1329713 九、發明說明： 【發明所屬之技術領域】 本發明係有關於一種多階動壓溝槽及具有該多階動壓 溝槽之動壓軸承，尤指一種於動壓軸承之套筒與心軸相對 轉動面設置有多階動壓溝槽，可提升動壓軸承之建壓效 果，克服動壓軸承微型化所導致建壓不足與洩流量過大等 問題之多階動壓溝槽及動壓軸承結構。 【先前技術】 為了降低長時間使用所產生之高溫問題，消費型電子 產品如：筆記型電腦、彩色顯示器、投影機等，幾乎皆裝 設一散熱用之微型主軸馬達風扇，為了讓主軸馬達有更優 越的轉動特性：例如低噪音、高轉速、高精度、長壽命等， 一般最常採用的對策，是以提升主軸馬達内之軸承性能為 目標。傳統軸承技術應用於主軸馬達設計，有含油軸承 (Sleeve bearing)與滾珠軸承（Ball bearing);含油軸承 雖有低單價優勢，但壽命短、精度差；滾珠軸承雖然精度 高，但其成本高且耐撞擊能力差、噪音大，上述兩者由於 軸與軸承内壁有接觸，而造成馬達的震動、噪音與壽命問 題。而動壓軸承具備低噪音、高精度、壽命長、耐衝擊之 優勢，目前漸漸成為主流。 習知動壓軸承是以上下兩組動壓溝槽支樓一心軸，以 取代傳統上下兩組滾珠軸承支撐一心轴之結構；動壓軸承 之原理在於利用微細溝槽之流力特性，促使軸與軸承間隙 13297131329713 IX. Description of the Invention: [Technical Field] The present invention relates to a multi-step dynamic pressure groove and a dynamic pressure bearing having the multi-step dynamic pressure groove, in particular to a sleeve of a dynamic pressure bearing and The multi-step dynamic pressure groove is arranged on the opposite rotating surface of the mandrel, which can improve the pressure-building effect of the dynamic pressure bearing, and overcome the multi-step dynamic pressure groove and motion of the problem of insufficient pressure build-up and excessive discharge caused by miniaturization of the dynamic pressure bearing. Pressure bearing structure. [Prior Art] In order to reduce the high temperature problem caused by long-term use, consumer electronic products such as notebook computers, color monitors, projectors, etc., are almost equipped with a micro-spindle motor fan for heat dissipation, in order to allow the spindle motor to have More excellent rotation characteristics: low noise, high speed, high precision, long life, etc. The most commonly used countermeasures are aimed at improving the bearing performance in the spindle motor. The traditional bearing technology is applied to the design of the spindle motor. There are oil bearings (Sleeve bearing) and ball bearings (Ball bearing). Although the oil bearing has a low unit price, the life is short and the precision is poor. The ball bearing has high precision but high cost. The impact resistance is poor and the noise is high. The two are in contact with the inner wall of the bearing, which causes vibration, noise and life of the motor. Dynamic pressure bearings have the advantages of low noise, high precision, long life and impact resistance, and are gradually becoming mainstream. The conventional dynamic pressure bearing is a mandrel of the above two sets of dynamic pressure grooved branches, which replaces the structure of the traditional upper and lower two sets of ball bearings supporting a mandrel; the principle of the dynamic pressure bearing is to use the flow characteristics of the fine groove to promote the shaft With bearing clearance 1329713
中充滿流體而達到充份潤滑與建壓的效果；為了將間隙内 之流體保存住’習知動壓軸承表面上設置有魚骨形 (her r i ngbone )之動壓溝槽，其目的除了讓動壓流體集中， 進而產生建壓力量外’更可使動壓轴承内部達到防漏功 能。然而，在動壓轴承微型化之後（直徑必<15匪），習知 徑向動壓溝槽②計在實際運作時，其建壓效果並不足於克 服本身與外加負載之不平衡量，導致動壓軸承内部零件接 觸’而無法發揮動壓軸承之優越特性。 針對習知專利而言，美國發明專利5911512號「Fluid bearing apparatus having a uniform dynamic pressure distribution」，該案提供之動壓軸承，係於轴承心軸轴向 6又有住向放射狀之W形動壓溝槽，以提供心轴轴向止推力 量使用；由於軸承轉速與心軸之軸徑有關，相同轉速下， 心軸軸徑越大，轉速越高’其w形動壓溝槽之槽寬或槽深， 必須隨不同心軸軸徑而改變，增加設計與加工之困難度。 美國發明專利 6364532 號「Hydrodynamic bearing and motor having the same」，該案所提之動壓軸承，乃是於 轴承套筒内面或心軸轴徑上，設置有一組魚骨形溝槽，當 動壓軸承微型化之後，由於液體建壓受限於魚骨形溝槽尖 端區，因此建壓效果之提升亦受限；此外，其溝槽末端開 口與轉轴方向平行，當流體内部壓力因高速運轉，大於外 界大氣壓力時，潤滑流體洩流量增加’導致建壓效果下降。 美國發明專利 6948852 號「Hydrodynamic bearing, spindle motor and hard disk drive」，該案所提之動壓 軸承，乃是以間格斷開排列方式’將原有軸承内面或者是 1329713 主軸軸徑上之動壓溝槽分開，為提升建壓效果，其排列角 • · 度隨轉速增加而加大’導致洩流量增加，影響整體建壓效 .. 果；此外，當動壓裝置微型化之後，等間格斷開之溝槽， 將近似於含油軸承之功用，導致建壓效果提升有限。 ’ 美國發明專利 7125170 號「Fluid dynamic bearing motor」，該案所提之動壓轴承，乃是於軸承套筒内面或主 軸軸徑上，設有一連續之兩段溝槽，由於液體建壓受限於 溝槽區，當動壓轴承機構微型化之後，連續兩段之溝槽分 Φ 佈受限，因此建壓效果之提升亦受限；此外，為提升建壓 效果，兩段漢槽間之夾角隨轉速提升而增加，但兩段溝槽 之夾角有一定關係，為避免潤滑流體洩流量增加，兩段溝 槽夾角之增加角度受限’因此建壓效果之提升亦受限。 另外如美國發明專利6769808號「Composite fluid dynamic bearing and its manufacturing method 」、 6877902 號「Hydrodynamic bearing device」、7229214 號 r Fluid dynamic bearing unit」、5908247 號「Sinusoidal • grooving pattern for grooved journal bearing」、公開 20040141666 號「Grooving pattern for grooved fluid bearing」，公開 20050232522 號「Fluid bearing device and spindle motor」等習知專利，其目的雖然均在於改善動壓 軸承建壓效果’然而均未能跳脫傳統上下兩段單階動壓溝 槽結構’因此無法能夠有效提升動壓軸承建壓效果，自然 也無法克服動壓軸承微型化所導致建壓不足與洩流量過大 之現象。 8 1329713 【發明内容】 ·' 有鑑於習知技術之缺失，本發明之目的在於提出一種 .- 多階動壓溝槽，可提升動壓軸承之建壓效果，克服動壓軸 承微型化所導致建壓不足與洩流量過大之現象。 ' 為達到上述目的，本發明提出一種多階動壓溝槽及具 有該多階動壓溝槽之動壓軸承，該動壓軸承包含一套筒及 一心軸，該套筒具有一軸孔，該心軸係可轉動地穿設於該 套筒之軸孔；於該套筒與心軸相對轉動面設有多階動壓溝 • 槽，該多階動壓溝槽包含複數溝槽單元，該溝槽單元包括 至少一第一溝槽及至少一第二溝槽，該第一溝槽具有一第 一延伸路徑，該第二溝槽具有一第二延伸路徑，該第二延 伸路徑與該第一延伸路徑間具有一夾角，使形成一 v形路 徑；且各個溝槽單元之V形路徑之頂點相連所構成之輪廓 線呈V形。 為使貴審查委員對於本發明之結構目的和功效有更 進一步之了解與認同，茲配合圖示詳細說明如后_。 【實施方式】 以下將參照隨附之圖式來描述本發明為達成目的所使 用的技術手段與功效，而以下圖式所列舉之實施例僅為輔 助說明，以利貴審查委員瞭解，但本案之技術手段並不限 於所列舉圖式。 請參閱第一圖至第三圖所示，本發明所提供之具有多 階動壓溝槽之動壓軸承，該動壓軸承包含一套筒10及一心 1329713 軸2〇，該套筒10具有一軸幻i，該心轴2〇係可轉動地穿 ά於該套筒10之軸孔U。 如第二圖所示，該心軸20與該套筒1〇之間具有間隙， =間隙填充㈣滑流體3G，該崎流體3()可為液體或 =體’本發明之特點即在於，該套筒1〇與心軸2〇相對轉 動面设有複數多階動壓溝槽40，亦即該多階動壓溝槽4〇 可没置於該軸孔11内側壁，亦可設置於該心轴2〇外側壁， 然通常係設置於該軸孔U内側壁；於第三圖所示該實施 例’該心軸20外側壁係軸向分為上下兩區域，於該上下兩 區域内分別設置有複數多階動壓溝槽4〇，至於該上下兩區 域之面積可相等或不相等，依實際所需而設計，或可如第 四圖所示實施例，將該多㉟動壓溝槽偏佈滿該心軸20外 側壁，同理’可將該多階動壓溝槽4〇設置於該轴孔^内 側壁’且該軸孔Π内側壁可軸向分為上下兩區域，於該上 下兩區域内分別設置有複數多階動壓溝槽4〇，該上下兩區 域之面積可相等或不相等；必須強調說明的是，必須採用 本發明所提供之多階動壓溝槽，方能達到如第四圖所示將 該多階動壓溝槽4GA佈滿心軸2G外側壁之設置態樣，此為 傳統單階魚骨形動壓溝槽無法達成的；關於本發明所提供 之多階動壓溝槽之特點將詳細說明於後。 請參閱第五圖所示，本發明所提供之多階動壓溝样 4〇，其包含複數賴單元4卜42、43，該溝槽單元41 ^ 括至少-第-溝槽4la及至少一第二溝槽仙，該溝槽 兀42包括至少-第一溝槽仏及至少一第二溝槽伽，該 溝槽單元43包括至少一第一溝槽43a及至少一第二溝槽 1329713 ,，以該賴單元41為說明例，該第-溝槽41a具有-第一延，路徑al ’該第二溝槽41b具有一第二延伸路徑 .· bl，該第二延伸路徑bl與該第一延伸路徑al間具有一夾 角θ 1’由該第一延伸路徑al與該第二延伸路徑μ形成一 v形路徑；於本實施例中，該第一溝槽41a〜43a及第二溝 槽41b〜43b均為單一線性溝槽，且該等溝槽41a〜43a、 41b〜43b相互連通，亦即溝槽單元41、42、43之乂形路徑 相互連通，藉此構成一具有多次轉折之連續路徑；此外， 鲁。亥夕化動壓溝槽40之另-特點在於’該各個溝槽單元4卜 42、43之頂點（亦即該溝槽單元41、42、43之v形路徑之 頂點）相連所構成之輪廓線u亦呈v形；換言之，本發明 所提供之多階動壓溝槽4〇係由複數小型¥形走向之溝^單 兀41、42、43構成，且其構成之整體輪廓又可呈現一大型 v形走向，至於該等溝槽41a〜43a、41b 43b，可藉由車床、 滾壓、蝕刻等方式加工成型。 於第五圖所示實施例中，該溝槽單元41、42、43分別 籲由長度不等之第一溝槽41a〜43a及第二溝槽41b〜43b構 成、，然除此之外，亦可如第六圖所示該多階動壓溝槽6〇， δ亥溝槽單元61、62、63分別由長度相等之第一溝槽 及第二溝槽61b〜63b構成；或如第七圖所示該多階動壓溝 槽70，其中該溝槽單元72由長度相等之第一溝槽72&及 第二溝槽72b構成，而其他二溝槽單元71、73分別由長度 不等之第一溝槽71a、73a及第二溝槽71b、73b構成；或 如第八圖所示該多階動壓溝槽8〇，其中二溝槽單元81、82 分別由長度相等之第一溝槽81a、82a及第二溝槽81b、82b 1329713The fluid is filled with fluid to achieve sufficient lubrication and pressure build-up; in order to preserve the fluid in the gap, the movable pressure groove on the surface of the conventional dynamic pressure bearing is provided with a fish-bone shape (her ri ngbone), the purpose of which is The concentration of the dynamic pressure fluid, which in turn generates the pressure build-up, can further prevent the leakage inside the dynamic pressure bearing. However, after the miniaturization of the dynamic pressure bearing (the diameter must be <15 匪), the conventional radial dynamic pressure groove 2 is not effective in overcoming the imbalance between itself and the applied load when the actual operation is performed. The dynamic parts of the dynamic pressure bearing are in contact with each other, and the superior characteristics of the dynamic pressure bearing cannot be exerted. For the conventional patent, the United States invention patent No. 5911512 "Fluid bearing apparatus having a uniform dynamic pressure distribution", the dynamic pressure bearing provided in the case is in the axial direction of the bearing spindle 6 and has a radial W-shaped movement. Pressing the groove to provide the axial thrust force of the mandrel; since the bearing speed is related to the shaft diameter of the mandrel, the spindle shaft diameter is larger at the same speed, and the higher the speed is, the groove of the w-shaped dynamic pressure groove The width or groove depth must be changed with different mandrel axis diameters, increasing the difficulty of design and processing. US Patent No. 6,634,532 "Hydrodynamic bearing and motor having the same", the dynamic pressure bearing mentioned in this case is a set of fishbone-shaped grooves on the inner surface of the bearing sleeve or the shaft diameter of the mandrel. After miniaturization, since the liquid build-up pressure is limited by the tip end region of the fishbone groove, the improvement of the pressure build effect is also limited; in addition, the groove end opening is parallel to the rotation axis direction, when the internal pressure of the fluid is operated at a high speed. When the pressure is greater than the external atmospheric pressure, the leakage of the lubricating fluid increases, resulting in a decrease in the pressure build-up effect. U.S. Patent No. 6,488,852, "Hydrodynamic Bearing, spindle motor and hard disk drive", the dynamic pressure bearing mentioned in this case is in the form of a disconnected arrangement of the original bearing or the shaft diameter of the 1329713 spindle. The pressure grooves are separated, and the pressure is increased. The arrangement angle of the angle increases with the increase of the rotational speed, which leads to an increase in the discharge flow, which affects the overall pressure effect. In addition, when the dynamic pressure device is miniaturized, etc. The groove of the broken grid will be similar to the function of the oil-impregnated bearing, resulting in limited improvement of the pressure build-up effect. 'Fluid dynamic bearing motor', the dynamic pressure bearing mentioned in this case is a continuous two-stage groove on the inner surface of the bearing sleeve or the shaft diameter of the main shaft. In the groove area, after the dynamic pressure bearing mechanism is miniaturized, the grooves of the two consecutive sections are restricted by the Φ cloth, so the improvement of the pressure-building effect is also limited; in addition, in order to improve the pressure-building effect, the two sections of the Hankou are The angle increases with the increase of the speed, but the angle between the two sections of the groove has a certain relationship. In order to avoid the increase of the leakage of the lubricating fluid, the angle of increase of the angle between the two sections of the groove is limited. Therefore, the improvement of the pressure build effect is also limited. Further, for example, U.S. Patent No. 6,769, 808 "Composite fluid dynamic bearing and its manufacturing method", No. 6,877,902 "Hydrodynamic bearing device", No. 7229214 r Fluid dynamic bearing unit, No. 5,908,247 "Sinusoidal grooving pattern for grooved journal bearing", public 20040141666 "Grooving pattern for grooved fluid bearing", the publication of the patents such as "Fluid bearing device and spindle motor" No. 20050232522, the purpose of which is to improve the pressure-bearing effect of the dynamic pressure bearing, but they have not escaped the traditional upper and lower two-stage single-step The dynamic pressure groove structure 'can therefore not effectively improve the pressure-bearing effect of the dynamic pressure bearing, and naturally cannot overcome the phenomenon of insufficient pressure build-up and excessive discharge due to miniaturization of the dynamic pressure bearing. 8 1329713 [Summary of the Invention] · In view of the lack of the prior art, the object of the present invention is to provide a multi-step dynamic pressure groove, which can improve the pressure-building effect of the dynamic pressure bearing and overcome the miniaturization of the dynamic pressure bearing. Insufficient pressure build-up and excessive discharge. In order to achieve the above object, the present invention provides a multi-step dynamic pressure groove and a dynamic pressure bearing having the multi-step dynamic pressure groove, the dynamic pressure bearing comprising a sleeve and a mandrel, the sleeve having a shaft hole, The mandrel is rotatably disposed in the shaft hole of the sleeve; the multi-step dynamic pressure groove/slot is disposed on the opposite rotating surface of the sleeve and the mandrel, and the multi-step dynamic pressure groove includes a plurality of groove units, The trench unit includes at least one first trench and at least one second trench, the first trench has a first extending path, and the second trench has a second extending path, the second extending path and the first An extension path has an angle to form a v-shaped path; and the contours formed by the vertices of the V-shaped paths of the respective groove units are V-shaped. In order to enable your review committee to have a better understanding and approval of the structural purpose and efficacy of the present invention, the detailed description of the figure is as follows. [Embodiment] Hereinafter, the technical means and effects of the present invention for achieving the object will be described with reference to the accompanying drawings, and the embodiments listed in the following drawings are only for the purpose of explanation, so that the reviewer understands, but the case Technical means are not limited to the illustrated figures. Referring to the first to third figures, the present invention provides a dynamic pressure bearing having a multi-step dynamic pressure groove, the dynamic pressure bearing comprising a sleeve 10 and a core 1329713 shaft 2〇, the sleeve 10 has The spindle 2 is rotatably threaded through the shaft hole U of the sleeve 10. As shown in the second figure, there is a gap between the mandrel 20 and the sleeve 1〇, and the gap is filled with (4) the slip fluid 3G, and the sacrificial fluid 3() can be a liquid or a body. The present invention is characterized in that a plurality of multi-step dynamic pressure grooves 40 are disposed on the opposite rotating surface of the sleeve 1 〇 and the mandrel 2 ,, that is, the multi-step dynamic pressure grooves 4 〇 may not be disposed on the inner side wall of the shaft hole 11 or may be disposed on the inner side wall of the shaft hole 11 The outer side wall of the mandrel 2 is usually disposed on the inner side wall of the shaft hole U. In the third embodiment, the outer side wall of the mandrel 20 is axially divided into upper and lower regions, and the upper and lower regions are A plurality of multi-step dynamic pressure grooves 4 设置 are respectively disposed, and the areas of the upper and lower regions may be equal or unequal, designed according to actual needs, or may be as shown in the fourth embodiment. The pressure groove is partially overlapped with the outer side wall of the mandrel 20. Similarly, the multi-step dynamic pressure groove 4〇 can be disposed on the inner side wall of the shaft hole, and the inner side wall of the shaft hole can be axially divided into upper and lower sides. In the region, a plurality of multi-step dynamic pressure grooves 4〇 are respectively disposed in the upper and lower regions, and the areas of the upper and lower regions may be equal or unequal; It is necessary to use the multi-step dynamic pressure groove provided by the present invention to achieve the arrangement of the multi-step dynamic pressure groove 4GA covering the outer side wall of the mandrel 2G as shown in the fourth figure. The single-step fishbone dynamic pressure groove cannot be achieved; the characteristics of the multi-step dynamic pressure groove provided by the present invention will be described in detail later. Referring to FIG. 5, the multi-step dynamic pressure groove sample 4 provided by the present invention includes a plurality of cells 4, 42 and 43. The groove unit 41 includes at least a first groove 44a and at least one a second trench, the trench 42 includes at least a first trench and at least a second trench. The trench unit 43 includes at least a first trench 43a and at least a second trench 1329713. For example, the first trench 41a has a first extension, and the second gate 41b has a second extension path . . . bl. The second extension path bl and the second extension path bl The first extending path a1 and the second extending path μ form a v-shaped path. In the embodiment, the first grooves 41a to 43a and the second groove are formed. 41b to 43b are all single linear grooves, and the grooves 41a to 43a, 41b to 43b are in communication with each other, that is, the meandering paths of the groove units 41, 42, 43 are connected to each other, thereby constituting a plurality of transitions. The continuous path; in addition, Lu. The other feature of the eccentric dynamic pressure groove 40 is that the contours of the apexes of the respective groove units 4, 42 and 43 (i.e., the vertices of the v-shaped paths of the groove units 41, 42, 43) are connected. The line u is also v-shaped; in other words, the multi-step dynamic pressure groove 4 provided by the present invention is composed of a plurality of small-sized shape-oriented grooves 41, 42 and 43, and the overall contour of the structure can be presented. A large v-shaped course, as for the grooves 41a to 43a, 41b 43b, can be formed by latheing, rolling, etching, or the like. In the embodiment shown in FIG. 5, the groove units 41, 42, 43 are respectively composed of the first grooves 41a to 43a and the second grooves 41b to 43b having unequal lengths, respectively. The multi-step dynamic pressure groove 6 〇 can also be formed as shown in FIG. 6 , and the δ-Hui groove units 61 , 62 , 63 are respectively composed of the first groove and the second groove 61 b to 63 b having the same length; or The multi-step dynamic pressure groove 70 is shown in FIG. 7, wherein the groove unit 72 is composed of the first groove 72& and the second groove 72b having the same length, and the other two groove units 71 and 73 are respectively not of the length. Or the first trenches 71a, 73a and the second trenches 71b, 73b; or the multi-step dynamic pressure trenches 8〇 as shown in the eighth figure, wherein the two trench cells 81, 82 are respectively equal in length a groove 81a, 82a and a second groove 81b, 82b 1329713
構另-溝槽單元83則由長度不等之第一溝槽咖及第 -溝U3b構成；由上述實施例可知，本發明所提供 階動壓溝槽可由至少―第—溝槽及第二溝槽長度相等之溝 至少一第一溝槽及第二溝槽長度不相等之溝The other-groove unit 83 is composed of a first groove coffee and a first groove U3b having different lengths. As can be seen from the above embodiments, the step pressure groove provided by the present invention can be at least a "first groove" and a second a groove having the same length of the groove, at least one groove having an unequal length of the first groove and the second groove
以第五圖所示實施例為基礎，可再衍生出如第九圖所 不實施例，該多階動壓溝槽90係由呈現曲線之溝槽單元 91〜95構成，且該溝槽單元91〜95之相連通處呈現弧角； 或如第十圖所示實施例，該多階動壓溝槽1〇〇係由呈現曲 線之溝槽單元101〜105構成，且該溝槽單元1〇1〜1〇5之相 連通處王現鈍角；或如第十一圖所示實施例，該多階動壓 溝槽110係由呈現線性之溝槽單元U1〜115構成，且該溝 ，單元111〜115之相連通處呈現弧角；至於第十二圖所示 實施例，該多階動壓溝槽120係由呈現線性之溝槽單元 121〜125構成，且該溝槽單元121〜125之相連通處呈現尖 角，本實施例與第五圖所示實施例相類似。Based on the embodiment shown in FIG. 5, the embodiment shown in FIG. 9 may be further derived. The multi-step dynamic pressure groove 90 is formed by groove units 91 to 95 which exhibit a curve, and the groove unit The intersection of 91 to 95 exhibits an arc angle; or as in the embodiment shown in the tenth embodiment, the multi-step dynamic pressure groove 1 is composed of groove units 101 to 105 which exhibit a curve, and the groove unit 1相1~1〇5 is connected to an obtuse angle; or as in the embodiment shown in FIG. 11, the multi-step dynamic pressure groove 110 is formed by groove units U1 to 115 which exhibit linearity, and the groove, The intersecting portions of the units 111 to 115 exhibit an arc angle; as for the embodiment shown in the twelfth embodiment, the multi-step dynamic pressure grooves 120 are formed by the groove units 121 to 125 which exhibit linearity, and the groove unit 121 is The phase intersection of 125 exhibits a sharp corner, and this embodiment is similar to the embodiment shown in FIG.
上述不同多階動壓溝槽實施例均顯示組成之溝槽單元 係相互連通，然除此之外，亦可如第十三圖所示實施例， 該多階動壓溝槽130係由呈現曲線之溝槽單元ι31〜135構 成，且該溝槽單元131〜135之間具有斷開之不相連處；以 溝槽單元132為例’其係由兩段第一溝槽132a以及一段第 二溝槽132b構成，且該第一溝槽132a與該溝槽單元131 相連通’而第二溝槽132b則與該溝槽單元133不相連。 再如第十四圖所示實施例，該多階動壓溝槽14〇係由 線性且具有鈍角之溝槽單元141、曲線且具有弧角之溝槽 1329713 單元142、線性且具有尖角之溝槽單元143、曲線且具有弧 角之溝槽單元144、線性且具有尖角之溝槽單元145構成； .. 而第十五圖所示實施例，該多階動壓溝槽150則係以第十 四圖該實施例為基礎’不同點在於該多階動壓溝糟150具 . 有複數之斷開處，亦即該多階動壓溝槽150並非一連續通 道。 請參閱第十六圖及第十七圖分別顯示習知動壓溝槽與 本發明多階動壓溝槽之設計圖，於第十八圖所示相同環境 φ 模擬參數下，如··潤滑油密度及黏度、元素内部Χ、γ方向 格點數目、起始偏心比、結束偏心比、總共計算之偏心比 數量、軸承與心轴間隙量、心軸半徑、轉速、溝槽數目、 上部及下部溝槽角度、軸承長度、溝槽深度與間隙量比、 溝槽寬度與溝槽間距比等參數固定之條件下’比較動壓轴 承上下兩部分，習知動壓溝槽與本發明多階動壓溝槽，其 偏心比與軸承負載能力（無因次化’ 一般在探討動壓軸承 的負載能力時，是以無因次化的軸承負載能力來表示，可 • 參考附件1之期刊論文·· G. H. Jang and D. I. Chang, “Analysis of a Hydrodynamic Herringbone Grooved Journal Bearing Considering Cavitation” ， Transactions of the ASME, Vol, 122，pp. 103-109, 2000.)之相對關係；第十九圖顯示習知單階動壓溝槽與本 發明多階動壓溝槽改變之高度，單位為公尺。 由第二十圖及第二十一圖可知，於該多階動壓溝槽之 可變參數調整得宜之情況下，在相同偏心比下，轴承負載 能力（無因次化），將可優於習知單階動壓溝槽。 1329713 综上所述，本發明所提供之多階動壓溝槽及具有該多 •- 階動壓溝槽之動壓軸承，請參閱第三圖所示，當心軸20與 .. 套筒10發生相對轉動時，潤滑流體30會集中於多階動壓 溝槽40之小型V形轉折處，因而產生複數個小建壓區，而 • 再由於該多階動壓溝槽40之整體外型亦為V形，因此也同 時具有一定之建壓效果，可明顯提升整體動壓溝槽之流體 建壓效果外，更加強並穩定動壓轴承裝置運作過程之動態 剛性；此外，由於該多階動壓溝槽40上之複數個小型V形 φ 轉折處，係沿著心軸20與套筒10之相對轉動面上分佈， 當動壓軸承實際運作時，其内部之潤滑流體30不易流出， 即可達成降低洩流量之功能。 惟以上所述者，僅為本發明之實施例而已，當不能以 之限定本發明所實施之範圍。即大凡依本發明申請專利範 圍所作之均等變化與修飾，皆應仍屬於本發明專利涵蓋之 範圍内，謹請貴審查委員明鑑，並祈惠准，是所至禱。 【圖式簡單說明】 第一圖係本發明動壓軸承俯視結構示意圖。 第二圖係第一圖之A-A剖面結構示意圖。 第三圖係第二圖之B部份放大結構，顯示於套筒及心 轴相對轉動面設置本發明之多階動壓溝槽之一實施例之結 構不意圖。 第四圖係本發明於套筒及心軸相對轉動面設置多階動 壓溝槽另一實施例之結構示意圖。 第五圖係本發明多階動壓溝槽之一實施例之結構示意 1329713 圖。 -- 第六圖至第十五圖係本發明多階動壓溝槽之不同實施 .. 例結構示意圖。 第十六圖係習知動壓溝槽之設計圖。 第十七圖係本發明多階動壓溝槽之設計圖。 第十八圖係動壓溝槽環境模擬參數表。 第十九圖係習知動壓溝槽與本發明多階動壓溝槽之參 數表。 • 第二十圖係習知動壓溝槽與本發明多階動壓溝槽偏心 比與軸承負載能力（無因次化）關係線性圖。 第二十一圖係第二十圖之具體數值表。 【主要元件符號說明】 10- 套筒 11- 轴孔 2 0 -心轴 30-潤滑流體 40、40A、60、70、80、90、100、110、120、130、140、 150-多階動壓溝槽 4卜43、6卜63、7卜73、81 〜83、91 〜95、10H05、 111 〜115、12卜 125、131 〜135、141 〜145-溝槽單元 41a、42a、43a、61a、62a、63a、71a、72a、73a、81a、 82a、83a、132a-第一溝槽 41b、42b、43b、61b、62b、63b、71b、72b、73b、81b、 1329713The different multi-step dynamic pressure groove embodiments described above all show that the groove units of the composition are connected to each other. Otherwise, as in the embodiment shown in FIG. 13, the multi-step dynamic pressure groove 130 is presented. The grooved cells ι 31 135 135 are formed, and the groove cells 131 135 135 have a disconnected disconnection; the groove unit 132 is taken as an example, which is composed of two first grooves 132 a and a second The trench 132b is formed, and the first trench 132a is in communication with the trench unit 131, and the second trench 132b is not connected to the trench unit 133. Further, as in the embodiment shown in FIG. 14, the multi-step dynamic pressure groove 14 is a linear and obtuse groove unit 141, a curved groove having an arc angle 1329713, a unit 142, linear and has a sharp angle. The groove unit 143, the groove unit 144 having a curved angle and an arc angle, and the groove unit 145 having a linear angle and having a sharp angle are formed; and the embodiment shown in the fifteenth figure is the multi-step dynamic pressure groove 150 Based on the embodiment of Fig. 14, the difference is that the multi-step dynamic pressure groove has 150. There is a plurality of breaks, that is, the multi-step dynamic pressure groove 150 is not a continuous passage. Please refer to the sixteenth and seventeenth figures for the design of the conventional dynamic pressure groove and the multi-step dynamic pressure groove of the present invention, respectively, under the same environment φ simulation parameters shown in Fig. 18, such as · Lubrication Oil density and viscosity, element internal enthalpy, number of gamma direction grids, initial eccentricity ratio, end eccentricity ratio, total calculated eccentricity ratio, bearing and mandrel clearance, mandrel radius, rotational speed, number of grooves, upper and Under the condition that the lower groove angle, the bearing length, the groove depth and the gap ratio, the groove width and the groove pitch ratio are fixed, 'comparing the upper and lower parts of the dynamic pressure bearing, the conventional dynamic pressure groove and the multi-stage of the present invention Dynamic pressure groove, its eccentricity and bearing load capacity (no dimensioning) is generally expressed in the dimensionless bearing load capacity when discussing the load capacity of dynamic bearing, can refer to the attached article ·· GH Jang and DI Chang, “Analysis of a Hydrodynamic Herringbone Grooved Journal Bearing Considering Cavitation” , Transactions of the ASME, Vol, 122, pp. 103-109, 2000.) FIG nine show conventional single stage hydrodynamic grooves of the present invention is a multi-order dynamic pressure groove height change, in units of meters. It can be seen from the twentieth and twenty-first figures that, under the condition that the variable parameters of the multi-step dynamic pressure groove are properly adjusted, the bearing load capacity (dimensionless) will be excellent under the same eccentricity ratio. In the conventional single-step dynamic pressure groove. 1329713 In summary, the multi-step dynamic pressure groove provided by the present invention and the dynamic pressure bearing having the multi-step dynamic pressure groove are shown in the third figure, when the mandrel 20 and the sleeve 10 are When the relative rotation occurs, the lubricating fluid 30 concentrates on the small V-shaped turning point of the multi-step dynamic pressure groove 40, thereby generating a plurality of small nips, and further due to the overall shape of the multi-step dynamic pressure groove 40. It is also V-shaped, so it also has a certain pressure-building effect, which can obviously improve the fluid pressure-building effect of the integral dynamic pressure groove, and strengthen and stabilize the dynamic rigidity of the dynamic pressure bearing device during operation; in addition, due to the multi-step A plurality of small V-shaped φ turns on the dynamic pressure groove 40 are distributed along the opposite rotating surfaces of the mandrel 20 and the sleeve 10. When the dynamic pressure bearing is actually operated, the lubricating fluid 30 inside thereof is not easily discharged. The function of reducing the discharge flow can be achieved. However, the above description is only for the embodiments of the present invention, and the scope of the invention is not limited thereto. That is to say, the equivalent changes and modifications made by the applicant in accordance with the scope of application of the present invention should still fall within the scope covered by the patent of the present invention. I would like to ask your reviewing committee to give a clear understanding and pray for it. BRIEF DESCRIPTION OF THE DRAWINGS The first figure is a schematic plan view of a dynamic pressure bearing of the present invention. The second figure is a schematic view of the A-A cross-sectional structure of the first figure. The third drawing is a partial enlarged structure of the second drawing of Fig. 2, showing the structure of one embodiment of the multi-step dynamic pressure groove of the present invention which is disposed on the opposite rotating surface of the sleeve and the mandrel. The fourth figure is a structural schematic view of another embodiment of the present invention in which a multi-step dynamic pressure groove is provided on a sleeve and a relative rotating surface of a mandrel. Fig. 5 is a schematic diagram showing the structure of one embodiment of the multi-step dynamic pressure groove of the present invention. -- Figure 6 to Figure 15 are different implementations of the multi-step dynamic pressure groove of the present invention. The sixteenth figure is a design diagram of a conventional dynamic pressure groove. The seventeenth drawing is a design diagram of the multi-step dynamic pressure groove of the present invention. The eighteenth figure is a dynamic pressure groove environment simulation parameter table. The nineteenth figure is a parameter table of a conventional dynamic pressure groove and a multi-step dynamic pressure groove of the present invention. • Figure 20 is a linear diagram of the relationship between the conventional dynamic pressure groove and the multi-step dynamic pressure groove eccentricity of the present invention and the bearing load capacity (dimensionless). The twenty-first figure is a specific numerical table of the twentieth chart. [Description of main component symbols] 10- Sleeve 11 - Shaft hole 2 0 - Mandrel 30 - Lubricating fluid 40, 40A, 60, 70, 80, 90, 100, 110, 120, 130, 140, 150-multiple-order Pressure groove 4, 43, 6, 63, 7, 73, 81 to 83, 91 to 95, 10H05, 111 to 115, 12, 125, 131 to 135, 141 to 145 - groove units 41a, 42a, 43a, 61a, 62a, 63a, 71a, 72a, 73a, 81a, 82a, 83a, 132a - first grooves 41b, 42b, 43b, 61b, 62b, 63b, 71b, 72b, 73b, 81b, 1329713
82b、83b、132b-第二溝槽 al-第一延伸路徑 bl-第二延伸路徑 θ 1-夾角 1682b, 83b, 132b - second trench al - first extension path bl - second extension path θ 1- angle 16