200526883 九、發明說明： 【考务明戶斤屬軒々貝】 發明領域 本發明係有關於一種等速接合件，用以將例如於一機 5 動驅動系統之一傳動軸連接於另一傳動軸。 發明背景 迄今為止，機動驅動系統利用一等速接合件來連接一 傳動軸於另一傳動軸且將旋轉動力傳送至轉軸。近年來， 10已曰愈需要更輕質的等速接合件及更小的等速接合件。等 速接合件的機械強度、耐用性、負載性能等，是由等速接 合件的不同構件的基本尺寸來決定。對於小型等速接合件 需決定這些基本尺寸而能將機械強度、耐用性、負載性能 等維持在所要的程度。 15 日本公開專利公告第2001-330051號揭露一種固定的 等速萬向接合件，其具有一外接合構件、一内接合構件、 八轉矩傳送珠體，及一固持件。根據揭露的技術内文中用 以建立該萬向接合件的基本設定，該内接合構件的軸向寬 度(W)對一線段的長度(PCR)的比率Rw(=W/PCR)是選定於 20 84 ’其中該線段是連接界定於該内接合構件 上的〜、昝 、〜^槽之中心與該轉矩傳送珠體之中心。 曰本公開專利公告第2003-97590號揭露一種固定的等 速萬向接合件，其具有一外環、一内環、六轉矩傳送珠體， 座箱。並且揭露有假設一驅動軸具有直徑d，且該等轉 200526883 矩傳送珠體具有直徑DB及節距圓直徑（pitch circle diameter)DP ’則該直徑％對該直徑d的比率DB/d值是設定為 自0.65至0.72的範圍中，且該節距圓直徑仏對該直徑仏的比 率DP/DB值是設定為自3 4至3 8的範圍中。 5 然而，日本公開專利公告第2001-330051號中所揭露的 固定等速萬向接合件是以大量的部件所構成，其製造成本 高，且實際上生產困難。 曰本公開專利公告第2003-97590號中所揭露的固定等 速萬向接合件之尺寸上的設定可提供以增加該座箱（固持 10件）的機械強度，其是用以固持該等轉矩傳送珠體，而並 不提供減少固定等速萬向接合件的尺寸之功效。200526883 IX. Description of the invention: [Examination of the family member Xuanyuanbei] FIELD OF THE INVENTION The present invention relates to a constant velocity joint used to connect, for example, one drive shaft of a 5-motor drive system to another drive. axis. BACKGROUND OF THE INVENTION Hitherto, motorized drive systems have used a constant velocity joint to connect one drive shaft to another drive shaft and transmit rotational power to the shaft. In recent years, there has been an increasing demand for lighter constant velocity joints and smaller constant velocity joints. The mechanical strength, durability, and load performance of a constant velocity joint are determined by the basic dimensions of the different components of the constant velocity joint. For small constant velocity joints, these basic dimensions need to be determined to maintain the mechanical strength, durability, load performance, etc. to the required level. 15 Japanese Laid-Open Patent Publication No. 2001-330051 discloses a fixed constant velocity universal joint having an outer joint member, an inner joint member, eight torque transmitting beads, and a retaining member. According to the basic settings of the disclosed technical text used to establish the universal joint, the ratio of the axial width (W) of the inner joint member to the length of a line segment (PCR) Rw (= W / PCR) is selected at 20 84 'wherein the line segment connects the center of the ~, 昝, ~ ^ grooves defined on the inner joint member with the center of the torque transmitting bead. Japanese Patent Publication No. 2003-97590 discloses a fixed constant velocity universal joint, which includes an outer ring, an inner ring, six torque transmitting beads, and a seat box. And it is disclosed that assuming that a driving shaft has a diameter d, and the rotation 200526883 moment transmission beads have a diameter DB and a pitch circle diameter DP ', the ratio of the diameter% to the diameter d is DB / d value is It is set in the range from 0.65 to 0.72, and the ratio of the pitch circle diameter 仏 to the diameter DP DP / DB is set in the range from 3 4 to 38. 5 However, the fixed constant velocity universal joint disclosed in Japanese Laid-Open Patent Publication No. 2001-330051 is composed of a large number of parts, which has a high manufacturing cost and is actually difficult to produce. The setting of the size of the fixed constant velocity universal joint disclosed in this published patent publication No. 2003-97590 can be provided to increase the mechanical strength of the seat box (holding 10 pieces), which is used to hold such transfers. The moment transfer beads do not provide the effect of reducing the size of the fixed constant velocity universal joint.
發行刊物”萬向接合件及驅動軸設計手冊，Advancesin Engineering Series Ν〇· 7”（United States)，由 EPublication "Design Manual for Universal Joints and Drive Shafts, Advancesin Engineering Series No. 7" (United States), published by E
Cooney，Jr.編輯，第二版，The s〇dety 〇f 八加刪· 15 Engineers, Inc” 1991，pp. 145_149 (以下稱為，，—般文件，，） 揭露-種Rzeppa(球€式）等速接合件。此揭露的以啊等速 接合件具有一外環及—内環，兩者内具有珠槽。該外環的 珠槽與該内環的珠槽分別具有中心是位於接合桿（一驅動 轴及-從動軸）上，而分別位於自該接合件中心偏離相同 20 距離之位置處。 當Rzeppa等速接合件作動時，該外環的珠槽與該内環 的珠槽相對移動’以將被該座箱固持之六珠體定位於一等 速平面或-對等分角平面上，其位於該等接合桿之間所形 成的接合角之-半處，以使驅動接觸點恆保持在該等速平 200526883 面上而可提供等速傳送。 此一般文件詳細說明了珠槽漏斗角度，其是形成於正 父於該等外環珠槽（導槽）與該等珠體之間的負載側接觸 點之共同區’與正交於該等内環珠槽（導槽）與該等珠體 5之間的負載側接觸點之共同區之間所形成的角度，該角度 、、、勺在15度至π度之範圍中。此角度範圍容許Rzeppa等速接 合件形成順暢的角度形狀，以當通過〇度接合角度時不會遭 受到摩擦卡鎖現象。 此一般文件亦揭露了該等珠槽通常具有圓弧或橢圓弧 的橫剖面形狀（垂直於該等接合桿），且具有橢圓弧橫剖面 的該等珠槽之間的接觸角度是在自3〇度至45度的範圍中， 通常以45度為常用者。 曰本公開專利公告第2003-4062號及日本公開專利公 告第9-317784號顯示固定的等速萬向接合件，分別具有一 5外環、一内環、八珠體，及一座箱。該外環具有導槽（執 跡槽），具有各別的槽底部，其包含一曲線區，該曲線區的 中、疋自邊外環的内徑表面的中心以一方向偏離一距離 (F) ’且該内環具有導槽（執跡槽），具有各別的槽底部，其 包含一曲線區’該曲線區的中心亦是自該内環的外徑表面 的中心以一相反方向偏離該距離(F)。 於曰本公開專利公告第2003-4062號中揭示該偏離距 離（F)與一線段的長度（PCR)的比率R1 (=F/PCR)是選定於 ，其中該線段是連接該外環的導槽之中 〜或該内環的導槽之中心與該等珠體之中心。 200526883 曰本公開專利公告終317784號揭露該偏離距離(巧與 線&的長度(pCR)的比率R J (=F/PCR)是選定於〇 _ _ $(^121 ’其中該線段是連接該外環的導槽之中心或該内環 的¥槽之中心與該等珠體之中心，且該等導槽與該等珠體 5之間的接觸角度是設定為等於或小於37度的值。 、以該外環的珠槽或該内環的珠制界定之珠體執跡是 漏斗形狀，其自内端以軸向方向漸進地擴展向該外環的外 開口。因該外環的珠槽及該内環的珠槽是自該接合件中心 偏離相同距離，因此該外及内環的珠槽之深度於抽向方向 10 上並不一致。 ^ ^ 奴文件中所揭露之結構，由於該外環的珠槽及 j内㈣珠槽之深度彳M、，當該等速接合件作動於大的接 合角度或在高負載之下作動時，該等珠體的接觸橢圓部會 自”亥等珠槽凸出，而將該等珠體帶至該等珠槽的肩部（邊 15緣）上，因而使該等珠體破裂或使該等珠槽的肩部（邊緣） 削弱’導致該等速接合件的耐用性減低。此外，當該等速 接合件放置於高負載之下時，該等珠槽與該等珠體相互接 ㈣位置是接近於該内環的端部，該等珠體的接觸橢圓部 自A等珠槽凸出，因此會增加料珠體施加於 !〇接觸壓力。 f j 根據日本公開專利公告第細-4062號及日本公開專 利a «第9 317784號’其揭露該偏離距離(F)與—線段的長 =CR)的比率叫聰)是設定為一特定值，其中該線段 疋連接該外環的導槽之中心或該内環的導槽之中心與該等 200526883 珠體之中d該等麵的錄減少或料速接 =侦少，轉持朗持件的„，其為機 構件，則該㈣及㈣的導槽必齡h足的深度，且該 等導槽的肩部如上述易破裂或磨損。 10 7公開專利公告第職·32贿號揭露—種固定的 荨速萬向接合件’具有-外接合構件、1接合構件、八 轉矩傳送珠體’及一固持件。該外接合構件的珠槽（執跡 槽）及仙接合構件的珠槽（軌跡槽）分別具有中心，其 位於以軸向上相反的方向相同距離偏離之位置處。該等珠 體軌跡中的謂« (該外接合構件的珠槽的節距圓直徑 (pitch circle diameter)與該内接合構件的珠槽的節距圓直徑 之間的差距）是在自5至20//m的範圍中。 根據日本公開專利公告第2002-323061號，選定於自5 至20 μ m的範圍中之該PCD間隙可有效增加該固定等速萬向 15接合件的耐用性且可在高負載之下穩定其使用壽命之變異 性0 於日本公開專利公告第2002-323061號亦揭露該外接 合構件與該内接合構件之間的徑向間隙是在自2〇至1〇〇//111 的範圍中，且該固持件與該内接合構件之間的徑向間隙亦 2〇 是在自20至100//m的範圍中。 曰本公開專利公告第2002-323061號詳述一具有八轉 矩傳送珠體之固定式等速萬向接合件，及一具有六轉矩傳 送珠體之固定式等速萬向接合件，兩者具有不同的基本構 造，且其PCM間隙是設定為適用其對應構造之固定值。於 200526883 此公告案中未揭露或暗示有關於對於具有六轉矩傳送珠體 之固疋式等速萬向接合件之一些設定，例如該PCD間隙等。 於上述態樣的固定式等速萬向接合件中，如何相對於 朱體軌跡化成PCD(卽距圓直徑(pitch circle diameter))間隙 5疋重要的’其中珠體執跡是由界定於該外及内接合構件的 面向珠槽所界定。若該PCD間隙過小 ，則要將該等珠體組 裝於β等珠體軌跡會很困難，且施於該等珠體上的限制力 會太大而使該等珠體無法順 暢滾動。若該PCD間隙過大， 則將會產生撞擊噪音於該等珠體與該固持件的窗口之間， 1〇且將會增加該接合件本身的震動。 如第24圖所示，一種上述態樣的習用等速接合件具有 -外構件（外環）卜其具有數軸向界定於_球内徑表面& 之彎曲導槽1b，及一内構件（内環）2,其具有數軸向界定 於一球外徑表面2a之彎曲導槽2b，及於其内徑表面上之鍵 15槽仏。該外構件1的導槽lb及該内構件2的導槽2b構成珠體 滾動槽，其内設置有轉矩傳送珠體3。該等轉矩傳送珠體3 分別固持於一實質呈環形固持件4上所界定之固持窗口知 内。 在該外構件1及該内構件2相互呈一角度時該接合件的 機械強度是由該固持件4的機械強度來決定。因此，為增加 该接合件在該外構件1及該内構件2相互呈-角度時的機械 強度，需要增加該固持件4的機械強度。 该固持件4的機械強度可於增加該固持件4的橫剖面積 蚪增加。該固持件4的橫剖面積是可以下方法來增加，其一 200526883 方法（之後稱為，，坌 大小且增加 方法，，）是減少該固持件4的内球直徑 4的壁厚，[==外球直徑大小，以增加該固持件 去（之後稱為，，第二方法，，）是增加該固拉 件4當該接合件角度移位時會遭受要將珠體3外推的力之— 區域的橫㈣積’或再-方法（之後稱為，，第三方法”）是 增加定位於_持件4的窗口欄段4b之橫剖面積。 然而，根據第-及第二方法，該固持件4會變得很重且 具有較大的寬度，且該等珠體3易咬卡於該等導㈣内，而 10 簡短該外構件1的耐用性。因此，儘可能使較寬的固持件4 適宜地不組裝於該外構件1内。 根據第二方法，若該等攔段扑被延長以減少該等固持 窗口4a的開放面積時，該等珠體3易於接觸到該等攔段仆且 無法恰好地組裝於該固持件4内。若該等固持窗口如過小， 則該内構件2無法輕易地組裝於該固持件4内。 曰本公開專利公告第2002-13544號揭露一種等速萬向 接合件，具有一固持件，其具有圓形角隅4c於固持窗口或 袋口 4a上，其中該等圓形角隅4c的曲率半徑r與該等珠體3 的直徑D之比率R/D是設定於0.22SR/D的範圍中。 根據日本公開專利公告第2002-13544號，於該固持件 2〇 的袋口4a上該等圓形角隅4c的曲率半徑R與該等珠體3的直 徑D之比率R/D是設定成可增加該固持件的耐用性與機械 強度為目的。然而，上述比率的設定並不足有效地增加該 固持件的機械強度。 I：發明内容3 200526883 發明概要 本發明的一般目的在於提供一種等速接合件，其可設 計用於不同尺寸的設定，可適用於小型接合件尺寸而可維 持不同特性，亦即機械強度、耐用性、負载能力等，在適 5 當程度上。 本發明的主要目的在於提供一種等速接合件，其中因 與珠體接觸而作用於導槽上的表面壓力可減低以增加其耐 用性。 本發明的另一目的在於提供一種等速接合件，其中可 · 10防止導槽的肩部破裂或磨損以增加其耐用性。 本發明的又一目的在於提供一種等速接合件，具有六 珠體，其中一固持件的固持窗口的不同間隙及偏離距離可 設定為最佳值以減低表面壓力，如此可直接有益於該等速 接合件的使用壽命，其作用於外環導槽與該等珠體之間及 15内環導槽與該等珠體之間，用以增加其耐用性。 本發明的再一目的在於提供一種等速接合件，其包含 具有所要求機械強度之一固持件，且其可更為有效地組裝。 鲁 本發明上述及其他目的、特徵及優點將可由以下詳細 説明配合參考圖式，對本發明的較佳實施例以舉例說明的 20方式顯示，來得以瞭解。 · 圖式簡單說明 t 第1圖是根據本發明一實施例的等速接合件，沿轴向方 向上之縱向橫剖圖； 弟2圖是第1圖所示等速接合件之放大斷面縱向橫剖 12 200526883 圖； 第3圖是等速接合件由第1圖的箭頭X所指，以軸向方向 視之且部分剖視之側視圖； 第4圖是第1圖所示等速接合件，沿垂直於軸向方向的 5 方向之放大斷面橫向橫剖圖； 第5圖是顯示根據實施例的等速接合件的一第一導槽 之深度之放大斷面縱向橫剖圖； 第6圖是顯示根據比較例的等速接合件的一第一導槽 之深度之放大斷面縱向橫剖圖； 10 第7圖是顯示一第二導槽與一珠體之間的耐用性與接 觸角度的相互關係之圖表； 第8A圖是顯示由一外杯體所界定的一第一導槽的節距 圓直徑(pitch circle diameter)之外PCD之縱向橫剖圖； 第8B圖是顯示由一内環體所界定的一第二導槽的節距 15 圓直徑(pitch circle diameter)之内PCD之縱向橫剖圖； 第9A圖是顯示一外杯體内球表面直徑之縱向橫剖圖， 其是該外杯體的内徑表面之直徑； 第9B圖是顯示一内環體外球表面直徑之縱向橫剖圖， 其是該内環體的外徑表面之直徑； 20 第9C圖是顯示一固持件外球表面直徑，其是一固持件 的外表面之直徑，及一固持件内球表面直徑，其是該固持 件的内表面之直徑之縱向橫剖圖； 第10圖是顯示該固持件的固持窗口的橫向中心自該固 持件的球内及外表面的中心偏離之距離之縱向橫剖圖； 13 200526883 第11圖是顯示該PCD間隙與耐用性之間關係之圖表； 第12圖是顯示該球面間隙與耐用性之間關係之圖表； 第13圖是顯示該窗口偏離與耐用性之間關係之圖表； 第14圖是等速接合件由第1圖的箭頭X所指，以軸向方 5 向視之且部分剖視之側視圖； 第15圖是等速接合件的放大斷面縱向橫剖圖，其顯示 一桿鋸齒區直徑（D)、一外/内PCD(Dp)、一外杯體外徑 (Do)，及一珠體直徑(Db); 第16圖是顯示一特徵線性曲線L之圖表，其表示一内環 10 體鋸齒區内徑表面與該外/内PCD(Dp)之間的關係； 第17圖是顯示一特徵線性曲線Μ之圖表，其表示該外/ 内PCD(Dp)與該外杯體的外徑之間的關係； 第18圖是顯示一特徵線性曲線N之圖表，其表示該外/ 内PCD(Dp)與該内環體的環體寬度之間的關係； 15 第19圖是顯示一特徵線性曲線Q之圖表，其表示該外/ 内PCD(Dp)與該珠體直徑(Db)之間的關係； 第2 0圖是根據本發明另一實施例的等速接合件沿軸向 方向之縱向橫剖圖； 第21圖是第20圖所示等速接合件的固持件與珠體之分 20 解透視圖； 第22圖是顯示第21圖所示不同尺寸的固持件及珠體之 環周側視圖， 第2 3圖是根據本發明又一實施例的等速接合件沿軸向 方向之縱向橫剖圖；及 14 200526883 第24圖是裔用等速接合件之分解透視圖。 【實施令式】 較佳實施例之詳細說明 5 10 15 20 第1圖是顯示根據本發明-實施例的等速接合件1〇β以 下詳細說明中，縱向横剖面是指沿一第—桿12及—第二桿 18的轴向方向的橫剖面，橫向剖面是指與軸向方向垂直的 橫剖面。 '亥等速接合件10基本上是以-底圓柱外杯體16 (外構 件）m於一第—桿12_端且具有一開口 14以遠離該 第一桿12開放’以及―内構件22固定於-第二桿18-端且 容置於該外杯體16内所構成。 如第1及3圖所示，該外杯體16於其内壁上具有一球面 内徑表面24。該内徑表面24具有六個第一導槽26a至26f以 軸向方向延伸且以60度間距繞其軸心呈角度間隔。 如第2圖所示，該等第一導槽26a至26f，其分別具有一 彎曲軸向的縱向橫剖面，具有共同曲率中心於一點Η上。該 點Η是位在以軸向方向朝向該外杯體16的開口 14，自該球面 内徑表面24中心Κ偏離一距離Τ1的位置（其中連接珠體28 的中心0[球心面]之一假想面與一接合軸27交錯）。 如第4圖所示，界定於該外杯體16内之各第一導槽26a 至26f具有橫向橫剖圖，其具有單一凹弧形狀，其曲率中心 A是位於一垂直線L上，該垂直線L延伸通過該珠體28的中 心0。各第一導槽26a至26f被保持與該珠體28的外表面接觸 於第4圖中單一點B上。 15 200526883 當負載實際施加於上以傳送一旋轉轉矩時，該珠體28 的外表面及各第一導槽26a至26f被保持相互呈面與面接 觸，而不是點對點的接觸。 該内徑表面24是於橫向的橫剖面上連續地形成於各第 5 一導槽26a至26f的兩側上。各第一導槽26a至26f與該内徑表 面24的邊緣之間的邊界具有一對第一肩部30a,30b，其是呈 斜角的。 該珠體28相對於該外杯體16的各第一導槽26a至26f之 接觸角度於該垂直線L上是設定為零。各第一導槽26a至26f 10 於橫向橫剖面的半徑Μ與該珠體28的直徑N之比率（M/N)是 設定為自〇·51至0.55的範圍中之值（見第4圖）。 該内構件22具有一内環34，其具有數第二導槽32a至 32f界定於其外環周表面内且以環周間隔與個別第一導槽 26a至26f對齊，數珠體28 (本實施例為六個）可滾動地設 15 置於界定在該外杯體16的内壁面内之第一導槽26a至26f與 界定在該内環體34的外徑表面35 (見第4圖）内之第二導槽 32a至32f之間，用以進行傳送旋轉轉矩之功能，以及一固 持件38，其具有數固持窗口 36界定於其上且於環周方向上 間隔用以分別固持該等珠體28於内，且介於該外杯體16與 20 該内環體34之間。 5亥内環體34是藉由界定於内之一中心孔鍵接於該第二 才干18的一端，或者藉由一環狀鎖固構件40安裝於該第二桿 18上所界定的環槽内一體固定於該第二桿18的一端。該等 第一 至32f ’其設置與該外杯體16的個別第一導槽 16 200526883 26a至26f對齊且於環周方向上以等角度間距間隔，是界定 於該内環體34的外徑表面35上。 如第2圖所示，該等第二導槽32&至32£，其各具有彎曲 軸縱向橫剖面，具有共同的曲率中心於一點尺上。該點尺是 5位於以軸向方向遠離該外杯體16的開口 14,自該球面内徑 表面24中心K偏離一距離T2的位置（其中連接珠體28的中 心Ο[球心面]之一假想面與該接合轴27交錯）。 該等第一導槽26a至26f的曲率中心所在之該點11及該 等第二導槽32a至32f的曲率中心所在之該點R是分別位在 10於軸向方向上以相反方向自該球面内徑表面24中心K偏離 之位置上（其中该珠體球心面與該接合軸27交錯），其偏離 距離相等（T1=T2)。該點Η是位於比該球面内徑表面24中心 Κ較接近該開口 14，且該點R是位於較靠近該外杯體16的一 内端46。該點Η的曲率半徑與該點尺的曲率半徑是延伸而相 15 互交錯（見第2圖）。 假設該等珠體28具有直徑Ν且該等第一導槽26a至26f 及該等第二導槽32a至32f的曲率中心（該點H，R)是自中心 K軸向地偏離一距離T，則該等珠體28的直徑τ與該偏離距 離Τ宜設定成距離Τ與直徑Ν之比率V(=T/N)須滿足以下： 20 0·12$ν$0·14 〇 如第4圖所示，各第二導槽仏至似具有橢圓狀彎曲形 狀之橫向橫剖面，其具有一對中心C，D，兩者相互水平地間 隔一預定距離。各第二導槽32a至32f被保持與該珠體烈的 外表面接觸於第4圖所示之二點E，F上。當一負載實際地施 17 200526883 於其上以傳达一旋轉轉矩時，該珠體28的外表面及各第二 V槽32a至32f被保持相互呈面與面接觸，而不是點對點的 接觸。 4外控表面35是於橫向的橫剖面上連續地形成於各第 一‘槽32a至32f的兩側上。各第二導槽32a至32f與該外徑表 面35的邊緣之間的邊界具有一對第二肩部42&，42^，其是呈 斜角的。 该珠體28是被保持與各第二導槽32&至32{在該垂直線 L各側上之一接觸角度α接觸。若該接觸角度以是設定為自13 1〇度至22度範圍中的角度，如第7圖所示，則會增加該等速接 合件的耐用性。若該接觸角度01是設定為自15度至2〇度範圍 中的角度，則可進一步增加該等速接合件的耐用性。各第 二導槽32a至32f於橫向的橫剖面上之半徑p，Q與該珠體28直 控N之比率(P/N，Q/N)可設定為自〇·5ΐ至〇·55範圍中之值（見 U 第4圖）。 舉例來說’該等珠體28是以鋼材製成，且可滾動地設 置於s亥外杯體16的各第一導槽26a至26f及該内環體34的第 一導槽32a至32f内。該等珠體28經由該内環體34及該外杯 體16傳送該第二桿18的旋轉轉矩至該第一桿12，且沿該等 2〇第一導槽26a至26f及遠專第一導槽32a至32f滾動於其内，夢 以使該第二桿18 (該内環體34)及該第一桿12 (該外杯體 16)可相互以角度移位。旋轉轉矩可以兩者其中一方向被 傳送於該第一桿12與該第二桿18之間。 如第8A及8B圖所示，若該等第一導槽26a至26f的節距 18 200526883 圓直徑(pitch circle diameter)，於該六珠體28被保持與該等 第一導槽26a至26f點對點接觸時是以外pcd表示，且該等第 一導槽32a至32f的卽距圓直徑（pitch circle diameter)，於該 六珠體28被保持與該等第二導槽32a至32f點對點接觸時是 5以内PCD表示，則PCD間距是建立為該外pcd與該内PCD 之間的差距（外PCD-内PCD)。 如第9A至9C圖所示，一球面間距是建立為外杯體内球 表面直徑與固持件外球表面直徑之差距，及固持件内球表 面直徑與内環體外球表面直徑之差距的總和，該外杯體内 10 球表面直徑是該外杯體16的内徑表面24的直徑，該固持件 外球表面直徑是該固持件38的外徑表面的直徑，該固持件 内球表面直徑是該固持件38的内徑表面的直徑，該内環體 外球表面直徑是該内環體34的外徑表面35的直徑。 亦即，該球面間距是由以下所定：球面間距=丨（該外杯 15 體内球表面直徑）_(該固持件外球表面直經）} + {(該固持件 内球表面直徑)-(該内環體外球表面直徑）}。 如第10圖所示，該固持件38的固持窗口 36之橫向中心 (在此”橫向”是指該固持件38的軸向方向）是自該固持件 38的球外及内表面38a，38b的中心於該固持件38的軸向方向 20 上偏離一預定距離。 根據本實施例该專速接合件10基本上以上述說明架構 而成。接著，該等速接合件10的作動情形及優點將詳細說 明於下。 當該第二桿18繞其本身軸心旋轉時，其旋轉轉矩被自 19 200526883 該内環體珠體28傳送至該外杯體16，而造成該 弟一 :!:2:如：第二桿18相同方向及以相同速率旋轉。 5 10 15 20 *若該第-桿12及該第二桿18相互相對角度移位時，該 等珠體28滚動於轉第—導槽2如至撕及該等第二導槽似 至32f之間以傾斜該固持_至—特定角度，而使該第一桿 12及第418可相互角度移動。 曰此時’ _於_持件38的固持窗口36内之該六珠體 =位於該第—桿12與第二桿18之間的-等速平面或一對 等:角平面上’以保持驅動接觸點恆於該等速平面上以提 等速傳動卩此方^，該第-桿I2及該第二桿18可以等 速旋轉且可相互適t地角度移位。 根據此貫施例，該等珠體28的直徑N與該等第一導槽 1 以及”亥等第一導槽32a至32f的曲率中心（點h，R)自 亥中、κ軸向偏離的距離之比率v(=t/n)是設定滿足以下 表示：〇.120魏14 (見第2圖）。 若”亥直扭Ν與該偏離距離Τ的比率是小於0.12時，則形 成於遠等第一導槽26a至2以與該等第二導槽32&至32£之間 的漏斗角度會減至最小，如此會使於該等速接合件1〇不旋 轉時該等珠體28易被卡住，且亦導致該等速接合件1〇組裝 時的效率變低。 反之，若該直徑N與該偏離距離T的比率是超過0.14 時’則由於該等第一導槽26a至26f及該等第二導槽32a至32f 形成彳艮深，該等珠體28容易移動於該等第一導槽26a至26f 的邊緣處之該等第一肩部30a，30b上，以及移動於該等第二 20 200526883 導槽32a至32f的邊緣處之該等第二肩部42a，42b上或造成破 裂及磨損。 因此藉設定該直徑N與該偏離距離τ的比率v滿足0·12 $V$0.14,可有效地防止該等珠體28移動於該等第一導槽 5 26a至26f的邊緣處之該等第一肩部3〇a,3〇b&該等第二導槽 32a至32f的邊緣處之該等第二肩部42心4213上或造成破裂及 磨才貝’精以使該等速接合件1 〇更為耐用。 第5圖顯示根據實施例等速接合件1〇的放大斷面縱向 橫剖圖。如第5圖所示，該直徑n與該偏離距離T之比率V是 10設定可滿足〇·12$ν$0·14的範圍，藉以可使偏離距離T1變 小。第6圖顯示根據比較例等速接合件1〇〇的放大斷面縱向 橫剖圖。如第6圖所示，該等速接合件1〇〇的一偏離距離Τ2 是大於該等速接合件10的偏離距離T1 (T1CT2)。 該等速接合件10，100之間對於該等第一導槽26a至26f 15 的深度之比較，其在自一直線S (以垂直於該接合軸27延伸 且通過該等珠體28的中心）傾斜約15度的區域上，表示如 下，根據本實施例該等速接合件10的第一導槽26a至26f之 深度DPI，是大於根據比較例該等速接合件1〇〇的第一導槽 26a至26f之深度DP2 (DP1>DP2)。因此，根據本實施例的 20 等速接合件10，可有效地防止該等珠體28移動於該等第一 導槽26a至26f的邊緣處之該等第一肩部30a，30b及該等第二 導槽32a至32f的邊緣處之該等第二肩部42a，42b上或造成破 裂及磨損。 此外，根據本發明，界定於該外杯體16内之各第一導 21 200526883 槽26a至26f具有壬弧形的橫向橫剖面，其被保持與該等珠 體28接觸於單—點處，且各第二導槽32a至32f具有橢圓弧 形橫向橫剖面’其被保持與該等珠體28接觸於二點處。以 此配置等珠體28接觸施予該等第―導槽施至施 5及°亥等第一‘槽32&至32[之表面壓力會小於習用的配置 者，用以增加耐用性。 根據此實施例，該等導槽半徑(M，p，Q)與該等珠體“的 直徑N在該等第—導槽施至26f及該等第二導槽❿至似 的杈向杈剖面上之各比率（M/N，p/N，Q/N)是設定為自〇 51至 10 0·55範圍中之值，該等珠體28相對於各第一導槽26a至26f 的接觸角度於該垂直線L上是設定為零，且該等珠體28保持 與各第二導槽32a至32f接觸之接觸角度〇1是設定為自13度 至22度範圍中之值，藉以降低表面壓力以增加耐用性。 將該等導槽半徑(M，P，Q)與該等珠體28的直徑n在該等 15第一導槽26&至2沉及該等第二導槽32a至32f的橫向橫剖面 上之各比率（M/N，P/N，Q/N.)設定為自〇.51至〇 55範圍中之值 的理由在於，若該比率小於〇·51，則由於該等導槽半徑 (M，P，Q)與該等珠體28的直徑Ν相互太近，該等珠體28會幾 乎是與該等導槽完全接觸且不易於滾動，因而導致耐用性 20不佳，並且若該比率大於〇·55，則由於該等珠體28的接觸 橢圓會減小，因此會增加接觸表面壓力，因而導致耐用性 不佳。 該等珠體28的直徑(N)與該等第一導槽26&至26€及該等 第二導槽32a至32f的曲率中心（點h，r)自該中心K軸向偏離 22 200526883 的距離τ之比率V(T/N)、該等珠體28保持與各第二導槽似 至3M接觸之接觸角度α，及該等導槽半徑(m,p,q)與該等珠 體28的直徑N在該等第-導槽施至施及該等第二導槽似 至32f的検向橫剖面上之比率是由重覆模擬及實驗所產生 5 之最佳值所決定。 將該等珠體28保持與各第二導槽32&至3^接觸之接觸 角度α设疋為自13度至22度範圍中之值的理由在於，若該接 觸角度α小於13度，則在該等珠體28上的負載會增加，因此 增加表面壓力，因而導致耐用性不佳，並且若該接觸角度α 10大於22度，則該等第二導槽32a至32f的邊緣（該等第二肩 部42a，42b)及該等珠體28的接觸位置會相互靠近，且該等 珠體的接觸橢圓會自該等導槽凸伸出，因而增加表面壓 力，因此降低耐用性。 此外’根據本實施例，該PCD間距，其建立為該外pcd 15 與該内PCD之間的差距（外PCD_内PCD)(見第8八及犯 圖），須設定為自0至ΙΟΟμηι範圍之值，或宜為自〇至㈧叫範 圍。該PCD間距須為自〇至i〇〇pm範圍之值是由於若該pcD 間距小於〇μιη，則該等珠體28無法有效地組裝定位且無法 順暢地滾動，因而導致耐用性不佳，且若該PCD間距超過 20 ΙΟΟμπι，則該等珠體28保持與該等第一及第二導槽接觸之 接觸橢圓會自該等導槽邊緣處的肩部凸伸出，而增加表面 壓力且造成肩部破裂，因而造成耐用性減低。若該PCD間 距設定於自〇至60μιη範圍中，則可達到甚佳的耐用性，此 藉實驗結果可表示，如第11圖所示。 23 200526883 此外’根據本實施例，如第9A至9C圖所示，該球面間 距’其定義為··{(外杯體内球表面直徑）-(固持件外球表面 直徑）} + {(固持件内球表面直徑Μ内環體外球表面直徑）}， 須e又疋為於自5〇至2〇〇μιη範圍令之值，或宜為自5〇至ΐ5〇μη! 5中。若該球面間距小於50μιη，則將因該外杯體16的内表面 與該固持件38的外表面38a之間缺乏潤滑而造成卡住，且該 内環體34的外表面與該固持件38的内表面38b之間亦同，如 此會對該等速接合件1〇的機械性造成不良影響。若該球面 間距大於200μιη，則該外杯體16及該内環體34，與該固持 10件38之間將產生撞擊噪音，而對該等速接合件1〇的商業價 值造成不良影響。若該球面間距設定為自5〇至15〇)11111範圍 中，則可達到甚佳的耐用性，此藉實驗結果可表示，如第 12圖所示。 根據本實施例，如第10圖所示，該固持件38的固持窗 15 口的橫向中心（在此，，橫向，，是指該固持件38的軸向方向） 疋自4固持件38的球外及内表面38a，38b的中心於該固持件 38的軸向方向上偏離，其偏離距離是自2〇至1〇%爪的範圍 中。若該距離，即該固持件38的固持窗口的橫向中心自該 球外及内表面38a，38b的中心偏離的距離，小於2〇μιη，則施 2〇加於該等珠體28上的限制力將不足以維持一等速傳輸性 能。若該距離，即該固持件38的固持窗口的橫向中心自該 球外及内表面38a，38b的中心偏離的距離，大於1〇〇μηι，則 ^加於違等珠體28上的限制力會過大而使該等珠體28不能 1員暢废動’因而導致而才用性不佳。若該距離，即該固持件 24 200526883 38的固持窗口的橫向中心自該球外及内表面38a，38b的中心 偏離的距離，設定在40至80μιη範圍中，則可達到甚佳的耐 用性，此藉實驗結果可表示，如第13圖所示。 因此，即使當該具有六珠體28的等速接合件10處於高 5 負載下時，仍可防止該等珠體28的接觸橢圓自該等導槽凸 伸出，因此可提高耐用性。 該等速接合件10的不同尺寸之設定將詳述於下。 假設如第8Α及8Β圖所示該外PCD及該内PCD相等（外 PCD=内PCD)，亦即，該外PCD與該内PCD之間的差距為 10 零。以下的該外PCD及該内PCD二者共同以”外/内PCD”來 表示。 一内環體鋸齒區内徑表面39的直徑（D)是設定為任何 要求值，且該外/内PCD表示該内環體34最小壁厚的尺寸是 基於該内環體鋸齒區内徑表面39的直徑(D)所建立（見第14 15 及15圖）。 該内環體鋸齒區内徑表面39的直徑（D)是表示該内環 體鋸齒區内徑表面39中的一凹谷底部與該内環體鋸齒區内 徑表面39橫過該内環體34的孔中心之一直徑相對凹谷底部 (見第15圖）之間的尺寸（最大直徑）。藉該内環體34的最 20 大壁厚可維持預定接合強度。該外/内PCD的值是從一特徵 線性曲線L來決定，該特徵線性曲線L是表示該内環體鋸齒 區内徑表面39的直徑與該外/内PCD之間的關係，如第16圖 所示。 若該内環體鋸齒區内徑表面39的直徑是以D表示且該 25 200526883 外/内PCD是以Dp表示（見第14及15圖），則該外/内PCD(Dp) 與該内環體鋸齒區内徑表面39的直徑（D)的尺寸比率（Dp/D) 宜須設定為1.9S(Dp/D)$2.2的範圍中之值。 若該尺寸比率（Dp/D)小於1.9，則該内環體34的壁厚會 5 過小，而導致其機械強度降低。若該尺寸比率（Dp/D)超過 2.2，則該等速接合件10的尺寸無法減小。 如第17圖所示，該外杯體16的外徑是基於一特徵線性 曲線Μ所建立，該特徵線性曲線Μ是表示該外/内PCD與該 外杯體16的杯體截面的外徑之間的關係。若該外杯體16的 10 外徑是以Do表示，則該外杯體16的外徑Do與該外/内 PCD(Dp)之尺寸比率（Do/Dp)宜須設定為1 ·4 $ (Do/Dp) $ 1 ·8 的範圍中之值。 若該尺寸比率（Do/Dp)小於1.4,則該外杯體16的壁厚會 過小，而導致其機械強度降低。若該尺寸比率(Do/Dp)超過 15 1.8，則該外杯體16的外徑會增加，使該等速接合件10的尺 寸無法減小。 如第18圖所示，該内環體34的環寬是基於一特徵線性 曲線N所建立，該特徵線性曲線N是表示該外/内P C D與該内 環體34沿該第二桿18軸心的環寬之間關係。若該内環體34 20 的環寬是以W表示，則該内環體34的環寬W與該外/内 PCD(Dp)之尺寸比率（W/Dp)宜須設定為〇·38 $ (W/Dp) $ 0.42的範圍中之值。 如第19圖所示，該等珠體28的直徑是基於一特徵線性 曲線Q所建立，該特徵線性曲線Q是表示該外/内PCD(Dp) 26 200526883 與該等珠體28直徑之間關係。若該等珠體28的直徑是&Db 表示，如第14及15圖所示，則該等珠體28的直徑(Db)與該 外/内PCD(DP)之尺寸比率（Db/Dp)宜須設定為0.2 $ (Db/Dp) S0.5的範圍中之值。 5 若該尺寸比率(Db/Dp)小於0.2，則該等珠體28的直徑會 過小，導致其機械強度降低。若該尺寸比率(pb/Dp)超過 〇_5 ’則該等珠體28會太大而使該外杯體16的壁厚相當小， 因而導致其機械強度降低。用以固持該等珠體28之該固持 件38的球外及内表面38\3813的直徑之值是根據其佈置來設 10 定。 以此方式，該等速接合件1〇的不同尺寸可建立具有小 接合尺寸，而可維持不同特性，亦即機械強度、耐用性、 負載能力等，在要求程度上。 第20圖顯示根據本發明另一實施例之等速接合件 15 uo。該等速接合件no中與第1圖所顯示該等速接合件10相 同的部件是以相同標號來表示，且以下將不再詳細說明。 如第20圖所示，該等速接合件110具有一底部圓柱外構 件16,其與一第一桿12的一端一體接合且其一端界定有一 開口 14以遠離該第-桿12呈開放，_内環體3相定於一第 20二桿端，其可相對於該第—桿⑽度移位且容置於 該外構件16内，數珠體28介於該外構件16與該内環體似 間，用以傳送其間的轉矩，及一固持件124，其固持該等珠 體28且設置於該外構件16與該内環體％之間。 該外構件16具有一内徑表面U6a，其具有六第一導槽 27 200526883 26a至26f以箭頭X所示的轴向方向延伸且繞其軸呈角度間 隔。各第一導槽26a至26f具有一平直區51自其彎曲區以箭 頭X所示的縱向方向一體延伸。 該内環體34具有一外環周面i2〇a，其具有與該等第一 5導槽26a至26f相同數目的第二導槽323至32[，該等第二導槽 32a至32f以軸向方向延伸。各第二導槽32&至32£具有一平直 區S2自其幫曲區以箭頭X所示的縱向方向一體延伸。該等平 直區S1，S2是位於以箭頭X所示的方向相對。 該内環體34具有一鍵孔130界定於其中心。該鍵孔13〇 10被保持與違第一桿18的一端上之一鍵桿132°齒合，以致於該 第二桿18及該内環體34相互耦接。 舉例來說’該等珠體28是以鋼材所製成，且可滾動地 设置於该外構件16的個別第一導槽26a至26f及該内環體34 的個別第二導槽32a至32f内。該等珠體28將該第二桿18的 15旋轉轉矩經由該内環體34及該外構件16傳送至該第一桿 12，且於該等第一導槽263至2以及該第二導槽32&至3%内並 沿其滾動，藉以使該第二桿18 (内環體34)及該第一桿12 (外構件16)可相互角度移位。旋轉轉矩可於該第一桿12 與該第二桿18之間以其中一方向傳送。 20 如第21及22圖所示，該固持件124是實質上呈環形且具 有例如六固持窗口 134用以固持個別珠體28於其内。該等固 持窗口 134是於環周方向上以相等角度間距呈角度間隔。 如第22圖所示，各固持窗口 134具有一開口長度WLk 忒固持件124的環周方向上。該開口長度WL與該等珠體28 28 200526883 的直徑D之比率(WL/D)是設定為於1 ·3〇 $ WL/D S 1.42範圍 中的值。各固持窗口 134具有角隅134a，其各具有一曲率半 徑R。該曲率半徑R與該等珠體28的直徑D之比率(R/D)是設 定為於0.23‘R/D$〇.45範圍中的值。 5 相對於各該等固持窗口 134，該開口長度WL與該等珠 體28的直徑D之比率(WL/D)是設定為WL/D$ 1.42範圍中的 值。因此’該固持件124可有效地維持該等固持窗口 134之 間的欄段136之環周長度。如此即無須增加該固持件丨24的 壁厚，且可增加該等欄段136的橫剖面積。 · 10 因此，5亥固持件124的機械強度可增加而無須減少其球 内徑表面的直徑，因而增加其球外徑表面的直徑，且增加 其於軸向方向上的寬度。 對該等速接合件110，各該等固持窗口 134的開口長度 WL與該等珠體28的直徑D之比率（WL/D)是設定為1.3〇$ 15 WL/D範圍中的值。因此，可增加該等固持窗口 134的開口 面積，而使該等珠體28可輕易地組裝且亦使該内環體34可 輕易地組裝。如此，該等速接合件110可具有簡單的構造且 ® 可輕易地組裝。 各該等固持窗口 134的角隅134a之曲率半徑r與該等珠 20體28的直徑D之比率（R/D)是設定為於〇.23$R/D範圍中的 值。此比率设疋可有效減少該等固持窗口 134之間該等棚段 136上之最大主要應力負載，因而用以增加該固持件124的 機械強度。 该比率（R/D)亦設定為於R/D € 0.45範圍中的值，以防 29 200526883 止該等珠體28及該内環體34因該等固持窗口 i34的角隅 134a之曲率半徑過大而造成組裝失敗。 各該等第-導槽施至26f具有―平直區仙其縱向方 向延伸，且各該等第二導槽瓜至32£具有—平直區幻以其 5縱向方向延伸。此平直區S1S2使該等速接合件則可具有 較大的最大接合角度。 ^ 第23圖顯示根據本發明又一實施例的等速接合件 150。該等速接合件150中與第2〇圖所顯示該等速接合件 相同的部件是以相同標號來表示，且以下將不再料說明。 10 如第23圖所示，該等速接合件150具有一外構件16及一 内環體34a。該外構件16具有一内徑表面116&，其具有數第 一導槽26a至26f以軸向方向延伸。該内環體3如具有一外環 周面120a，其具有與該等第一導槽26&至26£相同數目的第二 導槽32a至32f’该等第二導槽32a至32f以軸向方向延伸。 15 各該專第一導槽至26f及第二導槽32a至32f僅有一 彎曲區以其縱向方向延伸，而與前述實施例的等速接合件 110不同。該等速接合件150提供與該等速接合件11〇相同的 優點。 儘管已洋細說明本發明的特定較佳實施例，吾人需瞭 20解在此可作不同變化及變更而不脫離以下申請專利範圍的 範圍。 【圖式簡單說明】 第1圖是根據本發明一實施例的等速接合件，沿軸向方 向上之縱向橫剖圖； 30 200526883 第2圖是第1圖所示等速接合件之放大斷面縱向橫剖 圖， 第3圖是等速接合件由第1圖的箭頭X所指，以軸向方向 視之且部分剖視之側視圖， 5 第4圖是第1圖所示等速接合件，沿垂直於軸向方向的 方向之放大斷面橫向橫剖圖， 第5圖是顯示根據實施例的等速接合件的一第一導槽 之深度之放大斷面縱向橫剖圖； 第6圖是顯示根據比較例的等速接合件的一第一導槽 10 之深度之放大斷面縱向橫剖圖； 第7圖是顯示一第二導槽與一珠體之間的耐用性與接 觸角度的相互關係之圖表； 第8A圖是顯示由一外杯體所界定的一第一導槽的節距 圓直徑(pitch circle diameter)之外PCD之縱向橫剖圖； 15 第8B圖是顯示由一内環體所界定的一第二導槽的節距 圓直徑(pitch circle diameter)之内PCD之縱向橫剖圖； 第9A圖是顯示一外杯體内球表面直徑之縱向橫剖圖， 其是該外杯體的内徑表面之直徑； 第9B圖是顯示一内環體外球表面直徑之縱向橫剖圖， 20 其是該内環體的外徑表面之直徑； 第9C圖是顯示一固持件外球表面直徑，其是一固持件 的外表面之直徑，及一固持件内球表面直徑，其是該固持 件的内表面之直徑之縱向橫剖圖； 第10圖是顯示該固持件的固持窗口的橫向中心自該固 31 200526883 持件的球内及外表面的中心偏離之距離之縱向橫剖圖； 第11圖是顯示該PCD間隙與耐用性之間關係之圖表； 第12圖是顯示該球面間隙與耐用性之間關係之圖表； 第13圖是顯示該窗口偏離與耐用性之間關係之圖表； 5 第14圖是等速接合件由第1圖的箭頭X所指，以軸向方 向視之且部分剖視之側視圖； 第15圖是等速接合件的放大斷面縱向橫剖圖，其顯示 一桿鋸齒區直徑（D)、一外/内PCD(Dp)、一外杯體外徑 (Do)，及一珠體直徑(Db); 10 第16圖是顯示一特徵線性曲線L之圖表，其表示一内環 體鋸齒區内徑表面與該外/内PCD(Dp)之間的關係； 第17圖是顯示一特徵線性曲線Μ之圖表，其表示該外/ 内PCD(Dp)與該外杯體的外徑之間的關係； 第18圖是顯示一特徵線性曲線N之圖表，其表示該外/ 15 内PCD(Dp)與該内環體的環體寬度之間的關係； 第19圖是顯示一特徵線性曲線Q之圖表，其表示該外/ 内PCD(Dp)與該珠體直徑(Db)之間的關係； 第2 0圖是根據本發明另一實施例的等速接合件沿軸向 方向之縱向橫剖圖； 20 第21圖是第20圖所示等速接合件的固持件與珠體之分 解透視圖， 第22圖是顯示第21圖所示不同尺寸的固持件及珠體之 環周側視圖； 第2 3圖是根據本發明又一實施例的等速接合件沿軸向 32 200526883 方向之縱向橫剖圖；及 第24圖是習用等速接合件之分解透視圖。 【主要元件符號說明】 習知部分： 1···外構件（外環） la…球内徑表面 lb…導槽 2···内構件（内環） 2a…球外徑表面 2b…導槽 2c…鍵槽 3…轉矩傳送珠體 4…固持件 4a…固持窗口 4b···欄段 4c…角隅 本發明部分： 10,100,110，150···等速接合件 12,18…第一，二桿 14…開口 16…外杯體 22…内構件 24,116a…球面内徑表面 26a-26f···第一導槽 27…接合軸 28…珠體 30a，30b··.第一肩部 32a-32f···第二導槽 34,34a…内環體 35…外徑表面 36,134…固持窗口 38，124…固持件 38a，38b…球外及内表面 39…内環體鋸齒區内徑表面 40…鎖固構件 42a,42b…第二肩部 46…外杯體内端 120a…外環周面 130···鍵孔 132…鍵桿 134a···角隅 136…攔段 S1，S2···平直區Cooney, Jr. Editor, Second Edition, The s〇dety 〇f Eight Additions · 15 Engineers, Inc "1991, pp. 145_149 (hereafter referred to as ,,-general document,) Exposed-a kind of Rzeppa (ball €) constant velocity joint. The disclosed constant velocity joint has an outer ring and an inner ring, both of which have bead grooves. The bead grooves of the outer ring and the bead grooves of the inner ring respectively have centers on the engaging rod (a driving shaft and a driven shaft), and are located at positions that are offset by the same 20 distance from the center of the engaging member. When the Rzeppa constant velocity joint is actuated, the bead grooves of the outer ring and the bead grooves of the inner ring are relatively moved to position the six beads held by the seat box on a constant velocity plane or -equivalent angular plane , Which is located at -half of the joint angle formed between the joint rods, so that the driving contact point is constantly maintained on the surface of the speed level 200526883 to provide constant speed transmission. This general document specifies the angle of the bead groove funnel, which is formed at the common area of the load-side contact point between the positive father on the outer ring bead grooves (guide grooves) and the beads and is orthogonal to the The angle formed between the inner ring bead groove (guide groove) and the common area of the load-side contact point between the beads 5, the angle,, and spoon are in the range of 15 degrees to π degrees. This angle range allows Rzeppa constant velocity joints to form a smooth angular shape so that they will not be subject to frictional latching when passing through a 0 degree joint angle. This general document also discloses that the bead grooves usually have a circular or elliptical arc cross-section shape (perpendicular to the joint rods), and the contact angle between the bead grooves with elliptical arc cross sections is from 3 In the range of 0 ° to 45 °, 45 ° is usually used. The Japanese Patent Publication No. 2003-4062 and the Japanese Patent Publication No. 9-317784 show fixed constant velocity universal joints, each having an outer ring, an inner ring, an eight-bead body, and a box. The outer ring has a guide groove (tracking groove) with respective groove bottoms, which includes a curved area, and the middle of the curved area is offset from the center of the inner diameter surface of the outer ring by a distance (F ) 'And the inner ring has a guide groove (tracking groove), each with a groove bottom, which contains a curved area' The center of the curved area is also offset from the center of the outer diameter surface of the inner ring in an opposite direction The distance (F). It is disclosed in the Japanese Patent Publication No. 2003-4062 that the ratio R1 (= F / PCR) of the deviation distance (F) to the length (PCR) of a line segment is selected, where the line segment is a guide connecting the outer ring Among the grooves ~ or the center of the guide groove of the inner ring and the center of the beads. 200526883 Japanese Patent Publication No. 317784 discloses that the deviation distance (the ratio of the length to the length of the line (pCR) RJ (= F / PCR) is selected from 0 __ $ (^ 121 ', where the line segment is connected to the The center of the guide groove of the outer ring or the center of the ¥ groove of the inner ring and the center of the beads, and the contact angle between the guide groove and the beads 5 is set to a value equal to or less than 37 degrees The bead track defined by the bead groove of the outer ring or the bead of the inner ring is a funnel shape, which gradually expands from the inner end to the outer opening of the outer ring in an axial direction. Because of the outer ring's The bead groove and the bead groove of the inner ring are deviated by the same distance from the center of the joint, so the depth of the bead grooves of the outer and inner ring is not consistent in the pumping direction 10. ^ ^ The structure disclosed in the slave file, because The depth of the bead grooves of the outer ring and the inner bead grooves of the bead 彳 M. When the constant-velocity engaging member is actuated at a large joining angle or under a high load, the contact ellipse of the beads will automatically Hai beads and other beads are protruding, and the beads are brought to the shoulders (edge 15 edge) of the beads, thus making the beads Cracking or weakening the shoulders (edges) of the bead grooves results in reduced durability of the speed joints. In addition, when the speed joints are placed under high load, the bead grooves and the beads The mutual contact position of the bodies is close to the end of the inner ring, and the contact ellipse of the beads protrudes from the bead grooves such as A, so it will increase the contact pressure exerted by the bead body. Fj According to Japanese published patent announcement No.-4062 and Japanese published patent a «No. 9 317784 'which reveals that the ratio of the deviation distance (F) to-the length of the line segment = CR) is called Satoshi) is set to a specific value, where the line segment 疋 connects to the The center of the guide groove of the outer ring or the center of the guide groove of the inner ring and the 200526883 bead d. The recording of these faces is reduced or the material speed is connected = less detected, and the holding of the long-held part is The guide grooves of the ㈣ and ㈣ must have a sufficient depth, and the shoulders of the guide grooves are easily broken or worn as described above. 10 7 Public Patent Announcement Post No. 32 Bribery Disclosure—A kind of fixed net speed universal joint member ′ has an outer joint member, 1 joint member, eight torque transmitting beads, and a retaining member. The bead grooves (track grooves) of the outer joint member and the bead grooves (track grooves) of the fairy joint member each have a center and are located at positions deviated by the same distance in opposite directions in the axial direction. In the bead trajectory, «(the gap between the pitch circle diameter of the bead groove of the outer joint member and the pitch circle diameter of the bead groove of the inner joint member) is from 5 to 20 // m. According to Japanese Laid-Open Patent Publication No. 2002-323061, the PCD gap selected in the range from 5 to 20 μm can effectively increase the durability of the fixed constant velocity universal joint 15 and stabilize it under high loads. The variability of the service life is also disclosed in Japanese Laid-Open Patent Publication No. 2002-323061. The radial clearance between the outer joint member and the inner joint member is in a range from 20 to 100 // 111, and The radial clearance between the holder and the inner joint member is also in the range from 20 to 100 // m. This published patent publication No. 2002-323061 details a fixed constant velocity universal joint with eight torque transmitting beads, and a fixed constant velocity universal joint with six torque transmitting beads, two They have different basic structures, and their PCM gaps are set to a fixed value to which their corresponding structures are applied. In 200526883, this announcement did not disclose or imply some settings for the solid type constant velocity universal joint with six torque transmitting beads, such as the PCD gap. In the fixed constant velocity universal joint of the above aspect, how to form a PCD (pitch circle diameter) gap 5 relative to the trajectory of the Zhu body is important: where the bead track is defined by the The bead grooves of the outer and inner joint members are defined. If the PCD gap is too small, it will be difficult to assemble the beads on the trajectories of β and other beads, and the restrictive force exerted on the beads will be too large to prevent the beads from rolling smoothly. If the PCD gap is too large, impact noise will be generated between the beads and the window of the holder, and the vibration of the joint itself will increase. As shown in FIG. 24, a conventional constant velocity joint of the above aspect has an outer member (outer ring) having a curved guide groove 1b defined in the axial direction of the ball inner diameter surface & and an inner member. (Inner ring) 2, which has a curved guide groove 2b axially defined on a spherical outer diameter surface 2a, and a key 15 groove 仏 on its inner diameter surface. The guide groove 1b of the outer member 1 and the guide groove 2b of the inner member 2 constitute a bead rolling groove, and a torque transmitting bead 3 is provided therein. The torque transmitting beads 3 are respectively held in a holding window defined on a substantially annular holding member 4. When the outer member 1 and the inner member 2 are at an angle to each other, the mechanical strength of the joint is determined by the mechanical strength of the holder 4. Therefore, in order to increase the mechanical strength of the joint member when the outer member 1 and the inner member 2 are at an angle to each other, the mechanical strength of the holder 4 needs to be increased. The mechanical strength of the holder 4 can be increased by increasing the cross-sectional area 蚪 of the holder 4. The cross-sectional area of the holder 4 can be increased by the following method. One of the methods of 200526883 (hereinafter referred to as, 坌 size and increase method) is to reduce the wall thickness of the inner ball diameter 4 of the holder 4, [= = The diameter of the outer ball to increase the holding member (hereinafter referred to as, the second method ,,) is to increase the holding member 4 when the engaging member is angularly displaced, it will be subjected to the force to push the bead 3 outward The — transverse area product of the region 'or re-method (hereinafter, the third method ”) is to increase the cross-sectional area of the window column segment 4b positioned at the holder 4. However, according to the first and second methods The retaining member 4 will become very heavy and have a larger width, and the beads 3 will easily bite and jam in the guides, while 10 will shorten the durability of the outer member 1. Therefore, as much as possible, The wide holding members 4 are suitably not assembled in the outer member 1. According to the second method, if the stoppers are extended to reduce the open area of the holding windows 4a, the beads 3 are easy to contact the Wait for the block and cannot be assembled exactly in the holder 4. If the holding windows are too small, then The inner member 2 cannot be easily assembled in the holding member 4. Japanese Laid-Open Patent Publication No. 2002-13544 discloses a constant velocity universal joint member having a holding member having a round corner 4c in a holding window or bag. On the mouth 4a, the ratio R / D of the radius of curvature r of the rounded corners 与 4c to the diameter D of the beads 3 is set at 0. 22SR / D. According to Japanese Laid-Open Patent Publication No. 2002-13544, the ratio R / D of the radius of curvature R of the rounded corners 4c to the diameter D of the beads 3 on the pocket opening 4a of the holder 20 is set to The purpose is to increase the durability and mechanical strength of the holder. However, the setting of the above ratio is not sufficient to effectively increase the mechanical strength of the holder. I: Summary of Content 3 200526883 Summary of the invention The general purpose of the present invention is to provide a constant velocity joint, which can be designed for different size settings, can be applied to small joint sizes and can maintain different characteristics, that is, mechanical strength, durability Performance, load capacity, etc., to an appropriate degree. The main object of the present invention is to provide a constant velocity joint in which the surface pressure on the guide groove due to the contact with the bead can be reduced to increase its durability. Another object of the present invention is to provide a constant velocity joint in which the shoulder of the guide groove can be prevented from being cracked or worn to increase its durability. Another object of the present invention is to provide a constant velocity joint with six beads, in which the different gaps and deviation distances of the retaining windows of a retaining member can be set to the optimal value to reduce the surface pressure, which can directly benefit such The service life of the quick coupling is between the outer ring guide groove and the beads, and between the inner ring guide groove and the beads, to increase its durability. It is still another object of the present invention to provide a constant velocity joint, which includes a retaining member having a required mechanical strength, and which can be assembled more efficiently. The above and other objects, features, and advantages of the present invention will be understood from the following detailed descriptions with reference to the drawings, and the preferred embodiments of the present invention are shown in the illustrated 20 ways. · Brief description of the figure t Figure 1 is a longitudinal cross-sectional view of a constant velocity joint in an axial direction according to an embodiment of the present invention; Figure 2 is an enlarged sectional view of the constant velocity joint shown in Figure 1 Longitudinal cross section 12 200526883 Figure; Figure 3 is a side view of a constant velocity joint indicated by the arrow X in Figure 1, viewed in the axial direction and partially sectioned; Figure 4 is a constant velocity shown in Figure 1 An enlarged cross-sectional transverse cross-sectional view of the joint member along 5 directions perpendicular to the axial direction; FIG. 5 is an enlarged cross-sectional longitudinal cross-sectional view showing the depth of a first guide groove of the constant-speed joint member according to the embodiment Figure 6 is an enlarged cross-sectional longitudinal cross-sectional view showing the depth of a first guide groove of a constant velocity joint according to a comparative example; 10 Figure 7 is a diagram showing the durability between a second guide groove and a bead Diagram of the relationship between contact angle and contact angle; Figure 8A is a longitudinal cross-sectional view showing the PCD outside the pitch circle diameter of a first guide groove defined by an outer cup; Figure 8B Shows the pitch of a second guide groove defined by an inner ring body within 15 pitch circle diameter P CD longitudinal cross-section view; Figure 9A is a longitudinal cross-sectional view showing the diameter of the inner surface of the outer cup body, which is the diameter of the inner diameter surface of the outer cup; Figure 9B is a diagram showing the outer surface of the inner ring of the outer cup A longitudinal cross-sectional view of the diameter, which is the diameter of the outer diameter surface of the inner ring body; Figure 9C shows the diameter of the outer ball surface of a holder, which is the diameter of the outer surface of the holder, and the inside of the holder Ball surface diameter, which is a longitudinal cross-sectional view of the diameter of the inner surface of the holder; Figure 10 shows the distance the lateral center of the holding window of the holder deviates from the center of the ball's inner and outer surface of the holder Longitudinal cross-section view; 13 200526883 Figure 11 is a chart showing the relationship between the PCD gap and durability; Figure 12 is a chart showing the relationship between the spherical gap and durability; Figure 13 is showing the window deviation and Diagram of the relationship between durability; Figure 14 is a side view of a constant velocity joint indicated by the arrow X in Figure 1, viewed in the axial direction in 5 directions and partially cut; Figure 15 is a constant velocity joint A magnified longitudinal cross-sectional view of a section showing a sawtooth Diameter (D), an outer / inner PCD (Dp), an outer cup outer diameter (Do), and a bead diameter (Db); Figure 16 is a graph showing a characteristic linear curve L, which represents an inner ring The relationship between the diameter surface of the 10-body sawtooth region and the outer / inner PCD (Dp); Figure 17 is a graph showing a characteristic linear curve M, which shows the outer / inner PCD (Dp) and the outer cup The relationship between the outer diameters; Figure 18 is a graph showing a characteristic linear curve N, which shows the relationship between the outer / inner PCD (Dp) and the ring width of the inner ring; 15 Figure 19 shows A graph of a characteristic linear curve Q, which shows the relationship between the outer / inner PCD (Dp) and the bead diameter (Db); Figure 20 is a view of a constant velocity joint along an axis according to another embodiment of the present invention A longitudinal cross-sectional view in the direction; FIG. 21 is a 20-dimensional perspective view of the holder and the bead of the constant velocity joint shown in FIG. 20; FIG. 22 is a view showing the holders of different sizes shown in FIG. 21 and Side view of the circle of the bead, Fig. 23 is a longitudinal cross-sectional view of the constant velocity joint according to another embodiment of the present invention in the axial direction; and 14 200526883 Fig. 24 is an example of the same An exploded perspective view of the engaging member. [Implementation formula] Detailed description of the preferred embodiment 5 10 15 20 Figure 1 shows a constant velocity joint 1 10 β according to the embodiment of the present invention. In the following detailed description, the longitudinal cross section refers to 12 and—the cross section of the second rod 18 in the axial direction, and the cross section is a cross section perpendicular to the axial direction. 'The Hai constant velocity joint 10 is basically a bottom cylindrical outer cup 16 (outer member) m at the end of a first rod 12_ and has an opening 14 to be opened away from the first rod 12' and an inner member 22 The second rod 18 is fixed at the end of the second rod and is received in the outer cup 16. As shown in Figures 1 and 3, the outer cup 16 has a spherical inner diameter surface 24 on its inner wall. This inner diameter surface 24 has six first guide grooves 26a to 26f which extend in the axial direction and are angularly spaced around its axis at a pitch of 60 degrees. As shown in Fig. 2, the first guide grooves 26a to 26f each have a longitudinal cross-section in a curved axial direction and have a common curvature center on a point Η. This point is located at the opening 14 facing the outer cup 16 in the axial direction, a position deviated from the center K of the spherical inner diameter surface 24 by a distance T1 (where the center 0 [sphere center surface] of the bead 28 is connected) An imaginary plane is staggered with an engagement axis 27). As shown in FIG. 4, each of the first guide grooves 26 a to 26 f defined in the outer cup body 16 has a transverse cross-sectional view, which has a single concave arc shape, and the center of curvature A is located on a vertical line L. The vertical line L extends through the center 0 of the bead 28. Each of the first guide grooves 26a to 26f is held in contact with the outer surface of the bead body 28 at a single point B in Fig. 4. 15 200526883 When a load is actually applied to transmit a rotational torque, the outer surface of the bead 28 and each of the first guide grooves 26a to 26f are kept in surface-to-surface contact with each other instead of point-to-point contact. The inner diameter surface 24 is continuously formed on both sides of each of the fifth guide grooves 26a to 26f in a transverse cross section. The boundary between each of the first guide grooves 26a to 26f and the edge of the inner diameter surface 24 has a pair of first shoulder portions 30a, 30b which are beveled. The contact angle of the bead body 28 with respect to each of the first guide grooves 26a to 26f of the outer cup body 16 is set to zero on the vertical line L. The ratio (M / N) of the radius M of each of the first guide grooves 26a to 26f 10 in the transverse cross section to the diameter N of the beads 28 is set to be from 0.51 to 0.5. Value in the range of 55 (see Figure 4). The inner member 22 has an inner ring 34 having a plurality of second guide grooves 32a to 32f defined in its outer circumferential surface and aligned with the individual first guide grooves 26a to 26f at a circumferential interval. The bead body 28 (this There are six examples.) The first guide grooves 26a to 26f defined in the inner wall surface of the outer cup body 16 and the outer diameter surface 35 (see FIG. ) Between the second guide grooves 32a to 32f for transmitting rotation torque, and a retaining member 38 having a plurality of retaining windows 36 defined thereon and spaced in the circumferential direction for separate retaining The beads 28 are on the inside and are between the outer cup 16 and the inner ring 34. The inner ring body 34 is connected to one end of the second talent 18 through a central hole defined in the inside, or is mounted on a ring groove defined on the second rod 18 through an annular locking member 40. The inside is integrally fixed to one end of the second rod 18. The first to 32f ′ are aligned with the individual first guide grooves 16 200526883 26a to 26f of the outer cup body 16 and are spaced at equal angular intervals in the circumferential direction, and are defined by the outer diameter of the inner ring body 34 Surface 35. As shown in Fig. 2, the second guide grooves 32 & to 32 £ each have a longitudinal cross-section of a bending axis and have a common center of curvature on a point. The scoring point 5 is located at an opening 14 away from the outer cup 16 in the axial direction, and is offset from the center K of the spherical inner diameter surface 24 by a distance T2 (where the center of the bead 28 is [sphere center surface] An imaginary plane is staggered with the joint shaft 27). The points 11 where the centers of curvature of the first guide grooves 26a to 26f are located and the points R where the centers of curvature of the second guide grooves 32a to 32f are located are respectively located at 10 in the axial direction in opposite directions from the At the position where the center K of the spherical inner diameter surface deviates (where the spherical center surface of the bead is staggered with the joint axis 27), the deviation distances are equal (T1 = T2). The point Η is located closer to the opening 14 than the center K of the spherical inner diameter surface 24, and the point R is located closer to an inner end 46 of the outer cup 16. The radius of curvature of the point 与 and the radius of curvature of the point rule extend and intersect each other (see Figure 2). Assume that the beads 28 have a diameter N and the centers of curvature (the points H, R) of the first guide grooves 26a to 26f and the second guide grooves 32a to 32f are axially offset from the center K by a distance T , The diameter τ of the beads 28 and the deviation distance T should be set to the ratio V (= T / N) of the distance T to the diameter N, which must satisfy the following: 20 0 · 12 $ ν $ 0 · 14 〇 As shown in Figure 4 As shown, each of the second guide grooves 仏 to a transverse cross section with an elliptical curved shape has a pair of centers C and D, and the two are horizontally spaced from each other by a predetermined distance. Each of the second guide grooves 32a to 32f is held in contact with the outer surface of the bead body at two points E, F shown in Fig. 4. When a load is actually applied on 17 200526883 to convey a rotational torque, the outer surface of the bead 28 and each of the second V grooves 32a to 32f are kept in surface-to-surface contact with each other, rather than point-to-point contact. . The outer control surface 35 is continuously formed on both sides of each of the first 'grooves 32a to 32f in a transverse cross section. The boundary between each of the second guide grooves 32a to 32f and the edge of the outer diameter surface 35 has a pair of second shoulder portions 42 & The beads 28 are held in contact with each of the second guide grooves 32 & 32 {on one of the contact angles α on each side of the vertical line L. If the contact angle is set to an angle in the range from 13 10 degrees to 22 degrees, as shown in Fig. 7, the durability of the speed coupling will be increased. If the contact angle 01 is an angle set in a range from 15 degrees to 20 degrees, the durability of the constant velocity joint can be further increased. The radius p, Q of each second guide groove 32a to 32f in the transverse cross section (P / N, Q / N) of the bead 28 direct control N can be set in the range from 0.5 to 55 (See U figure 4). For example, 'the beads 28 are made of steel and are rotatably provided in each of the first guide grooves 26a to 26f of the outer cup body 16 and the first guide grooves 32a to 32f of the inner ring body 34. Inside. The beads 28 transmit the rotation torque of the second rod 18 to the first rod 12 via the inner ring body 34 and the outer cup body 16, and along the 20 first guide grooves 26a to 26f and the distance The first guide grooves 32a to 32f are rolled therein, so that the second rod 18 (the inner ring body 34) and the first rod 12 (the outer cup body 16) can be displaced at an angle to each other. The rotational torque may be transmitted between the first lever 12 and the second lever 18 in either direction. As shown in FIGS. 8A and 8B, if the pitch 18 200526883 of the first guide grooves 26a to 26f is a pitch circle diameter, the six bead body 28 is held in contact with the first guide grooves 26a to 26f. The point-to-point contact is expressed by outside pcd, and the pitch circle diameter of the first guide grooves 32a to 32f is maintained when the six beads 28 are kept in point-to-point contact with the second guide grooves 32a to 32f. It is expressed by the PCD within 5, and the PCD distance is established as the gap between the outer PCD and the inner PCD (outer PCD-inner PCD). As shown in Figures 9A to 9C, a spherical distance is established as the sum of the difference between the diameter of the spherical surface inside the outer cup and the diameter of the external spherical surface of the holder, and the difference between the diameter of the internal spherical surface of the holder and the external spherical surface The diameter of the 10-sphere surface in the outer cup body is the diameter of the inner-diameter surface 24 of the outer cup body 16. The diameter of the outer-ball surface of the holder is the diameter of the outer diameter surface of the holder 38 Is the diameter of the inner diameter surface of the holder 38, and the outer spherical surface diameter of the inner ring is the diameter of the outer diameter surface 35 of the inner ring body 34. That is, the spherical distance is determined by the following: spherical distance = 丨 (the diameter of the inner spherical surface of the outer cup 15) _ (the diameter of the outer spherical surface of the holder)} + {(the diameter of the inner spherical surface of the holder)- (Diameter of outer spherical surface of the inner ring)}. As shown in FIG. 10, the lateral center of the holding window 36 of the holding member 38 (here, “lateral” refers to the axial direction of the holding member 38) is from the ball outer and inner surfaces 38a, 38b of the holding member 38. The center of is offset by a predetermined distance in the axial direction 20 of the holding member 38. The special speed joint 10 according to this embodiment is basically constructed as described above. Next, the operation and advantages of the constant velocity joint 10 will be described in detail below. When the second rod 18 rotates around its own axis, its rotational torque is transmitted from 19 200526883 to the inner ring body bead 28 to the outer cup body 16, resulting in the brother 1:!: 2: such as: the first The two rods 18 rotate in the same direction and at the same rate. 5 10 15 20 * If the first rod 12 and the second rod 18 are displaced relative to each other, the beads 28 roll on the first guide groove 2 as if torn and the second guide grooves are as close as possible. Between 32f, the holding angle is tilted to a specific angle, so that the first rod 12 and the 418th angle can be moved with respect to each other. At this time, the six-ball body in the holding window 36 of the _ 于 _ holding piece 38 = a-constant velocity plane or a pair of equal: angular planes located between the first rod 12 and the second rod 18 to hold The driving contact point is constant on the plane of constant speed to increase the speed of the constant speed. The first rod I2 and the second rod 18 can rotate at a constant speed and can be displaced at an appropriate angle with each other. According to this embodiment, the diameters N of the beads 28 and the centers of curvature (points h, R) of the first guide grooves 1 and the first guide grooves 32a to 32f such as “Hai” deviate from the middle of the Hai and κ axes. The distance ratio v (= t / n) is set to satisfy the following expression: 〇. 120 Wei 14 (see Figure 2). If the ratio of "Straight Twist N" and the deviation distance "T" is less than 0. At 12:00, the funnel angle formed between the first guide grooves 26a to 2 and the second guide grooves 32 & to 32 £ will be minimized. The beads 28 are liable to be stuck when rotating, and also cause the efficiency of the constant speed joint 10 to be lowered during assembly. Conversely, if the ratio of the diameter N to the deviation distance T is more than 0. At 14 o'clock, because the first guide grooves 26a to 26f and the second guide grooves 32a to 32f are formed deep, the beads 28 are easy to move at the edges of the first guide grooves 26a to 26f. The first shoulders 30a, 30b and the second shoulders 42a, 42b moving at the edges of the second 20 200526883 guide grooves 32a to 32f may cause cracks and wear. Therefore, by setting the ratio v of the diameter N to the deviation distance τ to satisfy 0.12 $ V $ 0. 14, can effectively prevent the beads 28 from moving on the edges of the first guide grooves 5 26a to 26f of the first shoulders 30a, 30b & the second guide grooves 32a to 32f The second shoulders 42 and 4213 at the edges of the edges may cause cracking and grinding to make the constant-speed joint 10 more durable. Fig. 5 shows an enlarged sectional longitudinal cross-sectional view of the constant velocity joint 10 according to the embodiment. As shown in Fig. 5, the ratio V of the diameter n to the deviation distance T is set in a range of 10 · 12 $ ν $ 0 · 14 so that the deviation distance T1 can be made smaller. Fig. 6 shows an enlarged sectional longitudinal cross-sectional view of a constant velocity joint 100 according to a comparative example. As shown in FIG. 6, a deviation distance T2 of the constant velocity joint 100 is greater than the deviation distance T1 (T1CT2) of the constant velocity joint 10. The comparison of the depths of the first guide grooves 26a to 26f 15 between the constant velocity joints 10, 100 is at a straight line S (which extends perpendicular to the joint axis 27 and passes through the center of the beads 28). The area inclined at about 15 degrees is expressed as follows. The depth DPI of the first guide grooves 26a to 26f of the constant velocity joint 10 according to this embodiment is greater than the first guide of the constant velocity joint 10 according to the comparative example. The depths DP2 (DP1 > DP2) of the grooves 26a to 26f. Therefore, according to the 20 constant velocity joint 10 of this embodiment, the beads 28 can be effectively prevented from moving at the edges of the first guide grooves 26a to 26f of the first shoulders 30a, 30b and the The second shoulders 42a, 42b at the edges of the second guide grooves 32a to 32f may cause cracks and wear. In addition, according to the present invention, each of the first guides 21 200526883 grooves 26a to 26f defined in the outer cup 16 has a transverse cross-section of a non-arc shape, which is kept in contact with the beads 28 at a single point, And each of the second guide grooves 32a to 32f has an elliptical arc-shaped transverse cross section 'which is kept in contact with the beads 28 at two points. In this configuration, the beads 28 are contacted and applied to the first guide grooves, such as 5 and 5 °, and the first 'grooves 32 & to 32 [, whose surface pressure will be less than that of the conventional configuration to increase durability. According to this embodiment, the radius (M, p, Q) of the guide grooves and the diameter "N" of the beads are applied to the first guide grooves to 26f and the second guide grooves to the like. Each ratio (M / N, p / N, Q / N) on the cross section is set to a value in the range from 0 51 to 10 55. The beads 28 are relative to each of the first guide grooves 26 a to 26 f. The contact angle is set to zero on the vertical line L, and the contact angle of the beads 28 to keep in contact with each of the second guide grooves 32a to 32f is set to a value from 13 degrees to 22 degrees, thereby Reduce the surface pressure to increase the durability. The radius n (M, P, Q) of the guide grooves and the diameter n of the beads 28 are between the 15 first guide grooves 26 & 2 and the second guide grooves. The ratios (M / N, P / N, Q / N. ) Is set to 0. The reason for the value in the range of 51 to 〇55 is that if the ratio is less than 0.51, because the groove radius (M, P, Q) and the diameter N of the beads 28 are too close to each other, the beads The body 28 is almost in full contact with the guide grooves and is not easy to roll, so the durability 20 is poor, and if the ratio is greater than 0.55, the contact ellipse of the beads 28 will be reduced, so Increased contact surface pressure results in poor durability. The diameter (N) of the beads 28 and the centers of curvature (points h, r) of the first guide grooves 26 & to 26 € and the second guide grooves 32a to 32f deviate from the center K axis 22 200526883 Ratio V (T / N) of the distance τ, the contact angle α of the beads 28 maintaining contact with each second guide groove to 3M, and the radius of the guide grooves (m, p, q) and the beads The ratio of the diameter N of the body 28 on the cross sections of the first guide grooves to the second guide grooves to 32f is determined by the optimal value of 5 produced by repeated simulations and experiments. The reason why the contact angle α that the beads 28 keep in contact with each of the second guide grooves 32 & 3 ^ is set to a value ranging from 13 degrees to 22 degrees is that if the contact angle α is less than 13 degrees, then The load on the beads 28 will increase, thus increasing the surface pressure, resulting in poor durability, and if the contact angle α 10 is greater than 22 degrees, the edges of the second guide grooves 32 a to 32 f (such The contact positions of the second shoulders 42a, 42b) and the beads 28 will be close to each other, and the contact ellipse of the beads will protrude from the guide grooves, thereby increasing the surface pressure and thus reducing the durability. In addition, according to this embodiment, the PCD pitch, which is established as the gap between the outer pcd 15 and the inner PCD (outer PCD_inner PCD) (see Figure 88 and the figure), must be set from 0 to 100 μηι The value of the range may be from 0 to the howling range. The PCD pitch must be a value ranging from 0 to 100pm because if the pcD pitch is less than 0 μm, the beads 28 cannot be effectively assembled and positioned and cannot smoothly roll, resulting in poor durability, and If the PCD spacing exceeds 20 100 μm, the contact ellipse that the beads 28 keep in contact with the first and second guide grooves will protrude from the shoulders at the edges of the guide grooves, increasing surface pressure and causing Shoulder fracture, resulting in reduced durability. If the PCD interval is set in a range from 0 to 60 μm, excellent durability can be achieved, which can be expressed by experimental results, as shown in FIG. 11. 23 200526883 In addition, according to this embodiment, as shown in FIGS. 9A to 9C, the spherical distance is defined as ... {(outer cup surface diameter)-(retainer outer ball surface diameter)} + {( The diameter of the inner sphere surface of the holder M and the outer sphere surface diameter of the inner ring)}, shall be equal to a value in the range from 50 to 200 μm, or preferably from 50 to 50 μn! 5. If the spherical distance is less than 50 μm, it will be stuck due to lack of lubrication between the inner surface of the outer cup 16 and the outer surface 38 a of the holder 38, and the outer surface of the inner ring body 34 and the holder 38 The same is true between the inner surfaces 38b of the same, which will adversely affect the mechanical properties of the constant velocity joint 10. If the spherical distance is greater than 200 μm, an impact noise will be generated between the outer cup 16 and the inner ring body 34 and the holding 10 piece 38, which will adversely affect the commercial value of the constant velocity joint 10. If the spherical pitch is set in the range from 50 to 15111), excellent durability can be achieved. This experimental result can be expressed as shown in FIG. 12. According to this embodiment, as shown in FIG. 10, the lateral center of the opening 15 of the holding member 38 (here, lateral, refers to the axial direction of the holding member 38). The centers of the outer and inner surfaces of the ball 38a, 38b deviate from the axial direction of the holder 38, and the deflection distance is in the range from 20 to 10% of the claws. If the distance, that is, the distance that the lateral center of the holding window of the holding member 38 deviates from the center of the outer and inner surfaces of the ball 38a, 38b, is less than 20 μm, a limit of 20 is imposed on the beads 28 The force will not be sufficient to maintain a constant speed transmission performance. If the distance, that is, the distance that the lateral center of the holding window of the holding member 38 deviates from the center of the outer and inner surfaces of the ball 38a, 38b is greater than 100 μm, then the restriction force on the illegal beads 28 is added It will be too large, so that these beads 28 cannot be used by one member. If the distance, that is, the distance at which the lateral center of the holding window of the holder 24 200526883 38 deviates from the center of the outer and inner surfaces of the ball 38a, 38b, is set in the range of 40 to 80 μm, then excellent durability can be achieved, The results of this experiment can be expressed as shown in Figure 13. Therefore, even when the constant velocity joint 10 with the six beads 28 is under a high load, the contact ellipse of the beads 28 can be prevented from protruding from the guide grooves, so that the durability can be improved. The setting of the different sizes of the constant velocity joint 10 will be described in detail below. Assume that the outer PCD and the inner PCD are equal (outer PCD = inner PCD) as shown in Figs. 8A and 8B, that is, the gap between the outer PCD and the inner PCD is 10 zero. Both the outer PCD and the inner PCD are collectively referred to as "outer / inner PCD" below. The diameter (D) of the diameter surface 39 of the inner ring body in the zigzag area is set to any required value, and the outer / inner PCD indicates that the minimum wall thickness of the inner ring body 34 is based on the diameter surface of the inner ring body in the zigzag area 39 (D) is established (see Figures 14 15 and 15). The diameter (D) of the diameter surface 39 of the inner ring body in the zigzag region indicates the bottom of a valley in the diameter surface 39 of the inner ring body in the zigzag region and the inner surface of the inner ring body in the zigzag area 39 across the inner ring body. The diameter of one of the hole centers at 34 is relative to the dimension (maximum diameter) between the bottom of the valley (see Figure 15). By the maximum wall thickness of the inner ring body 34, a predetermined bonding strength can be maintained. The value of the outer / inner PCD is determined from a characteristic linear curve L, which represents the relationship between the diameter of the diameter surface 39 in the sawtooth region of the inner ring body and the outer / inner PCD. As shown. If the diameter of the inner diameter surface 39 of the inner ring body is D and the 25 200526883 outer / inner PCD is Dp (see Figures 14 and 15), then the outer / inner PCD (Dp) and the inner The size ratio (Dp / D) of the diameter (D) of the diameter surface 39 in the sawtooth region of the ring body should be set to 1. 9S (Dp / D) $ 2. Value in the range of 2. If the size ratio (Dp / D) is less than 1. 9, the wall thickness of the inner ring body 34 will be too small, resulting in a decrease in its mechanical strength. If the size ratio (Dp / D) exceeds 2. 2, the size of the constant velocity joint 10 cannot be reduced. As shown in FIG. 17, the outer diameter of the outer cup 16 is established based on a characteristic linear curve M, which is the outer diameter of the cross section of the cup representing the outer / inner PCD and the outer cup 16. The relationship between. If the 10 outer diameter of the outer cup 16 is expressed by Do, the size ratio (Do / Dp) of the outer diameter Do of the outer cup 16 to the outer / inner PCD (Dp) should be set to 1 · 4 $ (Do / Dp) Value in the range $ 1 · 8. If the size ratio (Do / Dp) is less than 1. 4, the wall thickness of the outer cup body 16 will be too small, resulting in a decrease in its mechanical strength. If the size ratio (Do / Dp) exceeds 15 1. 8, the outer diameter of the outer cup body 16 will increase, so that the size of the constant velocity joint 10 cannot be reduced. As shown in FIG. 18, the ring width of the inner ring body 34 is established based on a characteristic linear curve N, which indicates that the outer / inner PCD and the inner ring body 34 are along the second rod 18 axis The relationship between the ring width of the heart. If the ring width of the inner ring body 34 20 is expressed by W, the size ratio (W / Dp) of the ring width W of the inner ring body 34 to the outer / inner PCD (Dp) should be set to 0.38 $ (W / Dp) $ 0. Value in the range of 42. As shown in Fig. 19, the diameter of the beads 28 is established based on a characteristic linear curve Q, which represents the distance between the outer / inner PCD (Dp) 26 200526883 and the diameter of the beads 28 relationship. If the diameter of the beads 28 is & Db, as shown in Figures 14 and 15, then the ratio of the diameter (Db) of the beads 28 to the outer / inner PCD (DP) size (Db / Dp ) Should be set to 0. 2 $ (Db / Dp) S0. Value in the range of 5. 5 If the size ratio (Db / Dp) is less than 0. 2, the diameter of the beads 28 will be too small, resulting in a reduction in their mechanical strength. If the size ratio (pb / Dp) exceeds 0-5 ', the beads 28 will be too large and the wall thickness of the outer cup 16 will be relatively small, resulting in a reduction in its mechanical strength. The diameters of the outer and inner surfaces of the ball 38 and 38 \ 3813 of the holder 38 used to hold the beads 28 are set according to their arrangement. In this way, different sizes of the isokinetic joint 10 can be established with a small joint size while maintaining different characteristics, namely mechanical strength, durability, load capacity, etc., to the extent required. FIG. 20 shows a constant velocity joint 15 uo according to another embodiment of the present invention. The components of the constant velocity joint no that are the same as those of the constant velocity joint 10 shown in FIG. 1 are denoted by the same reference numerals, and will not be described in detail below. As shown in FIG. 20, the constant velocity joint 110 has a bottom cylindrical outer member 16 which is integrally engaged with one end of a first rod 12 and defines an opening 14 at one end to be opened away from the first rod 12, The inner ring body 3 is positioned at a 20th pole end, which can be displaced relative to the first pole and accommodated in the outer member 16, and the bead body 28 is interposed between the outer member 16 and the inner ring. The body is used for transmitting the torque therebetween, and a retaining member 124 which holds the beads 28 and is disposed between the outer member 16 and the inner ring body%. The outer member 16 has an inner diameter surface U6a having six first guide grooves 27 200526883 26a to 26f extending in an axial direction shown by an arrow X and being angularly spaced about its axis. Each of the first guide grooves 26a to 26f has a flat region 51 integrally extending from its curved region in the longitudinal direction shown by the arrow X. The inner ring body 34 has an outer ring peripheral surface i20a, which has the same number of second guide grooves 323 to 32 [as the first 5 guide grooves 26a to 26f, and the second guide grooves 32a to 32f. Extend in the axial direction. Each of the second guide grooves 32 & to 32 £ has a flat area S2 extending integrally from its lap area in the longitudinal direction shown by arrow X. The straight regions S1, S2 are located opposite to each other in a direction indicated by an arrow X. The inner ring body 34 has a key hole 130 defined at its center. The key hole 1310 is held in mesh with 132 ° of one of the key rods on the end of the first rod 18, so that the second rod 18 and the inner ring body 34 are coupled to each other. For example, the beads 28 are made of steel and are rotatably provided in the individual first guide grooves 26 a to 26 f of the outer member 16 and the individual second guide grooves 32 a to 32 f of the inner ring body 34. Inside. The bead bodies 28 transmit the 15 rotation torque of the second rod 18 to the first rod 12 through the inner ring body 34 and the outer member 16, and the first guide grooves 263 to 2 and the second The guide groove 32 is within 3% and rolled along it, so that the second rod 18 (inner ring body 34) and the first rod 12 (outer member 16) can be angularly displaced from each other. The rotational torque can be transmitted between the first lever 12 and the second lever 18 in one of the directions. 20 As shown in Figures 21 and 22, the retaining member 124 is substantially annular and has, for example, six retaining windows 134 for retaining individual beads 28 therein. The holding windows 134 are angularly spaced at equal angular intervals in the circumferential direction. As shown in FIG. 22, each of the holding windows 134 has an opening length WLk 上 in the circumferential direction of the holding member 124. The ratio of the opening length WL to the diameter D of the beads 28 28 200526883 (WL / D) is set to 1.30 $ WL / D S 1. Value in range 42. Each holding window 134 has a corner 134a, each of which has a radius of curvature R. The ratio (R / D) of the radius of curvature R to the diameter D of the beads 28 is set to 0. 23‘R / D $ 〇. Value in the range 45. 5 Relative to each of these holding windows 134, the ratio (WL / D) of the opening length WL to the diameter D of the beads 28 is set to WL / D $ 1. Value in range 42. Therefore, 'the holding member 124 can effectively maintain the circumferential length of the segments 136 between the holding windows 134. In this way, it is not necessary to increase the wall thickness of the retaining member 24, and the cross-sectional area of the columns 136 can be increased. · 10 Therefore, the mechanical strength of the 5H holder 124 can be increased without reducing the diameter of the inner diameter surface of the ball, thereby increasing the diameter of the outer diameter surface of the ball, and increasing its width in the axial direction. For the constant velocity joint 110, the ratio of the opening length WL of each of the holding windows 134 to the diameter D of the beads 28 (WL / D) is set to 1. 30 $ 15 Value in WL / D range. Therefore, the opening area of the holding windows 134 can be increased, so that the beads 28 can be easily assembled and the inner ring body 34 can also be easily assembled. In this way, the constant velocity joint 110 can have a simple structure and can be easily assembled. The ratio (R / D) of the radius of curvature r of the corners 134a of each of the holding windows 134 to the diameter D of the beads 20 body 28 is set to 0. Value in the 23 $ R / D range. This ratio setting can effectively reduce the maximum main stress load on the shed sections 136 between the holding windows 134, and thus is used to increase the mechanical strength of the holding member 124. The ratio (R / D) is also set at R / D € 0. The value in the range of 45 to prevent 29 200526883 from stopping the beads 28 and the inner ring body 34 from assembly failure due to the curvature radius of the corners 134a of the retaining windows i34 being too large. Each of the first guide grooves to 26f has a ―straight area> extending in the longitudinal direction, and each of the second guide grooves has a longitudinal direction extending to 32 £. This flat region S1S2 allows the constant velocity joint to have a larger maximum joint angle. ^ Figure 23 shows a constant velocity joint 150 according to yet another embodiment of the present invention. The same parts of the constant velocity joint 150 as those of the constant velocity joint shown in FIG. 20 are denoted by the same reference numerals, and will not be described below. 10 As shown in FIG. 23, the constant velocity joint 150 has an outer member 16 and an inner ring body 34a. The outer member 16 has an inner diameter surface 116 & having first guide grooves 26a to 26f extending in the axial direction. If the inner ring body 3 has an outer ring peripheral surface 120a, it has the same number of second guide grooves 32a to 32f as the first guide grooves 26 & Extend in the direction. Each of the first guide grooves 26f to 26f and the second guide grooves 32a to 32f has only one curved area extending in its longitudinal direction, which is different from the constant velocity joint 110 of the foregoing embodiment. The constant velocity joint 150 provides the same advantages as the constant velocity joint 110. Although specific preferred embodiments of the present invention have been described in detail, we need to understand that various changes and modifications can be made here without departing from the scope of the following patent application. [Brief description of the drawings] Fig. 1 is a longitudinal cross-sectional view of a constant velocity joint in an axial direction according to an embodiment of the present invention; 30 200526883 Fig. 2 is an enlargement of the constant velocity joint shown in Fig. 1 Sectional longitudinal cross-sectional view, FIG. 3 is a side view of the constant velocity joint indicated by the arrow X in FIG. 1 and viewed partially in the axial direction, 5 FIG. 4 is shown in FIG. 1 etc. An enlarged cross-sectional transverse cross-sectional view of the quick-engagement member in a direction perpendicular to the axial direction. FIG. 5 is an enlarged cross-sectional longitudinal cross-sectional view showing the depth of a first guide groove of the constant-speed joint according to the embodiment. Figure 6 is a longitudinal cross-sectional enlarged view showing the depth of a first guide groove 10 of a constant velocity joint according to a comparative example; Figure 7 is a diagram showing the durability between a second guide groove and a bead Diagram of the relationship between contact angle and contact angle; Figure 8A is a longitudinal cross-sectional view showing the PCD beyond the pitch circle diameter of a first guide groove defined by an outer cup; 15 Section 8B The figure shows the pitch circle diameter of a second guide slot defined by an inner ring body. Longitudinal cross-sectional view of PCD; FIG. 9A is a longitudinal cross-sectional view showing the diameter of the inner surface of the outer cup body, which is the diameter of the inner diameter surface of the outer cup; FIG. 9B is a diagram showing the outer surface of the outer ring of the inner cup A longitudinal cross-sectional view of the diameter, 20 is the diameter of the outer diameter surface of the inner ring body; FIG. 9C shows the diameter of the outer ball surface of a holder, which is the diameter of the outer surface of the holder, and the inside of the holder Ball surface diameter, which is a longitudinal cross-sectional view of the diameter of the inner surface of the holder; Figure 10 shows the lateral center of the holding window of the holder deviating from the center of the ball's inner and outer surfaces of the holder 31 200526883 The vertical cross-sectional view of the distance; Figure 11 is a chart showing the relationship between the PCD gap and durability; Figure 12 is a chart showing the relationship between the spherical gap and durability; Figure 13 is showing the window deviation Graph of the relationship between durability; 5 Figure 14 is a side view of a constant velocity joint indicated by the arrow X in Figure 1, viewed in the axial direction and partially cut away; Figure 15 is a constant velocity joint A magnified longitudinal cross-sectional view of a section showing a sawtooth Diameter (D), an outer / inner PCD (Dp), an outer cup outer diameter (Do), and a bead diameter (Db); 10 Figure 16 is a chart showing a characteristic linear curve L, which represents an inner The relationship between the diameter surface in the sawtooth zone of the annulus and the outer / inner PCD (Dp); Figure 17 is a graph showing a characteristic linear curve M, which shows the outer / inner PCD (Dp) and the outer cup The relationship between the outer diameters; FIG. 18 is a graph showing a characteristic linear curve N, which shows the relationship between the outer / inner PCD (Dp) and the ring width of the inner ring; FIG. 19 is a display A graph of a characteristic linear curve Q, which shows the relationship between the outer / inner PCD (Dp) and the bead diameter (Db); Figure 20 is a view of a constant velocity joint along an axis according to another embodiment of the present invention A longitudinal cross-sectional view in the direction; 20 FIG. 21 is an exploded perspective view of the holding member and the bead of the constant velocity joint shown in FIG. 20, and FIG. 22 is a view showing the holding members and beads of different sizes shown in FIG. 21 Side view of the circumference of the body; Figures 23 and 3 are longitudinal cross-sectional views of a constant velocity joint in the direction of the axial direction 32 200526883 according to another embodiment of the present invention; and Figure 24 is a conventional example. An exploded perspective view of the engaging member. [Description of symbols of main components] Known parts: 1 ··· outer member (outer ring) la ... ball inner diameter surface lb ... guide groove 2 ... · inner member (inner ring) 2a ... ball outer diameter surface 2b ... guide groove 2c ... keyway 3 ... torque transmitting bead 4 ... retaining member 4a ... retaining window 4b ... section 4c ... corner part of the present invention: 10,100,110,150 ... constant velocity joints 12,18 ... first, second Rod 14 ... Opening 16 ... Outer cup 22 ... Inner member 24, 116a ... Spherical inner diameter surface 26a-26f ... First guide groove 27 ... Engaging shaft 28 ... Beads 30a, 30b ... First shoulders 32a-32f ... Second guide grooves 34, 34a ... inner ring body 35 ... outer diameter surface 36,134 ... retaining windows 38,124 ... retaining members 38a, 38b ... ball outer and inner surface 39 ... inner ring body Zigzag inner diameter surface 40 ... Locking members 42a, 42b ... Second shoulder 46 ... Outer cup inner end 120a ... Outer ring peripheral surface 130 ... Key hole 132 ... Key lever 134a ... Angle 136 ... Stop Section S1, S2 ... Straight area
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