201038420 .六、發明說明： 【發明所屬之技術領域】 本創作是有關於一種行星齒輪式六速汽車自動變速器。 【先前技術】 • R_neaux[1]於1940年首先提出一顆可用於汽車自動變速器的八 桿二自由度之行星齒輪機構，其採用單一行星臂且存在兩顆相互鄰接 星齒輪，一般將這類行星齒輪機構稱為Ravigneaux式行星齒輪機構。2〇〇5 年Ravigneaux式行星齒輪機構首度出現六速自動變速器的設計[2]，由於 -般的變速機構欲達到六速至少需要十桿以上[3_5】，故Ravigneaux式行 星齒輪機構僅八桿便可達到六速，可視為一重大突破。遺憾的是該設計結 果目前尚未被實際採用，究其原因發現中心線與兩相鄰接的行星齒輪節圓 切線夾角（簡稱行星齒輪夾角）非常容易大於120°，造成無法在對稱位置 上配置至少三組兩相鄰接的行星齒輪，故在實際製造上並不可行。 [1] Ravigneaux, P. 1940, "Speed Changing Device," U. S. Patent No. 2220174.201038420. VI. Description of the invention: [Technical field to which the invention pertains] This creation relates to a planetary gear type six-speed automatic transmission. [Prior Art] • R_neaux [1] first proposed an eight-bar two-degree-of-freedom planetary gear mechanism that can be used in automotive automatic transmissions in 1940. It uses a single planetary arm and there are two adjacent star gears. The planetary gear mechanism is called a Ravigneaux planetary gear mechanism. For the first time, the Ravigneaux planetary gear mechanism has a six-speed automatic transmission design [2]. Since the general-purpose shifting mechanism needs to achieve at least six strokes or more [6_5] for the six-speed transmission, the Ravigneaux planetary gear mechanism is only eight. The pole can reach six speeds and can be regarded as a major breakthrough. Unfortunately, the design result has not yet been actually adopted. The reason is that the angle between the centerline and the two adjacent planetary gear pitch tangents (referred to as the angle of the planetary gear) is easily greater than 120°, making it impossible to configure at least symmetrical positions. Three sets of two adjacent planetary gears are not practical in terms of actual manufacturing. [1] Ravigneaux, P. 1940, "Speed Changing Device," U. S. Patent No. 2220174.
[2] Hwang, W. M_, and Huang. Y L_, 2005，“Configuration Design of Six-Speed 〇 Automatic Transmissions with Two-degree-of-freedom Planetary Gear Train”，[2] Hwang, W. M_, and Huang. Y L_, 2005, “Configuration Design of Six-Speed 〇 Automatic Transmissions with Two-degree-of-freedom Planetary Gear Train”,
Transactions of the Canadian Society of Mechanical Engineering, Vol. 29, No. 1, pp. 41-55.Transactions of the Canadian Society of Mechanical Engineering, Vol. 29, No. 1, pp. 41-55.
[3] Scherer, H., “ZF 6-Speed Automatic Transmission for Passenger Cars,” SAE paper 2003-01-0596, 2003.[3] Scherer, H., “ZF 6-Speed Automatic Transmission for Passenger Cars,” SAE paper 2003-01-0596, 2003.
[4] Katou, N., Taniguchi, T, and Tsukamoto, K., “Aisin AW new Six-Speed Automatic Transmission for FWD Vehicles,” SAE paper 2004-01 -0651，2004.[4] Katou, N., Taniguchi, T, and Tsukamoto, K., “Aisin AW new Six-Speed Automatic Transmission for FWD Vehicles,” SAE paper 2004-01 -0651, 2004.
[5] Nozaki, Y, Tanaka, Y, and Tomomatsu, H., “Toyota’ s New Six-speed Automatic Transmission A761E for RWD Vehicles,” SAE paper 2004-01-0650, 2004. 4 201038420 【發明内容】 考慮魏__面辭涵，從先前技觸探討魏八桿、二自由 Ϊ1ΓΓΓΧ式行錢輪麟在六速自動變速器的設計上，因^鄰接 輪夾角非常容易大於120。，實際製造上始終被認為不可行，經 •麵式行星齒輪機構存在唯一一組標位作動順 =其苐-棺、紅檔與第六猶速比在某—特定的小細内 =的行星齒輪爽角小於11。。，由於這項研究成果尚未被發現，故;出本 Ο 〇 —是—種行結輪式六速汽車自_«，主要包含-由箱f 輪入端、三組輸入離合器、三組固定離合器與一顆 顆星齒輪式變速機構由二顆太陽齒輪、二顆ί二了二 仃星UW輪與一行星臂所組成，第一顆太陽齒輪盥 ^ 一 =與第=顆行星齒輪相响合，行星w同時與 二轉 r;上 離合器控制丨第一顆摄去私』又到弟一、二、三組輸入 三組固定離4控制目二顆太陽齒輪與行星臂分別受到第一、二、 高的特點，^第單、構件數少與各檔位傳動效率 小於·。，使摘作成為-深具^值的六;^===夹角 顆行星齒輪相則二顆太陽齒輪與第二顆 顆行星 【實施方式】[5] Nozaki, Y, Tanaka, Y, and Tomomatsu, H., "Toyota's New Six-speed Automatic Transmission A761E for RWD Vehicles," SAE paper 2004-01-0650, 2004. 4 201038420 [Summary of the Invention] Wei __ face vocabulary, from the previous technical touches to discuss Wei Ba, two free Ϊ 1 行 行 在 在 in the design of the six-speed automatic transmission, because the angle of the adjacent wheel is very easy to exceed 120. Actual manufacturing is always considered infeasible. There is a unique set of positions in the surface planetary gear mechanism. The 苐-棺, red and sixth speed ratios are in a certain small size. Planet gears have a cool angle of less than 11. . Since the results of this research have not yet been discovered, the original 〇 〇 是 是 种 种 种 种 种 是 是 是 是 是 是 是 是 是 是 是 是 是 是 , , , , , , , , , , , , , , , , , , , , , The gear shifting mechanism with a star gear consists of two sun gears, two ί二二二星星 UW wheels and a planetary arm. The first sun gear 盥^ = matches the first planetary gear , the planet w and the second turn r; the upper clutch control 丨 the first shot to go private and the brothers one, two, three groups input three sets of fixed off 4 control two solar gears and planet arms respectively receive the first and second , high characteristics, ^ the first, the number of components is small and the transmission efficiency of each gear is less than ·. , making the excerpt into a deep-valued six; ^=== angle, the planetary gear phase, then two sun gears and the second planet [Embodiment]
1、前視圖，其由箱則、輸 其中行星錄式魏賴構3與—勤輪人端4所⑷ 顆太_ 33、/編輪31、第—_輪32、I 顆行星—，並藉 201038420 w 力輸入構件與固定構件，達到變換不同轉速比的功能。第一顆太陽齒輪31、 第二顆太陽齒輪33與行星臂34分別受到第一組輸入離合器11、》於 入離合器12與第三組輸入離合器13控制；第一顆環齒輪&二=: 齒輪33一與行星臂34分別受到第一組固定離合器21、第二组固^ ^ 22與第三組固定離合器23控制。第一顆太陽齒輪31、第一 口杰 =顆太陽齒輪33、行星臂34與第二顆環齒輪35具；t_的迴轉轴' 沿迴轉軸位做言的迴轉。引擎經扭力轉換器的動 - w輪傳輸至動力輸入端4,然後再藉輸入離合器”、^、口 :條或 制行星齒輪式變速機構3的輸入構件。 、用，可控 請參閱第一圖與第二圖所示，其中第二圖係本創作每 srr，第-顆太陽齒輪31舆 ^ 第顆仃生齒輪36相响合，第二顆太陽齒 、 二一顆行星齒輪36與第二顆行星齒輪37以迴轉“ 1 =嚙合的 35為仃星歯輪式變速機構的輸出構件。 ，弟一顆％齒輪 請參_二_示，帛—斯星絲36 =相鄰接的行星齒輪，考慮變速機構的強度通視為一 則的兩相鄰接的行星齒輪。為避免各組行i齿輪置 則兩相鄰接的行星齒輪的夾角α應小於輪之間的干涉， 〇星齒輪的配置，本創作實施例 保至>、二組兩相鄰接行 的夫角α為_，表示桃4^齒可^果與第二顆行星齒輪37 請參閱第-圖、第三圖與第四 例之立體體、第四圖所示係本 ^ ^第三圖所示係本創作實施 算式與轉軌，檔位作動表中的符例之雛作動表、轉速比計 -組輸入離合器1與第三組固定離不對應的離合器作用，當第 組輸入離合器11與第-組m定離合^^作㈣為第i狀態；當第-輸入離合器與第二組固定離 用％為第二播狀態，·當第一組 二:合器11與第三組輸入離合器13作用：^第三檔狀態’·當第-組輸 離合器13與第二組固定離合器2==，四歡態；當第三組輸入 合器13與第—組固定離合器2 第五檔狀態；當第三組輸入離 用時為第六槽狀態；當第二組輸入離合 201038420 • 1112與第三組固定離合器23作用時為倒退驗態。轉速比定減於入盘 輸出構件轉速的比值，本創作實施例之第—標 稽^速比 分別為m= 3.000、n5= 0.750與〜=〇.550 m结棺的轉速比 倒退檔的轉速比計算式中，可得對應的轉速比八別A入^二稽、第三樓與 與〜：_3 〇〇〇。 場的轉速比刀別為n2= 1.900，= 1500 • 陽^ ί分別表示第—顆太陽齒輪31、第一顆環齒輪 △弟一^負太陽齒輪33、弟二顆環味絡资 行星齒輪37的齒數，本創作實施例2 _^订星齒輪36與第二顆 細-ηπη目ο I 為齒，因〜=3._、〜=〇.750 〇 ζ,=4齒齒、& 44 #、心132齒、Z㈣齒與 本創作實施例各槽位之構件轉速⑻與傳動效率 第一顆環4輪32 =二4叫5咏與⑴37分別表示第-顆太陽齒輪31、 本創作具有零件磨損率低、傳祕紐的優點麟&在95/°以上，可知 〇 欠4=圖:Γ係本創作之第—檔、第五槽與第六棺轉速比之解 «四個⑽製㈣爾，本創作 (4)速級比變化：I"./ >1= 1.2 (/-1,2,3,4,5), 程式的運算後得本創‘二:^ f (/= 1, 2, 3, 4)，在透過電腦 播之轉且秘等於3.耽第五 為大於等於G.5GQ且小於等於㈣、於f75G，第六播之轉速比範圍 設計之變速器才具有可行性與具備較佳的性〜唯有在解答空間中，所 201038420 【圖式簡單說明】1, the front view, which is carried out by the box, the planetary record type Wei Lai structure 3 and the - Qin wheel end 4 (4) too _ 33, / braid 31, the first _ round 32, I planet - and borrowed 201038420 w Force input member and fixed member to achieve the function of changing different speed ratio. The first sun gear 31, the second sun gear 33 and the planet arm 34 are respectively controlled by the first group of input clutches 11, the in-line clutch 12 and the third group of input clutches 13; the first ring gear & The gear 33 and the planet arm 34 are controlled by a first set of fixed clutches 21, a second set of solids 22, and a third set of fixed clutches 23, respectively. The first sun gear 31, the first port = the sun gear 33, the planet arm 34 and the second ring gear 35; the rotary axis of t_ rotates along the axis of rotation. The engine is transmitted to the power input terminal 4 via the motion-w wheel of the torque converter, and then the input member of the clutch ", ", port: or the planetary gear type shifting mechanism 3 is used. The figure and the second figure are shown, wherein the second picture is the srr, the first sun gear 31 舆 ^ the first twin gear 36, the second sun tooth, the two one planet gear 36 and the first The two planetary gears 37 are rotated by "1 = the engaged 35 is the output member of the comet-type wheel shifting mechanism. Brother, a % gear Please refer to _二_示, 帛-Singer 36 = adjacent planetary gears, considering the strength of the shifting mechanism as one of the two adjacent planetary gears. In order to avoid the set of i gears, the angle α between the two adjacent planetary gears should be smaller than the interference between the wheels. The configuration of the comet gear is saved to the following two embodiments. The angle α is _, indicating that the peach 4^ tooth can be the same as the second planetary gear 37. Please refer to the three-dimensional body of the first, third and fourth examples, and the fourth figure. The following shows the implementation of the formula and the transition, the stall action table in the gear action table, the speed ratio meter - the group input clutch 1 and the third group fixed off the corresponding clutch action, when the first group of input clutch 11 and The first set of two sets of the second clutch and the third set of input clutches is the first set of two: the first input: the second and the third set of input clutches. 13 action: ^ third gear state '· when the first-group clutch 13 and the second group of fixed clutch 2 ==, four joy state; when the third group of input combiner 13 and the first set of fixed clutch 2 fifth gear state When the third group input is used, it is the sixth tank state; when the second group is input, clutching 201038420 • 1112 and the third group of fixed clutches 23 When it is acting, it is a backward test. The ratio of the speed ratio is reduced to the speed of the input member of the disk. In the present embodiment, the first-standard speed ratio is m= 3.000, n5=0.750 and ~=〇.550 m, the speed of the knot is higher than the speed of the reverse gear. Compared with the calculation formula, the corresponding speed can be obtained compared to the eight different A into the second, the third floor and the ~: _3 〇〇〇. The speed of the field is n2= 1.900, = 1500 • Yang ^ ί respectively indicates the first sun gear 31, the first ring gear △ brother one ^ negative sun gear 33, the second two ring-flavored planetary gears 37 The number of teeth, the present embodiment 2 _^ the star gear 36 and the second thin - ηπη mesh ο I are teeth, because ~=3._, ~=〇.750 〇ζ, =4 teeth, & 44 #,心132齿,Z(四)齿与部件的速度位(8) and transmission efficiency of the first embodiment of the present invention, the first ring 4 wheel 32 = 2 4, 5咏 and (1)37 respectively denote the first sun gear 31, the present creation has The wear rate of the parts is low, and the advantages of the secrets are the nucleus & at 95/° or above, it is known that the 〇 4 4=图: Γ is the first, third, and sixth 棺 speed ratio solutions of the creation « four (10) System (four), this creation (4) speed ratio change: I ". / > 1 = 1.2 (/-1, 2, 3, 4, 5), the program after the operation of the creation of the second two: ^ f ( /= 1, 2, 3, 4), in the transmission through the computer and secret is equal to 3. 耽 fifth is greater than or equal to G.5GQ and less than or equal to (four), in f75G, the sixth broadcast speed ratio range design of the transmission Feasible and better - only in the answer In the [201 038 420] Brief Description of the drawings
W 第一圖本創作實施例之前視圖 第二圖本創作實施例之變速機構前視圖與對應的側視圖 第三圖本創作實施例之立體圖 第四圖本創作實施例之檔位作動表、轉速比計算式與轉速比 - 第五圖本創作實施例之齒數關係式與各齒輪齒數 第六圖本創作實施例各檔位之構件轉速（ω)與傳動效率（/7) ' 第七圖本創作之第一檔、第五檔與第六檔轉速比之解答空間的三視圖 ^ 【主要元件符號說明】 〇 〇 箱體 1 輸入離合器 11第一組輸入離合器 12第二組輸入離合器 13第三組輸入離合器 2 固定離合器 21第一組固定離合器 22第二組固定離合器 q 23第三組固定離合器 ' 3 行星齒輪式變速機構 31第一顆太陽齒輪 32第一顆環齒輪 33第二顆太陽齒輪 34行星臂 35第二顆環齒輪 36第一顆行星齒輪 37第二顆行星齒輪 4 動力輸入端Front view of the first embodiment of the present invention, the front view of the shifting mechanism of the present embodiment and the corresponding side view, the third drawing, the perspective view of the present embodiment, the fourth figure, the gear position of the creation embodiment, the rotation speed Ratio calculation formula and rotation speed ratio - Fig. 5 is a diagram showing the relationship between the number of teeth of the present embodiment and the number of teeth of each gear. Fig. 6 is a diagram showing the component rotation speed (ω) and the transmission efficiency (/7) of each gear position in the present embodiment. Three views of the solution space of the first, fifth and sixth speed ratios of the creation ^ [Main component symbol description] 〇〇 box 1 input clutch 11 first group input clutch 12 second group input clutch 13 third Group input clutch 2 fixed clutch 21 first group fixed clutch 22 second group fixed clutch q 23 third group fixed clutch '3 planetary gear shifting mechanism 31 first sun gear 32 first ring gear 33 second sun gear 34 planet arm 35 second ring gear 36 first planet gear 37 second planet gear 4 power input