517124 A7 ___ B7____ 五、發明説明（1 ) 發.明背景 (請先閲讀背面之注意事項再填寫本頁) 本發明係關於一種洗衣機之防振裝置，其支撐外槽在 外框上。 習知洗衣機包含具有固持支撐桿的外框之防振器，其， 設有防振彈簧與吸振系統且是懸吊外槽。此吸振系統主要 包含支撐桿穿過之滑動缸，與滑動缸的內表面接觸且設在 支撐桿的下端之滑動件次組合，以及滑動缸的內表面與滑 動件次組合之間之防振彈簧。習知防振具有參個吸振元件 ，由滑動缸的內表面與滑動件次組合之間的接觸摩擦所造 成之摩擦吸振，由附在滑動件次組合上之潤滑油所造成之 黏性吸振及滑動缸與滑動件次組合之間的空間內發生之空 氣摩擦。這三個吸振作用可實現脫水旋轉的平順操作。 經濟部智慧財產局員工消費合作社印製 然而，於旋轉脫水的開始時，如果衣服集中於淸洗/ 脫水槽造成不平衡狀態，此些防振器無法阻止外槽振動。 尤其，當淸洗/脫水槽的旋轉頻率是通過等於物體的^然 頻率之頻率，也就是說，共振頻率，共振現象發生，其中 外槽大力地振動於垂直方向，且諸如外槽撞擊主體之問題 發生。 爲解決此共振現象的問題，吸振系統是需要具有高度 的吸振力。給定一個自由度的防振系統，振動傳遞率τ是 源自防振器的振輻X及外槽的振輻Ζ 〇如下。 (公式1 ) τ = ^ + (2ζω)2}/^1 - ω2)2 + (2ζω)7} () 本紙張尺度適用中國國家標準（CNS ) A4規格（210X 297公釐） -4 - 517124 A 7 __B7_ 五、發明説明（2 ) (請先閱讀背面之注意事項再填寫本頁) (r :振動傳遞率，％ :滑動缸與滑動件次組合之間 的相對振輻，Z。：外槽的振輻，Γ :吸振比，ω :淸洗/ 脫水槽的旋轉頻率） 自公式（1 )，圖9顯示淸洗/脫水槽ω的振動傳遞 率對旋轉頻率的特性曲線，用於表示吸振力的程度之不同 吸振比。特性曲線2 7是用於較低的吸振比Γ，而曲線 2 8是用於較高的吸振比（。 爲降低由於共振現象之問題，相似的振動傳遞率r是 需要在共振旋轉頻率2 9。因此，用於較高的吸振比Γ之 特性曲線2 8可預期在共振頻率2 9。另一方面，外框的 較小振動是需要在淸洗/脫水槽的較高的旋轉頻率ω。因 此，用於較低的吸振比Γ之特性曲線2 7可預期在固定頻 率3 0。也就是說，理想的Γ應變化致使較高在振動系統 的共振旋轉頻率2 9附近之淸洗/脫水槽的旋轉頻率ω， 而較低在超過振動系統的共振頻率2 9之旋轉頻率ω。 經濟部智慧財產局員工消費合作社印製 於習知的防振器中，彈簧機構包含兩個主要元件於吸 振系統中，一者是滑動缸的內表面與滑動件次組合之間的 防振彈簧，而另一者是由滑動缸與滑動件次組合之間的空 氣壓力所造成之空氣彈簧。尤其，空氣彈簧具有隨著淸洗 /脫水槽ω的旋轉頻率的增加而增加之彈簧常數，如圖 1 0所示之特性曲線3 1。此增加的整個防振器的彈簧常 數致使吸振現象發生且外框振動增加在淸洗/脫水槽的較 高的旋轉頻率。 爲解決以上問題，某些解決方法已被提供用於防振器 本紙張尺度適用中國國家標準（CNS ) Α4規格（210Χ 297公釐） -5- 517124 A7 B7 五、發明説明（3) (請先閱讀背面之注意事項再填寫本頁) 。.例如，檢測淸洗/脫水槽的旋轉頻率或驅動螞或檢測洗 衣機主體的振動在旋轉脫水操作上之即時判斷，附加電磁 石與類似物在防振器上爲了吸振力的可變化控制，以及配 置額外的驅動馬達爲了空氣室的開/關控制。 發明槪述 於此種防振器中，這是容易檢測淸洗/脫水槽的旋轉 頻率以判斷共振現象是否發生於旋轉脫水操作。然而，這 是困難去傳輸正確信號與.旋轉頻率的檢測信號至電磁石及 類似物用於吸振力的可變化控制，因爲防振器隨時垂直且 水平地振動於旋轉脫水操作時。於空氣室的開/關控制， 這亦困難去傳輸正確信號與檢測信號至驅動馬達。這亦困 難去實現可開/關空氣室之此種機構。於此兩者例子中， 許多附加部件亦是需要，使得於脫水的開始時，如果衣服 離心聚集於淸洗/脫水槽中且不平衡狀態使外槽撞擊外框 ，諸如可能發生作用錯誤之任何問題。 經濟部智慧財產局員工消費合作社印製 因此，本發明的目的在於提供一種洗衣機之防振裝置 ，其具有簡單結構，且不需要諸如旋轉頻率的檢測之任何 電控制以具有較高總共吸振比在不超過共振旋轉頻率之淸 洗/脫水槽的旋轉頻率爲了由共振現象所造成之問題的降 低，且具有較低總共吸振比在超過共振旋轉頻率之旋轉頻 率，以及減少由空氣壓力所造成之空氣彈簧發生，使得主 體的振動以及噪音可被減小。 爲解決上述問題，申請專利範圍第1項的本發明包含 本纸張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） -6- 517124 A7 B7 五、發明説明（4 ) (請先閲讀背面之注意事項再填寫本頁) ··.支撐桿，自主體的上部支撐淸洗/脫水槽與裝水用之外 槽；滑動缸，支撐桿穿過此滑動缸；及滑動件，經由防振 彈簧的配置在支撐桿的下端，滑動件是與滑動缸的內表面 接觸且能夠垂直地振動，其中防振器另包含：防振管，配 置在防振彈簧的外緣上；及環形彈簧，配置在滑動件的下 內表面上，以彈力使滑動件與滑動缸的內表面接觸，滑動 件具有穿過滑動件進入滑動缸之氣孔。 申請專利範圍第2項的本發明是依據申請專利範圍第 1項之發明，其中防振彈簧與防振管之間發生的摩擦，及 具有環形彈簧的滑動缸與被使用作爲吸振作用之滑動件之 間發生的摩擦。 申請專利範圍第3項的本發明是依據申請專利範圍第 1項之發明，其中滑動件上之氣孔上具有適於消除在淸洗 /脫水槽的較高旋轉之空氣吸振作用之區域。 申s靑專利範圍第4項的本發明是依據申請專利範圍第 1項之發明，其中潤滑油是配置於滑動件與滑動缸之間。 經濟部智慧財產苟員工消費合作钍印製 申請專利範圍第5項的本發明是依據申請專利範圍第 1項之發明，其中在等於振動系統的自然頻率之淸洗/脫 水槽的旋轉頻率，摩擦、黏性及空氣吸振比之間的比例爲 空氣吸振比是小於2，以及摩擦與黏性吸振比的總和是等 於或大於8。 具有足夠乾摩擦之振動系統將被考慮。首先，一般振 動系統之運動公式說明於以下的公式（2)。 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） 517124 A 7 B7 五、發明説明（5) (.公式2 ) mX+ci+lcZ^A,sina>f (2) (請先閱讀背面之注意事項再填寫本頁) (其中P Q :外槽次組合上之等效振動力，％ :滑動缸 與滑動件次組合之間的相對振輻，^ :滑動缸與滑動件次 組合之間的相對速度，X :滑動缸與滑動件部件之間的相 對加速度，m :外槽次組合上之質量，c :吸振分量’ k :彈簧常數） 自然頻率是說明於以下的公式（3)。 (M3) nr ⑶ = Vm 吸振比Γ是說明於以下的公式（4 )。 (公式4 ) ζ = ⑷ 以上公式（2 ) 、（ 3 )及（4 )被展開且吸振常數 經濟部智慧財產局員工消費合作社印製 c與吸振比Γ之間的關係可被說明於以下的公式（5 )。 (公式5 ) c = 2ζ · π\ωη (5) 次者，具有足夠乾摩擦的振動系統之運動公式是說明 於以下的公式（6 )。 (公式6 ) ιηχ+lri 士ft dntti (6) 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） -8- 517124 A7 B7 五、發明説明（6 ) (其中F c :乾摩擦） (請先閱讀背面之注意事項再填寫本頁} 於公式（6 )中，乾摩擦F c造成吸振力的固定量。 然而吸振力的方向依外槽上的等效振動力P ◦的方向而定。 乾摩擦F c可以其等效黏性吸振而代替，亦即，等效黏性 吸振係數C e。等效黏性吸振係數C e可藉由假設由乾摩 擦於振動的一個循環所發生的能量等於由黏性吸振所發生 的能量而獲得。 由乾摩擦於一個循環所發生的能量是4 % q F c。所以 此發生的能量與等效吸振之間的關係是說明於以下的公式 (7 )。 (公式7 ) 45C〇Fc = π〇：βωχ。2 ⑺ 因此，自以上公式（7)中，等於乾摩擦F c之等效 黏性吸振係數C e可獲得如以下的公式（8 )。 (公式8 ) πωχ0 經濟部智慧財產局員工消費合作社印製 以乾摩擦F c，吸振比Γ可自公式（5 )與（8 )說 明於以下的公式（9 )。 (公式9 ) ,„ 2Fc (9) ζ 一 ~~ πωχ0 · ιαω 因此，於具有乾摩擦F c之振動系統中，吸振比（主 要地依淸洗/脫水槽ω的旋轉頻率而定。自公式（1 )與 本紙張尺度適用中國國家標準（CNS ) Α4規格（210X297公釐） -9 - 517124 A7 B7 五、發明説明（7) .(.9 )，圖1 1顯示乾摩擦F c的例子中之振動傳遞率τ 與淸洗/脫水槽的旋轉頻率之間的關係之特性曲線3 2。 (請先閱讀背面之注意事項再填寫本頁) 再者，爲了降低來自空氣彈簧在淸洗/脫水槽r的較 高旋轉頻率之問題，由空氣所造成的吸振作用儘可能地降 低。也就是說，整個防振器的彈簧常數被抑制不增大使得 吸振現象可被消除在淸洗/脫水槽r的較高旋轉頻率。 依據本發明，滑動件次組合設有穿過次組合進入滑動 缸的內側之通道，以使空氣可有效地流動於外側與滑動缸 及滑動件次組合內的空間之間，致使空氣吸振力可被減小 。再者，爲了形成大部份由摩擦與黏性造成之吸振作用， 防振彈簧的外周是設有防振管，且滑動件次組合的下內表 面是設有環形彈簧，使得摩擦與黏性力可被增大。因此， 在共振頻率的吸振元件之間的比例致使空氣吸振比是不小 於2而摩擦與黏性吸振比的總和是等於或高於8。 經濟部智慧財產局員工消費合作社印製 於此種架構中，較高吸振比可被獲得用於淸洗/脫水 槽的旋轉頻率，其不會超過共振點。因此，於旋轉脫水操 作時，在衣服偏心聚集之不平衡狀態下，這是可能減小由 共振現象所造成的外槽的垂直振輻。 較低吸振比亦可被獲得用於超過共振點之槽的旋轉頻 率，使得可能地減小主體的振動以及噪音。 圖式簡單說明 現在將參考加註的圖式經由非限制性示範實施例之更 進一步的詳細說明本發明，其中相同參考數字代表相似部 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） -10- 517124 A7 __B7 五、發明説明（8) 件於所有的圖式中，且其中： (請先閱讀背面之注意事項再填寫本頁) 圖1顯示依據本發明實施例的完全自動洗衣機的橫截 面圖。 圖2顯示依據本發明之防振器的橫截面圖。 圖3顯示依據本發明之環形彈簧的前視圖。 圖4顯示依據本發明之環形彈簧的側視圖。 圖5顯示依據本發明之防振器的底視圖。 圖6顯示依據本發明之防振器的吸振比變化特性的實 施例。 圖7顯示依據本發明之滑動件及其周圍的放大圖。 圖8顯示依據本發明之吸振比對空氣流入/流出所經 過之區域的變化特性。 圖9顯示依據本發明之不同吸振比之振動傳遞率對旋 轉頻率的特性。 圖1 0顯示依據本發明之空氣彈簧常數對旋轉頻率的 特性。 經濟部智慧財產局員工消費合作社印製 Η 1 1顯示乾摩擦的不同的等效吸振比之振動傳遞率 對旋轉頻率的變化特性。 主要元件對照表 1 鋼片外框 2 支撐桿 3 防振器 4 合成樹脂外槽 本纸張尺度適用中國國家標準（CNS ) Α4規格（210X29*7公釐） -11 - 517124 A7 B7 五、發明説明（9) 5 6 7 811121314 經濟部智慧財產局員工消費合作社印製 161717 18 2 0 2 1 2 2 2 3 2 4 2 5 2 6 2 7 2 8 2 9 3 0 16b 淸洗/脫水槽 攪拌葉片 合成樹脂上蓋 合成樹脂蓋 防振彈簧 滑動缸 滑動件 防振管 環形彈簧 氣孔 狹縫 凸緣 黏性滑油 變化特性曲線 共振頻率 高吸振比 固定頻率 低吸振比 曲線 曲線 特性曲線 曲線 共振旋轉頻率 固定頻率 (請先閲讀背面之注意事項再填寫本頁) 本紙張尺度適用中國國家標準（CNS ) A4規格（210X 297公釐） -12- 517124 A7 B7 五、發明説明（ι〇) 3 1 特性曲線 3 2 特性曲線 (請先閱讀背面之注意事項#填寫本頁) 較佳實施例說明 以下將參考附圖說明本發明的實施例。圖1顯示如應 用依據本發明的防振器之洗衣機的實施例之完全自動洗衣 機的橫截面圖。洗衣機具有鋼片外框1 ，其中配置有四個 支撐桿2與防振器3。桿2與防振器3懸吊用以容納淸潔 水之合成樹脂外槽4。 由合成樹脂製成之淸洗/脫水槽5是旋轉地配置外槽 4內。諸如脈動器或攪拌器之攪拌葉片6是可旋轉地配置 在淸洗/脫水槽5的底部的中心。於淸潔或洗濯的操作中 ，淸洗/脫水槽5是停止且攪拌葉片6是以順時鐘及逆時 鐘而旋轉。於旋轉旋轉脫水操作中，淸洗/脫水槽5是旋 轉於單一方向。外槽1的上部是設有具有合成樹脂蓋8於 其上之合成樹脂上蓋7。 經濟部智慧財產笱員工消費合作社印說 圖2顯示依據本發明之防振器的橫截面圖。防振器3 具有滑動件1 3設在支撐桿2的下端，及防振彈簧1 1設 在桿2周圍，此桿是位於彈簧1 1的中心。滑動件1 3與 彈簧1 1兩者穿過防振器3。滑動缸1 2是配置在位於缸 1 2中心的桿2周圍，且包圍滑動件1 3與防振彈簧1 1 。滑動件1 3是與滑動缸1 2的內表面接觸，使得摩擦阻 抗可引起於共振現象發生時。防振彈簧1 1的外緣設有以 橡膠或不硬的聚氯乙烯製成之防振管1 4，使得因爲防振 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） -13- 517124 A7 B7 五、發明説明（11) 彈簧1 1的垂直振動之摩擦阻抗可上昇於共振現象發生時 時。 (請先閱讀背面之注意事項再填寫本頁) 圖3與圖4分別顯示依據本發明之環形彈簧1 5的前 視與側視圖。環形彈簧1 5是以圓形鋼絲而製成，且附在 滑動件1 3的下內表面上。在結合入防振器3之前環形彈 簧1 5的外徑是大於設有狹縫1 7之滑動件1 3的下部的 內徑。滑動件1 3的下部具有數個狹縫1 7，諸如六個狹 縫，以強化環形彈簧1 5的彈簧力且使此彈簧力均勻沿著 整個內徑。環形彈簧1 5的彈簧力使滑動件1 3與滑動缸 1 2的內表面接觸。如圖5所示，在滑動件1 3的底部， 各狹縫1 7具有凸緣1 7 a在其中心以防止環形彈簧1 5 脫離位置於滑動件1 3的垂直動作時。這些凸緣1 7 a限 制滑動件1 3與環形彈簧1 5之間的位移，使得均勻摩擦 力可被獲得。 經濟部智慧財產局員工消費合作社印製 結合入防振器3之環形彈簧1 5可產生彈簧力，其可 加入狹縫1 7的外徑以及滑動件1 3的下部。因此，大摩 擦力可獲得在滑動缸1 2與狹縫1 7之間。滑動件1 3亦 設有氣孔1 6 a、1 6 b，經由此氣孔，由滑動件1 3與 滑動缸1 2所界定的空間內之空氣可輕易地流入/流出。 滑動缸1 2較佳地是以高化動性能的聚乙烯而製成以 防止與滑動件1 3的摩擦，以及由於外槽4的振動之變形 。滑動件1 3較佳地是以聚乙烯對苯二酸脂製成以防止由 於與滑動件1 3的接觸摩擦之磨損。黏性滑油1 8被提供 在滑動件1 3與滑動缸1 2之間以獲得黏力在兩者構件之 本纸張尺度適用中國國家標準（CNS ) A4規格（210Χ297公釐） -14 - 517124 A7 B7 五、發明説明（12) 間的接觸部份，且防止由於兩者構件之間的摩擦之變形及 類似現象。 (請先閱讀背面之注意事項再填寫本頁) 圖6顯示依據本發明用以防振器3之淸洗/脫水槽5 的吸振比Γ對旋轉頻率的變化特性的實施例。變化特性曲 線2 0顯示在共振頻率2 1之較高的吸振比2 2，超過共 振頻率2 1逐漸地減小之吸振比Γ，及在固定頻率2 3之 較低的吸振比2 4。變化特性曲線2 0中吸振比Γ的値是 0 · 5 6的吸振比2 2在共振頻率2 1 ，0 · 1 4的吸振 比24在固定頻率23。 圖7顯示依據本發明之防振器3的滑動件1 3與其周 圍的放大圖。於圖7中，各組件具有如圖2之相同名稱與 參考數字，所以各組件的說明被省略。滑動件1 3的氣孔 .1 6 a、1 6 b必要作爲空氣吸振，當此頻綠通過共振頻 率21時。氣孔16a、16b亦是必要具有足夠降低在 固定頻率2 3中之空氣彈簧作用之區域。四個支撐桿2具 有兩對相對的桿2爲了均勻地流出滑動缸1 2與滑動件 1 3內的空氣。 經濟部智慧財產局P'工消費合作社印复 圖8顯示氣孔1 6 a、1 6 b的吸振比Γ對開口區域 的變化特性的實施例，經由此氣孔，滑動件1 3與滑動缸 1 2內之空氣流入/流出在共振頻率與固定頻率時。開口 區域與在共振頻率21之吸振比Γ之間之關係參考在固定 頻率之曲線2 1。開口區域與在固定頻率2 3之吸振比Γ 之間之關係參考在共振頻率之曲線2 5。曲線2 5的吸振 比Γ具有逐漸減小的特性因爲開口區域的增大及超過開口 本纸張尺度適用中國國家標準（CNS ) A4規格（210X 297公釐) -15- 517124 A7 B7 五、發明説明（13) 區域S 3的突然減小。曲線2 6的吸振比Γ具有突然減小 的特性因爲開口區域的增大及超過開口區域S 1之較低率 的減小。 因此，滑動件1 3的氣、1 6 b的開口區域 是較佳地設定在S 1與S 3 -之間使氣孔1 6 a、 1 6 b保持具有淸洗/脫水槽5 振頻率2 1的頻率之 空氣吸振的功效，以降低吸振功效及空氣彈簧作用在固定 頻率2 3的問題。本發明的各氣孔具有0 2的區域，且此 兩孔的總開口區域是6 · 2 8腿2。 依據本發明，甚至當脫水旋轉操作被實施在衣服聚集 於淸洗/脫水槽中之狀態下時，其可能地防止由於共振現 象之外槽的振動，且減少外槽撞擊外框或上蓋之問題。再 者固定旋轉中之外槽的振動不會傳送至支撐桿，使得主體 的振動以及振動時之噪音可被減小。 (請先閱讀背面之注意事項再填寫本頁) 經濟部智慧財產笱員工消費合作社印髮 本纸張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） -16-517124 A7 ___ B7____ V. Description of the invention (1) Development. Bright background (Please read the precautions on the back before filling out this page) The present invention relates to a vibration-proof device for a washing machine, the outer groove of which is supported on the outer frame. The conventional washing machine includes a vibration isolator with an outer frame holding a support rod. The vibration isolator is provided with an anti-vibration spring and a vibration absorption system and is a suspension outer tank. This vibration absorbing system mainly includes a sliding cylinder through which the support rod passes, a sliding member combination that is in contact with the inner surface of the sliding cylinder and is provided at the lower end of the supporting rod, and a vibration-proof spring between the inner surface of the sliding cylinder and the sliding member combination. . The conventional anti-vibration has various vibration absorbing elements, frictional vibration absorption caused by the contact friction between the inner surface of the sliding cylinder and the slider subassembly, and viscous vibration absorption and sliding caused by the lubricant attached to the slider subassembly. Air friction occurs in the space between the cylinder and the subassembly of the slider. These three vibration-absorbing effects enable smooth operation of dewatering rotation. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs. However, at the beginning of spin dehydration, if the clothes are concentrated in the washing / dehydration tank and cause an imbalance, these vibration isolators cannot stop the outer tank from vibrating. In particular, when the rotation frequency of the washing / dewatering tank passes a frequency equal to the natural frequency of the object, that is, the resonance frequency, a resonance phenomenon occurs, in which the outer tank vibrates vigorously in the vertical direction, and such as the outer tank hits the main body. The problem occurred. In order to solve the problem of resonance phenomenon, the vibration absorbing system needs to have a high vibration absorbing force. Given a degree of freedom of the vibration isolation system, the vibration transmission rate τ is derived from the vibration X of the vibration isolator and the radiation Z of the outer groove as follows. (Formula 1) τ = ^ + (2ζω) 2} / ^ 1-ω2) 2 + (2ζω) 7} () This paper size applies the Chinese National Standard (CNS) A4 specification (210X 297 mm) -4-517124 A 7 __B7_ V. Description of the invention (2) (Please read the precautions on the back before filling this page) (r: Vibration transmission rate,%: Relative vibration between the sub-assembly of the sliding cylinder and the sliding member, Z .: Outer The vibration amplitude of the tank, Γ: the vibration absorption ratio, ω: the rotation frequency of the washing / dewatering tank) From the formula (1), FIG. 9 shows the characteristic curve of the vibration transmission rate of the washing / dewatering tank against the rotation frequency. The degree of vibration absorption force varies with the ratio of vibration absorption. The characteristic curve 27 is used for a lower vibration absorption ratio Γ, and the curve 28 is used for a higher vibration absorption ratio (. In order to reduce the problem due to resonance phenomenon, a similar vibration transmission rate r is required at the resonance rotation frequency 2 9 Therefore, a characteristic curve 28 for a higher vibration absorption ratio Γ can be expected at a resonance frequency of 29. On the other hand, a smaller vibration of the outer frame is required for a higher rotation frequency ω in the washing / dehydration tank. Therefore, the characteristic curve 27 for a lower vibration absorption ratio Γ can be expected at a fixed frequency 30. That is, the ideal Γ should be changed to cause higher washing / desorption near the resonance rotation frequency 2 9 of the vibration system The rotation frequency ω of the water tank is lower than the rotation frequency ω which exceeds the resonance frequency of the vibration system 29. The consumer cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs printed the conventional vibration isolator. The spring mechanism contains two main components: In the vibration absorption system, one is an anti-vibration spring between the inner surface of the sliding cylinder and the slider sub-assembly, and the other is an air spring caused by the air pressure between the sliding cylinder and the slider sub-assembly. In particular, The air spring has The spring constant that increases with the increase of the rotation frequency of the washing / dehydration tank ω is shown in the characteristic curve 31 shown in Fig. 10. This increased spring constant of the entire vibration isolator causes the vibration absorption phenomenon to occur and the frame vibration to increase. The higher rotation frequency of the washing / dewatering tank. In order to solve the above problems, some solutions have been provided for the vibration isolator. The paper size is applicable to the Chinese National Standard (CNS) A4 specification (210 × 297 mm) -5- 517124 A7 B7 V. Description of the invention (3) (Please read the precautions on the back before filling out this page) .. For example, to detect the rotation frequency of the washing / dehydration tank or drive the worm or detect the vibration of the washing machine body in the spin dehydration operation Judging immediately, additional magnets and the like are used on the vibration isolator for variable control of the vibration absorption force, and an additional drive motor is provided for the on / off control of the air chamber. The invention is described in this type of vibration isolator, which is It is easy to detect the rotation frequency of the washing / dehydration tank to determine whether the resonance phenomenon occurs in the spin dehydration operation. However, it is difficult to transmit the correct signal and the detection signal of the rotation frequency to the electromagnetic Stone and the like are used for variable control of the vibration absorption force, because the vibration isolator vibrates vertically and horizontally at any time during the spin-drying operation. On / off control of the air chamber, it is also difficult to transmit the correct signal and detection signal to the drive Motor. It is also difficult to realize such a mechanism that can open / close the air chamber. In the two examples, many additional components are also needed, so that at the beginning of dehydration, if clothes are collected in the washing / dehydration tank by centrifugation And the imbalanced state causes the outer tank to hit the outer frame, such as any problems that may occur. It is printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economics. Therefore, the object of the present invention is to provide a vibration-proof device for a washing machine, which has a simple structure. And does not require any electrical control such as the detection of the rotation frequency to have a higher total vibration absorption ratio. The rotation frequency of the rinsing / dehydration tank which does not exceed the resonance rotation frequency is to reduce the problems caused by the resonance phenomenon and has a lower total The vibration absorption ratio is at a rotation frequency exceeding the resonance rotation frequency, and to reduce the occurrence of air springs caused by air pressure, Winners body, vibration and noise can be reduced. In order to solve the above-mentioned problems, the invention of item 1 of the patent application scope includes the paper size applicable to the Chinese National Standard (CNS) A4 specification (210X297 mm) -6- 517124 A7 B7 V. Description of the invention (4) (Please read first Note on the back, please fill in this page again.) ··. The support bar supports the washing / dewatering tank and the outer tank for water from the upper part of the body; the sliding cylinder, the supporting rod passes through this sliding cylinder; The vibration spring is arranged at the lower end of the support rod. The slider is in contact with the inner surface of the sliding cylinder and can vibrate vertically. The vibration isolator further includes: a vibration tube arranged on the outer edge of the vibration spring; and a ring spring. Is arranged on the lower inner surface of the sliding member, and the sliding member is brought into contact with the inner surface of the sliding cylinder by elastic force, and the sliding member has an air hole passing through the sliding member and entering the sliding cylinder. The invention according to item 2 of the scope of patent application is the invention according to item 1 of the scope of patent application, in which the friction between the anti-vibration spring and the anti-vibration tube, the sliding cylinder with a ring spring and the sliding member used as a vibration absorbing effect The friction that occurred between. The invention of claim 3 is based on the invention of claim 1, wherein the air holes on the sliding member have a region suitable for eliminating the air vibration absorbing effect of the higher rotation in the washing / dehydration tank. The invention claimed in item 4 of the scope of patent is based on the invention in item 1 of the scope of patent application, in which the lubricating oil is arranged between the sliding member and the sliding cylinder. The Intellectual Property of the Ministry of Economic Affairs and the Consumers' Co-operation of Consumers printed the invention in the scope of patent application No. 5 according to the invention in the scope of patent application No. 1, in which the rotation frequency of the washing / dehydration tank at the frequency equal to the natural frequency of the vibration system, friction The ratio between the viscosity and the air vibration absorption ratio is that the air vibration absorption ratio is less than 2 and the sum of the friction and the viscous vibration absorption ratio is equal to or greater than 8. Vibration systems with sufficient dry friction will be considered. First, the motion formula of the general vibration system is described in the following formula (2). This paper size applies the Chinese National Standard (CNS) A4 specification (210X297 mm) 517124 A 7 B7 V. Description of the invention (5) (.Formula 2) mX + ci + lcZ ^ A, sina > f (2) (please first Read the notes on the back and fill in this page) (where PQ: equivalent vibration force on the outer groove combination,%: relative vibration between the sliding cylinder and the slider combination, ^: the sliding cylinder and the slider combination Relative speed between the two, X: relative acceleration between the sliding cylinder and the slider part, m: mass on the combination of outer groove times, c: vibration absorption component 'k: spring constant) The natural frequency is described in the following formula (3 ). (M3) nr ⑶ = Vm The vibration absorption ratio Γ is described in the following formula (4). (Equation 4) ζ = ⑷ The above equations (2), (3), and (4) are expanded and the vibration absorption constant is printed by c and the vibration absorption ratio Γ, which is printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs. Formula (5). (Equation 5) c = 2ζ · π \ ωη (5) times, the motion formula of the vibration system with sufficient dry friction is described in the following formula (6). (Formula 6) ιηχ + lri ft dntti (6) This paper size is applicable to Chinese National Standard (CNS) A4 specification (210X297 mm) -8- 517124 A7 B7 V. Description of the invention (6) (where F c: dry friction ) (Please read the precautions on the back before filling this page} In formula (6), the dry friction F c causes a fixed amount of vibration absorption force. However, the direction of the vibration absorption force depends on the equivalent vibration force P on the outer groove. The dry friction F c can be replaced by its equivalent viscous vibration absorption, that is, the equivalent viscous vibration absorption coefficient C e. The equivalent viscous vibration absorption coefficient C e can be assumed by a cycle of dry friction to vibration The energy generated is equal to the energy generated by viscous vibration absorption. The energy generated by dry friction in a cycle is 4% q F c. So the relationship between the energy generated and the equivalent vibration absorption is explained below Formula (7). (Formula 7) 45C〇Fc = π〇: βωχ. 2 ⑺ Therefore, from the above formula (7), the equivalent viscous vibration absorption coefficient C e equal to the dry friction F c can be obtained as the following formula (8). (Formula 8) πωχ0 Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs With dry friction F c, the vibration absorption ratio Γ can be described from formulas (5) and (8) in the following formula (9). (Formula 9), 2Fc (9) ζ 1 ~~ πωχ0 · ιαω In the vibration system of friction F c, the vibration absorption ratio (mainly depends on the rotation frequency of the washing / dewatering tank ω. From the formula (1) and this paper size, the Chinese National Standard (CNS) Α4 specification (210X297 mm)- 9-517124 A7 B7 V. Description of the invention (7). (.9), Figure 1 1 shows the characteristic curve of the relationship between the vibration transmission rate τ and the rotation frequency of the washing / dehydration tank in the example of dry friction F c 3 2. (Please read the precautions on the back before filling in this page) Furthermore, in order to reduce the problem of the high rotation frequency of the air spring in the washing / dehydration tank r, the vibration absorbing effect caused by air is reduced as much as possible In other words, the spring constant of the entire vibration isolator is suppressed and does not increase, so that the vibration absorption phenomenon can be eliminated at the higher rotation frequency of the washing / dehydration tank r. According to the present invention, the slide sub-assembly is provided with a pass-through sub-assembly Access to the inside of the sliding cylinder for efficient air flow Between the outside and the space inside the sliding cylinder and the sliding subassembly, the air vibration absorbing force can be reduced. Furthermore, in order to form most of the vibration absorbing effect caused by friction and viscosity, the outer periphery of the anti-vibration spring is designed There is an anti-vibration tube, and the lower inner surface of the subassembly of the sliding member is provided with a ring spring, so that friction and viscous force can be increased. Therefore, the ratio between the vibration absorbing elements at the resonance frequency causes the air vibration absorbing ratio to be not less than 2 and the sum of friction and viscous vibration absorption ratio is equal to or higher than 8. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs In this structure, a higher vibration absorption ratio can be obtained for the rotation frequency of the washing / dewatering tank, which does not exceed the resonance point. Therefore, during the spin-drying operation, it is possible to reduce the vertical vibration of the outer groove caused by the resonance phenomenon in the unbalanced state where the clothes are eccentrically gathered. A lower vibration absorption ratio can also be obtained for the rotation frequency of the groove beyond the resonance point, making it possible to reduce the vibration and noise of the main body. Brief Description of the Drawings The present invention will now be described in further detail with reference to the attached drawings through non-limiting exemplary embodiments, in which the same reference numerals represent similar parts. This paper size applies the Chinese National Standard (CNS) A4 specification (210X297). (Centi) -10- 517124 A7 __B7 V. Description of the invention (8) In all the drawings, and among them: (Please read the notes on the back before filling this page) Figure 1 shows the fully automatic according to the embodiment of the present invention Cross-section view of a washing machine. Fig. 2 shows a cross-sectional view of a vibration isolator according to the present invention. Figure 3 shows a front view of a ring spring according to the invention. Figure 4 shows a side view of a ring spring according to the invention. Fig. 5 shows a bottom view of a vibration isolator according to the present invention. Fig. 6 shows an embodiment of the change characteristics of the vibration absorbing ratio of the vibration isolator according to the present invention. FIG. 7 shows an enlarged view of a sliding member and its surroundings according to the present invention. Fig. 8 shows the change characteristics of the vibration absorption ratio according to the present invention over the area through which air flows in / out. Fig. 9 shows the characteristics of the vibration transmission rate versus the rotation frequency according to the different vibration absorbing ratios of the present invention. Fig. 10 shows the characteristics of the air spring constant versus the rotation frequency according to the present invention. Printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs 1 1 1 Shows the change characteristics of the vibration transmission rate versus the rotation frequency with different equivalent vibration absorption ratios of dry friction. Comparison table of main components 1 Steel frame 2 Support rod 3 Vibration isolator 4 Synthetic resin outer groove The paper size is applicable to Chinese National Standard (CNS) A4 specification (210X29 * 7 mm) -11-517124 A7 B7 V. Invention Instructions (9) 5 6 7 811121314 Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs 161717 18 2 0 2 1 2 2 2 3 2 4 2 5 2 6 2 7 2 8 2 9 3 0 16b Synthetic resin cover Synthetic resin cover Anti-vibration spring Slide cylinder Slider Anti-vibration tube Ring spring Pore slit Flange Viscosity oil Change characteristic curve Resonant frequency High vibration absorption ratio Fixed frequency Low vibration absorption curve Curve characteristic curve Resonance rotation frequency Fixed frequency (Please read the precautions on the back before filling this page) This paper size is applicable to Chinese National Standard (CNS) A4 specification (210X 297 mm) -12- 517124 A7 B7 V. Description of the invention (ι〇) 3 1 Characteristic curve 3 2 Characteristic curve (please read the note on the back first # Fill this page) Description of the preferred embodiments The embodiments of the present invention will be described below with reference to the drawings. Fig. 1 shows a cross-sectional view of a fully automatic washing machine as an embodiment of a washing machine to which a shock absorber according to the present invention is applied. The washing machine has a steel sheet frame 1 in which four supporting rods 2 and a vibration isolator 3 are arranged. The rod 2 and the vibration isolator 3 are suspended to receive a synthetic resin outer groove 4 for cleaning water. The washing / dewatering tank 5 made of synthetic resin is arranged inside the outer tank 4 in a rotating manner. A stirring blade 6 such as a pulsator or a stirrer is rotatably disposed at the center of the bottom of the washing / dewatering tank 5. In the cleaning or washing operation, the washing / dewatering tank 5 is stopped and the stirring blade 6 is rotated clockwise and counterclockwise. In the rotary spin-drying operation, the rinsing / dewatering tank 5 is rotated in a single direction. The upper part of the outer tank 1 is provided with a synthetic resin upper cover 7 having a synthetic resin cover 8 thereon. Printed by the Ministry of Economic Affairs, Intellectual Property and Employee Consumer Cooperatives Figure 2 shows a cross-sectional view of a vibration isolator according to the present invention. The vibration isolator 3 has a sliding member 13 provided at the lower end of the support rod 2, and a vibration-proof spring 11 is provided around the rod 2. The rod is located at the center of the spring 11. Both the slider 13 and the spring 1 1 pass through the vibration isolator 3. The slide cylinder 12 is arranged around the rod 2 located at the center of the cylinder 12 and surrounds the slider 13 and the anti-vibration spring 1 1. The sliding member 13 is in contact with the inner surface of the sliding cylinder 12 so that the frictional impedance can be caused when a resonance phenomenon occurs. The outer edge of the anti-vibration spring 1 1 is provided with an anti-vibration tube 1 4 made of rubber or non-hard polyvinyl chloride, so that the paper size of the anti-vibration paper applies the Chinese National Standard (CNS) A4 specification (210X297 mm)- 13- 517124 A7 B7 V. Description of the invention (11) The frictional impedance of the vertical vibration of the spring 11 can be increased when the resonance phenomenon occurs. (Please read the precautions on the back before filling out this page) Figures 3 and 4 show the front and side views of the ring spring 15 according to the present invention, respectively. The ring spring 15 is made of a circular steel wire and is attached to the lower inner surface of the slider 13. The outer diameter of the ring spring 15 before being incorporated into the vibration isolator 3 is larger than the inner diameter of the lower portion of the slider 13 provided with the slit 17. The lower part of the slider 13 has several slits 17 such as six slits to strengthen the spring force of the ring spring 15 and make this spring force evenly along the entire inner diameter. The spring force of the ring spring 15 brings the slider 13 into contact with the inner surface of the slide cylinder 12. As shown in FIG. 5, at the bottom of the slider 13, each slit 17 has a flange 17 a at its center to prevent the ring spring 15 from disengaging from the position when the slider 13 is vertically moved. These flanges 17a limit the displacement between the slider 13 and the ring spring 15 so that a uniform frictional force can be obtained. Printed by the Consumer Cooperative of the Intellectual Property Bureau of the Ministry of Economic Affairs The ring spring 15 incorporated in the vibration isolator 3 can generate a spring force, which can be added to the outer diameter of the slit 17 and the lower part of the slider 13. Therefore, a large frictional force can be obtained between the slide cylinder 12 and the slit 17. The sliding member 13 is also provided with air holes 16 a and 16 b. Through this air hole, the air in the space defined by the sliding member 13 and the sliding cylinder 12 can easily flow in / out. The sliding cylinder 12 is preferably made of polyethylene with high dynamic performance to prevent friction with the sliding member 13 and deformation due to vibration of the outer groove 4. The slider 13 is preferably made of polyethylene terephthalate to prevent abrasion due to contact friction with the slider 13. Viscosity oil 18 is provided between the sliding member 13 and the sliding cylinder 12 to obtain the adhesive force. The paper size of the two components is applicable to the Chinese National Standard (CNS) A4 specification (210 × 297 mm) -14- 517124 A7 B7 5. Description of the invention (12) The contact part, and prevent deformation and similar phenomena due to friction between the two components. (Please read the precautions on the back before filling this page.) FIG. 6 shows an example of the variation characteristics of the vibration absorption ratio Γ of the vibration washer / dehydration tank 5 of the vibration isolator 3 with respect to the rotation frequency according to the present invention. The changing characteristic curve 20 shows a higher vibration absorption ratio 2 2 at the resonance frequency 21, a vibration absorption ratio Γ that gradually decreases beyond the resonance frequency 21, and a lower vibration absorption ratio 2 4 at a fixed frequency 23. In the variation characteristic curve 20, 値 of the vibration absorption ratio Γ is 0 · 5 6 and the vibration absorption ratio 2 2 is at the resonance frequency 2 1, and the vibration absorption ratio 24 of 0 · 1 4 is at the fixed frequency 23. Fig. 7 shows an enlarged view of the slider 13 and its surroundings of the vibration isolator 3 according to the present invention. In FIG. 7, each component has the same name and reference number as in FIG. 2, so the description of each component is omitted. The air holes .1 6 a and 16 b of the slider 1 3 must be used as air to absorb the vibration. When this frequency green passes the resonance frequency 21. The air holes 16a, 16b are also necessary to have an area sufficiently reducing the effect of the air spring in the fixed frequency 2 3. The four supporting rods 2 have two pairs of opposing rods 2 for uniformly flowing out the air in the sliding cylinder 12 and the sliding member 13. Printed by P'Industrial and Consumer Cooperatives of the Ministry of Economic Affairs of the People's Republic of China. Figure 8 shows an example of the change characteristics of the vibration absorption ratio Γ of the air holes 16 a and 16 b to the opening area. Through this air hole, the slider 13 and the slide cylinder 1 2 The inside air flows in / out at the resonance frequency and fixed frequency. The relationship between the open area and the vibration absorption ratio Γ at the resonance frequency 21 is referred to the curve 21 at a fixed frequency. The relationship between the opening area and the vibration absorption ratio Γ at the fixed frequency 2 3 is referred to the curve 25 at the resonance frequency. The vibration absorption ratio Γ of curve 25 has a gradually decreasing characteristic because the opening area increases and exceeds the opening. The paper size applies the Chinese National Standard (CNS) A4 specification (210X 297 mm) -15- 517124 A7 B7 V. Invention Explanation (13) The abrupt decrease of area S 3. The vibration absorption ratio Γ of the curve 26 has a characteristic of abrupt decrease because of the increase of the opening area and the decrease of the lower rate exceeding the opening area S1. Therefore, the opening area of the air and 16 b of the slider 1 3 is preferably set between S 1 and S 3-so that the air holes 1 6 a and 1 6 b keep the washing / dehydration tank 5 vibration frequency 2 1 The frequency of the air vibration absorption effect to reduce the vibration absorption effect and the air spring acting on the fixed frequency 2 3 problems. Each air hole of the present invention has an area of 0 2 and the total opening area of the two holes is 6 · 2 8 legs 2. According to the present invention, even when the spin-drying operation is performed in a state where the clothes are collected in the washing / dehydrating tank, it is possible to prevent the vibration of the tank outside due to the resonance phenomenon and reduce the problem that the outer tank hits the outer frame or the upper cover. . In addition, the vibration of the outer groove during the fixed rotation is not transmitted to the support rod, so that the vibration of the main body and the noise during the vibration can be reduced. (Please read the precautions on the back before filling out this page) Printed and issued by the Intellectual Property of the Ministry of Economic Affairs and the Employees' Cooperative Cooperative This paper size applies to China National Standard (CNS) A4 (210X297 mm) -16-