200906673 八、發明說明： 【杂明所屬之技術領域】 ㊉用的自订車變速11 —般可分為内變速ϋ與外變速哭 兩大類。β變速器通常是以行星齒 欠速- 體，且將變速機構安 ’、一夂速機構的主 r機構女置於後輪輪轂中，故稱之為 而國内稱之為變速花鼓（Multl_speedHub)。藉由切換:’ =入件、輪出件及固定件改變行星齒輪系之齒數比，以 達到不同之轉速比。 【先前技術】 以行星齒輪系為變速機構主體的内變速器具有下列優 點· 1 ·體積小；2.換檔作動穩….·3曰士 作動％疋，3·具有輪轂的保護而提高 便用哥命；4 口畢立，丨 、士 β 9 廷二優點正可適用於休閒與運動等 方面的自行車上。近年來， ^ 木對於非5熱門的電動助行車與 电動自行車而t ’内變速器更已經成為其標準配備，因^ :變速器的需求量大有增加之趨勢。目内的各大自行車廠 開始重視從事内變速器的研究開發與設計，故内變速器200906673 VIII. Description of the invention: [Technical field to which Zaoming belongs] Ten-purpose custom-made vehicle shifting 11 can be divided into two types: internal shifting and external shifting. The β-transmission is usually based on the underspeed of the planetary gear, and the main mechanism of the idling mechanism is placed in the rear wheel hub. Therefore, it is called the variable speed hub (Multl_speedHub). . By switching: ' = the input, the wheel and the fixture change the gear ratio of the planetary gear train to achieve different speed ratios. [Prior Art] The internal transmission with the planetary gear train as the main body of the shifting mechanism has the following advantages: 1. The volume is small; 2. The shifting is stable....·3 gentleman's actuation %疋, 3·With the protection of the hub, it is improved. Brother's life; 4 mouthfuls, 丨, 士 β 9 廷 2 advantages can be applied to bicycles for leisure and sports. In recent years, wood has become a standard equipment for non-five electric electric bicycles and electric bicycles, and the demand for transmissions has increased. The major bicycle factories in the project have begun to pay attention to the research and development and design of the internal transmission, so the internal transmission
的創新設計理論盥方、本P、x t上、A /、方法已逐漸成為國内各大自行車廠極欲 建立的重點工作。 一自行車内變速器的研究成果在過去二十年間大多在 '五速與七速之間，檢視自行車内變速機構的專利可 知’三至七速内變速器諸如已知的： π我國專利公告第284734號、第321624號、第327160 。’第 330544 唬、第 342795 號 '第 399534 號、第 501 572 化等等。美®專利第3433G97號 '第3492893號、第38091 95 200906673 號、第 3828627 號、第 3886811 號、第 4059028 號、第 4147243 號、第 4179953 號、第 4615423 號、第 4651853 號、第 4721013 號、第 4727965 號、第 5078664 號、第 5237500 號、第 5399128 號、第 5443279 號、第 5445573 號、第 5562563 號、第 58 1 3937 號、第 5855530 號、第 5961416 號、第 5967937 號、第 6478710 號、第 6692400 號等等。 而在多速（七速以上）内變速器方面一直沒有很大的突 破，直至美國專利第5527230號將三組行星齒輪系組合成 一款十二速内變速器，不但在檔位數目上有一個很大的進 步’且在轉速比倍率上更南達339% ;隨後在2〇〇〇年有美 國專利第6048287號也以類似的觀念推出了十四速内變速 器，其變速倍率高達526% ;其後2〇〇2年美國專利第 6368243號提出以連接離合器組合兩組複合行星齒輪系之 十二速内變速器。其相關專利和市面上的產品的設計理念 雖然與二十世紀初的專利大同小異，然而各個公司在其產 品上的控制機構與齒輪系上都有其創新研發。 目前多速内變速器產品仍存在有權位分佈不均、構件 數量過多、體積大和重量過重等問題，因此如何設計出構 造簡單、重量輕且多速的自行車内變速 夂逆态就成為一個極為 重要的研究課題。 ’ 【發明内容】 本創作之目的在於提供一種新型 1 1式的十六速變速機 構，其變速檔位高低速轉速分佈平 -J 且此進行有效的傳 200906673 動。其次’檔位變換時的轉速變動皆能維持在一固定值， 才画位變換穩定且均勻，能有效的減輕騎乘負擔，並以最小 的空間需求將變速機構加以設計緊緻排列。此外，本創作 之目的亦在於提供—種變速器之改良，其構件設計方式簡 單，加工製作容易，可節省加工成本與降低工時。 【實施方式】 請參閱第一圖所示，其為本創作實施例之組合剖視 ^，本創作之自行車十六速内變速器之變速機構主體齒輪 ，、且中，依序套固有—具有齒數122的第一太陽齒輪（21)、 數26的第二太陽齒輪（22)、一具有齒數26的第 輪（23)、一具有齒數73的第四太陽齒輪（24)、一 具有齒數15的第一行星齒輪（31)、一具有齒數乃的第二 打星齒輪（32)、一具有齒數69的第三行星齒輪（33)、一具 有齒數15及75的第四行星齒輪（34)、一具有齒數152的 第一環齒輪（41)、一具有齒數76的第二_環齒輪（42)、一 ^有齒數164的第三環齒輪(43)、一具有齒數163的第四 環f輪（44)、一聯結第一行星齒輪（3 1)與第二環齒輪（42) ' ^行生#、一聯結第二行星齒輪（32)與第三環齒輪（43) 的j二行星臂、一聯結第三行星臂（33)與第四行星臂（34) 的第三/四行星臂聯結件、一單向離合器（66)聯結固定主軸 ⑴與第四太陽齒輪（24)、一單向離合器（67)聯結第一環齒 輪（41)與車輪輪轂（76)、一凸輪控制單元（61)與三個平移 ^制制動單元（62、63、64)經由控制單元聯結套筒（65)整 合控制動作以控制四個太陽齒輪（21、22、23、Μ)。輸入 200906673 =?於側蓋(74>外環’而於侧蓋(74)内側-端 單元聯：：ΐ師υ’以棍裝固定套筒叫使控制 山、、'σ套同可自由旋轉以作控制動作傳遞。於其另一側 端之車輪輪轂(76)亦以滾珠軸承(773)連接固定套筒 (、）’、側蓋（74) ’用於車輪輪穀（76)能與in定主轴（1)做相 對運動。如此，即組成本創作之變速機構。 。本創作分別以第三圖至第十八圖的⑷部分說明九個 樓位的作動方式’其中箭號表示動力傳遞的路徑。其中專 線及箭號表示動力傳遞的路徑，實心黑色四方形表示控制 離合益有嚙合的連結作用。而第三圖至第十八圖的圖式(b) 邛伤均對應繪製圖式（a)之能量傳遞的路線圖。 (一）第一檔位 參閱第三圖所示，其為本創作實施例之第一檔位的組 合剖視圖及能量傳遞路線圖，輸入動力由使用者以腳踏方 式傳動鏈條帶動鏈輪（75)，再由鏈輪（75)經側蓋（74)帶動 第四環齒輪（44)轉動，因第四太陽齒輪（24)轉動方向與第 四環齒輪（44)相反，使得單向離離合器（66)作動並讓第四 太陽齒輪（24)與固定主軸（1)連結為同一構件，此時動力自 第四環齒輪（44)帶動第四行星齒輪（34)並驅動第四行星臂 (54)產生減速’另因第一太陽齒輪（21)、第二太陽齒輪 (22)、第三太陽齒輪（23)皆為自由無拘束狀態，由其第_ 環齒輪（41)轉速大於第一行星臂（51)、第二環齒輪（42)轉 速大於第二行星臂（52)、第三環齒輪（43)轉速大於第三行 星臂（53)，故迫使單向棘輪離合器（672、673、674)作用， 200906673 分別使得第一行星臂⑼與第一環齒輪(4i)聯結為同一構 2、第二行星臂（52)與第二環齒輪（42)聯結為同一構件、 第二行星臂（53)與第三環齒輪（43)聯結為同一構件，動力 由第四行星臂（54)經第三行星臂（53)、第二行星臂、 第订星臂（51)及第一環齒輪（41)經單向棘輪輸出離合器 (671)輸出至車輪輪轂◦，轉速比等於3.Μ w _ t 崎一减速 標並可作為自行車起步樓。 (一）第二樓位 參閱第四圖所示，其為本創作實施例之切換至第二樓 位的=合剖視圖及能量傳遞路線圖，當楷位由第_構位: 、至第-檔位％ ’控制單元聯結套筒（65)旋轉同時帶動 ^控制單元⑹）、第二控制單元㈣、第三控制單元（63)、 :控制“(64)，第一控制單元(61)經設定凸輪 程使得聯結離合器⑺3)停留於原位置，因第四太陽好 ⑽轉動方向與第四環齒輪（44)相反，使得單向離離合: =作動並讓第四太陽㈣（24)與以主轴⑴連結為同 一構件’第四控制單元（64)使平移控制制動單元⑺） Μ三太陽齒輪（23)與固定主轴⑴聯結並固定，第二控制 早凡（62)與弟二控制單元（63)使平移控制制動單元⑺卜 7白1Γ作動而，第一太陽齒輪⑼與第二太陽齒輪（22)呈 無拘束狀，由其第—環齒輪（41)轉速大於第 臂^、第二環絲（42)轉速大於第二行星臂⑽，故适 使早向棘輪離合器（672、673)作用，分別使得第一行星臂 200906673 (5 1)與第一環齒輪（41)聯結為 — 门u 構件、第二行星臂 與第二環齒輪（42)聯結為同-構件，輸人動力由使㈣以 :踏方式傳動鏈條帶動鏈輪（75)，再由鏈輪（75) :動第：《輪(44)轉動’並傳遞至第四行星齒輪二(、） 弟四行生臂（54)減速，並經由第— ^ 甶弟二仃星臂（53)、第三行星 齒輪（33)及第三環齒輪（43)作 生 (52) '第一行星臂（51)及單 ^ Π棘輪輸出離合器（671)輪出$ 車輪輪轂（76)，轉速比等於2 7 .，為一減速檔並可作為 弟一權。 (二）第三檔位 參閱第五圖所示，其為本創作實施例之切換至第三檀 位的：合剖視圖及能量傳遞路線圖，當稽位由第二構位切 換至弟二槽位時，控制單元聯結套筒旋轉同時帶動第 一控制單元（61)、第二控制單元㈣、第三控制單元（63)、 第四控制單元（64)，第-控制單元（61)經設定凸輪轴向行 程使得聯結離合器⑺3)停留於原位置，目第四太陽齒輪 (24)轉動方向與第四環齒輪（44)相反，使得單向離離合器 (:)作動並讓第四太陽齒輪(24)與固定主軸⑴連結為同 一構件’第三控制單元（63)使平移控㈣動單元（川）作 動1並使„第：太陽齒輪（22)與固定主軸⑴聯結並固定，第 —制單το (62)與第四控制單元（6句使平移控制制動單 兀（712 71)不作動而使第—太陽齒輪（2ι)與第三太陽齒輪 (23)呈自由無拘束狀態，由其第一環齒輪⑷）轉速大於第 10 200906673 一行星臂（51)故迫使單向棘輪離合器（672)作用，使得第一 行生#(51)與第一環齒輪（41)聯結為同一構件，第三環齒 輪（4 3 )轉速大於第三行星臂（5 3 )故迫使單向棘輪離合葬 (674)作用，使得第三行星臂（53)與第三環齒輪（43)聯結為 同一構件，輸入動力由使用者以腳踏方式傳動鏈條帶動鏈 輪（75)，再由鏈輪（75)經側蓋（74)帶動第四環齒輪（44)轉 動’並傳遞至第四行星齒輪（34)、第四行星臂（54)減速， 經第三行星臂(53)後’經由第二行星臂(52)、第二行星齒 輪（32)及第二環齒輪（42)作增速，最後由第一行星臂（^) 及單向棘輪輸出離合器（671)輸出至車輪輪轂（％)，轉速比 等於2.4136，為一減速檔並可作為第三檔。 I四）弟四擋位 參閱第六圖所示，其為本創作實施例之切換至第四標 位的組合剖視圖及能量傳遞路線圖，當槽位由第三樓位切 換至第四槽位時，控制單元聯結套筒(65)旋轉同時帶動第 :控制單元（6丨）、第二控制單元（62)、第三控制單元⑻）、 第四控制單元(64)’第一控制單元(61)經設定凸輪轴向行 =得聯結離合器⑺3)停留於原位置，㈣四太陽齒輪 轉動方向與第四環齒輪（44)相反，使得單向離離合器 (66)作動並讓第四太陽齒輪(24)與固定主軸 ：； —構件，帛四控制單元（64)使平移控制制動單元（7’；；= 使平移控制制動單元（71)作動使第二太^ | 主轴〇)聯結並固定，第^制Γ元固定 U疋弟一拴制早几（63)使平移控制制動單 200906673 元（711)作動使平移控制制動單元（71丨）作動使第二太陽齒 輪（22)與固定主軸（1)聯結並固定，第二控制單元（62)使平 移控制制動單7C (7 1 2)不作動而使第一太陽齒輪（2丨）呈自 由無拘束狀態，由其第一環齒輪（4 1)轉速大於第一行星臂 (51)故迫使單向棘輪離合器（672)作用，使得第一行星臂 (51) 與第一環齒輪（41)聯結為同一構件，輸入動力由使用 者以腳踏方式傳動鏈條帶動鏈輪（75),再由鏈輪（75)經側 1 (74)可動第四環齒輪（44)轉動，並傳遞至第四行星齒輪 (34)、第四行星臂（54)減速，經第三行星臂、第三行 星齒輪（33)及第三環齒輪（43)作增速，並經由第二行星臂 (52) 、第二行星齒輪（32)及第二環齒輪作增速，最後 由第一仃星臂（51)及單向棘輪輪出離合器（671)輸出至車 輪輪數（671)，轉速比等於2.〇833，為一減速檔並可作為 第四檔。 (五）第五檔位 參閱第七圖所不，其為本創作實施例之切換至第五檔 位的組合剖視圖及能量傳遞路線圖，當檔位由第四檔位切 換至第五檑位時，控制單元聯結套筒（65)旋轉同時帶動第 I控制單元⑹)、第二控制單元(62)、第三控制單元(6”、 弟四控制單元（64)，第一控制單元（61)經設定凸輪轴向行 程使得聯結離合器⑺3)停留於原位置，因第四太陽齒輪 (24)轉動方向與第四環齒輪（44)相反，使得單向離離合器 (66)作動亚讓第四太陽齒輪（24)與固定主軸⑴連結為同 12 200906673 使第—太陽―:：早元(62)使平移控制制動單元(7_ 二3=⑼與固定主轴〇)聯結並固定，第三控制 Ί四控解元⑽使平移控制”單元（71、 7⑺不作動而使第二太陽#輪（22)與第 自由無拘束狀態，由其第二環齒輪(42)轉速: 《⑼故迫使單向棘輪離合器（673)作用，使得第二行星臂 (52)與第二環齒輪(42)聯結為同—構件 ⑽轉速大於第三行星臂（53)故 齒輪 作用，使得第三行星臂（5⑽第輪離合器州） ^ 厂、弟—％齒輪（43)聯結為同一 (75) ’再Γ動力由使用者以卿踏方式傳動鏈條帶動鏈輪 ^:由鏈輪(75)經側蓋(7_ / 饤星齒輪（34)、第四行星臂（54)減速，經第 Γ星！(53)、第二行星臂(52)、並經由第-行星臂⑻、 棘於Π齒輪（31)及第一環翁輪（41)作增速，最後由單向 :出離合器陶輸出至車輪輪轂(%)，轉速比等於 •7970，為一減速檔並可作為第五檔。 (六）第六槽位 參閱第八圖所示，Μ本創作實施例之㈣ 位的組合剖視圖及能量傳 八才田 換至第六綱，控制=::，當槽位由第五槽位切 … 則早凡聯結套_)旋轉同時帶動第 #控制早：(61)、第二控制單元(62)、第三控制 、 弟四控制早兀(64) ’第—控制單元(6”經設定凸輪軸 程使得聯結離合器（713)停留於原位置，因第四太陽齒輪 13 200906673 (24)轉動方向與第四環齒 ^ 119 ()相反’使得單向離離合器 —構件 “4#輪（24)與以主轴⑴連結為同 使第控制單元（62)使平移控制制動單元⑺2)作動 ^ 一场齒輪⑺）與固定主軸⑴聯結並固定，第四控制 早το (64)使平移控制制動 f2 )作動使第三太陽齒輪 )，、口疋主軸〇)聯結並固定，第三控制單元(63)使平移 控制制動單元（711)不作動而μ 早W城十移 ^ 動而使第一太陽齒輪（22)呈自由The innovative design theory, the party, the P, the x, the A /, the method has gradually become the key work of the major bicycle factories in China. The research results of a bicycle internal transmission have been mostly between the 'five speeds and seven speeds' in the past two decades. The patent for the internal shifting mechanism of bicycles is known. 'Three to seven speed internal transmissions are known: π China Patent Notice No. 284734 , No. 321,624, No. 327160. 'No. 330544 唬, No. 342795 'No. 399534, No. 501 572, etc. US® Patent No. 3433G97, No. 3492893, No. 38091 95 200906673, No. 3828627, No. 3886811, No. 4059028, No. 4147243, No. 4179953, No. 4615423, No. 4651853, No. 4721013, No. 4,727,965, No. 5,078,864, No. 5,237,500, No. 5,399,128, No. 5,443,279, No. 5,445,573, No. 5,562,563, No. 5,1, 3,937, No. 5,855,530, No. 5,961,416, No. 5,967,937, No. 6478710, No. 6692400 and so on. In the multi-speed (seven-speed or higher) internal transmission, there has been no major breakthrough. Until US Patent No. 5527230 combines three sets of planetary gear trains into a 12-speed internal transmission, not only has a large number of gears. The progress 'and the speed ratio is up to 339% south; then in the next two years, US Patent No. 6048287 also introduced a four-speed internal transmission with a similar concept, the gear ratio is as high as 526%; A two-speed internal transmission of a combination of two sets of compound planetary gear trains with a clutch is proposed in US Pat. No. 6,636,243. The design concepts of its related patents and products on the market are similar to those of the early 20th century. However, each company has its own innovative research and development in the control mechanism and gear train of its products. At present, multi-speed internal transmission products still have problems such as uneven distribution of power, excessive number of components, large volume and heavy weight. Therefore, how to design a bicycle with a simple structure, light weight and multiple speeds is an extremely important Research topics. 】 [Description of the Invention] The purpose of this creation is to provide a new type of 16-speed six-speed transmission mechanism, the gear position of the high and low speed speed distribution flat -J and this effective transmission 200906673 movement. Secondly, the change of the rotational speed during the gear shift can be maintained at a fixed value, and the position change is stable and uniform, which can effectively reduce the riding burden, and the shifting mechanism is designed to be tightly arranged with the minimum space requirement. In addition, the purpose of this creation is to provide an improved transmission, which is simple in design and easy to manufacture, which saves processing costs and reduces man-hours. [Embodiment] Please refer to the first figure, which is a combined sectional view of the creation embodiment. The main body gear of the shifting mechanism of the bicycle 16-speed internal transmission of the present invention, and the inherent set of the gears are inherently-having the number of teeth a first sun gear (21) of 122, a second sun gear (22) of number 26, a first wheel (23) having a number of teeth 26, a fourth sun gear (24) having a number of teeth 73, and a tooth having a number of teeth of 15. a first planetary gear (31), a second planetary gear (32) having a number of teeth, a third planetary gear (33) having a tooth number 69, a fourth planetary gear (34) having a number of teeth 15 and 75, a first ring gear (41) having a tooth number 152, a second ring gear (42) having a tooth number 76, a third ring gear (43) having a tooth number 164, and a fourth ring f having a tooth number 163 a wheel (44), a coupled first planetary gear (3 1) and a second ring gear (42) '^行生#, a coupled second planetary gear (32) and a third ring gear (43) The arm, a coupled third planetary arm (33) is coupled to the third/fourth planetary arm coupling of the fourth planetary arm (34), and a one-way clutch (66) The fixed spindle (1) is coupled with the fourth sun gear (24) and a one-way clutch (67) to the first ring gear (41) and the wheel hub (76), a cam control unit (61) and three translation brake units ( 62, 63, 64) The control action is integrated via the control unit coupling sleeve (65) to control the four sun gears (21, 22, 23, Μ). Enter 200906673 =? on the side cover (74 > outer ring 'and on the side cover (74) inside - end unit connection:: ΐ υ υ 以 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍 棍For the control action transmission, the wheel hub (76) at the other side is also connected by a ball bearing (773) to the fixed sleeve (, ) ', side cover (74) 'for the wheel valley (76) can In the fixed spindle (1) to do relative motion. Thus, constitute the shifting mechanism of this creation. This creation describes the operation of the nine buildings in part (4) of the third to the eighteenth figure respectively, where the arrow indicates the power The path of the transmission. The special line and the arrow indicate the path of the power transmission. The solid black square indicates the control of the clutch and the meshing effect. The drawings of the third to the eighteenth figure (b) are corresponding to the drawing. (a) The first gear is shown in the third figure, which is a combined sectional view and energy transmission route diagram of the first gear of the creation embodiment, and the input power is provided by the user. Drive the chain with a pedal to drive the sprocket (75), and then pass the sprocket (75) through the side cover (74) driving the fourth ring gear (44) to rotate, because the fourth sun gear (24) rotates in the opposite direction to the fourth ring gear (44), so that the one-way clutch (66) is actuated and the fourth sun gear (24) ) is connected to the fixed member (1) as the same member. At this time, the power drives the fourth planetary gear (34) from the fourth ring gear (44) and drives the fourth planetary arm (54) to generate a deceleration. 21) The second sun gear (22) and the third sun gear (23) are all free and unconstrained, and the speed of the first ring gear (41) is greater than the first planetary arm (51) and the second ring gear (42). The rotation speed is greater than that of the second planetary arm (52) and the third ring gear (43) is greater than the third planetary arm (53), so the one-way ratchet clutch (672, 673, 674) is forced to act, and 200906673 makes the first planetary arm respectively. (9) coupled with the first ring gear (4i) as the same structure 2, the second planetary arm (52) and the second ring gear (42) are coupled to the same member, the second planetary arm (53) and the third ring gear (43) Linked to the same component, powered by the fourth planet arm (54) via the third planet arm (53), the second planet arm, the first star (51) and the first ring gear (41) is output to the wheel hub through the one-way ratchet output clutch (671), and the rotation speed ratio is equal to 3. Μ w _ t Saki-speed deceleration standard and can be used as a bicycle starting building. The second floor is shown in the fourth figure, which is the cross-sectional view and the energy transfer route map of the second embodiment of the creative embodiment, when the position is from the _position: to the first gear % ' The control unit coupling sleeve (65) rotates while driving the control unit (6), the second control unit (4), the third control unit (63), : control "(64), the first control unit (61) is set by the cam path The coupling clutch (7) 3) stays in the original position, because the fourth sun is good (10), the direction of rotation is opposite to that of the fourth ring gear (44), so that the one-way clutch is: = actuating and connecting the fourth sun (four) (24) with the main shaft (1) The same component 'fourth control unit (64) causes the translation control brake unit (7)) to connect and fix the sun gear (23) to the fixed main shaft (1), and the second control (62) and the second control unit (63) make the translation Control braking unit (7) Bu 7 white 1 Γ actuation, first sun gear (9) and second too The male gear (22) is unconstrained, and the rotation speed of the first ring gear (41) is greater than that of the first arm and the second ring wire (42) is greater than that of the second planetary arm (10), so that the early ratchet clutch (672, 673) acting to cause the first planet arm 200906673 (5 1) to be coupled with the first ring gear (41) as a door u member, the second planet arm and the second ring gear (42) are coupled to the same member, The power is made by (4): the treading drive chain drives the sprocket (75), and then the sprocket (75): the moving: "the wheel (44) turns" and passes to the fourth planetary gear two (,) The arm (54) is decelerated, and the first planet arm (51) is generated by the first - the second brother's arm (53), the third planetary gear (33), and the third ring gear (43). The single ^ Π ratchet output clutch (671) rotates out the wheel hub (76), and the speed ratio is equal to 2 7 ., which is a deceleration gear and can be used as a disciple. (2) The third gear position is shown in the fifth figure, which is the switch to the third position of the creative embodiment: a cross-sectional view and an energy transfer route diagram, when the position is switched from the second configuration to the second slot In the position, the control unit couples the sleeve rotation while driving the first control unit (61), the second control unit (4), the third control unit (63), the fourth control unit (64), and the first control unit (61) is set. The cam axial stroke causes the coupling clutch (7) 3) to stay in the home position, and the fourth sun gear (24) rotates in the opposite direction to the fourth ring gear (44), so that the one-way clutch (:) acts and the fourth sun gear (the fourth sun gear) 24) The same as the fixed spindle (1) is connected to the same component 'The third control unit (63) makes the translation control (four) moving unit (Chuan) actuate 1 and makes the „第:Sun gear (22) and fixed spindle (1) to be connected and fixed, the first system Single το (62) and the fourth control unit (6 sentences make the translation control brake unit 兀 (712 71) not actuate, so that the first sun gear (2 ι) and the third sun gear (23) are free and unconstrained. The first ring gear (4)) rotates more than the 10th 200906673 one planetary arm (51 Therefore, the one-way ratchet clutch (672) is forced to act such that the first line #(51) and the first ring gear (41) are coupled to the same member, and the third ring gear (43) is rotated more than the third planetary arm (5). 3) Therefore, the one-way ratcheting and burial (674) is forced to make the third planetary arm (53) and the third ring gear (43) are connected to the same member, and the input power is driven by the user to drive the chain with the pedal driving chain ( 75), the sprocket (75) drives the fourth ring gear (44) to rotate by the side cover (74) and transmits to the fourth planetary gear (34) and the fourth planetary arm (54) to decelerate through the third planet. After the arm (53), the speed is increased by the second planetary arm (52), the second planetary gear (32) and the second ring gear (42), and finally the first planetary arm (^) and the one-way ratchet output clutch ( 671) Output to the wheel hub (%), the speed ratio is equal to 2.4136, which is a deceleration gear and can be used as the third gear. I4) The fourth gear is shown in the sixth figure, which is the switch to the first embodiment. Combined sectional view of four standard positions and energy transfer route diagram, when the slot is switched from the third floor to the fourth slot, the control unit is coupled The sleeve (65) rotates while driving: the control unit (6丨), the second control unit (62), the third control unit (8), and the fourth control unit (64) 'the first control unit (61) is set by the cam The axial row = the coupling clutch (7) 3) stays in the original position, and (4) the four sun gears rotate in the opposite direction to the fourth ring gear (44), so that the one-way clutch (66) is actuated and the fourth sun gear (24) is fixed. Spindle:; - Member, 帛4 control unit (64) enables the translation control brake unit (7';; = to make the translation control brake unit (71) actuate to make the second too ^ | spindle 〇) joint and fixed, the first system The fixed U 疋 拴 拴 ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( Fixed, the second control unit (62) causes the translational control brake 7C (7 1 2) to be inactive to cause the first sun gear (2丨) to be free and unconstrained, and the first ring gear (4 1) has a rotational speed greater than The first planet arm (51) forces the one-way ratchet clutch (672) to act so that the first line The star arm (51) is coupled to the first ring gear (41) as the same member, and the input power is driven by the user to drive the chain sprocket (75) in a pedal mode, and then moved by the sprocket (75) via the side 1 (74). The fourth ring gear (44) rotates and is transmitted to the fourth planetary gear (34) and the fourth planetary arm (54) to be decelerated, via the third planetary arm, the third planetary gear (33), and the third ring gear (43). The speed is increased, and the second planetary arm (52), the second planetary gear (32) and the second ring gear are used for speed increase, and finally the first comet arm (51) and the one-way ratchet wheel out clutch (671) Output to the number of wheels (671), the speed ratio is equal to 2. 〇 833, is a reduction gear and can be used as the fourth gear. (5) The fifth gear position is referred to in the seventh figure. It is a combination sectional view and energy transmission route diagram of the switching to the fifth gear position of the present embodiment, when the gear position is switched from the fourth gear position to the fifth gear position. At the same time, the control unit coupling sleeve (65) rotates while driving the first control unit (6), the second control unit (62), the third control unit (6", the fourth control unit (64), and the first control unit (61) The set cam axial stroke causes the coupling clutch (7) 3) to stay in the original position, because the fourth sun gear (24) rotates in the opposite direction to the fourth ring gear (44), so that the one-way clutch (66) acts as the seventh. The sun gear (24) is connected to the fixed main shaft (1) as the same 12 200906673. The first sun -:: early element (62) connects and fixes the translational control braking unit (7_2 = 3 = (9) with the fixed spindle ,), the third control Ί The four control solutions (10) make the translation control unit (71, 7 (7) not actuate and make the second sun # wheel (22) and the free unconstrained state, by its second ring gear (42) rotation speed: "(9), therefore forced one-way The ratchet clutch (673) acts such that the second planet arm (52) is coupled to the second ring gear (42) For the same component (10), the rotation speed is greater than that of the third planetary arm (53), so that the third planetary arm (5 (10) first clutch state) ^ factory, brother -% gear (43) is connected to the same (75) 're-power The sprocket is driven by the user to drive the chain by the Qing stepping method. ^: The sprocket (75) is decelerated by the side cover (7_ / Comet gear (34), the fourth planetary arm (54), via the first comet! (53) The second planetary arm (52) is increased in speed via the first-planetary arm (8), the ratcheting gear (31) and the first ring gear (41), and finally by the one-way: the out clutch gear is output to the wheel hub ( %), the speed ratio is equal to • 7970, which is a deceleration gear and can be used as the fifth gear. (6) The sixth slot is shown in the eighth figure, the combined sectional view of the (four) position of the present creation example and the energy transmission Yacai Tian Change to the sixth class, control =::, when the slot is cut by the fifth slot... then the early connection sleeve _) rotation simultaneously drives the ## control early: (61), the second control unit (62), the third Control, brother four control early (64) 'the first control unit (6) set the camshaft range so that the coupling clutch (713) stays in the original position, because the fourth sun gear 13 200906673 (24) The direction of rotation is opposite to that of the fourth ring gear 119 () so that the one-way clutch-member "4# wheel (24) is coupled with the main shaft (1) so that the first control unit (62) causes the translation control brake unit (7) 2) Actuation ^ A gear (7) is coupled and fixed to the fixed spindle (1). The fourth control is early το (64) to make the translation control brake f2) actuate to make the third sun gear), and the spindle 〇) is coupled and fixed. The three control unit (63) causes the translation control brake unit (711) to be inactive and the first sun gear (22) is free.
無拘束狀態，由JL第-戸I 由/、弟一％齒輪（42)轉速大於第二行星臂 故迫使單向棘輪離合器(673)作用，使得第二行星臂(52) 與第二環齒輪（42)聯結為同—構件，輸入動力由使用者以 :踏方式傳動鏈條帶動鏈輪（75)，再由鏈輪（75)經側蓋（Μ) 〒動第四環齒輪（44)轉動，並傳遞至第四行星齒輪⑽、 弟四订星臂（54)減速，經第三行星臂（53)、第三行星齒輪 ⑽及第三環齒輪⑷）增速，經第二行星臂（52)後，經由 弟m臂（51)、第—行星會輪⑴）及第一環齒輪⑷）作 增速，最後由單向棘輪輸出離合器（671)輪出至車輪輪數 (76)轉速比等於15511，為一減速樓並可作為第六槽。 (七）第七檔位 麥閱第九圖所tf ’其為本創作實施例之切換至第七檔 位的組合剖視圖及能量傳遞路線圖，當樓位由第六標位切 換至第七樓位時，控制單元聯結套筒（65)旋轉同時帶動第 -控制單元（61)、第二控制單元（62)、第三控制單元、 第四控制單元（64)，第一控制單元（61)經設定凸輪轴向行 14 200906673 ==寻聯結離合器⑺3)停留於原位置，因第四太陽齒輪 ()轉動方向與第四環齒輪㈤相反，使得單向離離合器 (66)作動並讓第四太陽齒輪（24)盥gj $ ± π 一 I、U疋主軸（1)連結為同 一構件n制單元（62)使平移控制制動單元（712)作動 使弟—太陽齒輪（21)與固定主軸⑴聯結並固定，第三控制 單元（63)使平移㈣㈣單元（川）作較第：太陽齒工輪 ⑽與固定主軸⑴聯結並固定，第四控制單元州使平移 控制制動單元㈤不作動而使第三太陽齒輪⑼呈自由無 拘束狀g ’由其第二環齒輪（43)轉速大於第三行星臂⑸） 故迫使單向棘輪離合器（674)作用，使得第三行星臂 與第三環齒輪（43)聯結為同—構件，輸入動力由使用者以 腳踏方式傳動鏈條帶_輪（75)，再由鏈輪（75)_蓋（74) 帶動第四環齒輪（44)轉動，並傳遞至第四行星齒輪⑼' 第四行星臂⑽減速，經第三行星臂⑼後，由第二行星 臂（52)、第二行星齒輪（32)及第二環齒輪（42)作增速，並 經由第一行星臂（5 1 )、笛 , 1 ^弟一订星齒輪（31)及第一環齒輪（41) 作〜速，取後由早向棘輪輸出離合器（671)輸 轂⑽，轉速比等—為-減速楷並可作為第七標。 (八）第八檔位 參閱第十圖所示，其為本創作實施例之切換至第八檔 位的組合剖視圖及能量傳遞路線圖，當樓位由第七標位切 換至第八杬位時’ 制單元聯結套筒旋轉同時帶動第 -控制單7L (61)、第—控制單元㈣、第三控制單元、 15 200906673 =制早凡（64)，第—控制單元（6i)經設定凸輪轴向行 結離合器⑺3)停留於原位置1第四太陽齒輪 :動方向與第四環齒輪(44)相反，使得單向離離合器 =動並讓第四太陽齒輪（24)與固定主軸⑴連結為同 ，弟-控制單元（62)使平移控制制動單元⑺2)作動 使第—太陽齒輪⑺）與固定主軸⑴聯結並固定，第三控制 二了)使平移控制制動單元⑺丨)作動使第二太陽齒輪 )人固定絲⑴聯結並固定，第吨制單元（64)使平移 ㈣制動單元（71)作動使細太陽齒輪（24則定主抽⑴ ^結並固定’輸入動力由使用者以腳踏方式傳動鏈條帶動 鏈輪⑼，再由鏈輪（75)、經側蓋（74)帶動第四環齒輪州 動一亚傳遞至第四行星窗輪（Μ)、第四行星臂（Η)減速， 經第三行星臂（53)、第三行星齒輪（33)及第三環錄⑷） 作增速’由第二行星臂（52)、第二行星齒輪（32)及第二環 齒輪⑷)作料’並經由第一行星臂⑴）、第一行星齒輪 (^1)及第-續齒輪⑷）作增速，最後由單向棘輪輸出離合 益（671)輸出至車輪輪毅（76)，轉速比等於1 1557,為一減 速檔並可作為第八檔。 (九）第九檔位 ^參閱第十一圖所示，其為本創作實施例之切換至第九 杌位的組合剖視圖及能量傳遞路線圖，當檔位由第八檔位 刀換至第九檔位時，控制單元聯結套筒（65)旋轉同時帶動 16 200906673 第一控制單元（61)、第二控制單元（62) '第三控制單元 (63)、第四控制單元（64)，除了第一控制單元（61)經設定 凸輪轴向行程使得聯結離合器（7 1 3)經犬齒式離合器（7丨4) 與第三行星臂（53)聯結外，其於變速機構中各構件之作動 與第一檔位相同，轉速比等於丨，為一直接驅動檔並可作 為弟九槽。 (十）第十槽位 參閱第十二圖所示，其為本創作實施例之切換至第十 #位：的組合剖視圄芨能晉僂诚政綾园，洛诚，、.In the unconstrained state, the second planetary arm (52) and the second ring gear are forced by the JL first-戸I//D-% gear (42) to rotate more than the second planetary arm to force the one-way ratchet clutch (673). (42) coupled to the same member, the input power is driven by the user: the stepping drive chain drives the sprocket (75), and then the sprocket (75) rotates the fourth ring gear (44) via the side cover (Μ) And transmitted to the fourth planetary gear (10), the fourth four-spindle arm (54) decelerates, and accelerates through the third planetary arm (53), the third planetary gear (10) and the third ring gear (4), via the second planetary arm ( 52) After that, the speed is increased by the younger arm (51), the first planetary gear (1) and the first ring gear (4), and finally the one-way ratchet output clutch (671) is rotated to the number of wheels (76). The ratio is equal to 15511, which is a deceleration building and can be used as the sixth slot. (7) The seventh gear position of the ninth map of the wheat is tf' which is the combination sectional view and energy transmission road map of the creative embodiment switching to the seventh gear position, when the building is switched from the sixth standard to the seventh floor In the position, the control unit coupling sleeve (65) rotates while driving the first control unit (61), the second control unit (62), the third control unit, the fourth control unit (64), and the first control unit (61) After setting the cam axial line 14 200906673 == looking for the coupling clutch (7) 3) to stay in the original position, because the fourth sun gear () rotation direction is opposite to the fourth ring gear (five), so that the one-way clutch (66) is actuated and let the fourth Sun gear (24) 盥gj $ ± π I, U 疋 main shaft (1) is connected to the same component n unit (62) to make the translation control brake unit (712) actuate the brother-sun gear (21) and fixed spindle (1) Coupling and fixing, the third control unit (63) makes the translation (4) (four) unit (Chuan) the first: the sun tooth (10) is coupled and fixed to the fixed main shaft (1), and the fourth control unit state makes the translation control brake unit (5) not actuated The third sun gear (9) is free and unconstrained g 'by The second ring gear (43) rotates faster than the third planet arm (5)), thereby forcing the one-way ratchet clutch (674) to act such that the third planet arm and the third ring gear (43) are coupled to the same member, and the input power is used by the user. The chain belt _ wheel (75) is driven by the pedal, and then the fourth ring gear (44) is rotated by the sprocket (75) _ cover (74) and transmitted to the fourth planetary gear (9) 'the fourth planetary arm (10) is decelerated After passing through the third planetary arm (9), the second planetary arm (52), the second planetary gear (32) and the second ring gear (42) are accelerated, and are passed through the first planetary arm (5 1 ) and the flute. 1 ^ brother one star gear (31) and the first ring gear (41) for the speed, take the early ratchet output clutch (671) transport hub (10), the speed ratio, etc. - for - deceleration 楷 and can be used as the seventh Standard. (8) The eighth gear position is shown in the tenth figure, which is the combined sectional view and energy transmission road map of the creative embodiment switched to the eighth gear position, when the building is switched from the seventh standard position to the eighth position When the unit coupling sleeve rotates, the first control unit 7L (61), the first control unit (four), the third control unit, 15 200906673 = system (64), the first control unit (6i) is set to cam The axial line junction clutch (7) 3) stays in the home position 1 fourth sun gear: the moving direction is opposite to the fourth ring gear (44), so that the one-way clutch = movement and the fourth sun gear (24) is connected to the fixed main shaft (1) For the same, the control unit (62) causes the translational control brake unit (7) 2) to actuate to cause the first sun gear (7) to be coupled and fixed to the fixed main shaft (1), and the third control has made the translation control brake unit (7) 作) actuate Two sun gears) The fixed wire (1) is coupled and fixed, and the first ton unit (64) causes the translation (four) brake unit (71) to actuate the fine sun gear (24 is the main pumping (1) ^ knot and fixed 'input power by the user's foot The stepping drive chain drives the sprocket (9), and then The wheel (75) and the side cover (74) drive the fourth ring gear to move the state to the fourth planet window wheel (Μ), the fourth planet arm (Η) to decelerate, and the third planet arm (53), The three planetary gears (33) and the third ring (4) are used to increase the speed 'by the second planetary arm (52), the second planetary gear (32) and the second ring gear (4) and pass through the first planetary arm (1). The first planetary gear (^1) and the first-continuous gear (4) are used for increasing speed, and finally outputted by the one-way ratchet output from the benefit (671) to the wheel wheel (76), and the speed ratio is equal to 1 1557, which is a speed reduction gear. And can be used as the eighth gear. (9) The ninth gear position ^ Refer to the eleventh figure, which is a combination sectional view and energy transmission route diagram of the creative embodiment switching to the ninth position, when the gear position is changed from the eighth gear to the first In the nine-position position, the control unit coupling sleeve (65) rotates while driving 16 200906673 first control unit (61), second control unit (62) 'third control unit (63), fourth control unit (64), Except that the first control unit (61) sets the cam axial stroke so that the coupling clutch (7 1 3) is coupled to the third planetary arm (53) via the dog clutch (7丨4), which is in the components of the shifting mechanism The actuation is the same as the first gear position, and the speed ratio is equal to 丨, which is a direct drive gear and can be used as a nine-slot. (10) The tenth slot Referring to the twelfth figure, it is the combination of the creation example to the tenth place: the combination of the cross-section can be Jincheng Chengzheng Park, Luo Cheng,,.
(十一）第十一標位 其為本創作實施例之切換 至第十(11) The eleventh standard position is the switching of the creation example to the tenth
除了第一 參閱苐十三圖所示，其為本創作實 一播位的組合剖視圖及能 位切換至第十一檔位時， 帶動第一 元（62)、第三控制單 一控制單元（6 1)經設 %劲弟—控制單元（61)、第二 凡（63)、第四控制單元（64)， 17 200906673 定凸輪軸向行程使得聯結離合器⑺3)經犬嵩式離合号 (714)與第三行星f(53)聯結外，其於變速機構中各構件^ 作動與第三播位相同，轉速比等於〇 7451，為一 可作為第十—檔。 曰迷檔並 (十二）第十二檔位 ^參閱第十四圖所示，其為本創作實施例之切換至第^ =檔位的組合剖視圖及能量傳遞路線圖，當檔位由第十一 枯位切換至第十二檔位時，控制單元聯結套筒(65)旋轉^ 時讀第-控制單元(61)、第二控制單元(62)、第三控弟 ::⑹)、第四控制單元(64)，除了第一控制單元；: 设定凸輪轴向行程使得聯結離合器（713)經犬齒式離合罗 (714)與第三行星臂(53)聯結外’其於變速機構中各構：: 作動與第四稽位相同，轉速比等於Q 643 — 可作為第十二檔。 曰迷^3 (十三）第十三檔位 一*參閱第十五圖所示，其為本創作實施例之切換至第一 二檔位的組合剖視圖及能量傳遞路線圖，當檔位由第十 it::至弟十三檔位時，控制單元聯結套筒(65)旋轉丨 二動弟-控制單元(61)、第二控制單元(62)、第三控彳 〇Π )第四控制單元（64)，除了第一控制單元（6 i )《 Μ凸輪“行程使得聯結離合器（713) 、 (714)ik m ^ u ^ ^ 口 ，、 仃星臂（53)聯結外，其於變速機構中各構件 18 200906673 轉速比等於 作動與第五檔位相同 可作為第十三檔。 0.5547，為一增速檔並 (十四）第十四檔位 .參閱弟十六圖所示，其為本創作實施例之切換至第十 四檔位的Μ合剖視圖及能量傳遞路線圖，當標位由第十三 檔：切換至第十四檔位時，控制單元聯結套筒⑻)旋轉同In addition to the first reference to Fig. 13, it is a combination of a cross-sectional view of the actual broadcast position and the energy level is switched to the eleventh gear, which drives the first element (62) and the third control unit (6). 1) By setting % Jindi - control unit (61), second (63), fourth control unit (64), 17 200906673 fixed cam axial stroke so that the coupling clutch (7) 3) is passed through the canine clutch number (714) In addition to the connection with the third planet f (53), the components in the shifting mechanism act the same as the third broadcast position, and the rotational speed ratio is equal to 〇7451, which is a tenth-speed.曰 曰 并 and (12) twelfth gear position ^ see the fourteenth figure, which is a combination of the creative embodiment switching to the ^ = gear combination sectional view and energy transfer road map, when the gear position by When the eleven dry position is switched to the twelfth gear position, the control unit coupling sleeve (65) rotates to read the first control unit (61), the second control unit (62), and the third control brother: (6)), a fourth control unit (64), except for the first control unit;: setting the cam axial travel such that the coupling clutch (713) is coupled to the third planetary arm (53) via the dog-toothed clutch (714) In the following structure: The actuation is the same as the fourth position, and the speed ratio is equal to Q 643 — it can be used as the twelfth gear.曰迷^3 (13) Thirteenth gear position 1 * See the fifteenth figure, which is a combination sectional view and energy transmission route diagram of the first embodiment of the present embodiment, when the gear position is The tenth it:: When the thirteenth gear is in the thirteenth, the control unit coupling sleeve (65) rotates the second motion control unit (61), the second control unit (62), and the third control unit. The control unit (64), except that the first control unit (6 i ) "Μ cam" stroke causes the coupling clutch (713), (714) ik m ^ u ^ ^ port, and the comet arm (53) to be coupled, Each component of the shifting mechanism 18 200906673 has the same speed ratio as the fifth gear and can be used as the thirteenth gear. 0.5547, which is an increased speed and (fourteenth) fourteenth gear. It is a cross-sectional view and an energy transfer route diagram of the switching to the fourteenth gear position of the creative embodiment. When the position is changed from the thirteenth gear to the fourteenth gear, the control unit coupling sleeve (8) rotates. with
h動第-控制單元（61)、第二控制單元（62)、第三控制 单元（63)、第四控制單元（64)，& 了第—控制單元㈣經 攻定凸輪軸向行程使得聯結離合器（Μ)經犬齒式離合器 ⑺4)與第三行星臂（53)聯結外，其於變速機構中各構件之 作動與第六標位相同，轉速比等於Q.侧，為_增速樓並 可作為第十四槽。 ' '' (十五）第十五檔位 芩閱第十七圖所示，其為本創作實施例之切換至第十 五檔位的組合剖視圖及能量傳遞路線圖，當檔位由第十四 榀位切換至第十五檔位時，控制單元聯結套筒⑽旋轉同 時帶動第一控制單元（61)、第二控制單元（62)、第三控制 單元（63)、第四控制單元（64)，除了第一控制單元經 設定凸輪軸向行程使得聯結離合器（713)經犬齒式離合哭 (714)與第三行星臂（53)聯結外，其於變速機構中各構件之 作動與第七檔位相同，轉速比等於〇·4丨33，為—增速檔並 可作為第十五；j：當。 、' ' 19 200906673 (十六）第十六槽位 八圖所示，其為本創作實施例之切換至第十 的組合剖視圖及能量傳遞路線圖，當槽位由第十五 檔位切換至第十六稽位時， 瞎〜策 … 聯結套筒(65)旋轉同 W 控制單元（6〗）、第二控 结一…、 仏利早兀（62)、第三控制 ::第四控制單元(64)，除了第_控制單元㈣經 (714)二由向…吏得聯結離合器⑺3)經犬齒式離合器 上:三行星臂(53)聯結外，其於變速機構中各構件之 可作為第十六標。 手於。潘為一增速播並 综合以上所述之各樓位作動方式中，可知其 位分別為咖3、2.796G、2.4136、2.G833、1 797G、15511、 丨·3389、1，1557、1、0.8632……、。·……^ :二788、°.4133、0.3568，其中具有八檔低速檔、一直接 動棺及七樓高速樓位，變速倍率達到908%。 …康上述說明’本創作的特點在於其為第一個提出的十 :速内變速n設計，除了變速機構構型與習知的不同外， 、槽位時’由於1^輪及離合11經特殊設計後之排列方 ^使變逮機構的設計為最緊密設計，達到最少的空間需 白。此外，更重要的是槽位與轉速比以高低速樓位分佈均 :7式呈現’且棺位間的變動均趨近為0.863的安排則 二-最佳的動力傳遞方式。本創作係為—優良之設計，由 ;新穎的變速機構設計’再加上各構件有效之利用，改善 20 200906673 了習知的缺弊，無疑是一符合新穎性、實用性與可行性之 佳作，符合專利申請之要件。 f 21 200906673 【圖式簡單說明】 第一圖係為本創作實施例之組合剖視圖。 第二圖係為本創作實施例之機構簡圖。 第二圖係為本創作實施例之切換到第—檔位組合剖視圖及能量傳 遞路線圖》 第圖係為本創作實施例之切換到第二樓位組合剖視圖及能量傳 遞路線圖。 第五圖係為本創作實施例之切換到第三槽位組合剖視圖及能量傳 遞路線圖。 ★圖係為本創作貫施例之切換到第四標位組合剖視圖及能量傳 遞路線圖。 弟七圖係為本創作實施例之切換到第五槽位組合剖視圖及能量傳 遞路線圖。 第八圖係為本創作實施狀城到帛六標他合剖㈣及能量傳 遞路線圖。 第九圖係為本創作實施例之切換到第七槽位組合剖視圖及能量傳 遞路線圖。 第十圖係為本創作實施例之切換到第人檔位組合剖視圖及能量傳 遞路線圖。 第十β係為本創作實施例之切換到第九播位組合剖視圖及能量 傳遞路線圖。 第十一圖料袖作實施例之城到第Ή纽組合剖視圖及能量 傳遞路線圖。 弟十-圖係為本創作實施例之切換到第十—樓位組合魏圖及能 22 200906673 量傳遞路線圖。 卜 囷係為本創作實施例之切換到第十二檀位組合剖視圖及能 量傳遞路線圖。 第十五圖係為土名 ’、’、創作貫施例之切換到第十三檔位組合剖視圖及能 量傳遞路線圖。 弟十六圖係為本創作實施例之切換到第 量傳遞路線圖。H-moving-control unit (61), second control unit (62), third control unit (63), fourth control unit (64), & the first control unit (four) is determined by the axial travel of the cam The coupling clutch (Μ) is coupled to the third planetary arm (53) via the dog clutch (7) 4), and the movement of each member in the shifting mechanism is the same as the sixth standard position, and the rotational speed ratio is equal to the Q. side, which is the speed increasing building. And can be used as the fourteenth slot. ' '' (15) The fifteenth gear is shown in Figure 17, which is the combined sectional view and energy transmission route diagram of the fifteenth gear position of the creative embodiment, when the gear position is tenth When the four clamps are switched to the fifteenth gear position, the control unit coupling sleeve (10) rotates while driving the first control unit (61), the second control unit (62), the third control unit (63), and the fourth control unit ( 64), except that the first control unit sets the cam axial stroke such that the coupling clutch (713) is coupled to the third planetary arm (53) via the dog-tooth clutch crying (714), and the actuation of each component in the shifting mechanism The seven gears are the same, the speed ratio is equal to 〇·4丨33, which is the speed increase gear and can be used as the fifteenth; j: when. , ' ' 19 200906673 (16) The sixteenth slot in the eight-figure diagram, which is the combination sectional view and the energy transmission route diagram of the creation example to the tenth, when the slot is switched from the fifteenth gear to In the sixteenth position, the 瞎~ policy... The coupling sleeve (65) rotates with the W control unit (6), the second control knot..., 仏利早兀 (62), the third control:: the fourth control The unit (64), in addition to the first_control unit (four) via (714) two, the coupling clutch (7) 3) is coupled to the dog clutch: the three planetary arms (53) are coupled to each other in the shifting mechanism. Sixteenth standard. Hand on. Pan Weiyi increased the speed of the broadcast and integrated the above-mentioned various floor operation modes, it can be known that the positions are coffee 3, 2.796G, 2.4136, 2.G833, 1 797G, 15511, 丨·3389, 1,1557, 1 , 0.8632......,. ·......^ : Two 788, °.4133, 0.3568, which has eight low-speed gears, one direct-moving and seven-story high-speed building, and the transmission ratio reaches 908%. ... Kang said the above description, the characteristic of this creation is that it is the first proposed ten: speed internal speed n design, in addition to the difference between the configuration of the shifting mechanism and the conventional, in the slot position, due to the 1^ wheel and the clutch 11 The specially designed arrangement makes the design of the change mechanism the most compact design, and the minimum space needs to be white. In addition, it is more important that the slot-to-speed ratio is distributed at both high and low speeds: the 7-form is presented and the variation between the clamps approaches 0.863. The second-optimal power transmission mode. This creation is an excellent design, and the design of the novel transmission mechanism, together with the effective use of various components, improves the familiarity of the 20 200906673, which is undoubtedly a masterpiece of novelty, practicality and feasibility. , in line with the requirements of the patent application. f 21 200906673 [Simple description of the drawings] The first figure is a combined sectional view of the present embodiment. The second figure is a schematic diagram of the mechanism of the present embodiment. The second figure is a cross-sectional view of the switch to the first gear position and the energy transfer route diagram of the present embodiment. The first figure is a sectional view and a energy transfer route diagram of the second embodiment of the present embodiment. The fifth figure is a cross-sectional view of the switch to the third slot and an energy transfer route diagram of the present embodiment. ★ The diagram is a cross-sectional view of the fourth index position and an energy transfer route map. The seventh diagram is a cross-sectional view of the combination of the fifth embodiment of the present embodiment and an energy transfer route diagram. The eighth picture is the road map of the creation of the city from the creation of the city to the sixth standard and the energy transfer road map. The ninth figure is a cross-sectional view of the switch to the seventh slot combination and an energy transfer route diagram of the present embodiment. The tenth figure is a cross-sectional view of the switching to the first gear position and an energy transfer route diagram of the present embodiment. The tenth beta is the cross-sectional view of the switching to the ninth broadcast position and the energy transfer roadmap of the present embodiment. The eleventh figure is used as a sectional view of the city to the Dijon combination and an energy transfer route diagram of the embodiment. The tenth-picture is the switch to the tenth-floor combination Wei Tu and Neng 22 200906673. The diagram is a cross-sectional view of the twelfth place combination and an energy transfer route diagram of the present embodiment. The fifteenth figure is a cross-sectional view of the combination of the soil name ', ', the creation of the example to the thirteenth gear position and the energy transfer route map. The sixteenth figure is the switch to the first delivery route diagram of the present embodiment.
十四檔位組合剖視圖及能 十五檔位組合剖視圖及能 第十七圖係兔士 &, ‘”、本創作實施例之切換到第 量傳遞路線圖。 十六檔位組合剖視圖及能 第十八圖係為本創 量傳遞路線圖。 作實施例之切換到第 第十九圖係為本 釗作實施例之檔位作動表。The fourteen-position combination sectional view and the fifteen-position combination sectional view and the seventeenth figure of the rabbits &, '", the present embodiment switch to the first volume transmission road map. The eighteenth figure is a roadmap for the creation of the load. The switching to the nineteenth embodiment of the embodiment is the gear operation table of the embodiment.
23 200906673 【主要元件符號說明】 1 固定主軸 61 第一控制單元 21 第一太陽齒輪 62 第二控制單元 22 第二太陽齒輪 63 第三控制單元 23 第三太陽齒輪 64 第四控制單元 24 第四太陽齒輪 65 控制單元聯結套筒 31 第一行星齒輪 66 單向離合器 32 第二行星齒輪 671 單向棘輪輸出離合器 33 第三行星齒輪 672 、673、674單向棘輪離合器 34 第四行星齒輪 71、 711、712平移控制制動單元 41 第一環齒輪 713 聯結離合器 42 第二環齒輪 714 犬齒式離合器 43 第三環齒輪 721 ' 722 固定套筒 44 第四環齒輪 731 、732 定位螺帽 51 第一行星臂 733 鎖固螺帽 52 第二行星臂 74 側蓋 53 第三行星臂 75 鏈輪 54 第四行星臂 76 車輪輪轂 55 第三/四行星臂連結件 771 、772、773 轴承 2423 200906673 [Description of main component symbols] 1 Fixed spindle 61 First control unit 21 First sun gear 62 Second control unit 22 Second sun gear 63 Third control unit 23 Third sun gear 64 Fourth control unit 24 Fourth sun Gear 65 control unit coupling sleeve 31 first planetary gear 66 one-way clutch 32 second planetary gear 671 one-way ratchet output clutch 33 third planetary gear 672, 673, 674 one-way ratchet clutch 34 fourth planetary gear 71, 711, 712 translation control brake unit 41 first ring gear 713 coupling clutch 42 second ring gear 714 dog clutch 43 third ring gear 721 ' 722 fixed sleeve 44 fourth ring gear 731 , 732 positioning nut 51 first planet arm 733 Locking nut 52 second planet arm 74 side cover 53 third planet arm 75 sprocket 54 fourth planet arm 76 wheel hub 55 third/four planet arm link 771, 772, 773 bearing 24