200942149 九、發明說明： 【發明所屬之技術領域】 本發明涉及一種散熱風扇，尤係涉及一種具有高潤滑 特性之散熱風扇。 【先前技術】 風扇是電腦散熱系統之一個關鍵組成部件，對提高風 扇之運行壽命、可靠性及保障電腦系統之穩定運行至關重 要。風扇軸承一般採用潤滑油潤滑’而習知風扇軸承之保 油效果一般不甚理想，隨著軸承内潤滑油之損耗，風扇轉 軸與軸承内壁之間之摩擦會相應增加，從而降低軸承之壽 命’進而減少風扇之使用壽命。 目前，本領域技術人貞主要是通過於散減扇之轴承 系統中導入保油結構，以達到增強軸承之潤滑和密封之效 果。如於軸承之上方設置一環形之擋油環，該擋油環與軸 承之間形成-儲油空間，擋油環之内緣與轉軸之外表面之 〇間形成間隙，以避免轉轴轉動時兩者之間之摩擦。工作時， =之部分潤滑油在離心力作用下沿轉軸向上運動，經 :诚衣阻# $集在儲油空間内，然後回流至軸承内，從 放之㊁漏:然而’該種結構之風扇-般只能在正 時，二、m、、二當具有該種結構之風扇側放與倒放使用 滑油之;二。沿著擋油環與轉軸之間之間隙流出，造成潤 【發明内容】 有鑒於此， 有必要提供一種在正放、側放與倒放使用 6 200942149200942149 IX. Description of the Invention: [Technical Field] The present invention relates to a heat dissipation fan, and more particularly to a heat dissipation fan having high lubrication characteristics. [Prior Art] A fan is a key component of a computer cooling system, which is essential for improving the operating life and reliability of the fan and ensuring the stable operation of the computer system. The fan bearing is generally lubricated with lubricating oil. The conventional oil retaining effect of the fan bearing is generally not ideal. As the lubricating oil in the bearing is lost, the friction between the fan rotating shaft and the inner wall of the bearing will increase accordingly, thereby reducing the life of the bearing. Thereby reducing the service life of the fan. At present, the skilled person in the art mainly introduces the oil retaining structure into the bearing system of the fan reduction to enhance the lubrication and sealing effect of the bearing. If an annular oil retaining ring is arranged above the bearing, an oil storage space is formed between the oil retaining ring and the bearing, and a gap is formed between the inner edge of the oil retaining ring and the outer surface of the rotating shaft to prevent the rotating shaft from rotating. The friction between the two. When working, some of the lubricating oil moves along the rotating axis under the action of centrifugal force. After the: Chengyi resistance # $ is collected in the oil storage space, and then flows back into the bearing, and leaks from the two: however, the fan of this structure - Generally only at the right time, two, m, and two when the fan with this kind of structure is placed on the side and inverted using the oil; Flowing along the gap between the oil retaining ring and the rotating shaft, causing lubrication [Invention] In view of this, it is necessary to provide a use in the front, side and reverse playback 6 200942149
一種散熱風扇，包括一扇框、一定子構件及一轉子構 件，該扇框包括一軸座及—收容於該轴座内之軸承，該軸 座從扇框之底部突設形成，該軸承之内部設有一軸孔，該 轉子構件具有一轉軸，該轉軸收容於該軸承内部之通孔 内，該定子構件套設於該軸座外緣，該轉軸上套設有一扣 環，該扣環固定於轴座頂端，所述扣環、轉軸與軸承共同 於軸承上方形成一儲油空間，該儲油空間内設有一儲油元 ^^件。 與習知技術相比，該風扇工作時，潤滑油在離心力作 用下沿轉軸向上運動，經扣環阻擋被聚集在儲油空間，被 儲油7C件吸收，然後渗透並回流至轴承内，無論該風扇為 正放、侧放或者倒放使用，該儲油元件吸收潤滑油可防止 被聚集在儲油空間内之潤滑油繼續沿轉轴外池，從而避免 潤滑油_，保證軸承和轉軸之間良好之潤滑性能，提高 ❹風扇之品質，大大延長風扇之使用壽命。 门 月多閱圖1至圖3’該散熱風扇包括-扇框1〇，一軸A cooling fan includes a frame, a certain sub-member and a rotor member, the frame includes a shaft seat and a bearing received in the shaft seat, the shaft seat is formed from a bottom of the fan frame, and the inside of the bearing a shaft hole is provided, the rotor member has a rotating shaft, the rotating shaft is received in the through hole of the bearing, the stator member is sleeved on the outer edge of the shaft seat, and the rotating shaft is sleeved with a buckle, and the buckle is fixed on the buckle The top end of the shaft seat, the buckle ring, the rotating shaft and the bearing form an oil storage space together with the bearing, and an oil storage unit is arranged in the oil storage space. Compared with the prior art, when the fan is in operation, the lubricating oil moves in the axial direction under the centrifugal force, and is blocked by the buckle ring to be collected in the oil storage space, absorbed by the oil storage 7C, and then infiltrated and returned to the bearing, regardless of The fan is used for forward, side or reverse. The oil absorbing element absorbs the lubricating oil to prevent the lubricating oil accumulated in the oil storage space from continuing along the outer shaft of the rotating shaft, thereby avoiding lubricating oil _, ensuring the relationship between the bearing and the rotating shaft Good lubrication performance, improve the quality of the fan, and greatly extend the service life of the fan. The door is more than 1 to 3'. The cooling fan includes - the fan frame 1〇, one axis
4〇對應設置於該定子構件30之外圍 構件30分別收容於扇框10内。 ^仟4U，該轉子構件 轉子構件40和定子The peripheral members 30 corresponding to the stator member 30 are housed in the frame 10, respectively. ^仟4U, the rotor member rotor member 40 and stator
扇框10包括__ 10之底部12中央向 其中央形成一收容空 200942149 座14頂端部分之内圓周處，並與收容空間142相連通。軸 ' 座14頂端於該環形凹陷144所在位置之内徑大於軸座14 ' 内部其餘部分之内徑。該扇框10之底部12中央從底面向 内凹陷形成一圓柱狀之收容槽120 (圖3)。該收容槽120 與軸座14内之收容空間142相對但不連通。 定子構件30包括一電路板31以及一由複數層矽鋼片 疊設形成之電樞33，電樞33外部纏繞繞線35用以產生交 替變化之磁場，繞線35與電路板31電性連接，電樞33上 w下分別罩設有絕緣片37，以避免電樞33與繞線35之間電 性接觸。 轉子構件40包括一輪轂42，從輪轂42外緣呈放射狀 突設之複數扇葉44以及貼設於輪轂42内側緣之一環形磁 鐵45。該輪轂42中央形成一固定轉軸47頂端之固定座46。 該轉軸47於靠近頂端之位置設有一環形槽471。該輪轂42 於固定座46之外圍，且與固定座46間隔一定距離之位置 ^處設有一環形之突起48。該突起48環繞固定座46，在突 起48與固定座46之間形成一環形腔室480。 軸承系統20包括一耐磨片21，一軸承23，一儲油元 件24，一扣環25以及一磁吸結構27。該軸承23為一内部 具有大量孔隙之含油軸承。軸承23通過軸座14頂端之開 口收容於其收容空間142内。軸承23内部形成一軸向延伸 之軸孔231，以供轉軸47穿設延伸。請參閱圖2，軸承23 頂端之内周緣處設有一環形之凹槽232。該凹槽232與軸承 8 200942149 • 23内部之軸孔231相連通。該軸承23之凹槽232之直徑大 於-軸孔231之直控，於軸承23頂端形成一環形之台階。 該軸承23之外表面對稱之形成有兩條溝槽⑽。每一溝槽 234從軸承23之頂面沿軸向延伸至轴承23之底面，並於軸 承23之頂面和底面分別與軸承23内部之軸孔231相連通， 以供潤滑油回流。 儲油元件24呈圓環型柱狀體。該儲油元件24可恰好 ❹收容於該軸承23頂端之凹槽232内，該儲油元件24之底 面在凹槽232内與軸承23之頂面相互接觸，且該儲油元件 24之外圓周表面在凹槽232内與軸承23之側面相互接觸。 即在凹槽232内，儲油元件24同時與該軸承23之頂面和 侧面接觸。該儲油元件24由多孔材料，如聚氨醋塑膠泡沫 (俗稱海綿）或發泡金屬等製成。該儲油元件24之内部形 成大置之孔隙，用以吸收當轉軸47高速運轉時從軸承幻 ❹内甩出之潤滑油。 扣環25由韌性好，表面光滑，摩擦係數小且耐磨之材 料，如尼龍（Nyl0n，P0lyamide，簡稱PA)製成。如圖4所 示，該扣環25包括一環形之定位部251，從定位部251之 頂端向内水平延伸之擋油環253及從擋油環253之上表面 向上垂直延伸之環形之突緣255。該定位部251之形狀、高 度及厚度分別與軸座14頂端部分之環形凹陷144之形狀、 高度及寬度相對應。該定位部251通過緊配合之方式收容 9 200942149 於軸座14頂端之環形凹陷144内，將該扣環25與扇框10 結合成一體。定位部251位於轴承23頂端部分之外表面與 ' 軸座14頂端部分之内表面之間，擋油環253從定位部251 之頂端向轉軸47所在方向延伸，用以蓋住該軸座14頂端 之開口。該擋油環253之中心形成供轉軸47穿設通過之穿 孔250，該穿孔250之内徑略大於轉軸47上環形槽471部 分之直徑，且小於該轉軸47上其餘部分之直徑。該擋油環 ❹253向内延伸至該轉軸47之環形槽471内，並在環形槽471 内與轉軸47之外表面之間形成一微小之間隙，該間隙可避 免轉軸47轉動時與擋油環253之間產生摩擦。擋油環253 與環形槽471共同限制轉軸47之軸向運動。該擋油環253、 轉軸47與軸承25頂端之間共同形成一近似封閉之儲油空 間50，該儲油元件24收容於儲油空間50内。如圖5所示， 突緣255之外徑小於定位部251之内徑，定位部251與突 ❹緣255相互錯開，從而於擋油環253之上表面靠近突緣255 之位置形成一台階254。組裝時，將軸座14之頂端水平向 内折彎形成一突出部145，該突出部145壓合在所述台階 254上，從而將扣環25固定於軸座14之頂端。該突緣255 之外徑小於該輪轂42上突起48之外徑，突緣255從擋油 環253之上表面向上延伸指向轉子構件40之環形腔室480 所在之位置。 耐磨片21由耐磨之材料做成，位於軸座14之收容空 200942149 間142之底部，並與轉軸47之末端相抵觸，以旋轉地支持 轉轴47。 磁吸結構27包括一圓柱狀之磁鐵271及一導磁軛鐵 273。該導磁軛鐵273呈底端封閉且頂端開口之圓筒狀，其 沿軸向之橫截面為“U”型。該磁鐵271收容於導磁軛鐵 273内部，磁鐵271之底面及侧面分別與導磁軛鐵273之内 表面相互貼附而形成一個整體。該導磁軛鐵273與磁鐵271 ❹共同收容於扇框10底部12之收容槽120内，通過粘合或 者緊配合之方式與扇框10結合為一體。該導磁軛鐵273包 覆於磁鐵271之外圍，僅使磁鐵271之上表面暴露出導磁 軛鐵273以與扇框10之底部12接觸。由於導磁軛鐵273 之磁通量較大，可使得磁鐵271於被其覆蓋之表面之各個 方向均不會產生漏磁，而僅產生一向上之轴向磁通量用以 吸附轉子構件40之轉軸47，以維持轉子構件40之轉動平 ©衡，避免轉子構件40高速運轉時沿軸向方向向上浮動。該 磁鐵271與轉軸47之間通過扇框10分隔，一方面可以避 免磁鐵271與轉軸47直接接觸而容易磨損，另一方面可以 避免磁鐵271生銹產生生成物污染軸承23。 工作時，定子構件30和轉子構件40之磁場交互作用 驅動轉子構件40旋轉。由於離心力作用沿轉軸47飛濺出 來之潤滑油，通過軸承23頂端和轉軸47之間形成之縫隙 聚集到上方之儲油空間50。該轉軸47之環形槽471使得由 11 200942149 .2心力作用沿轉軸47向上運動之潤滑油之路徑不連續， • μ 253與轉軸47之間形成之間隙寬度足夠小， ^卜觝濺之潤滑油通過擋油環2 集在儲油空間^〈阻检4手全部被聚 工間50内’被儲油元件24吸附。本實施例中， =與扇框1〇結合為一體，該擋油環253、轉軸47與 之間共同形成近似封閉之儲油空間5〇，從而於軸承 内部形成—近似封閉之軸承潤滑系統。該儲油元件％ :防止被聚集在儲油空間5G内之潤滑油繼續沿轉轴们甩 ，特別是當風扇側放或者倒放使用時，該儲油元件2 4借 2内权大1孔隙產生較強之毛吸力，將聚集在儲油空間 5〇之潤滑油吸收過來，同時由於該轴承幻本身也是内建大 量孔隙之結構，儲油元件24回收之潤滑油進—步傳遞至該 含油轴承23中，從而防止潤滑油沿擋油環253與轉轴 之間的間陳流出。進一步的，為了實現較好之回油轉效轴果- ❹该軸承23本权内部孔隙可以設計成比儲油元件μ内部 之孔隙小，從而使含油軸承23能夠產生比儲油元件24更 大之毛吸力，便於從儲油元件24中將潤滑油吸收過來 到更好之潤滑效果。 該扣環25之突緣255環設於轉軸47上環形槽切之 外圍’可進-步阻擋沿轉軸47飛濺出儲油空間％外之部 分潤滑油。該儲油空間5G内被儲油轉24所吸附之㈣ 油，通過儲油元件24之底面及外圓周表面滲回軸承23 : 12 200942149 部，或沿軸承23外表面上之溝道234回流至軸承23底部， 從而充分地防止了潤滑油之洩漏，保證了轴承23與轉軸47 之間良好之潤滑性能，減少磨損，降低噪音，提高了風扇 之品質’延長了風扇使用壽命。另外，該磁吸結構27產生 一向下之磁性力以吸附轉子構件40之轉軸47,可避免轉轴 47高速運轉時沿轴向方向向上浮動時帶出部分潤滑油，特 別當該風扇側放或者倒放使用時，可維持轉子構件4〇之持 ❹續轉動平衡而避免甩出潤滑油。 綜上所述，本發明符合發明專利要件，爰依法提出專 利申請。惟，以上所述者僅為本發明之較佳實_，舉凡 熟悉本案技藝之人士’在爰依本發明精神所作之等效 或變化，皆應涵蓋於以下之申請專利範圍内。 > 【圖式簡單說明】 圖1為本發明散熱風扇之組合示意圖。 © 圖2為圖1所示散熱風扇之立體分解示意圖。 圖3為圖1所示散熱風扇另— 圖4為圖1所示散熱風扇沿Γ 圖5為圖4所示散熱風扇之圈 '角度之立體分解示意圖。 IV-IV線之剖面示意圖。 之局部放大圖。 【主要元件符號說明】The center of the bottom portion 12 of the frame 10 including the __ 10 is formed at an inner circumference of a receiving portion of the seat portion of the seat portion 200942149, and communicates with the accommodating space 142. The inner diameter of the top end of the shaft 'seat 14 at the position of the annular recess 144 is larger than the inner diameter of the rest of the inner portion of the shaft seat 14'. The center of the bottom portion 12 of the frame 10 is recessed from the bottom surface to form a cylindrical receiving groove 120 (Fig. 3). The receiving groove 120 is opposite to the receiving space 142 in the shaft seat 14, but is not in communication. The stator member 30 includes a circuit board 31 and an armature 33 formed by stacking a plurality of layers of silicon steel sheets. The armature 33 is externally wound around the wire 35 for generating an alternating magnetic field, and the winding 35 is electrically connected to the circuit board 31. The insulating sheet 37 is respectively disposed on the armature 33 under w to avoid electrical contact between the armature 33 and the winding 35. The rotor member 40 includes a hub 42 having a plurality of blades 44 projecting radially from the outer edge of the hub 42 and a ring magnet 45 attached to one of the inner edges of the hub 42. A fixing seat 46 for fixing the top end of the rotating shaft 47 is formed in the center of the hub 42. The rotating shaft 47 is provided with an annular groove 471 at a position close to the top end. The hub 42 is disposed at a periphery of the fixing seat 46 and is provided with an annular protrusion 48 at a position spaced apart from the fixing seat 46. The projection 48 surrounds the mounting seat 46 and defines an annular chamber 480 between the projection 48 and the mounting seat 46. The bearing system 20 includes a wear plate 21, a bearing 23, an oil storage member 24, a buckle 25 and a magnetic structure 27. The bearing 23 is an oil-impregnated bearing having a large number of voids therein. The bearing 23 is received in the accommodating space 142 through the opening of the top end of the shaft seat 14. An axially extending shaft hole 231 is formed inside the bearing 23 for the shaft 47 to extend. Referring to FIG. 2, an annular groove 232 is formed at the inner periphery of the top end of the bearing 23. The groove 232 communicates with the shaft hole 231 inside the bearing 8 200942149 • 23. The groove 232 of the bearing 23 has a diameter larger than that of the - shaft hole 231, and an annular step is formed at the top end of the bearing 23. The outer surface of the bearing 23 is symmetrically formed with two grooves (10). Each groove 234 extends axially from the top surface of the bearing 23 to the bottom surface of the bearing 23, and communicates with the shaft hole 231 inside the bearing 23 at the top and bottom surfaces of the bearing 23, respectively, for the lubricating oil to recirculate. The oil storage element 24 is a ring-shaped columnar body. The oil storage member 24 can be received in the groove 232 at the top end of the bearing 23. The bottom surface of the oil storage member 24 is in contact with the top surface of the bearing 23 in the groove 232, and the outer circumference of the oil storage member 24 The surface is in contact with the sides of the bearing 23 in the recess 232. That is, in the recess 232, the oil reservoir member 24 is simultaneously in contact with the top surface and the side surface of the bearing 23. The oil accumulating member 24 is made of a porous material such as polyurethane foam (commonly known as sponge) or foamed metal. The inside of the oil accumulating member 24 is formed with a large aperture for absorbing the lubricating oil which is ejected from the bearing illusion when the rotary shaft 47 is operated at a high speed. The buckle 25 is made of a material having good toughness, a smooth surface, a small coefficient of friction and wear resistance, such as nylon (Nyl0n, P0lyamide, abbreviated as PA). As shown in FIG. 4, the buckle 25 includes an annular positioning portion 251, an oil retaining ring 253 extending horizontally inward from the top end of the positioning portion 251, and a ring-shaped flange extending vertically upward from the upper surface of the oil retaining ring 253. 255. The shape, height and thickness of the positioning portion 251 correspond to the shape, height and width of the annular recess 144 at the top end portion of the shaft seat 14, respectively. The positioning portion 251 is received in the annular recess 144 at the top end of the shaft seat 14 by a tight fit, and the buckle ring 25 is integrated with the fan frame 10. The positioning portion 251 is located between the outer surface of the top end portion of the bearing 23 and the inner surface of the top end portion of the shaft seat 14. The oil retaining ring 253 extends from the top end of the positioning portion 251 toward the direction of the rotating shaft 47 for covering the top end of the shaft seat 14. The opening. The center of the slinger 253 forms a through hole 250 through which the rotating shaft 47 passes. The inner diameter of the through hole 250 is slightly larger than the diameter of the annular groove 471 portion of the rotating shaft 47 and smaller than the diameter of the remaining portion of the rotating shaft 47. The slinger ❹ 253 extends inwardly into the annular groove 471 of the rotating shaft 47, and forms a slight gap between the annular groove 471 and the outer surface of the rotating shaft 47. The gap prevents the rotating shaft 47 from rotating and the oil retaining ring. Friction occurred between 253. The slinger 253 and the annular groove 471 together limit the axial movement of the shaft 47. The oil slinger 253, the rotating shaft 47 and the top end of the bearing 25 together form an approximately closed oil storage space 50, and the oil storage element 24 is received in the oil storage space 50. As shown in FIG. 5, the outer diameter of the flange 255 is smaller than the inner diameter of the positioning portion 251, and the positioning portion 251 and the protruding edge 255 are offset from each other, so that a step 254 is formed at a position above the upper surface of the oil retaining ring 253 near the flange 255. . When assembled, the top end of the shaft seat 14 is bent horizontally inwardly to form a projection 145 which is pressed against the step 254 to fix the buckle 25 to the top end of the shaft seat 14. The outer diameter of the flange 255 is smaller than the outer diameter of the projection 48 on the hub 42, and the flange 255 extends upward from the upper surface of the oil retaining ring 253 toward the position of the annular chamber 480 of the rotor member 40. The wear-resistant piece 21 is made of a wear-resistant material, and is located at the bottom of the housing 142 of the shaft seat 14 and intersects with the end of the rotating shaft 47 to rotatably support the rotating shaft 47. The magnetic structure 27 includes a cylindrical magnet 271 and a yoke 273. The yoke 273 has a cylindrical shape with a bottom end closed and a top end open, and its cross section in the axial direction is "U" shaped. The magnet 271 is housed inside the yoke 273, and the bottom surface and the side surface of the magnet 271 are attached to the inner surface of the yoke 273 to form a single body. The yoke 273 and the magnet 271 are housed in the receiving groove 120 of the bottom portion 12 of the sash frame 10, and are integrated with the sash frame 10 by bonding or tight fitting. The yoke 273 is wrapped around the periphery of the magnet 271, and only the upper surface of the magnet 271 is exposed to the yoke 273 to come into contact with the bottom 12 of the sash 10. Since the magnetic flux of the magnetic yoke 273 is large, the magnet 271 can be prevented from leaking magnetic flux in all directions of the surface covered by the magnet 271, and only an upward axial magnetic flux is generated for adsorbing the rotating shaft 47 of the rotor member 40, In order to maintain the rotation of the rotor member 40, the rotor member 40 is prevented from floating upward in the axial direction when the rotor member 40 is operated at a high speed. The magnet 271 and the rotating shaft 47 are separated by the frame 10, and on the one hand, the magnet 271 can be prevented from coming into direct contact with the rotating shaft 47 to be easily worn, and on the other hand, the magnet 271 can be prevented from being rusted to cause the product to contaminate the bearing 23. In operation, the magnetic field interaction of the stator member 30 and the rotor member 40 drives the rotor member 40 to rotate. The lubricating oil splashed along the rotating shaft 47 due to the centrifugal force is concentrated to the upper oil storage space 50 through the gap formed between the top end of the bearing 23 and the rotating shaft 47. The annular groove 471 of the rotating shaft 47 makes the path of the lubricating oil moving upward along the rotating shaft 47 by the force of 11 200942149 .2 discontinuous, and the gap formed between the μ 253 and the rotating shaft 47 is sufficiently small, and the lubricating oil splashed The oil retaining ring 2 is collected by the oil retaining ring 2 in the oil storage space. In this embodiment, = is integrated with the fan frame 1〇, and the oil retaining ring 253 and the rotating shaft 47 together form an approximately closed oil storage space 5〇, thereby forming an approximately closed bearing lubrication system inside the bearing. The oil storage component %: prevents the lubricating oil accumulated in the oil storage space 5G from continuing to linger along the rotating shaft, especially when the fan is placed sideways or used upside down, the oil storage member 2 borrows 2 internal weight and 1 pore Producing a strong hair suction, the lubricating oil accumulated in the oil storage space is absorbed, and since the bearing itself is also a structure with a large number of pores built therein, the lubricating oil recovered by the oil storage component 24 is further transferred to the oil. In the bearing 23, the lubricating oil is prevented from flowing out along the gap between the oil retaining ring 253 and the rotating shaft. Further, in order to achieve better oil return effect, the internal pores of the bearing 23 can be designed to be smaller than the pores inside the oil storage member μ, so that the oil bearing 23 can be produced larger than the oil storage member 24. The suction of the hair facilitates the absorption of the lubricating oil from the oil storage element 24 to a better lubrication effect. The flange 255 of the retaining ring 25 is disposed on the outer periphery of the annular groove cut on the rotating shaft 47. The lubricating oil which splashes out of the oil storage space % along the rotating shaft 47 can be prevented. The (4) oil adsorbed by the oil storage port 24 in the oil storage space 5G is oozing back through the bottom surface and the outer circumferential surface of the oil storage member 24 to the bearing 23: 12 200942149, or is returned to the channel 234 on the outer surface of the bearing 23 to The bottom of the bearing 23 is sufficient to prevent leakage of the lubricating oil, ensuring good lubrication between the bearing 23 and the rotating shaft 47, reducing wear, reducing noise, and improving the quality of the fan to prolong the service life of the fan. In addition, the magnetic structure 27 generates a downward magnetic force to adsorb the rotating shaft 47 of the rotor member 40, which can prevent a part of the lubricating oil from being taken up when the rotating shaft 47 floats in the axial direction at a high speed, especially when the fan is placed sideways or When used in reverse, the rotor member 4's continuous rotation balance can be maintained to avoid oil leakage. In summary, the present invention complies with the requirements of the invention patent and submits a patent application according to law. However, the above description is only the preferred embodiment of the present invention, and equivalents or variations made by those skilled in the art of the present invention should be included in the following claims. > BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic view showing the combination of a cooling fan of the present invention. © Fig. 2 is a perspective exploded view of the cooling fan shown in Fig. 1. 3 is a perspective view showing the angle of the heat-dissipating fan shown in FIG. 1 along the ' FIG. Schematic diagram of the IV-IV line. Partial enlarged view. [Main component symbol description]
收各空間 142 環 突出部 145 耐磨片 21 軸孔 231 底部 軸座 環形凹陷 軸承系統 轴承 凹槽 12 14 144 20 23 232 13 200942149 溝槽 234 儲油元件 24 扣環 25 穿孔 250 定位部 251 擔油環 253 台階 254 突緣 255 磁吸結構 27 磁鐵 271 導磁輛鐵 273 定子構件 30 電路板 31 電樞 33 繞線 35 絕緣片 37 轉子構件 40 輪轂 42 扇葉 44 環形磁鐵 45 固定座 46 轉軸 47 環形槽 471 突起 48 環形腔室 480 儲油空間 50 14Each space 142 ring protrusion 145 wear plate 21 shaft hole 231 bottom shaft seat annular recess bearing system bearing groove 12 14 144 20 23 232 13 200942149 groove 234 oil storage element 24 buckle 25 perforation 250 positioning portion 251 oil Ring 253 Step 254 Flange 255 Magnetic structure 27 Magnet 271 Magnetic iron 273 Stator member 30 Circuit board 31 Armature 33 Winding 35 Insulation sheet 37 Rotor member 40 Hub 42 Blade 44 Ring magnet 45 Mounting bracket 46 Shaft 47 Ring Slot 471 protrusion 48 annular chamber 480 oil storage space 50 14