省人力 之損耗。 【實施方式】 本創作揭示一種可依受力速度而自動調整阻尼係數之阻尼器其 組合圖如圖2所示，其中活塞缸⑴内含有主活塞(11)並且兩者相互 固接聯動，該活塞缸(1)内套接一主缸體(2)，該主缸體⑺一端具有 -主紅體頂端蓋(4)封閉該端’另___端具有___主缸體底端蓋⑼以封 閉該h，且該主缸體底端蓋(41)中具有一通孔可供主活塞桿(I〗)穿 過，並與固接管(21)相互固接及封閉該固接管(21)之一端，該固接 管(21)之另一端與阻尼靜子(3)相互固接。其中，底油室(61)内至少 一部份空間含有氣體或為真空，下油室(62)内至少一部份空間含有 氣體或為真空，上油室(63)内至少一部份空間含有油液，頂油室(64) 内至少一部份空間含有氣體或為真空。 其中’阻尼靜子(3)内之構造如圖3所示，該阻尼靜子(3)本體具有 至少兩組通孔，分別容納壓縮侧與回彈侧之閥門元件；壓縮侧閥 門元件包括壓縮侧阻尼動子(311)，其受到彈性件(312)之推擠並保 持常停留於阻尼靜子(3)之一侧，該彈性件(312)之另一端受止推 (313)之阻擋，該止推(313)固接於該阻尼靜子(3)之另一侧；壓縮侧 閥門元件另包括一壓縮側逆止閥球(331)，其受到彈性件(332)之推 擠並保持常停留於阻尼靜子⑶之一側，該彈性件(332)之另一端受 5 止推(333)之阻擋，該止推(333)固接於該阻尼靜子(3)之另一側。另、 一方面，回彈侧閥門元件之配置與壓縮侧閥門元件類似，僅有配 置方向之相反，在此並不贅述。 而壓縮側阻尼動子(311)與回彈側阻尼動子(321)之構造相同，在此 僅以壓縮側阻尼動子(311)為例說明，請見圖4，其中該壓縮側阻 尼動子(311)之構造含有一第四流口(3114)，可供上油室(63)之高壓 流體流入該動子内部，並經由至少一組第一流口 (3丨丨丨)向該壓縮侧 阻尼動子(311)之徑向朝外流出（為求該流率之增加，可增設至少 一組第二流口(3112)，該第二流口(3112)之長度、位置及寬度可與 該第一流口(3111)呈一預先決定之對應關係，例如長度相同、寬度 較寬、位置較左侧），該流體再經由至少一組第三流口(3113),向 圖3中之彈性件(312)方向流動，並通過止推(313)中之孔洞，流入 頂油室(64)之低壓側。上述壓縮侧阻尼動子(311)各流口之尺寸設 計’可使得該阻尼動子運動至一預定位置時，高低壓侧流體之流 率，會與該些流口之尺寸、彈簧之常數、預壓、止推(313)上之通 孔尺寸’呈一預定之對應關係。 以本創作受極低速(低於第一值)壓縮力量作用時為例，其回彈侧之 各閥門元件均會受到孔壁之阻擋進行閉鎖，而對壓縮程序並無任 何貢獻，故在壓縮程序中可忽略各回彈侧閥門元件之作動；請參 考圖5 ’外力(5)向左推動’造成主活塞(11)向左侧移動，使得上油 室(63)内之流體壓力增加，然而若該液壓所作用於壓縮側阻尼動子 (311)上之總力未克服彈性件(312)之推力時，壓縮側阻尼動子(311) 1354*741 並不移動’越幾乎並不會從上油室(63)流往頂油室(64)，或者， 僅有極少部分流體透過各元件機械加工上之誤差所造成之縫隙流 在頂油至(64)，此即達成本創作之自動鎖定功效。 若有稍低速(高於第一值)外力(5)進行壓縮時，如圖6所示，上油室 (63)内之壓力作用於壓縮侧阻尼動子(311)上之力量已克服部分彈 性件(312)之彈力，故壓縮側阻尼動子(311)即開始向左移動，此時 第一流口（3111)已有至少一部分與阻尼靜子(3)上之孔穴相互導 •通’故流體將可經由第三流口(3113)流往低壓侧頂油室(64)，完成 洩壓動作，故此時可達成本創作之低速度外力輸入時之稍大阻尼 效果。 若有稍高速(低於第二值)外力(5)進行壓縮時，如圖7所示，上油室 (63)内之壓力作用於壓縮侧阻尼動子(311)上之力量已克服大部分 彈性件(312)之彈力，故壓縮侧阻尼動子(311)向左大幅移動，此時 第一流口 (3111)已有絕大部分與阻尼靜子⑶上之孔穴相互導通(且 鲁若有第二流口(3112)者，該第二流口(3112)將有至少一部份與阻尼 靜子(3)上之孔穴相互導通，可更增加其有效流口面積），故流體 將可經由第二流口(3113)大1流往低壓侧頂油室(64)，完成較快速 之洩壓動作，故此時可達成本創作之高速度外力輸入時之較低阻 尼效果。 若有極高速(第二值以上)外力(5)進行壓縮時，如圖8所示，上油室 (63)内之壓力不但已使壓縮側阻尼動子(311)向左大幅移動，且更進 一步克服彈性件(332)之推力，使得壓縮側逆止閥球(331)亦開始向 7 1354*741 左移動’因此流體將可經由第三流口(3113)及壓縮側逆止閥球_ 處大里流往健側頂油室(64)，完成極快速之沒壓動作，故此時 可達成本創作之極高速度外力輸入時之極低阻尼效果。 上述圖5至圖8之說明，已充分顯示本創作在極低速、低速、高 迷、及極高速各種不同外力施力條件下之作動特性，因此可達成： L外力速度低於第一值時，達成自動鎖定之功效； 2. 外力速度高於第一值時，達成自動解除鎖定之功效； 3. 外力速度高於第二值時，達成快速洩壓之功效； 4. 外力速度介於第-值與第二值之間時，達成連續自動調變阻尼 係數之功效； 5. 上述所有阻尼調變程序，並不需外界能源供應即可進行自動 操作。 另一方面，若外力(5)之施力方向相反，亦即外力(5)對本創作進行 拉伸方向施力時，上述之各項壓縮側閥門元件，均受到其孔壁之 阻擔而閉鎖，因此對於轉方向並無任何貢獻；至於各項回彈侧 閥門元件之運作模式與壓關作動模式完全相同，僅有方向相 反，故在此並不贅述。 值得注意者為，壓縮側與回彈侧之閥門元件（包含各止推上之孔 徑、彈簧之彈力常數、彈簧之預壓、閥球之尺寸、動子上之第一 流口(3111)、第二流口(3112)、第三流口(3113)、第四流口(3114) 之各項尺寸），均可設計為相同或不同，藉以達成對稱或非對稱之 壓縮回彈系統祕；例如，將雜件(312)之雜絲設計得較彈 8 1354741 性件(322)者為大’财制麵方向流體不易赫、回彈較易流 動之效亦即達成麗縮時阻尼力較大、回彈時阻尼力小之緩壓快 放效果。 再者，主活塞(u)上可設計至少一第一流口(13)，與箸片闕⑽及 貫片閥彈性件(16)搭配，可於壓縮或回彈行程中，供流體快速流經 該第机口（13)，可更為增進其高速反應性能；另可設計一第二流 口（14)’可供使用者調整其有效流口面積亦可供流體從活塞之第 側决速流經該第二流口(M)，到達主活塞第二侧(17)，可更為 增進其间速反應性能，且使用者可藉由控制端(18)調整該第二流口 (14)之開口面積。 本創作之另—魏•圖1G所示，此實施赚示當虹⑴或主 缸體(2)過大無法置放於同一位置時，或當阻尼靜子⑶所處之位置 空間過於狹小時，可將主活塞⑼上方之上油室(63)分割為壓力端 上油室(631)及控制端上油室(632)兩部分，其中壓力端上油室(则 可設置於避震ϋ本身’而儀軟#(22)將壓力導送至_端上油室 (632)，而該㈣端上油室(632)位於避震器本體之鄰近處所或利於 =力操作之位置，其㈣關較為寬裕，且操作者麵於操作設 定其運作參數，而其運作原理與上述運作方式相同。 【圖式簡單說明】 圖1傳統之阻尼器結構 圖2本創作組合實施例 圖3阻尼靜子組合實施例(壓縮側及回彈側） 9 1354741 圖4阻尼動子零件實施例 圖5本創作受極低速壓縮示意圖 圖6本創作受稱低速壓縮示意圖 圖7本創作受稍高速壓縮示意圖 圖8本創作受極高速壓縮示意圖 圖9本創作之主活塞流口實施例 圖10本創作之分離式阻尼控制實施例 【主要元件符號說明】 1 活塞缸 11 主活塞 12 主活塞桿 13 第一流口 14 第二流口 15 簧片閥 16 簧片閥彈性件 17 主活塞第二側 18 控制端 2 主缸體 21 固接管 軟管 阻尼靜子 22 1354741 311 壓縮側阻尼動子 3111第一流口 3112第二流口 3113第三流口 3114第四流口 312 彈性件 313 止推 • 321 回彈侧阻尼動子 322 彈性件 323 止推 331 壓縮側逆止閥球 332 彈性件 333 止推 341 回彈側逆止閥球 • 342彈性件 343 止推 4 主缸體頂端蓋 41 主缸體底端蓋 5 外力 61 底油室 62 下油室 63 上油室 1354741 631 壓力端上油室 632 控制端上油室 64 頂油室1354741 IV. Designated representative circle (1) The representative representative of the case is: (2). (2) The symbol of the symbol of this representative diagram is simple: 1 Piston cylinder 11 Main piston 12 Main piston rod 2 Master cylinder 21 Fixing pipe 3 Damping stator 4 Master cylinder top cover 41 Main cylinder bottom end cover 5 External force 61 Base oil Room 62 lower oil chamber 63 upper oil chamber 64 top oil chamber 5, chemical formula 6, invention description [Technical field of invention] This creation discloses a damping automatic slamming shock absorber, which can automatically adjust its damping according to the force speed The coefficient can be automatically locked when the force is below the first value. When the force is above the first value, the lock can be automatically released. When the force is above the second value, the high pressure can be released. The damping coefficient can be continuously and automatically changed between the first value and the second value, and no additional driving energy is needed during the coefficient adjustment. 2 1354741 [Prior Art] A conventional damper, as shown in Fig. 1, 'the main principle is that during the operation, when the fluid passes through the orifice, the damping effect due to the fluid viscous property constitutes the rigidity of the damper as a whole. Characteristics. The advantage is that the structure is simple 'but the disadvantage is that during the operation, since the cross-sectional area of the orifice is fixed, the damping coefficient cannot be automatically modulated according to the force characteristic. This characteristic will make the cylinder group tend to directly direct the peak energy. The mechanical structure docked on it is introduced, causing the mechanical structure to be subjected to high frequency vibration and being easily damaged. • The Republic of China Patent No. 431390 discloses a damper design that can quickly adjust the damping coefficient, but it does not have the effect of automatically adjusting the damping coefficient according to the force condition; the Republic of China Patent No. M253544 discloses an easy-to-control and lockable damper It can help the user to achieve the function of damping coefficient switching through a simple pressing action. When the Nie coefficient is switched to the maximum state, it can provide a nearly locking function, so that the human vehicle can reduce the acceleration action. Manpower loss, but still does not have the function of automatic adjustment of damping coefficient; Republic of China Patent No. 458229 discloses a damper that can automatically adjust the damping coefficient according to the force rate, however, the range of automatic adjustment must be given during the design or manufacturing period. It is decided that it cannot be tuned according to the actual operating conditions. The Republic of China Patent No. VI299798 discloses a variable-variable self-adjusting damper whose main configuration is to provide a pressure-dependent orifice on the piston. When there is a large pressure difference between the two sides, it will move to a distance from the equilibrium point. This can open the mouth to a larger section, causing the flow rate before and after the piston to increase and the damping coefficient to decrease. However, the piston of this design is bulky and of high quality, so it is highly susceptible to the influence of fluid pressure t and does not obey. High-speed reciprocating motion. 3 1354741 The electronic damping coefficient device can overcome some problems. The main principle is to obtain the parameters such as the size and speed of the operation, and the output signal 'to control the ship' H' to charge and discharge the flow. The flow rate of the body, or the effective cross-sectional area of the orifice, or the viscosity coefficient of the fluid (such as electro-viscous fluid, magnetic fluid), etc., to achieve the effect of controlling the damping coefficient. However, electronic dampers usually require a more expensive and expensive electric drive system to drive their (10) actuators. In the case of heavy load and high frequency operation, the actuator consumes higher power; Electronic circuit drive secrets require good protection. In the environment of high temperature, humidity, pollution, and insufficient power supply, it is difficult to ensure its reliability and availability. Therefore, its application has its limitations. SUMMARY OF THE INVENTION In view of the above-mentioned conventional damper H and electronic damper design and the disadvantages of the above, we propose that the damping coefficient can be automatically changed according to the speed or magnitude of the force without the need to supply additional actuation energy. The damper has a smaller control unit of the flow port, so that a higher reaction speed can be achieved, and the user can manually change and increase the damping adjustment according to the operating conditions at any time, and the operation is too expensive. Electricity 'especially _ in the case of heavy load and high frequency actuation, Wei Zuo ring electronic secret is not suitable, or can not provide driving energy and other occasions. The creation body has both low-frequency and high-frequency energy i-filtering characteristics, which can be used to reduce the damping coefficient when the shock is just occurring, so that the high-frequency energy is filtered out as much as possible; The damping coefficient can be automatically increased, and the energy of continuous oscillation is attenuated as soon as possible, so that the structure tends to be stable in a short time; and the provided user can adjust the function of 4 135*4741 to allow the user to manually follow the operating conditions at any time. Change the automatic modulation range of the damping coefficient' and it is still difficult to extend the test to achieve the effect of complete locking. This Wei_ has a human-powered vehicle system, which can reduce the loss of manpower. [Embodiment] The present invention discloses a combination of a damper that can automatically adjust a damping coefficient according to a force rate, as shown in FIG. 2, in which a piston cylinder (1) contains a main piston (11) and the two are fixedly coupled to each other. The piston cylinder (1) is sleeved with a main cylinder body (2), and the main cylinder body (7) has a main red body top end cover (4) at one end to close the end. The other ___ end has a ___ main cylinder bottom end The cover (9) is closed to the h, and the main cylinder bottom end cover (41) has a through hole for the main piston rod (I) to pass through, and is fixed to the fixing tube (21) and closes the fixing tube ( 21) At one end, the other end of the fixing pipe (21) is fixed to the damping stator (3). Wherein at least a portion of the space in the bottom oil chamber (61) contains a gas or a vacuum, and at least a portion of the space in the lower oil chamber (62) contains a gas or a vacuum, and at least a portion of the space in the oil chamber (63) Containing oil, at least a portion of the space in the top oil chamber (64) contains a gas or is a vacuum. The structure in the 'damper stator (3) is as shown in FIG. 3. The body of the damping stator (3) has at least two sets of through holes respectively accommodating the valve elements on the compression side and the rebound side; the compression side valve elements include compression side damping The mover (311) is pushed by the elastic member (312) and remains constantly on one side of the damping stator (3), and the other end of the elastic member (312) is blocked by the thrust (313). Pushing (313) is fixed to the other side of the damping stator (3); the compression side valve member further includes a compression side check valve ball (331) which is pushed by the elastic member (332) and remains constantly One side of the damping stator (3), the other end of the elastic member (332) is blocked by a 5 thrust (333), and the thrust (333) is fixed to the other side of the damping stator (3). On the other hand, the configuration of the rebound-side valve member is similar to that of the compression-side valve member, and only the configuration direction is reversed, and will not be described herein. The compression side damping mover (311) has the same structure as the rebound side damping mover (321). Here, only the compression side damping mover (311) is taken as an example, see FIG. 4, wherein the compression side is damped The configuration of the sub (311) includes a fourth flow port (3114) through which the high pressure fluid for the oiling chamber (63) flows into the mover and is compressed by the at least one set of first flow ports (3丨丨丨) The side damper (311) flows radially outward (in order to increase the flow rate, at least one set of second flow ports (3112) may be added, and the length, position and width of the second flow port (3112) may be Corresponding to the first flow port (3111), for example, the same length, the width is wider, the position is to the left side, and the fluid is further passed through at least one set of third flow ports (3113) to FIG. The elastic member (312) flows in the direction and flows into the low pressure side of the top oil chamber (64) through the hole in the thrust (313). The size of each of the orifices of the compression side damping mover (311) is such that when the damping mover moves to a predetermined position, the flow rate of the high and low pressure side fluids, the size of the flow ports, the constant of the spring, The through hole size ' on the preloading and thrusting (313) is in a predetermined correspondence relationship. For example, when the creation is subjected to a very low speed (below the first value) compression force, each valve element on the rebound side is blocked by the wall of the hole, and does not contribute to the compression process, so it is compressed. The operation of each rebound-side valve element can be ignored in the program; please refer to Figure 5 'External force (5) pushes left' to cause the main piston (11) to move to the left, so that the fluid pressure in the oil-up chamber (63) increases, however If the total force applied by the hydraulic pressure on the compression side damper (311) does not overcome the thrust of the elastic member (312), the compression side damper mover (311) 1354*741 does not move 'the more almost does not The oiling chamber (63) flows to the top oil chamber (64), or only a small portion of the fluid flows through the gap caused by the machining error of each component to the top oil to (64), which is the automatic realization of the creation. Locking effect. If there is a lower speed (higher than the first value) external force (5) for compression, as shown in Fig. 6, the pressure in the oiling chamber (63) acts on the compression side damping mover (311). The elastic force of the elastic member (312), so that the compression side damping mover (311) starts to move to the left, and at this time, at least a part of the first flow port (3111) and the hole on the damping stator (3) are mutually conductive. The fluid will flow through the third flow port (3113) to the low pressure side top oil chamber (64) to complete the pressure relief action, so that the damping effect of the low speed external force input created by the cost can be achieved. If there is a slight high speed (below the second value) external force (5) for compression, as shown in Fig. 7, the force in the oiling chamber (63) acts on the compression side damping mover (311). The elastic force of part of the elastic member (312), so that the compression side damping mover (311) moves to the left, and the first flow port (3111) has a large majority of the holes on the damping stator (3) (and Lu Ruo has The second flow port (3112), the second flow port (3112) will have at least a portion of the holes in the damping stator (3), which can increase the effective flow port area thereof, so that the fluid will be The second flow port (3113) flows to the low pressure side top oil chamber (64) to complete a relatively rapid pressure relief operation, so that the low damping effect of the high speed external force input at the time of cost creation can be achieved. If there is an extremely high speed (second or more) external force (5) for compression, as shown in Fig. 8, the pressure in the oiling chamber (63) not only causes the compression side damping mover (311) to move to the left, and Further overcome the thrust of the elastic member (332), so that the compression side check valve ball (331) also begins to move to the left of 7 1354*741 'so the fluid will pass through the third flow port (3113) and the compression side check valve ball _ Dali flows to the top side oil chamber (64), which completes the extremely fast no-pressure action, so it can achieve the extremely low damping effect of the extremely high speed external force input at the time of cost creation. The above description of FIG. 5 to FIG. 8 has fully demonstrated the actuation characteristics of the present invention under extremely low speed, low speed, high speed, and extremely high speed various external force application conditions, and thus can be achieved: When the external force speed is lower than the first value , to achieve the effect of automatic locking; 2. When the external force speed is higher than the first value, the effect of automatic unlocking is achieved; 3. When the external force speed is higher than the second value, the effect of rapid pressure relief is achieved; 4. The external force speed is between the first - When the value is between the second value and the second value, the effect of continuously adjusting the damping coefficient is achieved; 5. All the above damping modulation programs can be operated automatically without external energy supply. On the other hand, if the biasing force of the external force (5) is opposite, that is, when the external force (5) exerts a tensile force on the creation direction, the above-mentioned various compression side valve elements are blocked by the wall of the hole and blocked. Therefore, there is no contribution to the direction of rotation; as for the operation mode of each of the rebound-side valve elements, the mode of operation is exactly the same as that of the pressure-off mode, and the direction is reversed, so it will not be described here. It is worth noting that the valve components on the compression side and the rebound side (including the aperture on each thrust, the spring constant of the spring, the preload of the spring, the size of the valve ball, the first flow port on the mover (3111), the first The second flow port (3112), the third flow port (3113), and the fourth flow port (3114) can be designed to be the same or different, thereby achieving a symmetric or asymmetric compression rebound system secret; for example; The miscellaneous wire of the miscellaneous piece (312) is designed to be more elastic than the 8 1354741 piece (322). The fluid in the direction of the large 'financial plane is not easy to move, and the rebound is easier to flow, that is, the damping force is larger when the refining is achieved. The rebound pressure is small and the damping force is small. Furthermore, the main piston (u) can be designed with at least one first flow port (13), which is matched with the cymbal cymbal (10) and the sipe valve elastic member (16) for allowing fluid to flow rapidly during the compression or rebound stroke. The first port (13) can further improve its high-speed reaction performance; and a second flow port (14) can be designed to allow the user to adjust the effective flow port area for the fluid to be decelerated from the first side of the piston. Flowing through the second flow port (M) to reach the second side (17) of the main piston can further improve the speed response performance thereof, and the user can adjust the second flow port (14) by the control end (18). The opening area. Another example of this creation - Wei Figure 1G, this implementation earns when the rainbow (1) or the master cylinder (2) is too large to be placed in the same position, or when the position of the damping stator (3) is too narrow, The oil chamber (63) above the main piston (9) is divided into two parts: a pressure end oil chamber (631) and a control end oil chamber (632), wherein the pressure end oil chamber (which can be set in the shock absorber itself) The instrument soft #(22) conducts the pressure to the _ terminal oil chamber (632), and the (four) end oil chamber (632) is located in the vicinity of the shock absorber body or facilitates the operation of the force, and (4) It is more plentiful, and the operator sets its operating parameters in operation, and its operation principle is the same as the above operation mode. [Simple diagram of the figure] Figure 1 Traditional damper structureFig. 2 This creative combination embodiment Fig. 3 Damping stator combination implementation Example (compression side and rebound side) 9 1354741 Figure 4 Damping mover part embodiment Figure 5 This creation is subject to very low speed compression diagram Figure 6 This creation is called low speed compression diagram Figure 7 This creation is subject to slightly high speed compression diagram 8 The schematic diagram of the high-speed compression of the pole is shown in Figure 9. Example FIG. 10 Separate damping control embodiment of the present invention [Description of main components] 1 Piston cylinder 11 Main piston 12 Main piston rod 13 First flow port 14 Second flow port 15 Reed valve 16 Reed valve elastic member 17 Main piston Second side 18 Control terminal 2 Master cylinder 21 Fixing pipe hose damping stator 22 1354741 311 Compression side damping mover 3111 First flow port 3112 Second flow port 3113 Third flow port 3114 Fourth flow port 312 Elastic member 313 Thrust • 321 rebound side damping mover 322 elastic member 323 thrust 331 compression side check valve ball 332 elastic member 333 thrust 341 rebound side check valve ball • 342 elastic member 343 thrust 4 master cylinder top cover 41 main Cylinder bottom end cover 5 external force 61 bottom oil chamber 62 lower oil chamber 63 upper oil chamber 1354741 631 pressure end oil chamber 632 control end oil chamber 64 top oil chamber