200839098 九、發明說明： 【發明所屬之技術領域】 本發明係針對一種磁力驅動輪葉泵。 【先前技術】 輪葉泵在該項技藝中已被廣泛已知（例如，如曰本 專利公開案第53-2704 A號中所揭示）。通常，輪葉泵包 括一具有一泵空腔之外殼及一可在該泵空腔内關於一偏 心轴而旋轉之轉子。該轉子承載複數個輪葉，該等輪葉 徑向移動以便在轉子旋轉時使其外端保持與泵空腔之一 内壁密封接觸，藉此將流體抽吸至泵空腔中、壓縮流體 並將其排出泵空腔。轉子耦接至一待驅動而藉此旋轉之 外部馬達。爲此目的，轉子具備一於外殼向外處延伸以 用於與馬達耦接之軸。因此，軸與外殼之間密封。然而， 由於該轴係一恒定移動部件，所以總是存有在不斷之使 用期間密封可變得退化而導致流體非預期地洩漏的問 題。 【發明内容】 鑒於以上問題，已達成本發明以提供一具有一無洩 漏結構之磁力驅動輪葉泵。根據本發明之輪葉泵包括： 一具有一泵空腔之外殼；一用於將流體引入至該泵空腔 中之入口；及一用於將流體排放出泵空腔之出口。一轉 子安置於泵空腔内以相對於該泵空腔而可關於一偏心軸 旋轉。複數個輪葉承載於轉子上且可徑向移動以便在轉 子被驅動旋轉以將流體抽吸至泵空腔中及將其排出泵空 腔時保持輪葉與泵空腔之一内壁密封接觸。轉子經組態 200839098 以具有一轉子磁鐵，該轉子磁鐵磁力耦接至一被安裝於 泵空腔向外處之外殼上的定子磁鐵以用於驅動轉子。本 發明之特徵存在於轉子磁鐵經組態以使其主要部分被安 置成與定子磁鐵成一重疊關係。因此，轉子磁鐵可與安 置於外殼外部之定子磁鐵機械隔離以在其間建立一無缝 耦接而使得泵無洩漏，但在泵之軸向方向上仍僅需泵之 最小厚度。 較佳地’將轉子磁鐵安置於定子磁鐵之徑向向外處 使得定子磁鐵可配置於定子之一徑向尺寸内，此確保該 泵沿徑向方向是一緊密結構。 又，較佳地，定子磁鐵經組態以使其軸中心自轉子 磁鐵之一轴中心偏移以便相對於偏心軸而使其安置於比 該轉子磁鐵更遠離轉子處。就此配置而言，轉子在一軸 向方向上被吸向定子磁鐵使得轉子可關於其軸向方向而 以一恒定水準旋轉，從而不産生實質軸向波動。 此外，較佳將轉子磁鐵裝配於一自外殼之中心軸向 延伸之軸周圍，一振動吸收構件被插入於其中。該振動 吸收構件可很好地吸收可能由轉子之一偏心旋轉運動所 産生之徑向振動，藉此確保一平滑及無聲之旋轉運動。 此外，分別被可滑動地裝配於轉子中之徑向槽中的 每一輪葉經組態以僅可徑向移動而未導致在軸向方向上 波動。爲此目的，分別使每一輪葉藉由肋狀物而形成於 其相對側上，該等肋狀物嚙合至形成於界定其間之徑向 槽的轉子之相對面中的導引槽中。 當結合附圖時，本發明之此等及還有其他有利特徵 將自本發明之較佳實施例之以下描述而變得更加顯雨易 8 200839098 見。 【實施方式】 現參看第一圖至第四圖，展示了根據本發明之第一 實施例之磁力驅動輪葉泵。該泵包括一在其内部形成有 一圓柱型泵空腔12之外殼10，該圓柱型泵空腔12使一 具有一自泵空腔12之軸偏移之偏心軸的轉子40容納於 其中。外殼10由一下半部分20及一上半部分30組成， 該下半部分20與該上半部分30藉由一被固持於其間之 密封環14而緊固至彼此。下半部分20及上半部分30分 別形成有一下凹區21及一上凹區31，該下凹區21及該 上凹區31連接界定泵空腔12。如在第三圖及第四圖中 所見，下半部分20經形成以具有一錨定一軸23之中心 螺栓22及一位於該中心螺栓22與一周邊壁28之間的環 形突出物26。軸23自中心螺栓22突出進入下半部分20 之一中心凹面29中以界定偏心軸，並由一軸承套筒24 圍繞。一環32被裝配於上半部分30之内部以延伸圍繞 上凹區31之周邊，且其之一軸端搁置於下半部分20之 周邊壁28上。上半部分30形成有一用於經由環32中之 一埠35而將流體引入至泵空腔12中的入口 34及一用於 經由環32之一淳37而將流體排出泵空腔的出口 36。 轉子40被成形爲一安置於上凹區21内之圓盤且承 载複數個輪葉50，該等輪葉50分別被可滑動地收納於 圓周分佈之徑向隙缝42中。當驅動轉子40旋轉時，每 一輪葉50藉由一離心力而徑向向外移位以使其外端與 環32之内部密封接觸，藉此形成一被限制於鄰近輪葉之 間及環32與轉子之間的移位腔室。該移位腔室在轉子 200839098 40關於偏心軸旋轉的同時經歷擴張及收縮，藉此將流體 抽吸至泵空腔12及將其排出泵空腔12。 轉子40承載一轉子磁鐵60，該轉子磁鐵60磁力耦 接至一安置於外殼10之外部的定子磁鐵70以便受驅動 而藉此旋轉。轉子磁鐵60係一與轉子40整合而形成一 整體結構之永久磁鐵。轉子磁鐵60經成形而具有一緊固 於轉子40之一軸端表面上的薄基底62、一自基底62之 中心轴向突出之輪轂64及一自基底62之周邊軸向突出 之外環67。輪轂64被收納至中心凹面29中以關於偏心 轴之徑向方向而與定子磁鐵70成重疊關係。輪轂64形 成有一轴承孔65，軸23連同軸承套筒24延伸至該轴承 孔65中使得轉子磁鐵60可連同轉子40而關於轴23自 由旋轉。外環67突出至一形成於環突出物26與下半部 分20之周邊壁28之間的環形槽27中從而關於徑向方向 而亦與定子磁鐵70成重疊關係。外環67與輪轂64構成 轉子磁鐵60之一主要部分，其安置於定子磁鐵70之徑 向向外處從而與之成重疊關係，此促使泵之轴向尺寸以 及徑向尺寸最小化。 爲減小可在轉子40關於偏心軸旋轉期間發生的該 轉子40之徑向振動，將一振動吸收構件25插入於轴承 孔65與軸23之軸承套筒24之間。 定子磁鐵70由複數個電磁鐵組成，該等電磁鐵安裝 於一形成於環形突出物26之下侧的開放空間内且延伸 圍繞中心螺栓22。如第三圖中所示，定子磁鐵70使其 軸向的中心C70自轉子磁鐵60之一軸向的中心C60軸 向地偏移，以便其與轉子40比其與轉子磁鐵60相對於 200839098 偏心軸之軸向方向更遠離。因此，定子磁鐵70産生一吸 附力以吸附轉子磁鐵60且使轉子40軸向朝向定子磁鐵 70，藉此使轉子磁鐵60保持與環形突出物26之上面鄰 接且因此在轉子40旋轉期間最小化其之軸向波動。 如第五圖中所示，每一輪葉50具有肋狀物54形成 於其相對侧上，該等肋狀物54可滑動地收納至形成於徑 向隙缝42之相對面的導引槽44中，使得輪葉50僅被可 滑動地固持於徑向隙缝42内而不會被軸向移位至隙缝 外。 第六圖及第七圖說明根據本發明之第二實施例之輪 葉泵，其基本上與第一實施例相同，除了轉子40自身由 一永久磁鐵製成以構成轉子磁鐵60之外。類似之部件由 類似之參考標號來指明且爲簡單性起見本文中不進行重 復解釋。轉子40安置於被界定於外殼10之下半部分20 與上半部分30之間的泵空腔12中且被限制於環32之圓 周内。將轉子40成形爲一通常之平坦圓盤以具有複數個 分佈在圓周上的徑向隙缝42 (每一徑向隙缝42收納徑 向可滑動的輪葉50)，及具有一位於其中心中之軸承孔 65以用於收納軸13及軸承套筒24,使得轉子40可關於 由轴13所界定之偏心轴而自由旋轉。定子磁鐵70安置 在位於環32之徑向向外處的下半部分20與上半部分30 之間’且由一具有一輕環7 2之電磁鐵組件組成，該輛環 72具有複數個圓周核心73，每一圓周核心73承載一線 圈74 〇 第八圖及第九圖說明瞭根據本發明之第三實施例之 輪葉泵，除了轉子40自身由一永久磁鐵製成以構成轉子 11 200839098 磁鐵60及定子磁鐵70安置於轉子40之直徑内之外，其 基本上與第一實施例相同。類似之部件由類似之參考標 號來指明且爲簡單性起見本文中不進行重復解釋。轉子 40安置於被界定於外殼之下半部分20與上半部分30之 間的泵空腔12中且被限制於環22之圓周内。轉子40經 成形以具有借助於一橋69而被整合連接之一輪轂64及 一外環67。輪轂64具有一轴承孔65，軸13連同轴承套 筒24而被裝配至該軸承孔65中使得轉子40得以支撐至 下半部分10從而可關於轴13或藉此所界定之偏心軸自 由旋轉。上半部分30形成有一延伸於輪轂64與轉子40 之外環67之間的環形槽38以將定子磁鐵70收納於其 中。因此，定子磁鐵70經配置而相對於關於偏心轴之徑 向方向與轉子磁鐵60或轉子40成一重疊關係以便最小 化泵之軸向尺寸。定子磁鐵70係一由複數個核心73 (每 一核心承載一線圈74)組成之電磁鐵組件。 儘管特定參看上文之實施例來解釋本發明，但不應 將本發明定界至該等實施例而是其可涵蓋上文之實施例 中所揭示之個別特徵之任何組合。 【圖式簡單說明】 第一圖：係根據本發明之第一實施例之輪葉泵的立 體分解圖； 第二圖：係上文之輪葉泵的水平剖面圖； 第三圖··係沿第二圖之線X-X所截取的剖面圖； 第四圖：係沿第二圖之線Y-Y所截取的剖面圖； 第五圖：係上文之輪葉泵之一部分的立體分解圖； 12 200839098 月之第二實施例之輪葉泵的水 第六圖：係根據本發 平剖面圖； ^ 弟六圖之線7_7所截取的剖面圖； 平叫2圖··係根據本發明之第三實施例之輪葉泵的水 卞Μ面圖；以及 面圖 弗圖·係沿第八圖之線9-9所截取的剖 【主要元件符號說明】 10外殼 12泵空腔 13轴 14密封環 20下半部分 21下凹部 22中心螺栓 23軸 24軸承套筒 25振動吸收構件 26環形突出物 27環形槽 28周邊壁 29中心凹面 3〇上半部分 31上凹區 200839098 36出口 37埠 38環形槽 40轉子 42徑向隙缝 44導引槽 50輪葉 54肋狀物 60轉子磁鐵 62薄基底 64輪轂 65軸承孔 67外環 69橋 7 0定子磁鐵 72輛環 73圓周核心 74線圈200839098 IX. DESCRIPTION OF THE INVENTION: TECHNICAL FIELD OF THE INVENTION The present invention is directed to a magnetically driven vane pump. [Prior Art] A vane pump is widely known in the art (for example, as disclosed in Japanese Patent Laid-Open Publication No. 53-2704 A). Typically, a vane pump includes a housing having a pump cavity and a rotor rotatable within the pump cavity with respect to an eccentric shaft. The rotor carries a plurality of vanes that move radially to maintain their outer ends in sealing contact with the inner wall of one of the pump cavities as the rotor rotates, thereby drawing fluid into the pump cavity, compressing the fluid and Drain it out of the pump cavity. The rotor is coupled to an external motor to be driven for rotation therewith. For this purpose, the rotor has a shaft that extends outwardly of the housing for coupling to the motor. Therefore, the shaft is sealed from the outer casing. However, since the shaft is a constantly moving part, there is always a problem that the seal can become degraded during continuous use, causing undesired leakage of fluid. SUMMARY OF THE INVENTION In view of the above problems, the present invention has been achieved to provide a magnetically driven vane pump having a leak-free structure. A vane pump in accordance with the present invention includes: an outer casing having a pump cavity; an inlet for introducing fluid into the pump cavity; and an outlet for discharging fluid out of the pump cavity. A rotor is disposed within the pump cavity for rotation with respect to an eccentric shaft relative to the pump cavity. A plurality of vanes are carried on the rotor and are radially movable to maintain the vanes in sealing contact with the inner wall of one of the pump cavities when the rotor is driven to rotate to draw fluid into the pump cavity and out of the pump cavity. The rotor is configured 200839098 to have a rotor magnet that is magnetically coupled to a stator magnet mounted on an outer casing that is outwardly of the pump cavity for driving the rotor. A feature of the invention resides in the rotor magnet being configured such that its major portion is placed in an overlapping relationship with the stator magnet. Therefore, the rotor magnet can be mechanically isolated from the stator magnets placed outside the casing to establish a seamless coupling therebetween so that the pump is leak free, but only the minimum thickness of the pump is required in the axial direction of the pump. Preferably, the rotor magnet is disposed radially outward of the stator magnet such that the stator magnet can be disposed within one of the radial dimensions of the stator, which ensures that the pump is a compact structure in the radial direction. Still preferably, the stator magnet is configured such that its shaft center is offset from the center of one of the rotor magnets so as to be positioned further away from the rotor than the rotor magnet relative to the eccentric shaft. With this configuration, the rotor is attracted to the stator magnet in the axial direction so that the rotor can be rotated at a constant level with respect to its axial direction so as not to cause substantial axial fluctuation. Further, it is preferable that the rotor magnet is fitted around a shaft extending axially from the center of the outer casing, and a vibration absorbing member is inserted therein. The vibration absorbing member can well absorb radial vibrations which may be generated by an eccentric rotational motion of the rotor, thereby ensuring a smooth and silent rotational motion. Moreover, each of the vanes, respectively slidably fitted in the radial slots in the rotor, is configured to be only radially movable without causing fluctuations in the axial direction. For this purpose, each of the vanes is formed on its opposite side by ribs, respectively, which engage into guide grooves formed in the opposite faces of the rotor defining the radial grooves therebetween. These and other advantageous features of the present invention will become more apparent from the following description of the preferred embodiments of the invention. [Embodiment] Referring now to the first to fourth figures, a magnetically driven vane pump according to a first embodiment of the present invention is shown. The pump includes a housing 10 having a cylindrical pump cavity 12 formed therein, the cylindrical pump cavity 12 housing a rotor 40 having an eccentric shaft offset from the axis of the pump cavity 12. The outer casing 10 is composed of a lower half 20 and an upper half 30 which are fastened to each other by a sealing ring 14 held therebetween. The lower half 20 and the upper half 30 are formed with a lower recess 21 and an upper recess 31, respectively, and the lower recess 21 and the upper recess 31 are connected to define the pump cavity 12. As seen in the third and fourth figures, the lower half 20 is formed to have a central bolt 22 that anchors a shaft 23 and an annular projection 26 between the central bolt 22 and a peripheral wall 28. The shaft 23 projects from the center bolt 22 into a central concave surface 29 of the lower half 20 to define an eccentric shaft and is surrounded by a bearing sleeve 24. A ring 32 is fitted inside the upper half 30 to extend around the periphery of the upper recess 31, and one of the axial ends rests on the peripheral wall 28 of the lower half 20. The upper portion 30 defines an inlet 34 for introducing fluid into the pump cavity 12 via one of the ports 32 and an outlet 36 for discharging fluid out of the pump cavity via one of the rings 32. . The rotor 40 is shaped as a disc disposed in the upper recess 21 and carries a plurality of vanes 50 which are each slidably received in a circumferentially distributed radial slot 42. As the drive rotor 40 rotates, each of the vanes 50 is radially outwardly displaced by a centrifugal force such that its outer end is in sealing contact with the interior of the ring 32, thereby forming a restriction between adjacent vanes and the ring 32. A displacement chamber between the rotor and the rotor. The displacement chamber undergoes expansion and contraction while the rotor 200839098 40 rotates about the eccentric shaft, thereby drawing fluid into the pump cavity 12 and discharging it out of the pump cavity 12. The rotor 40 carries a rotor magnet 60 that is magnetically coupled to a stator magnet 70 disposed outside the outer casing 10 for being driven thereby rotated. The rotor magnet 60 is a permanent magnet integrated with the rotor 40 to form a unitary structure. The rotor magnet 60 is shaped to have a thin base 62 fastened to one of the axial end surfaces of the rotor 40, a hub 64 projecting axially from the center of the base 62, and an outer ring 67 projecting axially from the periphery of the base 62. The hub 64 is housed in the central concave surface 29 in an overlapping relationship with the stator magnet 70 with respect to the radial direction of the eccentric shaft. The hub 64 is formed with a bearing bore 65 into which the shaft 23 extends, along with the bearing sleeve 24, such that the rotor magnet 60 is free to rotate with respect to the shaft 23 in conjunction with the rotor 40. The outer ring 67 projects into an annular groove 27 formed between the ring projection 26 and the peripheral wall 28 of the lower half 20 so as to be in overlapping relationship with the stator magnet 70 with respect to the radial direction. The outer ring 67 and the hub 64 form a major portion of the rotor magnet 60 which is disposed radially outwardly of the stator magnet 70 so as to overlap therewith, which minimizes the axial dimension and radial dimension of the pump. To reduce the radial vibration of the rotor 40 that can occur during rotation of the rotor 40 about the eccentric shaft, a vibration absorbing member 25 is inserted between the bearing bore 65 and the bearing sleeve 24 of the shaft 23. The stator magnet 70 is composed of a plurality of electromagnets mounted in an open space formed on the lower side of the annular projection 26 and extending around the center bolt 22. As shown in the third figure, the stator magnet 70 has its axial center C70 axially offset from the center C60 of one of the rotor magnets 60 so that it is eccentric with the rotor 40 from the rotor magnet 60 with respect to the 200839098. The axial direction of the shaft is further away. Accordingly, the stator magnet 70 generates an absorbing force to attract the rotor magnet 60 and axially direct the rotor 40 toward the stator magnet 70, thereby maintaining the rotor magnet 60 abutting the upper surface of the annular projection 26 and thus minimizing it during rotation of the rotor 40. Axial fluctuations. As shown in the fifth figure, each of the vanes 50 has ribs 54 formed on opposite sides thereof, the ribs 54 being slidably received into the guide grooves 44 formed on the opposite faces of the radial slits 42. The vanes 50 are only slidably retained within the radial slots 42 without being axially displaced out of the slots. The sixth and seventh figures illustrate a vane pump according to a second embodiment of the present invention, which is substantially the same as the first embodiment except that the rotor 40 itself is made of a permanent magnet to constitute the rotor magnet 60. Similar components are designated by like reference numerals and are not repeatedly explained herein for the sake of simplicity. The rotor 40 is disposed in a pump cavity 12 defined between the lower half 20 and the upper half 30 of the outer casing 10 and is confined within the circumference of the ring 32. Forming the rotor 40 into a generally flat disk having a plurality of circumferentially spaced radial slots 42 (each radial slot 42 receiving radially slidable vanes 50) and having a bearing in its center Apertures 65 are provided for receiving the shaft 13 and the bearing sleeve 24 such that the rotor 40 is free to rotate about the eccentric shaft defined by the shaft 13. The stator magnet 70 is disposed between the lower half 20 and the upper half 30 located radially outward of the ring 32 and consists of an electromagnet assembly having a light ring 72 having a plurality of circumferences The core 73, each circumferential core 73 carries a coil 74. The eighth and ninth drawings illustrate a vane pump according to a third embodiment of the present invention, except that the rotor 40 itself is made of a permanent magnet to constitute the rotor 11 200839098 magnet 60 and the stator magnet 70 are disposed outside the diameter of the rotor 40, which is substantially the same as the first embodiment. Like parts are designated by like reference numerals and are not repeatedly explained herein for the sake of simplicity. The rotor 40 is disposed in a pump cavity 12 defined between the lower half 20 and the upper half 30 of the outer casing and is confined within the circumference of the ring 22. The rotor 40 is shaped to have a hub 64 and an outer ring 67 integrally connected by means of a bridge 69. The hub 64 has a bearing bore 65 into which the shaft 13 is fitted in conjunction with the bearing sleeve 24 such that the rotor 40 is supported to the lower half 10 so as to be free to rotate about the shaft 13 or the eccentric shaft defined thereby. The upper half 30 is formed with an annular groove 38 extending between the hub 64 and the outer ring 67 of the rotor 40 to receive the stator magnet 70 therein. Accordingly, the stator magnet 70 is configured to have an overlapping relationship with the rotor magnet 60 or the rotor 40 with respect to the radial direction with respect to the eccentric shaft to minimize the axial dimension of the pump. The stator magnet 70 is an electromagnet assembly composed of a plurality of cores 73 (each of which carries a coil 74). Although the invention is specifically described with reference to the above embodiments, the invention should not be limited to the embodiments but may encompass any combination of the individual features disclosed in the above embodiments. BRIEF DESCRIPTION OF THE DRAWINGS The first drawing is an exploded perspective view of a vane pump according to a first embodiment of the present invention; the second drawing is a horizontal sectional view of the above-described vane pump; A cross-sectional view taken along line XX of the second figure; a fourth view: a cross-sectional view taken along line YY of the second figure; Figure 5: an exploded perspective view of one of the above-described vane pumps; The sixth figure of the water of the vane pump of the second embodiment of the method of the second embodiment of the present invention is based on the cross-sectional view of the present invention; ^ the cross-sectional view taken by the line 7_7 of the six-figure diagram; The water raft diagram of the vane pump of the third embodiment; and the cross section taken along line 9-9 of the eighth figure [main symbol description] 10 casing 12 pump cavity 13 shaft 14 seal Ring 20 lower half 21 lower recess 22 central bolt 23 shaft 24 bearing sleeve 25 vibration absorbing member 26 annular projection 27 annular groove 28 peripheral wall 29 central concave surface 3 〇 upper half 31 upper concave area 200839098 36 outlet 37 埠 38 ring Slot 40 Rotor 42 Radial Slot 44 Guide Slot 50 Vane 54 Rib 60 Rotor Magnet 62 Thin Base 64 hub 65 bearing hole 67 outer ring 69 bridge 7 0 stator magnet 72 ring 73 circumference core 74 coil