200925380 九、發明說明： 【發明所屬之技術領域】 ❹ 本發明關於一種鉸鏈，特別是傢倶用者，具有-鉸鏈 β至夕彈簧及一直線緩衝器；該鉸鏈部固定在一門或 一翻板上’該鉸鏈部支承在—側部上，可經—攜帶橘桿及 -導引槓桿樞轉，其中該側部保持在一個安裝板上，安裝 板可安裝在-傢俱體上；利用該彈著將较鏈部在-自拉區 域施預應力到一關閉位置；該直線緩衝器具有一活塞桿， 可相對於-緩衝器殼體運動，用於將较鏈部的關閉運動緩 衝。 【先前技術】 德專利DE 20 2_ 003 196發表了 一種像俱錢鍵，其中 -⑽部以可樞轉的方式支承在一「攜帶槓桿」及一「導 引相桿」上。在導引槓桿上設有一懸臂（細卜㈣，與一 ❹緩衝器的-活塞㈣合。當鉸鍵部作關閉運動時，該緩衝 器起作用，其中活塞桿將活塞從緩衝器殼體拉出來，因此 活塞呈拉力緩衝器的作用。固然，此傢俱鉸鏈構造緊密， 但有-缺點：由於活塞桿直接輕合在導引横桿上，緩衝曲 ^很敏感地敎。特別是還有—問題：對拉力作用的緩 衝器在密封區域會受磨損，因此緩衝性質會改變。 歐洲專利EP i 555 372發表一種傢俱鉸鏈，其中一鉸 2部經—導引槓桿及1帶桿桿支承在—侧部上，在侧部 中谷納著-直線緩衝器，其活塞桿突出來，呈一種元件串 5 200925380 *歹，j方式與導引槓桿上的-懸臂連接。如此，利用懸臂與連 接兀件的幾何性質’在錢鍵部關閉時緩衝性質改變，然而 仍有一問題：在緩衝器的使用壽命之間緩衝性質會改變， 特別是因為在緩衝器殼體的開放側上，密封件受磨損 此緩衝器的可負荷性受限’如果緩衝力量太“生因 則有一問題：傢俱門在關閉運動時會彈回，這點對使用者 而言报困擾。當緩衝作用調整成太弱冑，會由於 ❹到傢俱體產生碰然巨響（Knallen)。 【發明内容】 因此本發明的目的在提供一種鉸鏈，特另4是像俱用 者，它可使得在關閉時即使在許多次關閉過程時’仍能將 较鏈部可靠地緩衝，且其中緩衝作用最加地配合不同 入情況。 · 此目_用具中請專利範圍第1項的特點的欽鏈達成。 © 依本發明該緩衝器碑計成壓力緩衝器形式，且設有一 轉向元件’該轉向元件與該緩衝器耗合且可在鉸鏈部的關 閉運動時紐-拉桿運動。如此，當欽鍵部關閉時，在拉桿 上的一股拉力被轉換成一股壓力，它在關閉時作用到緩衝 器上。緩衝器在關閉運動時只受到壓力的應力，因此繞著 活塞桿設置的密封件的負荷比較小。如此’廢力只作用到 罐形殼體的關閉側上（該殼體比較穩定）。如此，至少將 T體密封的密封件不會受到應力（它們設在一可動的活塞 θ周圍）這點可確保有長的使用壽命，此外，即使在許 6 200925380 . 多動作循環之後，該緩衝性質仍保持近似相同。 依本發明一較佳實施例，轉向元件以可轉動的方式支 承在側部上，且當受拉桿施一拉力時，施一廢力到緩衝器 上。在此，轉向元件可直接與活塞桿一端耦合，因此轉向 凡件的旋轉運動被轉換成活塞桿的直線往復運動。為此， 緩衝器以可樞轉的方式支承在緩衝器殼體的封閉端上。 緩衝器宜在一開放角度（至少25。，且至少4〇。）及鉸 鏈部的一關閉位置之間作用，因此在一較長的樞轉路徑中 造成緩衝作用。這點使鉸鏈部能有一定的關閉作用，它比 較不受到該鉸鏈部最初的速度以及與鉸鏈部連接的構件的 一些重量力量的影響。如此，利用該緩衝器可將最初的動 能吸收，直到該由彈簧及緩衝器預定的關閉參數達成為止。 為了要能有效造成一長的緩衝路徑，緩衝器的行程為4 〜20毫米，且為5〜10毫米，如此，可在造成緊密構造的 同時，在鉸鏈部關閉時得到足夠的緩衝作用。 ❹ 為了在此鉸鍵造成一定的緩衝曲線，故該敍鏈關閉運 動時’在關閉位置前1 5。直到關閉位置的範圍中，轉換比例 且選設成使得在鉸鏈部的樞轉角度與緩衝器的行程之間， 每度的樞轉運動造成的行程為〇.〇5毫米〜0.24毫米，且宜 0.14毫米〜0.18毫米，在關閉位置前在終區域中，緩衝器 用於使一門或一蓋板作一定的關閉作用，因此在此處，相 對於關閉運緩衝器須有較大的緩衝力量及大的行程。但此 行程不得太大，否則鉸鏈會有受過負荷的力量損壞之虞。 如果緩衝作用在絞鏈部關閉時一直上升，則很有利，如此 7 200925380 放 擊此外，該緩衝器可在關閉位置以及一 30。的開 度之間的開放範圍中移動其總行程# 6〇%以上 上），如此在關閉位置前方一終區域中就可達到大 放緩衝作用。儘管緩衝器的活塞桿有對應的運動但沿開 方向緩衝作用卻很小，然而這點可利用緩衝器殼體中活 '應的叹汁達成。适些大致單向作用的緩衝器係習知者。 立最好利用彈簧的作用造成鉸鍵部的自拉作用，其中錢 ❹’ P自動移到關閉位置’在這種自拉範圍中，鉸鏈部只利 用彈簧的力量移到關閉位置且不需其它力量。此範圍終止 於彈簧力量不夠將鉸鏈部移到關閉位置之處。舉例而言， :拉區域在20。〜50。（且宜30。〜45。）間的範圍開始：且 一直作用到關閉位置為止。 為了使得在鉸鏈建入的狀態時，操作能儘量舒適，故 彈黃宜在鄰接到關閉位置的一第一開放範圍中向關閉方向 作用（自拉作用），而在一第二開放範圍中，彈簧將鉸鏈 φ 部向開放方向施預應力。 彈簧力量宜可在I5。〜45。（特別是2〇。〜4〇。）的開放 角度範圍中達到最大，而在其他範圍中再變較小。如此， 彈簧的材料負荷在鉸鏈部打開時保持很小，這點使得使用 壽命加長。 在此，彈簧可設計成彈簧夾（Schenkelfeder)形式它 有一第一腿，與鉸鏈部耦合，並有一第二腿，與導引槓捍 的懸臂上的一軸搞合。為了使彈簧能後導引 (Nachfiihrung)，在此彈簧可用可轉動的方式支承在攜帶 8 200925380 槓桿的一軸上。 為了使鉸鏈部在彈簧上運動時材料的負荷減少，該彈 簧之與轉向元件耦合的腿可倚在一轉向滾子上。轉向滾子 減少彈簧（其中令發方大的負荷）的腿（它大多設計成較 短）的摩擦力。如此，彈簧及整個鉸鏈的使用壽命都大大 延長。 在本發明另一有利設計中，緩衝器與彈簧設計成在鉸 鏈關閉運動時，在4。〜0。間（且宜8。〜〇。間）的開放範圍 ❹ 中’關閉速度保持大致相同’如此藉著將緩衝器及彈簧及 轉換比例對應地設定，可將一個所要關閉的蓋板或門的動 態緩衝’使得不論開始的關閉速度如何，在關閉位置前不 遠處的一開放範圍内，關閉速度幾乎完全依彈簧力及緩衝 器而定且可最佳化。這點達成之道，係使緩衝器在較大的 開放角度時已產生逆著關閉方向的力量。 本發明在以下利用實施例配合附圖詳細說明。 【實施方式】 一鉸鏈（1)包含一鉸鏈部（2)，它以可柩轉的方式支承在 一側部（3)上。側部（3)保持在一安裝板（4)上，安裝板可安裝 在一傢俱體（5)(例如一櫥）上》有一門、蓋板或其他構件 固定在鉸鏈部（2)上。如圖1所示’ (6)可從一關閉位置移 到一開放位置（6，）（用虛線表示）’其中最大開放角度p在 90。〜120。（且宜100°〜110°)範圍。 在圖2及圖3中所示之鉸鏈（1)該側部設計成可調 9 200925380 整，其中一第一調整螺絲（16)用於將側部（3)相對於安裝板 移動’另一調整螺絲（17)用於作放置部調整。 鉸鏈部（2)以可轉動的方式支承在一攜帶槓桿（7)和一導 引槓桿（8)來，其中在導引槓桿（8)的懸臂（25)上柩接著一拉 桿（9)。拉桿（9)與一可轉動的轉向元件（10)連接，轉向元件 與一直線緩衝器（11)耦合。 緩衝器（11)有一罐形緩衝器殼體（12)，活塞桿（13)由該 〇 殼體突伸出來。活塞桿（13)與轉向元件（10)樞接。在緩衝器 (12)背向活塞桿（13)上。在此，侧部可經由一受彈簧預繃 緊的卡合槓桿（15)固定在安裝板（4)上。 圖4中顯示鉸鏈的細節的分解圖。在攜帶槓桿與導 引槓桿（8)之間設有一彈簧（18)，它有二條腿（19)(2〇)，且鉸 鏈部可被向一開放位置或關閉位置施預應力。 在圖5A〜5G中，顯示鉸鏈（1)之相關部分，它們各鉸 鏈部（2)作關閉運動時的緩衝性質有關。鉸鏈部（2)經一轴（21) ❹與攜帶槓桿（7)連接，並經一轴（22)與導引槓桿（8)連接。彈 簧（18)設在攜帶槓桿（7)與導引槓桿（8)間，其中彈簧（18)設計 成彈簧夾形式且在其螺旋形區域中支承成可繞一軸（2 3)轉 動的方式，其中該軸（23)也形成攜帶槓桿（7)在側部（8)上的 旋轉支承部，導引槓桿（8)以可轉動的方式經一轴（24)支承在 側部（3)上。 在導引槓桿（8)上形成一懸臂（25)，其上設有一轴（26)， 拉桿（9)以可轉動的方式支承在其上。在拉桿（9)的對立端上 設有一軸（29)，它將拉桿（9)與轉向槓桿（1〇)連接《«轉向元件 200925380 (10)繞一軸（27)支承在侧部（3)上。其中軸（27)設在用於與拉 桿（9)連接的軸（29)及用於將轉向元件（1〇)與活塞桿（13)耦合 的一轴（28)之間。此外顯示在背向活塞桿（13)那一側上緩衝 殼體（12)上的一卡合容納部，因此緩衝器殼體（12)以可轉動 的方式在卡合容納部（30)與側部（3)連接，且可避免橫向力作 用到活塞私（13)上。藉著將活塞桿（丨3)與轴（28)之間的連接 的設計’緩衝器（n)也可作加裝。 在圖5A中顯示鉸鏈部（2)在最大開放位置，其中彈簧 (18) 第一腿（19)倚在轴（22)上，而第二腿（2〇)倚在一轉向滚子 (40)上（圖4)，轉向滾子（4〇)支承在軸（26)上。 圖5B中顯示的较鏈部（2)的位置中，较鏈部（2)從最大 開放位置一直移到約85。的開放角度。此處，彈簧（18)的腿 (19) 同時倚在軸（22)及轴（21)上且在此位置似乎從轴（22)「過 渡」到轴（21)。從此最大開放位置直到開放角度85。為止， 不會有力量經由彈簧（18)導入。因為彈簧（18)更進一步被繃 g 緊。對立的腿（20)更倚在軸（26)上的轉向滾子（40)上，因此 彈簧（18)在約85。〜55。之間的範圍（見圖5C)沿門或鉸鏈 •部（2)的開放方向作用，換言之，反抗關閉運動。在此鉸鏈 位置，緩衝器的作用很小，因為耦合元件的角位置在，導 引槓桿（8)上的懸臂（25)、拉桿（9)及轉向槓桿（1〇)預設成如 此。 圖5D中顯示鉸鏈部的開放置，其角度約55。。當達到 此開放角度時，軸（21)(22)及（24)形成一條線，彈簧（18)在最 大繃緊的位置，在此位置，腿〇 9)及（2〇)張開得最大。如果 200925380 通過此位置，日& 鏈°卩（2)繼續向關閉方向移動，則彈簧（18) I: Ϊ於有摩擦、容許誤差及其他影響，彈簧(18)的小小 ^能追踪，因此實際的自拉角度〔在此角度時 文預應力到關閉位置〕約在4〇。。200925380 IX. Description of the invention: [Technical field to which the invention pertains] ❹ The present invention relates to a hinge, particularly a furniture user, having a hinge β-to-night spring and a linear buffer; the hinge portion is fixed to a door or a flap 'The hinge portion is supported on the side portion and is pivotable via the carrying orange bar and the guiding lever, wherein the side portion is held on a mounting plate, and the mounting plate can be mounted on the home; The chain portion is prestressed in a self-tensioning region to a closed position; the linear buffer has a piston rod movable relative to the - damper housing for buffering the closing motion of the chain. [Prior Art] German Patent DE 20 2_003 196 discloses a coin-like key in which - (10) is pivotally supported on a "portable lever" and a "guide rod". The guide lever is provided with a cantilever (fine (4), which is combined with a piston-four (four) buffer. When the hinge portion is closed, the buffer acts, wherein the piston rod pulls the piston from the buffer housing Out, so the piston acts as a tension buffer. Of course, the hinge of the furniture is tightly constructed, but there are - disadvantages: because the piston rod is directly attached to the guide rail, the cushioning is very sensitive. Especially, Problem: The damper acting on the tension is subject to wear in the sealing area, so the cushioning properties are changed. European Patent EP 555 372 discloses a furniture hinge in which a hinge 2 is guided by a guide lever and 1 with a lever. On the side, in the side part of the valley is a linear buffer, the piston rod protrudes, and is a kind of component string 5 200925380 *歹, j way and the cantilever connection on the guiding lever. Thus, using the cantilever and connecting the piece The geometric nature of the buffer property changes when the money key is closed, however there is still a problem: the cushioning properties change between the service life of the bumper, especially because on the open side of the bumper housing, the seal The loadability of this buffer is limited by wear. 'If the cushioning force is too high, there is a problem: the furniture door will bounce back when the movement is closed. This is troublesome for the user. When the cushioning effect is adjusted too weak胄 会 具体 具体 具体 具体 具体 具体 【 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 When the process is closed, 'the chain can be reliably buffered, and the buffering effect can be matched with the different conditions. · The purpose of this item is to achieve the realization of the characteristics of the first item of the patent scope. © According to the invention, the buffer The monument is in the form of a pressure damper and is provided with a steering element that is compliant with the damper and that can move the link during the closing movement of the hinge. Thus, when the key is closed, on the ram One of the pulling forces is converted into a pressure that acts on the damper when it is closed. The damper is only subjected to pressure stress during the closing motion, so the load placed around the piston rod is relatively small. Thus, the 'disuse force only acts on the closed side of the can-shaped housing (the housing is relatively stable). Thus, at least the seals that seal the T-body are not stressed (they are placed around a movable piston θ) The point ensures a long service life and, in addition, the cushioning properties remain approximately the same even after a multi-action cycle. According to a preferred embodiment of the invention, the steering element is rotatably supported on the side. Above, and when a tension is applied by the tie rod, a waste force is applied to the buffer. Here, the steering element can be directly coupled to one end of the piston rod, so that the rotational motion of the steering member is converted into a linear reciprocating motion of the piston rod. To this end, the damper is pivotally supported on the closed end of the damper housing. The damper preferably acts between an open angle (at least 25° and at least 4 〇) and a closed position of the hinge portion. Therefore, a buffering effect is caused in a longer pivoting path. This allows the hinge portion to have a certain closing effect, which is less affected by the initial speed of the hinge portion and some of the weight strength of the member connected to the hinge portion. Thus, the initial kinetic energy can be absorbed by the buffer until the predetermined closing parameters of the spring and the buffer are achieved. In order to effectively create a long buffer path, the stroke of the damper is 4 to 20 mm and 5 to 10 mm, so that a tight cushioning effect can be obtained while the hinge portion is closed. ❹ In order to create a certain buffer curve at this hinge, the chain is closed when the motion is '1' before the closed position. Up to the range of the closed position, the conversion ratio is selected such that between the pivoting angle of the hinge portion and the stroke of the damper, the pivoting motion per degree is caused by a stroke of 〇. 5 mm to 0.24 mm, and preferably 0.14 mm~0.18 mm, in the final area before the closed position, the buffer is used to make a door or a cover cover a certain closing action, so here, there must be a large buffering force and a large relative to the closing buffer. Itinerary. However, this stroke must not be too large, otherwise the hinge will be damaged by the force of the load. It is advantageous if the cushioning action is always raised when the hinge is closed, so that the buffer can be in the closed position and a 30. In the open range between the opening degrees, the total stroke #6〇% or more is moved, so that the buffering effect can be achieved in a final area in front of the closing position. Although the piston rod of the damper has a corresponding movement, the buffering effect in the opening direction is small, but this can be achieved by using the sighing juice in the damper housing. Appropriate buffers that are generally unidirectional are conventional. It is best to use the action of the spring to cause the self-tensioning of the hinge part, wherein the money ❹ 'P automatically moves to the closed position'. In this self-tensioning range, the hinge part only uses the force of the spring to move to the closed position and no other power. This range ends when the spring force is insufficient to move the hinge to the closed position. For example, the pull area is at 20. ~50. (and should be 30. ~ 45.) The range begins: and always acts until the closed position. In order to make the operation in the state of the hinge, the operation can be as comfortable as possible, so the spring should be acted in the closing direction (self-pull) in a first open range adjacent to the closed position, and in a second open range, The spring pre-stresses the hinge φ in the open direction. The spring force should be at I5. ~45. (especially 2〇.~4〇.) The opening angle range reaches the maximum, while in other ranges it becomes smaller. Thus, the material load of the spring is kept small when the hinge portion is opened, which makes the service life longer. In this case, the spring can be designed in the form of a spring clip which has a first leg, which is coupled to the hinge and has a second leg which engages with a shaft on the cantilever of the guide bar. In order to enable the spring to be guided, the spring can be rotatably supported on a shaft carrying the 8 200925380 lever. In order to reduce the load on the material as the hinge portion moves over the spring, the legs of the spring coupled to the steering member can lean against a steering roller. Steering roller Reduces the friction of the springs (which are mostly designed to be short). In this way, the service life of the spring and the entire hinge is greatly extended. In a further advantageous embodiment of the invention, the damper and the spring are designed to be at 4 when the hinge is closed. ~0. The open range of Between (and should be 8. ~ 〇.) ❹ The 'closing speed remains roughly the same'. By setting the damper and the spring and the conversion ratio accordingly, the dynamics of a cover or door to be closed can be set. The cushioning is such that, regardless of the initial closing speed, the closing speed is almost entirely dependent on the spring force and the damper and can be optimized within an open range not far before the closing position. This is achieved by making the bumper have a force against the closing direction at a large opening angle. The invention will be described in detail below with reference to the accompanying drawings. [Embodiment] A hinge (1) includes a hinge portion (2) which is rotatably supported on one side portion (3). The side portion (3) is held on a mounting plate (4) which can be mounted on a specific (5) (e.g., a cabinet) with a door, cover or other member attached to the hinge portion (2). As shown in Fig. 1, '(6) can be moved from a closed position to an open position (6,) (indicated by a broken line) where the maximum opening angle p is 90. ~120. (and preferably 100 ° ~ 110 °) range. The side of the hinge (1) shown in Figures 2 and 3 is designed to be adjustable 9 200925380, with a first adjustment screw (16) for moving the side portion (3) relative to the mounting plate 'another The adjusting screw (17) is used for the placement adjustment. The hinge portion (2) is rotatably supported by a carrying lever (7) and a guiding lever (8), wherein a lever (9) is attached to the cantilever (25) of the guiding lever (8). The drawbar (9) is coupled to a rotatable steering element (10) that is coupled to a linear buffer (11). The damper (11) has a can damper housing (12) from which the piston rod (13) projects. The piston rod (13) is pivotally connected to the steering element (10). The buffer (12) faces away from the piston rod (13). Here, the side portions can be fastened to the mounting plate (4) via a snap-fit lever (15) that is pretensioned by a spring. An exploded view of the detail of the hinge is shown in FIG. Between the carrying lever and the guiding lever (8) is provided a spring (18) having two legs (19) (2 turns) and the hinge portion can be prestressed to an open or closed position. In Figs. 5A to 5G, the relevant portions of the hinge (1) are shown, and their respective hinge portions (2) are related to the cushioning property at the time of closing movement. The hinge portion (2) is connected to the carrying lever (7) via a shaft (21) and connected to the guiding lever (8) via a shaft (22). a spring (18) is provided between the carrying lever (7) and the guiding lever (8), wherein the spring (18) is designed in the form of a spring clip and is supported in its helical region for rotation about an axis (23). Wherein the shaft (23) also forms a rotary bearing on the side portion (8) of the carrying lever (7), the guiding lever (8) being rotatably supported on the side portion (3) via a shaft (24) . A cantilever (25) is formed on the guiding lever (8), and a shaft (26) is provided thereon, and the pull rod (9) is rotatably supported thereon. A shaft (29) is provided on the opposite end of the tie rod (9), which connects the tie rod (9) to the steering lever (1〇). «The steering element 200925380 (10) is supported on the side (3) around a shaft (27) on. The shaft (27) is disposed between a shaft (29) for coupling to the pull rod (9) and a shaft (28) for coupling the steering member (1) to the piston rod (13). Furthermore, a snap-fit receptacle on the buffer housing (12) on the side facing away from the piston rod (13) is shown, so that the bumper housing (12) is rotatably mounted in the latching receptacle (30) The side portions (3) are connected and lateral forces are prevented from acting on the piston private (13). The design 'buffer (n) by means of the connection between the piston rod (丨3) and the shaft (28) can also be retrofitted. The hinge portion (2) is shown in Fig. 5A in the maximum open position, wherein the spring (18) first leg (19) leans against the shaft (22) and the second leg (2) leans against a steering roller (40). Upper (Fig. 4), the steering roller (4〇) is supported on the shaft (26). In the position of the chain portion (2) shown in Fig. 5B, the chain portion (2) is moved from the maximum open position to about 85. The opening angle. Here, the legs (19) of the spring (18) rest on the shaft (22) and the shaft (21) at the same time and appear to "transfer" from the shaft (22) to the shaft (21) at this position. From this maximum open position until the opening angle of 85. Up to now, no force is introduced through the spring (18). Because the spring (18) is further tightened. The opposing leg (20) rests more on the steering roller (40) on the shaft (26), so the spring (18) is at about 85. ~55. The range between (see Figure 5C) acts along the opening direction of the door or hinge • section (2), in other words, against the closing motion. In this hinge position, the effect of the damper is small because the angular position of the coupling element is such that the cantilever (25), the tie rod (9) and the steering lever (1 〇) on the guide lever (8) are preset. The open placement of the hinge portion is shown in Figure 5D with an angle of about 55. . When this opening angle is reached, the shafts (21) (22) and (24) form a line, and the spring (18) is in the most tight position, in which the leg squats 9) and (2 〇) are maximally opened. . If 200925380 passes this position, the day & chain 卩(2) continues to move in the closing direction, then the spring (18) I: Ϊ with friction, tolerance and other effects, the spring (18) can be traced, Therefore, the actual self-pull angle [the pre-stress to the closed position at this angle] is about 4 〇. .
口 t衝器（11)利用轉向元件（1〇)從約45。的開放角度起以 L踪的方式動作’其中，此處也由於有某些空轉行程、 ::誤差及其他影響，緩衝作用從30。〜40。間的角度時才 付月顯地可追踪。這點係由於緩衝器（11)在一開放範圍 。〔在開放角度3G°及開關位置之間〕在其整個形程路徑中60 z 乂上（且在7G%以上）移動之故’但在3G。外的開放範圍 只作很小的往復運動。 為了在出伸直位置後，將彈簧（18)的工作行程減少且 同時將沿關閉方向之作用到系統上的力量保持夠大，故將 腿（20)在轉向滾子向⑽）向後導進，換言之，在通過伸直位 置腿（2〇)利用轉向滾子（40)的支承件在轴（26)向逆時針方 向運動，而腿(19)利用支承件在轴(21)上同樣地逆時針方向 運動。因此腿（19)與（20)的相對運動很小，且彈簧（18)繞軸 (23)樞轉。如此可使該彈簧力在鉸鏈部（2)關閉時先上升然後 再下降。 圖5F顯示鉸鏈部（2)在約25。的開放位置。此處，彈簧 (18)將鉸鏈部（2)壓到閉位置，其中彈簧（18)經由腿（19)及（2〇) 繃緊。在此位置，當關閉時，轉向元件（1〇)繞轴（27)轉動且 使活塞桿（13)相對於緩衝器殼體（12)的工作行程比鉸鏈部（2) 先前的關閉運動的場合更大。 200925380 圖5G顯示鉸鏈在一過關閉角度，其中鉸鏈部（2)已移到 略超過關閉位置。在此過關閉位置中，彈簧〇 8)才不再經由 腿（19)及（20)施力量到鉸鏈部（2)。如此可確保在正常關閉角 度（〇°)時’鉸鏈部（2)利彈簧（18)施預應力到關閉位置。在關 閉位置時，活塞桿（13)進入該近乎最大移入的位置設在緩衝 器（12)中。 所用緩衝器可為一直線緩衝器，如在申請索 PCT/EP2007/051849所揭示者，也可用其他類型的直線緩衝 ^器。 圖6顯示緩衝路徑與鉸鏈（2)的開放角度的關係，藉著 將鉸鏈部（2)的關閉運動利用導引槓桿（8)、拉桿（9)、轉向元 件傳到緩衝器（11)，產生各種轉換比例，依開放角度預定， 它們確保最佳的關閉作用。如圖所示，在關閉運動時，一 直到開放角度45。為止，造成之行程不利緩衝器的總行程的 10%，因此活塞桿（13)只在緩衝器殼體（12)中稍微運動。產 Q 生的緩衝力量幾乎不能追踪，但在較大速度時，緩衝作用 已可作用，使一移動的傢倶剎止下來，而不會阻止安全的 關閉作用。此外在多直線緩衝器的場合，考 办 程，約毫米…毫米，特別是⑽到丄;轉： 此，在此結構可確保緩衝器大約在3〇。及45。間的角度範圍 才能有效到可檢出的程度。 在此，鉸鏈部設計成使緩衝器在關閉運動時，先產生 弱的緩衝力量，然後在恆定的關閉速度時上升。如此該緩 衝器的工作行程在開放角度25。與關閉位置之間的開放範 13 200925380 圍中近乎呈線性增加，而在較大開放角度時，緩衝器相對 於關閉運動幾乎不動。在此，轉換比例選設成使得在關閉 位置於開放角角度15。之間的開放範圍内，轉換比例為每度 的鉸鏈部開關運動造成的工作行程在〇 〇5mm〜〇 2mm間， 且宜 0.0 8mm 〜〇. 12mm。 在此，緩衝器的工作行程並非突然發生，而係呈曲線 狀上升，如此可確保不會有衝擊式的力量作用到緩衝器 上，而係使一傢倶門的動能先稍微緩衝。 該鉸鏈部（2)的枢轉運動轉換成緩衝行程旳轉換作用 (它係可變化者）係利用導引槓桿（8)、拉桿（9)及轉向槓桿 (10)上的懸臂（25)互相的角位置而達成。在大的開放角度 時，它們幾乎成一線，特別是懸臂（25)與拉桿^而當開放 角度小時，則互相幾乎成垂直，如此拉桿（9)將懸臂（25)的運 動很直接地傳送到轉向槓桿（10) ^ 在此鉸鏈部（2)與緩衝器（11}之間的轉換比例設成使得 在欽鍵部（2)的開放角度約80。〜11〇。時，在導引槓桿（8)與 拉桿（9)上的懸臂（25)的角位置近乎18〇。，因此導引槓桿的 轴（24)、用於支承拉桿（9)一端的轴（26)、以及用於將拉桿（9) 相反端支承在轉向槓桿（1〇)上的軸（29)大約在一線上。在 此，轉向槓桿（10)和拉桿（9)形成一銳角。當鉸鏈部（？）的開 放角度約2°〜40°時，在導引槓桿（8)及拉桿（9)上的懸臂（25) 的角位置大致形成90。的角度，特別是軸（24)(26)及（29)的連 線形成直角’其中轉向槓桿（10)同樣地與拉桿（9)形成一直 角，其中’如此該軸（26)(29)及（27)可互相經由二條互相約 200925380 呈直角交叉的線互相連接。 圖7中顯示彈簧（18)的關閉力量相對於開放角度的關 係。由圖可看出，彈簧（18)在一自拉範圍將鉸鏈部壓入關 閉位置，彈簧（18)的力量在15。〜25。的開放角度範圍為最大 值’然後遞減，直到彈簧（18)力量在50。〜75。之間達一最小 值為止。如此彈簧（18)的最大應力受限制。 ❹The mouth t-punch (11) utilizes a steering element (1 〇) from about 45. The opening angle is acted in the manner of an L track. Here, the buffering action is from 30 due to some idling strokes, :: errors and other effects. ~40. The angle between the two is only traceable. This is due to the fact that the buffer (11) is in an open range. [Between the open angle 3G° and the switch position] moves over 60 z ( (and above 7G%) in its entire path, but at 3G. The open range outside is only a small reciprocating motion. In order to reduce the working stroke of the spring (18) and to maintain the force acting on the system in the closing direction sufficiently large after the extended position, the leg (20) is guided backwards in the steering roller (10)) In other words, the support member of the steering roller (40) is moved counterclockwise in the shaft (26) by the straightening leg (2), and the leg (19) is similarly supported on the shaft (21) by the support member. Move counterclockwise. Therefore, the relative movement of the legs (19) and (20) is small, and the spring (18) pivots about the shaft (23). This allows the spring force to rise and then lower as the hinge portion (2) closes. Figure 5F shows the hinge portion (2) at about 25. Open location. Here, the spring (18) presses the hinge portion (2) to the closed position, wherein the spring (18) is tightened via the legs (19) and (2). In this position, when closed, the steering element (1〇) rotates about the shaft (27) and the working stroke of the piston rod (13) relative to the damper housing (12) is earlier than the hinge portion (2) The occasion is bigger. 200925380 Figure 5G shows the hinge at a closed angle where the hinge (2) has moved slightly past the closed position. In this over-closed position, the spring 〇 8) no longer applies force to the hinge (2) via the legs (19) and (20). This ensures that the hinge (2) spring (18) is prestressed to the closed position at the normal closing angle (〇°). In the closed position, the piston rod (13) is placed in the buffer (12) into the near maximum displacement position. The buffers used may be line buffers, as well as other types of linear buffers as disclosed in the application PCT/EP2007/051849. Figure 6 shows the relationship between the buffer path and the opening angle of the hinge (2), by means of the closing movement of the hinge portion (2) using the guiding lever (8), the tie rod (9), the steering element to the buffer (11), Various conversion ratios are generated, predetermined according to the opening angle, which ensure an optimal closing action. As shown, when the motion is turned off, it is until the opening angle 45. As a result, the stroke caused 10% of the total stroke of the bumper, so the piston rod (13) only moves slightly in the damper housing (12). The cushioning force produced by Q is hardly trackable, but at higher speeds, the cushioning action is already effective, so that a moving home can be stopped without stopping the safe closing. In addition, in the case of multi-linear buffers, the test procedure is about mm...mm, especially (10) to 丄; turn: This, in this structure, ensures that the buffer is about 3 〇. And 45. The range of angles between them can be valid to the extent that they can be detected. Here, the hinge portion is designed such that when the damper is closed, a weak cushioning force is first generated and then raised at a constant closing speed. Thus the working stroke of the buffer is at an opening angle 25. The open range between the closed position and the closed position 13 200925380 is almost linearly increased, while at larger open angles, the damper is almost motionless with respect to the closing motion. Here, the conversion ratio is selected such that it is at the open angle angle 15 in the closed position. Within the open range, the conversion ratio is the working stroke caused by the movement of the hinge part per degree between 〇 5mm~〇 2mm, and preferably 0.0 8mm ~ 〇. 12mm. Here, the working stroke of the damper does not occur suddenly, but rises in a curve, thus ensuring that no impact force is applied to the damper, but the kinetic energy of a slamming door is slightly buffered first. The pivoting movement of the hinge portion (2) is converted into a cushioning stroke/switching action (which is changeable) by means of the guiding lever (8), the tie rod (9) and the cantilever (25) on the steering lever (10). The angular position is reached. At large open angles, they are almost in line, especially the cantilever (25) and the tie rods. When the opening angle is small, they are almost perpendicular to each other, so that the pull rod (9) transmits the movement of the cantilever (25) directly to Steering lever (10) ^ The conversion ratio between the hinge portion (2) and the damper (11} is set such that the opening angle of the key portion (2) is about 80. ~11 〇. (8) The angular position of the cantilever (25) on the tie rod (9) is approximately 18 〇. Therefore, the shaft (24) of the guiding lever, the shaft (26) for supporting one end of the rod (9), and The shaft (29) supported on the steering lever (1) at the opposite end is approximately on a line. Here, the steering lever (10) and the tie rod (9) form an acute angle. When the hinge portion (?) is opened When the angle is about 2° to 40°, the angular position of the cantilever (25) on the guiding lever (8) and the tie rod (9) is substantially 90. The angle, especially the shafts (24) (26) and (29) The wires form a right angle 'where the steering lever (10) likewise forms a right angle with the tie rod (9), wherein 'the shafts (26) (29) and (27) are mutually The strips are connected to each other at a right angle to each other at 200925380. Figure 7 shows the closing force of the spring (18) relative to the angle of opening. As can be seen, the spring (18) presses the hinge into the self-pull range. Close the position, the force of the spring (18) is 15.15. The opening angle range is the maximum 'and then decremented until the spring (18) force is between 50 and ~75. A minimum between the two. So the spring (18 The maximum stress is limited.
G 圖8中顯示關閉運動速度相對於開放角度的關係，其 中有不同的起始關閉速度。各依關閉運動的速度而變，須 先作緩衝’以將門刹止減速β刹止區域約在4 5。〜15 °間， 起始速度越大，則越晚達到一低的終速度。當角度較小時， 由於變化的槓桿傳送，緩衝力量增加（見圖6)，如此可確 保：即使起始速度很高也能有效剎止下來。 關閉速度的走勢在關閉位置前不遠處（例如在〇。與至 少3°之間的範圍）大約保持線性相同。由於在動能剎止後， 該系統獨立地工作，因此彈簧（18)的力量和缓衝器決定關閉 速度。 在達到該直線終速度前，有小小的「小擺」，換言之， 降低到終關閉速度以下。這種下擺係由於個別之鉸鏈元件 的彈性的性質所致。當剎止作用較強時，這種作用受該運 動繃緊再彈回（如果忽略緩衝力量的話），由於所有元件 以及特別是柩接之連接部設計成強韌，因此造成报小的「反 彈」（Rebound)效果，而速度不會經過零值，因此鉸鏈部 (2)不會受回撞擊。 如圖8所不，約從45。起，自拉作用利用彈簧達成， 15 200925380 利用緩衝器剎止》 由於緩衝器施一股依速而定的力量逆著關閉方向’且 彈簧沿關閉方向施一股不受速度影響的力量’因此即使較 大的起始關閉速度也可有效地剎止下來，因此在關閉前在 最後的角度範圍，關閉速度與起速關閉速度無關。 【圖式簡單說明】 圖1係一本發明的鉸鏈在建入位置的側視圖； ® 圖2係圖1的鉸鏈的一立體圖； 圖3係圖1的较鏈的一側剖視圖； 圖4係圖1的鉸鏈的立體分解圖； 圖5 A〜5G係圖1的鉸鏈在不同開放位置時的數個侧剖 視圖， 圖6係緩衝路徑和鉸鏈開放角度的關係圖； 圖7係鉸鏈的彈箸的關閉力量和開放角度的關係圖； ❹ 目8係鉸鏈的彈簧的關閉迷度和開放角度的關係圖。 【主要元件符號說明】 (1) 錢鍵 (2) 鉸鍵部 (3) 側部 (4) 安裝板 (5) 傢俱體 (6) 門 16 200925380G Figure 8 shows the relationship between the closing motion speed and the opening angle, with different initial closing speeds. Each will change according to the speed of the closing motion, and must be buffered first to decelerate the door brake and the braking area is about 4 5 . Between ~15 °, the higher the starting speed, the later the lower the final speed. When the angle is small, the damping force increases due to the changing lever transmission (see Figure 6), which ensures that the starting speed is effectively stopped even if the starting speed is high. The trend of the closing speed is approximately the same in the vicinity of the closed position (for example, in the range between 〇 and at least 3°). Since the system works independently after the kinetic energy is stopped, the force of the spring (18) and the damper determine the closing speed. Before reaching the final speed of the line, there is a small "small pendulum", in other words, lowering below the final closing speed. This hem is due to the elastic nature of the individual hinge elements. When the braking effect is strong, this effect is stretched and rebounded by the movement (if the cushioning force is ignored), because all the components and especially the connecting part of the splicing are designed to be strong, thus causing a small rebound. (Rebound) effect, and the speed does not pass the zero value, so the hinge part (2) will not be hit back. As shown in Figure 8, it is about 45. Since the self-pull action is achieved by the spring, 15 200925380 utilizes the buffer brake. Because the buffer applies a force according to the speed against the closing direction 'and the spring applies a force that is not affected by the speed in the closing direction' Even a large initial closing speed can be effectively stopped, so in the final angular range before closing, the closing speed is independent of the starting speed. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a side view of a hinge of the present invention in a built-in position; Figure 2 is a perspective view of the hinge of Figure 1; Figure 3 is a side cross-sectional view of the chain of Figure 1; Figure 3 is a perspective view of the hinge of Figure 1 in different open positions, Figure 6 is a relationship between the buffer path and the hinge opening angle; Figure 7 is the hinge of the hinge The relationship between the closing force and the opening angle of the ; 目 8 series hinged spring closeness and open angle diagram. [Explanation of main component symbols] (1) Money key (2) Hinge key part (3) Side part (4) Mounting plate (5) Home specific (6) Door 16 200925380
(6，） 開放位置 ⑺ 攜帶槓桿 (8) 導引槓桿 (9) 拉桿 (10) 轉向元件 (11) 緩衝器 (12) 緩衝器殼體 (13) 活塞桿 (15) 卡合槓桿 (16)(17) 調整螺絲 (18) 彈簧 (19)(20) 腿 (21) 軸 (22) 轴 (23) 軸 (24) 轴 (25) 懸臂 (26) 轴 (27) 軸 (28) 轴 (29) 轴 (30) 卡合容納部 (40) 轉向滾子 17(6,) Open position (7) Carrying lever (8) Guide lever (9) Pull rod (10) Steering element (11) Buffer (12) Buffer housing (13) Piston rod (15) Engagement lever (16) (17) Adjustment screw (18) Spring (19) (20) Leg (21) Axis (22) Axis (23) Axis (24) Axis (25) Cantilever (26) Axis (27) Axis (28) Axis (29 ) Shaft (30) Engagement housing (40) Steering roller 17