201244342 六、發明說明： 【發明所屬之技術領域】 本發明係有關一種電動車輪内齒輪馬達模組，特別是指一 種將馬達與齒輪減速機構整合成一體之電動車輪内齒輪馬達 模組，其兼具動態平衡性佳、安裝空間小、可變換減速比及裝 配容易等優點及功效。 【先前技術】 齒輪減速機是一種傳達動力的機構裝置，因具有降低輸出 轉速和產生高於馬達輸出軸之扭矩的兩個主要功能，常與馬達 作組合搭配，廣泛使用於機器人、自動化生產設備、工具機、 電動載具以及電動手工具等需要高扭矩低轉速的應用場合。 一般來說，馬達與齒輪減速機通常係個別製造完成後，再 進行連結傳動，故，常存在著以下缺點： [1]動態平衡性不佳。習知技術之馬達與齒輪減速機係藉 由連結達到傳動，並非整合於一體，動態平衡性不佳，容易於 傳動時產生振動及噪音。 、，ra整體的*裝空間較大：由於馬達與減速齒輪機個别製 ^後連結’裝設之空間固定而不易變化，無法有效規劃安裝的 二間，故’具有安裝空間較大之缺點。 因此’有必要研發新產品，以解決上 。 【發明内容】 I目明之目的在於提供-種電動車輪内錄馬賴組，其 佳、安裝空間小、可變換減速比及裝配容易等 ==£^以解決習城術動態平衡性不佳及整體的安裝 齒輪題之技術手段係、提供—種電動車輪内 齒難I鋪’祕具有殼體如及m個第一行星 201244342 一第二殼體，其係具有一第二殼體空間及一環齒輪部； 一定子部，其係固定於該第一殼體空間内；該定子部係具 有一環狀殼體及複數線圈部，複數線圈部係大體上 . 設於該環狀殼體上； τ 轉子，，其係具有一轉軸、複數永久磁石及一太陽齒 輪；該轉⑽具有-第—樞接端及—第二樞接端，該第一梅接 端係樞接於該第一殼體上，而該第二樞接端係樞接於該第二殼 體上；複數永久磁石係環狀排列的設於該轉軸上，並對應複^ 線圈部；而該太陽齒輪係設於該轉軸上；及 〜 一行星齒輪組，其係具有一行星架及Μ個行星齒輪；該 行星架係固疋於該第一殼體上，且具有Μ個第一行星齒輪固 定部，该行星齒輪係具有一軸部及一齒輪部，該齒輪部梓^ 於該軸部上，該軸部係具有兩端，其一端係樞接於J第：；行^ 齒輪樞轉部，另一端係固定於該第一行星齒輪固定部，而該齒 輪部係分別嚅合該環齒輪部及該太陽齒輪;Μ係為該太陽齒輪 之齒數與該環齒輪部之齒數的公因數，且Μ為一正整數；又： 該轉軸係可樞轉的穿設於該行星架上，且該轉子部、該環 部及及該行星架係為共軸。 輪 藉此，當電源供應至該定子部之線圈部中時，該等線圈部 產生磁場並與該轉子部之永久磁石產生磁作用，以推動該轉子 部轉動，並連動該行星齒輪、該環齒輪部轉動，進而帶動誃 二殼體達到轉動。 Χ 本發明之上述目的與優點，不難從下述所選用實施例之 細說明與附圖中，獲得深入暸解。 兹以下列實施例並配合圖式詳細說明本發明於後： f實施方式】 如第至第二圖所示，本發明係為一種電動車輪内齒輪馬 達模組，其包括··一第一殼體10、一第二殼體20、一定子部 30、一轉子部40及一行呈齒輪組5〇。 關於該第一殼體10，其係具有一第一殼體空間u及]^個 201244342 =星齒輪樞轉部12 ;在設計上，該第一殼體10係由一後 ^ —蓋10A、一彀部10B、一前馬達蓋10C所組成，並由複數 二^螺絲/0D進行固定，且該後馬達蓋10A上又固定有一樞轉 架0E ’該彳區轉架10E係以複數樞轉架固定螺絲10F而鎖合於 該後馬達蓋10A上。 .該第二殼體20係具有一第二殼體空間21及一環齒輪部 22 ’在設計上，該第二殼體20係由該環齒輪部22 ' —滚珠軸 承24、一滾珠軸承外環24A、一環齒輪輸出外殼23、一密封 蓋25及一環齒輪固定螺絲26所組成。 關於該定子部3〇，其係固定於該第一殼體空間11内；該 定子部30係具有環狀殼體31及複數線圈部32 ;該環狀殼體 31係由複數矽鋼片311及複數定位銷312組成，該複數定位 銷312係固定於該第一殼體1〇之後馬達蓋10A上；複數線圈 部32係大體上平均排列的設於該環狀殼體31上。 該轉子部40係具有一轉抽41、複數永久磁石42及一太 陽齒輪43 ;該轉軸41係具有一第一樞接端411及一第二樞接 端412 ’該第一樞接端411係枢接於該第一殼體10上，而該 第二樞接端412係樞接於該第二殼體20上；複數永久磁石42 係環狀排列的設於該轉轴41上，並對應複數線圈部32 ;而該 太陽齒輪43係設於該轉軸41上；在設計上，該轉軸41之第 二樞接端412係套設有一滚子軸承412A及鎖合一堡型螺帽 412C，並設有一墊片412B。 而該行星齒輪組50係具有一行星架51及Μ個行星齒輪 52 ;該行星架51係固定於該第一殼體10上（固定不動），且 具有Μ個第一行星齒輪固定部511及複數複數行星架固定螺絲 512，該行星架固定螺絲5丨2係用以將該行星架51固定於該第 一殼體10之前馬達蓋10c上；該行星齒輪52係具有一軸部 521及一齒輪部522 ’該齒輪部522係樞設於該軸部521上， 該軸部521係具有兩端’其一端係樞接該第一行星齒輪樞轉部 12,另一端係固定於該第一行星齒輪固定部5丨1(該軸部521 201244342 輛部固定銷犯⑻，而該齒輪部 ΐίί又^^齒輪部22之齒數的公因數，且Μ為一 却鐘^ μ轉軸41係可樞轉的穿設於該行星架51上，且 該轉子σΜ0、騎練部22錢行絲5 子部作為轴心達到連結，動態平衡性佳）。^ 線圈f供應至該定子部3G之線圈部32中時，該等 ί 與轉作4G之永久啦42產生磁作 輪部22轉^ 轉動，並連動該行星齒輪52、該環齒 輪4躺it而帶動該第二殼體12達到轉動。 I數的數量(M)，其係、為該太陽齒輪43之 齒心齒輪。卩22之齒數的公因數，且M為—正 陽錄43之絲為十二齒，耗齒輪部& ί數it r齒^則該行星齒輪52之數量m即為為十二及 2四的么隨’也就是該行星錄52的數量(m)可為兩個或 更詳細的說，該第二殼體20即為 由該43太陽齒輪43而將該轉子部4〇產生 ^ 最後再由該環齒輪部22作動力輸出，使該第^ 體轉動。 本發明之純伽減速tt方面，似下列之實施例進行說 明： 如第四圖所不，假設該太陽齒輪43之齒數為十二齒，該 環齒輪部22之齒數為四十四齒，而該行星錄52之數量(M) 為四個’且每-行星齒輪52之齒數為十六齒；根據相對速度 法可知： ^carrier sg 44x16 ^χ^'ΤΙ^ = -3·6667 12〜+ 44% = 56〇)_er (輪系方程式）； 201244342 由於該行星架51係固定於該第二殼體2〇 代入輪系方程式可得：12〜=_44〜； 故 而減速比 gr(gear ratio)=i=^=-3 6667 .甘丄 ω⑽出 · °/，具中， 為該環齒輪部22至該太陽齒輪43之輪系值. 〜為該太陽齒輪43之角度速； ~為該環齒輪部22之角速度； ^carrier 為該行星架51之角速度； \為该太陽齒輪43之齒數； 為該環齒輪部22之齒數； '為该行星齒輪52之齒數。 -及Ϊ於體2G ’其又包括—環齒輪輸出外殼观如第 ϊίί ΐ it ί ’Π於該環齒輪部22上’用以鎖固 =輪圈n(如第五a及第五B圖所示，其係本發明與〇 鎖固之不意圖）；也就是說，#該轉子部4 力 最後再由該，，22作動力輸 ±轉動時’係會使㈣環齒輪輸出外殼23同步轉動， ==輪70轉動;在設計上，該環齒輪輸出外殼23係具 ^巧咖定_ 231，肋鎖合車輪_ 71，達到該環齒 輪輸出外殼23與車輪70之固定。 關，该太陽齒輪43、該行星齒輪52及該環齒輪部22之 t式，係可為螺旋齒輪或正齒輪配合。 關於本發明之特點，係至少包括下列四種： [a]行星齒輪數量設計。本發明之行星齒輪52之數量，係 為該太陽齒輪43之齒數與該環齒輪部22之齒數的公因數。 軸設計。本發明之該轉子部4〇、該環齒輪部22及 該行星架51係為共軸設計，動態平衡特性佳，可有效降低振 動與噪音。 201244342 改減速比。本發明只需改變該太陽錄43、該環步 「ϋ該行星齒輪52之齒數，即可變更齒輪減速比。 ^1]機構整合。本發縣馬達(也就是由該奸部3 賴f I0構成之無獅達)與該行星餘組5G整合成一體了 可縮小輪内馬達（即本發明）之軸向與徑向體積。 及一圖所示’本發明之又包括-轉向懸吊架60 馬達轉向拉桿8〇 ;該轉向懸吊帛6〇係具有係固定於 ^ ’而該第-殼體1〇係樞接於該轉向懸吊架 歹 有了上臂61、—下臂62及—避震㈣Ϊί 拉杯80係设於電動車上，用以控制該第—殼體10於 該轉向懸吊架60上之轉動角度。 ； 鍾的說，該第一殼體10係以該樞轉架⑽拖接於誃 Ϊ向^架⑽之上臂6卜下臂62及該馬達轉向轉8〇 ;、Ϊ 殼體〇 Ξ2ΪΪ:拉桿80之直線位置變化’而控制該第二 模组;角度(也就是本發明之電動車輪_輪馬達 模組於該轉向懸吊架60上轉動）。 ^ 動車左前方車輪來說，如第七A圖所示，當該馬達轉 80位於一第-位置P1時，該第-殼體1 〇係往-第一 去;預定角度卜也就是右轉；如第七B圖所示’ 轉向拉桿80位於一第二位置P2時’該第-殼體10 轉向拉之狀態，也就是直行；如第七C圖所示，當該馬達 80位於—第三位置p3時，則該第—殼體1〇係往j 第一^A2轉動—缺角度Θ，也就是左轉。 ^上所述，本發明之優點及功效可歸納為： 遠Ιΐ態平離佳。f知技狀馬賴錄減速機係藉由 動ί逢’並非整合於一體，動態平衡性$佳，容易於傳 及噪音；而本發明之轉子部40、該環齒輪部22 與ϋ星架51係、為共轴之設計，動態平衡性佳，可降低振動 [2]安裝空間小。本發明之馬達(也就是由該定子部3〇及 201244342 該轉子部40構成之無刷馬達)與該行星齒輪組5〇整合成一 體，可縮小輪内馬達（即本發明）之軸向與徑向體積，故，具有 安裝空間小之優點。 〃 [3] 可變換減速比。本發明在設計上’只需改變該太陽齒 輪43、該環齒輪部22或該行星齒輪52之齒數，即可變更齒 輪減速比。 [4] 裝配容易《本發明之行星齒輪52數量(μ)為該太陽齒 輪43之齒數與該環齒輪部22之齒數的公因數，可以減少因該 行星齒輪52相位誤差問題造成的裝配困難。 以上僅疋藉由較佳貫施例詳細說明本發明，對於該實施例 所做的任何簡單修改與變化，皆不脫離本發明之精神與範圍。 ^以上詳細說明，可使熟知本項技藝者明瞭本發明的確可 達成前述目的’實已符合專利法之規定，爰提出發明專利申 【圖式簡單說明】 第一圖係本發明之電動車輪内齒輪馬達模組之分解示意圖 第二A圖係本發明之電動車輪内齒輪馬達模組之示意圖 第二B，係本發明之電動車輪内齒輪馬達模組之剖視示意圖 第三圖係本發明之電動車輪内齒輪馬達模組之局部剖視示音 圖 〜 第四圖係本發明之電動車輪内齒輪馬達模組之齒輪連動關係 之示意圖 第五A圖係本發明裝設於一車輪之視角一之示意圖 第五B圖係本發明裝設於一車輪之視角二之示意圖 第六圖係本發明之轉向懸吊架及馬達轉向拉桿之組裝示意圖 第七A圖係本發明之車輪轉向狀態一之示意圖 〜 第七B圖係本發明之車輪直行狀態之示意圖 第七C係本發明之車輪轉向狀態二之示意圖 【主要元件符號說明】 1〇第一殼體 10A後馬達蓋 10B殼部 l〇C前馬達蓋 201244342 10D固定螺絲 10F樞轉架固定螺絲 12第一行星齒輪樞轉部 21第二殼體空間 23環齒輪輸出外殼 24A滚珠軸承外環 26環齒輪固定螺絲 31環狀殼體 312定位銷 40轉子部 411第一樞接端 412A滚子軸承 412C堡型螺帽 43太陽齒輪 51行星架 512行星架固定螺絲 521軸部 521B軸部固定銷 60轉向懸吊架 62下臂 70車輪 80馬達轉向拉桿 P2第二位置 6>預定角度 A2第二方向 10E樞轉架 11第一殼體空間 20第二殼體 22環齒輪 24滾珠軸承 25密封蓋 30定子部 311矽鋼片 32線圈部 41轉軸 412第二樞接端 412B墊片 42永久磁石 50行星齒輪組 511第一行星齒輪固定部 52行星齒輪 521A滾針轴承 522齒輪部 61上臂 63避震器 71車輪輪圈 P1第一位置 P3第三位置 A1第一方向201244342 VI. Description of the Invention: [Technical Field] The present invention relates to an electric wheel internal gear motor module, and more particularly to an electric wheel internal gear motor module in which a motor and a gear reduction mechanism are integrated into one body, It has the advantages of good dynamic balance, small installation space, variable reduction ratio and easy assembly. [Prior Art] The gear reducer is a mechanism for transmitting power. It has two main functions of reducing the output speed and generating a torque higher than the output shaft of the motor. It is often combined with the motor and is widely used in robots and automated production equipment. High-torque, low-speed applications such as machine tools, electric vehicles, and electric hand tools. Generally speaking, the motor and the gear reducer are usually separately manufactured and then connected and transmitted. Therefore, the following disadvantages often exist: [1] The dynamic balance is not good. The motor and gear reducer of the prior art are connected by a link, and are not integrated into one body, and the dynamic balance is not good, and it is easy to generate vibration and noise during transmission. , the overall installation space of ra is larger: because the motor and the reduction gear machine are individually connected, the installation space is not easy to change, and the two installations cannot be effectively planned. Therefore, the installation space has a large disadvantage. . Therefore, it is necessary to develop new products to solve the problem. SUMMARY OF THE INVENTION I aim to provide a kind of electric wheel in the Malay group, which is good, small installation space, convertible reduction ratio and easy assembly, etc. ==£^ to solve the poor dynamic balance of the Xicheng The technical means of the overall installation of the gear problem is to provide a kind of electric wheel inner tooth difficult I shop 'secret with a housing such as m first planet 201244342 a second housing, which has a second housing space and a ring a fixed portion, which is fixed in the first housing space; the stator portion has an annular housing and a plurality of coil portions, and the plurality of coil portions are substantially disposed on the annular housing; a τ rotor having a rotating shaft, a plurality of permanent magnets and a sun gear; the rotating (10) has a -th pivotal end and a second pivoting end, the first plumbing end being pivotally connected to the first shell The second pivotal end is pivotally connected to the second housing; a plurality of permanent magnets are arranged in an annular shape on the rotating shaft, and corresponding to the coil portion; and the sun gear is disposed on the body On the shaft; and ~ a planetary gear set with a planet carrier and cymbal a planetary gear; the carrier is fixed to the first housing, and has a first planetary gear fixing portion, the planetary gear has a shaft portion and a gear portion, and the gear portion is disposed on the shaft portion The shaft portion has two ends, one end of which is pivotally connected to the J:: row gear shifting portion, the other end is fixed to the first planetary gear fixing portion, and the gear portion is respectively coupled to the ring gear And the sun gear; the tether is a common factor of the number of teeth of the sun gear and the number of teeth of the ring gear portion, and Μ is a positive integer; and: the shaft is pivotally disposed on the planet carrier, and The rotor portion, the ring portion, and the planet carrier are coaxial. Thereby, when the power is supplied to the coil portion of the stator portion, the coil portions generate a magnetic field and magnetically interact with the permanent magnet of the rotor portion to push the rotor portion to rotate, and interlock the planetary gear, the ring The gear portion rotates, thereby driving the second housing to rotate. The above objects and advantages of the present invention will be readily understood from the following detailed description of the embodiments of the invention. The present invention will be described in detail below with reference to the following drawings: f embodiment: As shown in the second to second figures, the present invention is an electric wheel internal gear motor module including a first shell The body 10, a second housing 20, a fixed sub-section 30, a rotor portion 40 and a row are in the gear set 5A. The first housing 10 has a first housing space u and a 201244342 = star gear pivoting portion 12; in the design, the first housing 10 is composed of a rear cover 10A, A cymbal 10B, a front motor cover 10C, and fixed by a plurality of screws / 0D, and the rear motor cover 10A is fixed with a pivot frame 0E 'the turret rotation frame 10E is a plurality of pivots The turret fixing screw 10F is locked to the rear motor cover 10A. The second housing 20 has a second housing space 21 and a ring gear portion 22'. The second housing 20 is composed of the ring gear portion 22' - a ball bearing 24, a ball bearing outer ring A 24A, a ring gear output housing 23, a sealing cover 25 and a ring gear fixing screw 26 are formed. The stator portion 3 is fixed in the first housing space 11; the stator portion 30 has an annular housing 31 and a plurality of coil portions 32; the annular housing 31 is composed of a plurality of steel sheets 311 and The plurality of positioning pins 312 are fixed to the motor cover 10A behind the first casing 1; the plurality of coil portions 32 are substantially evenly arranged on the annular casing 31. The rotor portion 40 has a rotary 41, a plurality of permanent magnets 42 and a sun gear 43. The rotating shaft 41 has a first pivoting end 411 and a second pivoting end 412. The first pivoting end 411 is The second pivoting end 412 is pivotally connected to the second housing 20; the plurality of permanent magnets 42 are arranged in an annular shape on the rotating shaft 41, and corresponding to The plurality of coils 32 are disposed on the rotating shaft 41. The second pivoting end 412 of the rotating shaft 41 is sleeved with a roller bearing 412A and a lock-type nut 412C. A spacer 412B is also provided. The planetary gear set 50 has a carrier 51 and a plurality of planetary gears 52. The carrier 51 is fixed to the first housing 10 (fixed) and has a first planetary gear fixing portion 511 and a plurality of planet carrier fixing screws 512 for fixing the carrier 51 to the motor cover 10c before the first housing 10; the planetary gear 52 has a shaft portion 521 and a gear The gear portion 522 is pivotally disposed on the shaft portion 521. The shaft portion 521 has two ends, one end of which is pivotally connected to the first planetary gear pivoting portion 12, and the other end of which is fixed to the first planet. The gear fixing portion 5丨1 (the shaft portion 521 201244342 is fixed by the driver (8), and the gear portion ΐ ίίί^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^^ It is disposed on the planet carrier 51, and the rotor σΜ0 and the riding portion 22 are connected as the axis of the shaft, and the dynamic balance is good. When the coil f is supplied to the coil portion 32 of the stator portion 3G, the ί and the permanent switch 42 which is turned into 4G generates the magnetic wheel portion 22 to rotate, and the planetary gear 52 is interlocked, and the ring gear 4 lies. The second housing 12 is driven to rotate. The number (M) of I numbers is the tooth center gear of the sun gear 43. The common factor of the number of teeth of 卩22, and M is—the filament of Zhengyang recorded 43 is twelve teeth, and the gear part & it number it r tooth ^ then the number m of the planetary gear 52 is twelve and two four </ RTI> </ RTI> </ RTI> </ RTI> the number (m) of the planet records 52 can be two or more detailed, the second housing 20 is generated by the 43 sun gear 43 and the rotor portion 4 ^ finally The ring gear portion 22 is powered to rotate the second body. In the aspect of the pure gamma deceleration tt of the present invention, the following embodiments are explained: As shown in the fourth figure, the number of teeth of the sun gear 43 is twelve teeth, and the number of teeth of the ring gear portion 22 is forty-four teeth. The number of the planet records 52 (M) is four 'and the number of teeth per planetary gear 52 is sixteen teeth; according to the relative speed method: ^carrier sg 44x16 ^χ^'ΤΙ^ = -3·6667 12~+ 44% = 56〇)_er (wheel train equation); 201244342 Since the carrier 51 is fixed to the second housing 2, the equation of the train is obtained: 12~=_44~; Therefore, the reduction ratio gr (gear ratio) =i=^=-3 6667. Ganzi ω(10) out·°/, in the middle, is the wheel train value of the ring gear portion 22 to the sun gear 43. ~ is the angular velocity of the sun gear 43; ~ is the ring The angular velocity of the gear portion 22; ^carrier is the angular velocity of the carrier 51; \ is the number of teeth of the sun gear 43; is the number of teeth of the ring gear portion 22; 'is the number of teeth of the planetary gear 52. - and the body 2G 'which in turn includes a ring gear output housing as viewed ϊ ίί ΐ it ί ' on the ring gear portion 22 'for locking = rim n (such as the fifth and fifth B As shown, it is not intended to be locked by the present invention; that is, #the rotor portion 4 force is finally used by, and 22 is used for power transmission ± rotation when the system is synchronized with the (four) ring gear output casing 23 Rotating, == wheel 70 is rotated; in design, the ring gear output housing 23 is equipped with a _ 231, rib-locking wheel _ 71, to achieve the ring gear output housing 23 and the wheel 70 fixed. The sun gear 43, the planetary gear 52, and the ring gear portion 22 may be a helical gear or a spur gear. With regard to the features of the present invention, at least the following four types are included: [a] Planetary gear number design. The number of the planetary gears 52 of the present invention is the common factor of the number of teeth of the sun gear 43 and the number of teeth of the ring gear portion 22. Shaft design. The rotor portion 4A, the ring gear portion 22, and the carrier 51 of the present invention are coaxially designed, and have good dynamic balance characteristics, and can effectively reduce vibration and noise. 201244342 Change the reduction ratio. The invention only needs to change the sun record 43, the loop step "the number of teeth of the planetary gear 52 can be changed, the gear reduction ratio can be changed. ^1] The mechanism is integrated. The county motor (that is, by the traitor 3 ff I0 The composition of the lionless) is integrated with the planetary group 5G to reduce the axial and radial volume of the in-wheel motor (ie, the present invention). And the figure of the present invention includes the steering suspension. 60 motor steering rod 8 〇; the steering suspension 帛 6 具有 has a system fixed to the ′′ and the first housing 1 is pivotally connected to the steering suspension 歹 with the upper arm 61, the lower arm 62 and Suspension (4) 拉ί Pull cup 80 is provided on the electric vehicle for controlling the rotation angle of the first housing 10 on the steering suspension frame 60. The first housing 10 is pivoted by the clock. The frame (10) is dragged to the upper arm 6 of the yoke (10), the lower arm 62, and the motor is turned to rotate 8 〇; Ϊ the casing 〇Ξ 2 ΪΪ: the linear position of the tie rod 80 is changed to control the second module; That is, the electric wheel_wheel motor module of the present invention rotates on the steering suspension frame 60. ^ The left front wheel of the motor car is as shown in FIG. When the motor rotation 80 is at a first position P1, the first housing 1 is slid to the first; the predetermined angle is the right rotation; as shown in the seventh BB, the steering rod 80 is located at the second At the position P2, the first housing 10 is turned to the state of pulling, that is, straight; as shown in the seventh C, when the motor 80 is located at the third position p3, the first housing 1 is connected to the j The first ^A2 rotation - the lack of angle Θ, that is, the left turn. ^ Above, the advantages and effects of the present invention can be summarized as: The far-off state is better than the best. The knowing technique Ma Lai recorded reducer is driven by逢 ' ' is not integrated, dynamic balance is good, easy to pass and noise; and the rotor portion 40, the ring gear portion 22 of the present invention and the ϋ star frame 51 are coaxial design, good dynamic balance The vibration can be reduced [2]. The installation space is small. The motor of the present invention (that is, the brushless motor composed of the stator portion 3〇 and 201244342) is integrated with the planetary gear set 5〇 to reduce the wheel. The axial and radial volume of the inner motor (ie, the present invention) has the advantage of a small installation space. 〃 [3] Convertible deceleration The present invention is designed to change the gear reduction ratio by simply changing the number of teeth of the sun gear 43, the ring gear portion 22 or the planetary gear 52. [4] Easy assembly "The number of planetary gears 52 of the present invention (μ The common factor of the number of teeth of the sun gear 43 and the number of teeth of the ring gear portion 22 can reduce the assembly difficulty caused by the phase error of the planetary gear 52. The present invention will be described in detail by way of preferred embodiments only. Any simple modifications and variations of this embodiment are possible without departing from the spirit and scope of the invention. The above detailed description will enable those skilled in the art to understand that the invention can be The first drawing is an exploded view of the electric wheel internal gear motor module of the present invention. The second A is a schematic view of the electric wheel internal gear motor module of the present invention. FIG. 3 is a cross-sectional view showing the electric wheel internal gear motor module of the present invention. FIG. 3 is a partial cross-sectional view of the electric wheel internal gear motor module of the present invention. Figure 5 is a schematic view showing the gear linkage relationship of the electric wheel internal gear motor module of the present invention. Figure 5A is a schematic view of the present invention installed on a wheel. Figure 5B is a perspective view of the present invention installed on a wheel BRIEF DESCRIPTION OF THE DRAWINGS FIG. 6 is a schematic view showing the assembly of the steering suspension frame and the motor steering rod of the present invention. FIG. 7A is a schematic view of the steering state of the wheel of the present invention - FIG. 7B is a schematic diagram of the wheel straight state of the present invention. C is a schematic diagram of the steering state of the wheel of the present invention [main component symbol description] 1〇first housing 10A rear motor cover 10B shell part l〇C front motor cover 201244342 10D fixing screw 10F pivot frame fixing screw 12 first planet Gear pivoting portion 21 second housing space 23 ring gear output housing 24A ball bearing outer ring 26 ring gear fixing screw 31 annular housing 312 positioning pin 40 rotor portion 411 first pivot end 412A roller bearing 412C fort type screw Cap 43 sun gear 51 planet carrier 512 planet carrier fixing screw 521 shaft portion 521B shaft portion fixing pin 60 steering suspension bracket 62 lower arm 70 wheel 80 motor steering rod P2 second position 6 > predetermined angle A 2 second direction 10E pivot frame 11 first housing space 20 second housing 22 ring gear 24 ball bearing 25 sealing cover 30 stator portion 311 steel plate 32 coil portion 41 shaft 412 second pivot terminal 412B gasket 42 permanent Magnet 50 planetary gear set 511 first planetary gear fixing portion 52 planetary gear 521A needle bearing 522 gear portion 61 upper arm 63 shock absorber 71 wheel rim P1 first position P3 third position A1 first direction