200945740 六、發明說明： 【發明所屬之技術領域】 本發明係有關-種電動馬達，其包括轉子、定子、扇輪、 及設在扇輪徑向上的導風元件，扇輪具有與扇輪轉動方向相 反的扇葉’其躲在轉盤上，且被蓋板所«，並具有其f 孔直徑及總直徑。 【先前技術】 此種電動馬達為習知。例如，參閱w〇 98/38899。此種電 動馬達例如設作成馬料輪單元。為提高扇輪效率，扇輪< 連接-個由擴散ϋ構成的導風元件，即，徑向回流導風葉， 其將空氣導入馬達内部，以使其散熱。 導風7L件’例如，螺旋罩及無導風葉的板形擴散器，皆增 大了徑向㈣，而使得空氣離開馬達，故該種裝置只在不需 以扇輪之魏對馬達進行散熱時才有意義。在該種情形下需 在馬達上m風扇H以另—個馬達驅動的散熱風扇 k供散熱氣流。設在扇輪徑向上的徑向導風元件，可連接徑 向回流導風葉而對馬達散熱。但，連接的徑向回流導風葉位 在徑向上，而如徑向導風元件一般大。 【發明内容】 上述之電動馬達，使其在徑 ’並以該馬達驅動的扇輪達 本發明之目的在於進一步改良 向及軸向上的尺寸可縮減至最小 到散熱。 098104038 200945740 本目的由申請專利範圍第1項之標的物達成，其使穿孔直 徑與總直徑的比例成為0.5至0.65，尤其是0.55至0.6， 且蓋板與轉盤的徑向外部為彼此平行，而該徑向外部為總直 徑的6至15%，尤其是8至12%。扇輪尤其適合於上述快 速旋轉的電動馬達，特別是轉速高於400轉/分，尤其是1000 轉/分至60000轉/分的磁阻電動馬達。習知的扇輪使用相反 於旋轉方向的扇葉，後彎的扇葉通常設有一個錐角為5°至 Q 30 °的錐形蓋板、或一個雙曲線蓋板。此種扇輪通常連接一 個軸向的導風元件。蓋板與轉盤彼此平行的徑向外部，對快 轉電動馬達的效率及穩定性皆為有利。此外，該種設計亦對 扇輪平衡之製程安全性為有利。故，本發明扇輪之平衡可利 用一個轴平行的衝壓工具進行，可使用該工具而加工蓋板之 徑向外部。此種工具加工比使蓋板產生傾角的工具加工為有 利。 〇 本發明之其他特徵將在下面依據附圖而說明，尤其是依據 申請專利範圍第1項或其他申請專利範圍。其亦可只依據申 請專利範圍第1項或其他申請專利範圍之單項特徵或獨立 特徵。 在本發明之進一步設計，使穿孔直徑與平行部間之進風處 的扇葉半徑為穿孔直徑的〇. 25至0. 35倍，尤其是0. 3倍。 該進風半徑明顯大於先前技術。該處之半徑乘數只為0.14 至 0. 2。 098104038 5 200945740 藉由使進風處扇葉咼度的四倍等於穿孔直徑的丨.6至2. 3 倍，尤其是1.8至2. 1倍，可達到高效率。故可得到直徑小 及轉速尚的扇輪，其雖然尺寸小，但可確保足夠的負壓及高 效率’尤其是空氣的流^ ’使得，所連接的導風元件可將氣 流此量轉換成壓力。藉由使總直徑與定子直徑的比例為〇 9 至1.05 ’尤其是0.95幻，可進一步縮小電動馬達之徑向 尺寸，而得到輕薄短小的馬達扇輪單元。 連接在扇輪後方的導風元件具有軸向的導風葉。該導風元 件將扇輪流出的空氣轴向地導引至定子，而對馬達散熱。導 風元件至少部分徑向包圍電動馬達。不同於切技術，其只 使用軸向的設計，而導致延遲、氣流衰減及效率降低，本發 明導風兀件之軸向長度與扇葉高度的比例為2 3至2 9,尤 其是2.45至2_75。扇葉外徑為導風元件外徑的Q 6至〇 85 倍’尤其是〇· 68至0· 72倍。導風元件内徑為導風元件外徑 的0· 52至0. 82倍，尤其是〇· 62至〇 72倍。此種尺寸使得 轴向導風元件可設在馬達橋部上，故只需將扇輪設在電動馬 達軸向刚方。因此’馬達扇輪單元可縮賴向長度。 本發明之進一步設計，使導風葉具有小的彎曲半裡尤呈 是在葉片高度上保射H故’導風荦f曲丰n ’、 外徑的比例為〇.㈣.34,尤= 曲: 風葉彎曲半彳f销.3G °小的導 到定子月面H 被導至輪向，平直地流 到疋子周面虱錢動會導至氣流損失。而且，在導風元件 098104038 200945740 由塑膠射出成形件構成時’恆定的彎曲半徑可確保其 形模具之賴。導風元件軸向錢與其外彳^_為射= 至0. 33 ’尤其是〇 25至〇, 26。 之進—步設計’使導風葉以軸向來料扇葉轉動方 =傾斜。I由於延遲降至最小，而達到較隹的馬達散熱。 於該傾斜设計，氣流之徑向部分朝向 ‘、、、 ❹ :_定子表面。如此，對電動馬達:二較 、心又強郎流時為有必要。導風葉在導風元件出風 傾斜角度為25。至50。，尤其是30。至44、 為進-步改良馬達散熱，導風元件設有—個或多個窗口狀 徑向向内的開孔，例如，2個至6個，尤其是4個此種開孔。 ,、位在子之由口處，故’由導風元件窗口狀開孔流出的空 氣，可經由馬達橋部之相應開孔而流入馬達中。 上述數子範圍如未舉例則包括所有中間值，甚至是1/1〇 ©之值、下限及/或上限推至另一極限值的1/1〇，此處「及」 表示可由極限值推出數十分之一。 以下將依據附圖詳細說明本發明之兩個實施例。 【實施方式】 圖1至3顯示本發明之電動馬達1，其包括一個設在轉子 軸2上的扇輪3及-個導風元件4。扇輪3框設在轉子袖2 上，可被該轉子軸驅動旋轉，而轉子軸2與電動馬達丨之未 示出的轉子@]疋連接。轉子與電動馬達丨之定子5互相作 098104038 200945740 用。導風元件4不可旋轉地固定在定子5上，尤其是與未示 出的軸承橋鉚接，而轉子轴2穿過該轴承橋。 以下將依據圖4至6詳細說明扇輪3。 扇輪3在本實施例中具有7個朝扇輪3轉動方向r之相反 方向彎曲的扇葉6。該等彎曲扇葉徑向向外延伸，並設在一 個圓環形轉盤7上，其中心有一個穿孔8。扇葉6由穿孔邊 緣徑向向外延伸至轉盤7邊緣。 設在轉盤7上的扇葉6被一個蓋板9所覆蓋。該蓋板具有 一個徑向外部10，其係平行於轉盤7。環形的外部10之徑 向内侧連接一個雙曲線彎曲的、且與轉盤7距離漸增的中心 部。其凸起部分延伸至蓋板9之中心穿孔之邊緣，而該中心 穿孔11直徑與轉盤中心穿孔8相同，並與其同軸。 轉盤7、蓋板9、及扇葉6由金屬材料或塑膠所製成，必 要時可與鋁製上蓋連接，例如，使用鉚接。 在所示實施例中，穿孔直徑D!為扇輪3之總直徑D2的0. 55 至0. 6倍。總直徑D2約為定子D3之直徑的0. 84至0. 99倍， 尤其是0. 89至0. 94倍，例如0. 91倍。 平行的外部10為D4/D2=0. 88至0. 92，故，外部10約佔 總直徑D2的8至12%。 在本實施例中，進風半徑Re為穿孔直徑仏的0.3倍。扇 葉進風部高度h的四倍，為穿孔直徑D!的1. 8至2. 1倍， 故，利用大進風半徑Re而達到高效率。扇葉6在進風口處 098104038 200945740 的角度（角A)為29°，在出風口處的角度（角冷2)為32.5°， 而兩角度大約相同。 圖7至11說明導風元件4之第一實施例。 導風元件4為一個塑膠射出成形件，並為一個軸向導風元 件，而該導風元件具有基本上為轴向延伸的導風葉12。在 本實施例中，導風元件4具有20個環狀平均分佈的導風葉 12 ° 〇 相較於習知的轴向導風元件，導風元件4具有較小的轴向 長度。故，其長度{為扇輪3之扇葉高度h的2. 45至2. 75 倍，例如2. 6倍。外徑D5為D2/D5=0. 68至0. 72。内徑De 約等於扇輪總直徑D2，而導風元件4之内徑De約為外徑Ds 的0. 62至0. 72倍，例如0. 665倍。 由於上述尺寸，軸向的導風元件4可設在上述馬達橋部 上，故，只有扇輪3設在電動馬達1軸向前方。因此，馬達 〇 扇輪單元可具有較小的軸向長度。 導風葉12之彎曲半徑RL為Rl/D5=0.22至0.30，例如 0. 255，而屬相當小，並在葉片高度上保持恆定。該小彎曲 半徑確保空氣在極短距離後即被導向軸向，而平直地流向定 子5周面。 導風元件之軸向長度約為導風元件之外徑D5的0.18至 0. 33倍，例如0. 253倍。 導風葉12傾斜於扇輪3之轉動方向r。故每一導風葉12 098104038 9 200945740 在導風元件出風口處皆傾斜約35。（見圖11角泠在另 一實施例中，/3 3為31。或43。。 導風葉進風角石4,亦即，導風元件與進風面的爽角，為 Γ至5°。出風角則為90。，亦即，空氣軸向流出導风元件心 在本實施例中扇輪3與導風元件4葉片的比例為7 : 2Q， 而最佳化旋轉噪音。 為進一步改良馬達散熱，4個在導風扇12中間的通道13 在出風口側被一個徑向擋板14所封閉。流經通道13的办 再由馬達橋相應的 氣，由窗口狀的開孔15徑向流入内部， 開孔流入馬達中。 擋板14可進一步用於固定跨設在扇輪3上的扇輪蓋。 在本實施例中，導風元件4與扇輪3之轴向距離a，約為 扇輪3在轉盤7與蓋板9間之平行部分高度比的〇1至〇 * 倍’例如0. 13倍。 軸向導風元件4設在馬連橋部上而節省空間，在結構強度 方面可承受外部機械負冑’例％，由扇輪蓋輸人。由於傾二 的導風葉12，扇輪蓋可藉預應力而在徑向呈無縫隙。 圖12至Η顯示導風元件4之第二實施例，其在導風葉 12之位置、外塑、及方向，以及導風元件4之直徑及長度 方面，皆與第實施例一致。 圖12顯示與電動馬達1及包圍電動馬達的馬達殼16之相 對位置。導風元件4經由與支撐導風扇12的導風環 17相同 098104038 200945740 #料的十子形橋部18 ’而與馬達殼16連接，尤其是利用娜 接（比較圖13)。橋部18中心有一個使轉子軸2通過的穿 孔19。 ~ 馬独16之頂部，並與之有數毫米之距 離’例如2ηπη。 相鄰於馬達殼16之導風元件固定部的馬達殼頂部設有穿 通口 20，由導風環17之徑 Ο 向開口 15流入的空氣，可由該 穿通口進入馬達殼内部，而 直接對電動馬達1進行散埶。 使整麵料料元達龍小_向及軸向 同時’可達_6Q%之高扇輪效率。此處= 2_導風元件4,而確保足夠的馬達散熱。藉由平行於 轉盤7的蓋板9之環形外、 y KP1G ’可簡單地利用衝壓工且而 使扇輪3平衡。 发工具而 ❹ 所有揭示特徵本身皆具有發明性質。本發明揭示之特徵完 全包含於本案之申請專利範圍中。 70 【圖式簡單說明】 視圖 圖1係本發明電動馬達第實施例扇輪與導風元件之側 圖2係扇輪之俯視圖。 圖3係本發明電動馬達之後視立體圖 圖4係扇輪之立體圖。 圖5係扇輪之侧視圖。 098104038 11 200945740 圖6係圖5線VI-π之剖面圖。 圖7係導風元件導風葉出風口側之立體圖。 圖8係導風元件導風葉進風口侧之立體圖。 圖9係圖8線IX-IX之剖面圖。 圖10係導風葉之側視圖。 圖11係圖10線XI -XI之剖面圖。 圖12係本發明電動馬達第二實施例導風元件之立體圖。200945740 VI. Description of the Invention: [Technical Field] The present invention relates to an electric motor including a rotor, a stator, a fan wheel, and a wind guiding member disposed in a radial direction of the fan wheel, the fan wheel having a rotation with the fan wheel The opposite direction of the blade's hides on the turntable and is covered by the cover, and has its f-hole diameter and total diameter. [Prior Art] Such an electric motor is conventional. See, for example, w〇 98/38899. Such an electric motor is provided, for example, as a horse wheel unit. In order to increase the efficiency of the fan wheel, the fan wheel < connects a wind deflecting element composed of a diffusing weir, i.e., a radial return air deflecting vane, which introduces air into the interior of the motor to dissipate heat. The guide air 7L piece 'for example, the spiral cover and the plate-shaped diffuser without the guide vane increase the radial direction (4), so that the air leaves the motor, so the device only needs to dissipate the motor by the fan wheel. It only makes sense. In this case, the fan fan H is required to dissipate the airflow by the fan fan H driven by another motor. A radial air guiding element disposed in the radial direction of the fan wheel is connected to the radial return air guide vane to dissipate heat from the motor. However, the connected radial return air guide vanes are radially, as is generally the case with radial wind deflecting elements. SUMMARY OF THE INVENTION The above-described electric motor has a diameter of a fan wheel driven by the motor. The object of the present invention is to further improve the size in the axial direction and the axial direction to minimize heat dissipation. 098104038 200945740 The object is achieved by the subject matter of claim 1 which has a ratio of the diameter of the perforation to the total diameter of 0.5 to 0.65, in particular 0.55 to 0.6, and the radially outer portions of the cover plate and the turntable are parallel to each other. The radially outer portion is from 6 to 15% of the total diameter, in particular from 8 to 12%. The fan wheel is particularly suitable for the above-mentioned fast-rotating electric motor, in particular a reluctance electric motor having a rotational speed of more than 400 rpm, in particular from 1000 rpm to 60,000 rpm. Conventional fan wheels use blades that are opposite to the direction of rotation, and the back-curved blades typically have a tapered cover with a taper angle of 5° to Q 30°, or a hyperbolic cover. Such a fan wheel is typically coupled to an axial wind deflecting element. The radially outer portion of the cover plate and the turntable are parallel to each other, which is advantageous for the efficiency and stability of the fast-turning electric motor. In addition, this design is also beneficial to the process safety of the fan wheel balance. Therefore, the balance of the fan wheel of the present invention can be performed by a parallel punching tool which can be used to machine the radially outer portion of the cover. This tooling is advantageous for machining tools that produce an angle of inclination of the cover. Other features of the present invention will be described below with reference to the accompanying drawings, particularly in accordance with claim 1 or other patent claims. It may also be based solely on the individual features or independent features of claim 1 or other patent applications. 5倍。 In particular, the radii of the perforation is 0.25. This inlet radii are significantly larger than prior art. The radius multiplier here is only 0.14 to 0.2. 098104038 5 200945740 High efficiency can be achieved by making the fan blade of the inlet air four times equal to the diameter of the perforation of 丨.6 to 2.3 times, especially 1.8 to 2.1 times. Therefore, a small diameter and a rotating speed fan wheel can be obtained, which, although small in size, can ensure sufficient negative pressure and high efficiency, especially the flow of air, so that the connected air guiding element can convert the air flow amount into pressure. By making the ratio of the total diameter to the stator diameter 〇 9 to 1.05 ', especially 0.95 illusion, the radial size of the electric motor can be further reduced, resulting in a light and short motor fan unit. The air guiding element connected behind the fan wheel has an axial wind guide vane. The air guiding member axially guides the air flowing out of the fan wheel to the stator to dissipate heat from the motor. The wind deflecting element at least partially radially surrounds the electric motor. Unlike the cutting technique, which uses only the axial design, resulting in delay, airflow attenuation and efficiency reduction, the axial length of the air guiding element of the present invention is proportional to the blade height of 23 to 2 9, especially 2.45 to 2_75. The outer diameter of the blade is Q 6 to 〇 85 times the outer diameter of the air guiding element, especially 〇·68 to 0·72 times. The inner diameter of the air guiding element is from 0. 52 to 0.82 times the outer diameter of the air guiding element, especially 〇·62 to 〇 72 times. This size allows the shaft guide element to be placed on the motor bridge, so the fan wheel only needs to be placed in the axial direction of the motor. Therefore, the 'motor fan unit can be retracted to the length. According to a further design of the present invention, the guide vane has a small curved half, and the heat is maintained at the height of the blade. Therefore, the ratio of the outer diameter is 〇. (4).34, especially = 曲: The wind blade bends half a 彳f pin. The small 3G ° guide to the stator lunar surface H is guided to the wheel direction, and flows straight to the circumference of the rafter. Moreover, when the wind guiding element 098104038 200945740 is formed of a plastic injection molded part, the constant bending radius ensures the shape of the mold. The axial direction of the wind guiding element and its external enthalpy ^_ is shot = to 0.33 ' especially 〇 25 to 〇, 26. The advance-step design 'turns the guide vane in the axial direction of the fan blade = tilt. I achieves a cooler motor heat dissipation due to the minimization of the delay. In this inclined design, the radial portion of the airflow faces the ‘, , ❹:_ stator surface. In this way, it is necessary for the electric motor: when the heart is strong and the heart is strong. The guide vane is inclined at an angle of 25 at the wind deflecting element. To 50. Especially 30. To 44, to improve the heat dissipation of the motor, the air guiding element is provided with one or more window-like radially inward openings, for example, 2 to 6, especially 4 such openings. , located at the mouth of the sub-port, so the air flowing out of the window-shaped opening of the wind guiding element can flow into the motor through the corresponding opening of the motor bridge. The above range of numbers includes all intermediate values if not exemplified, even 1/1〇© value, lower limit and/or upper limit are pushed to 1/1 of the other limit value, where "and" means that the limit value can be derived. One tenth. Two embodiments of the present invention will be described in detail below with reference to the accompanying drawings. [Embodiment] Figs. 1 to 3 show an electric motor 1 of the present invention comprising a fan wheel 3 provided on a rotor shaft 2 and a wind guiding member 4. The fan wheel 3 is framed on the rotor sleeve 2 and is rotatable by the rotor shaft, and the rotor shaft 2 is coupled to an unillustrated rotor @]疋 of the electric motor unit. The rotor and the stator 5 of the electric motor are used for each other 098104038 200945740. The wind deflecting element 4 is non-rotatably fixed to the stator 5, in particular to a bearing bridge not shown, and the rotor shaft 2 passes through the bearing bridge. The fan wheel 3 will be described in detail below with reference to Figs. In the present embodiment, the fan wheel 3 has seven blades 6 which are curved in the opposite direction to the direction r of rotation of the fan wheel 3. The curved blades extend radially outwardly and are disposed on a circular turntable 7 having a perforation 8 in the center thereof. The blade 6 extends radially outward from the perforated edge to the edge of the turntable 7. The blade 6 provided on the turntable 7 is covered by a cover 9. The cover has a radially outer portion 10 that is parallel to the turntable 7. The outer portion 10 of the ring is connected to the inside by a hyperbolic curved center portion which is gradually spaced from the turntable 7. The raised portion extends to the edge of the central perforation of the cover plate 9, and the central perforation 11 has the same diameter as the central opening 8 of the turntable and is coaxial therewith. The turntable 7, the cover 9, and the blade 6 are made of a metal material or plastic, and may be connected to the aluminum upper cover if necessary, for example, by riveting. 5倍。 In the embodiment of the present invention, the total diameter D2 of the fan wheel 3 is 0. 55 to 0.6 times.倍倍。 For example, the total diameter D2 is about 0. 84 to 0. 99 times, such as 0. 91 times. The parallel outer portion 10 is D4/D2 = 0.88 to 0.92, so the outer portion 10 accounts for about 8 to 12% of the total diameter D2. In the present embodiment, the inlet air radius Re is 0.3 times the diameter of the perforation 仏. Four times the height h of the fan blade inlet portion is 1.8 to 2.1 times the diameter of the perforation D!, so that the high inlet radii Re is used to achieve high efficiency. The angle of the blade 6 at the air inlet 098104038 200945740 (angle A) is 29°, and the angle at the air outlet (angle cold 2) is 32.5°, and the two angles are approximately the same. 7 to 11 illustrate a first embodiment of the wind guiding member 4. The wind deflecting element 4 is a plastic injection molded part and is a shaft-guided wind element having a substantially axially extending guide vane 12. In the present embodiment, the air guiding member 4 has 20 annularly distributed wind guide vanes 12 ° 导 The wind guiding member 4 has a smaller axial length than the conventional axial wind guiding member. 5倍。 For example, the length of the fan blade 3 is 2.45 to 2.75 times, such as 2.6 times. The outer diameter D5 is D2 / D5 = 0.60 to 0.72. The inner diameter De is approximately equal to the total diameter D2 of the fan wheel, and the inner diameter De of the air guiding member 4 is about 0.62 to 0.72 times, for example, 0. 665 times. Due to the above dimensions, the axial air guiding member 4 can be provided on the motor bridge portion, so that only the fan wheel 3 is provided in the axial forward direction of the electric motor 1. Therefore, the motor 扇 fan wheel unit can have a small axial length. The bending radius RL of the guide vane 12 is Rl / D5 = 0.22 to 0.30, for example 0. 255, and is relatively small and remains constant at the blade height. This small bending radius ensures that the air is guided to the axial direction after a very short distance and flows straight to the stator 5 circumference. 253倍。 The axial length of the air guiding element is about 0.18 to 0.33 times the outer diameter D5 of the air guiding element, for example, 0. 253 times. The guide vane 12 is inclined to the direction of rotation r of the fan wheel 3. Therefore, each guide vane 12 098104038 9 200945740 is inclined at about 35 at the air outlet of the wind guide member. (See Fig. 11 corners. In another embodiment, /3 3 is 31. or 43. The wind guide vanes 4, that is, the cool angle of the wind deflecting element and the air inlet surface, is Γ to 5°. The air exit angle is 90. That is, the air axially flows out of the air guiding member core. In the present embodiment, the ratio of the fan wheel 3 to the air guiding member 4 blade is 7:2Q, and the rotation noise is optimized. The motor dissipates heat, and the four passages 13 in the middle of the guide fan 12 are closed by a radial baffle 14 on the air outlet side. The flow through the passage 13 is further controlled by the motor bridge, and the radial opening 15 is formed by the window. Flowing into the interior, the opening flows into the motor. The baffle 14 can be further used to fix the fan wheel cover spanning over the fan wheel 3. In the present embodiment, the axial distance a between the air guiding member 4 and the fan wheel 3 is about The ratio of the height ratio of the parallel portion of the fan wheel 3 between the turntable 7 and the cover plate 9 is 〇1 to 〇* times ', for example, 0.1 times. The shaft guide member 4 is disposed on the Malian bridge portion to save space in the structural strength. The aspect can withstand the external mechanical negative 胄 'example%, input by the fan wheel cover. Due to the diverting guide vane 12, the fan wheel cover can be seamless in the radial direction by prestressing Figures 12 through 12 show a second embodiment of the wind deflecting element 4 which is consistent with the first embodiment in terms of the position, outer shape, and direction of the guide vanes 12, and the diameter and length of the wind deflecting member 4. The position relative to the electric motor 1 and the motor casing 16 surrounding the electric motor is displayed. The wind guiding member 4 is connected to the motor casing 16 via the ten-shaped bridge portion 18' which is the same as the air guiding ring 17 that supports the guide fan 12. The connection, in particular the use of the splicing (compare Fig. 13), the center of the bridge 18 has a perforation 19 through which the rotor shaft 2 passes. ~ The top of the horse 16 and has a distance of a few millimeters 'eg 2 ηπη. Adjacent to the motor The top of the motor casing of the air guiding member fixing portion of the casing 16 is provided with a through opening 20, and the air flowing in from the opening 15 of the air guiding ring 17 can enter the inside of the motor casing through the through opening, and directly disperse the electric motor 1.埶. Make the whole fabric material element Dalong small _ direction and axial simultaneous 'reachable _6Q% high fan efficiency. Here = 2_ wind deflecting element 4, and ensure sufficient motor heat dissipation. By parallel to the turntable The outer cover of the cover plate 9 of 7 is y KP1G 'can be simple The fan wheel 3 is balanced by the stamping machine. The hair tool is all invented. All the features disclosed are inherent in the invention. The features disclosed in the present invention are fully included in the scope of the patent application of the present application. 70 [Simple description of the drawing] View 1 Fig. 3 is a perspective view of the rear view of the fan wheel and the air guiding member of the first embodiment of the present invention. Fig. 3 is a perspective view of the electric motor of the present invention. Fig. 5 is a side view of the fan wheel. 098104038 11 200945740 Fig. 6 is a cross-sectional view taken along line VI-π of Fig. 5. Fig. 7 is a perspective view of the air outlet side of the air guiding member of the air guiding member. Figure 8 is a perspective view of the air inlet side of the air guiding member of the air guiding member. Figure 9 is a cross-sectional view taken along line IX-IX of Figure 8. Figure 10 is a side view of the guide vane. Figure 11 is a cross-sectional view taken along line XI-XI of Figure 10. Figure 12 is a perspective view of a wind deflecting member of a second embodiment of the electric motor of the present invention.
圖13係圖12、線ΧΙΙΙ-χπκ剖面圖，其中電動馬達被省 略。 圖14係圖12線XIV-XIV之剖面圖，其中只顯示導風元件 圖15係本發明電動馬達、扇輪、及導風元件尺寸Figure 13 is a cross-sectional view of the line ΧΙΙΙ-χπκ in Fig. 12, in which the electric motor is omitted. Figure 14 is a cross-sectional view taken along line XIV-XIV of Figure 12, in which only the wind guiding member is shown. Figure 15 is the size of the electric motor, the fan wheel, and the wind guiding member of the present invention.
圖。 【主要元件符號說明】 1 電動馬達 2 轉子轴 3 扇輪 4 導風元件 5 定子 6 扇葉 7 轉盤 8 穿孔 9 蓋板 098104038 200945740 10 (徑向、環形）外部 11 (中心）穿孔 12 導風葉 13 通道 14 擋板 15 開孔 16 馬達殼 〇 17 導風環 18 橋部 19 穿孔 20 穿通口 a (軸向）距離 Di (穿孔）直徑 d2 總直徑；（扇葉）外徑 ❹ D3 (定子）直徑 d4 内徑 . Ds (導風元件）外徑 d6 (導風元件）内徑 h (扇葉）高度 hi (扇輪）高度 i (軸向）長度 r 轉動方向 098104038 13 200945740 Re (進風處扇葉）半徑 Rl (導風葉彎曲）半徑 β' (進風口侧扇葉）角度 β 2 (出風口側扇葉）角度 (出風口側扇葉）角度 β在 (進風口側扇葉）角度Figure. [Main component symbol description] 1 Electric motor 2 Rotor shaft 3 Fan wheel 4 Wind deflector 5 Stator 6 Fan blade 7 Turntable 8 Perforation 9 Cover plate 098104038 200945740 10 (radial, ring) Exterior 11 (Center) Perforation 12 Guide vane 13 Channel 14 baffle 15 opening 16 motor housing 〇 17 air guiding ring 18 bridge 19 perforation 20 through port a (axial) distance Di (perforation) diameter d2 total diameter; (fan blade) outer diameter ❹ D3 (stator) diameter D4 inner diameter. Ds (air guide element) outer diameter d6 (air guide element) inner diameter h (fan blade) height hi (fan wheel) height i (axial) length r direction of rotation 098104038 13 200945740 Re (wind fan Leaf) Radius Rl (window blade bending) Radius β' (air inlet side fan blade) Angle β 2 (air outlet side fan blade) angle (air outlet side fan blade) angle β at (air inlet side fan blade) angle
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