TW530015B - Transmission devices, for ground vehicles and more particularly for motors-cars - Google Patents

Transmission devices, for ground vehicles and more particularly for motors-cars Download PDF

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Publication number
TW530015B
TW530015B TW090128455A TW90128455A TW530015B TW 530015 B TW530015 B TW 530015B TW 090128455 A TW090128455 A TW 090128455A TW 90128455 A TW90128455 A TW 90128455A TW 530015 B TW530015 B TW 530015B
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TW
Taiwan
Prior art keywords
patent application
scope
ratio
item
clutch
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TW090128455A
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Chinese (zh)
Inventor
Roumen Antonov
Frederic Morant
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Antonov Automotive Europ
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Publication of TW530015B publication Critical patent/TW530015B/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
    • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D45/00—Freewheels or freewheel clutches combined with automatic clutches

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

The epicyclic train is able to operate as a speed reducing gear when sun-wheel (5) is stuck by a one-way clutch (8), and in direct drive when clutch (10) is engaged. The whole coupling and control structure for the ratio change is essentially grouped on the sun-wheel element (5) which is slidingly movable and integral with an inverter control means (111) which engages brake (9) when disengaging clutch (10), and conversely. The brake (9) is mounted mechanically in parallel with a one way clutch (8), and allows speed reducing operation when the torque applied to the input shaft (31) is a retarding torque. The one-way clutch is mounted in parallel with an axially unslidable bearing (54) between a stator shaft (21) and a support (51) coupled for common rotation with and mutual slidability with respect to the sun-wheel element (5). For actuation of the control member (111) there is provided an hydraulic actuator (116), springs (114), and involvement of the helical teeth axial thrust (F1, F2). Useful for simplifying the control, keeping a possibility of other selective couplings, allowing other operating conditions, with the other rotary elements (6, 7) of the train, and avoiding the thrust bearings.

Description

A7 530015 __________B7_______ 五、發明說明（ί ) 【發明領域】 此發明有關於用於地面交通工具特別是用於汽車之傳 動裝置。 本發明更明確地有關於能夠自動化和/或能夠以相對 簡單結構提供無數傳動比率的傳動裝置。 【發明背景】 【相關先前技藝說明】 幾乎所有的自動傳動裝置使用差動機構或更特別地使 用行星齒輪系，其中選擇性的耦合裝置，例如：制動器、 離合器和/或單向離合器允許改變由每個基本齒輪系所提供 的傳動比率。傳統上，一行星齒輪系提供一個或其它兩個 比率，其中一個比率爲一可藉由一離合器與齒輪系其它兩 個互相嚙合旋轉元件相結合所得的直接驅動。提供多於兩 個比率的行星齒輪系係習知的，但是它們通常包含所謂的” 複雜的”行星齒輪系，也就是說，具有多於三個互相嚙合旋 轉元件的行星齒輪系，並且其實際上相當於至少兩個基本 的行星齒輪系。 因爲針對目前自動傳動裝置提供大數目的不同傳動比 •率的需要’例如：五個或甚至六個，所以其形成通常需要 設計包含有四個或甚至五個行星齒輪系的自動傳動裝置。 此類傳動裝置很笨重、昂貴、難處理，並且以活力效率的 字眼形容其效率是很差的。 並且’該多數個行星齒輪系造成特別複雜且昂貴的自 4 (請先閱讀背面之注意事項再填寫本頁) --------訂·-------- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公爱） A7 530015 __B7____ 五、發明說明（> ) 動控制。 ΕΡ-Α-0 683 877所揭露的自動傳動裝置，其中由於利 用螺旋齒的軸向推力，所以該自動控制作得比較簡單’同 時揭露該傳動力偶的量度和與此力偶成比例的一作動力量 。當該行星齒輪系當作一減速齒輪來操作時，此力量保持 於脫離狀況，一直接驅動離合器被安裝於該行星齒輪系的 輸入元件與輸出元件之間。同時地’該齒輪系的第三元件 ，當該引擎力偶被驅動時，藉由一單向離合器（飛輪）保 持於靜止狀態，並當該引擎力偶被逆轉時（引擎制動操作 )，則藉由一輔助制動器而受到一液壓作動。當該旋轉速 度高到足以允許此類飛行重量克服軸向齒推力時’該直接 驅動離合器的嚙合在離心飛行重量的效果下發生。該液壓 作動力量同時被使用於影響該傳動的自動化行爲’換句話 說其能夠改變該齒推力與離心作動力之間的”自然”平衡。 以此習知的裝置，該控制允許較小的複雜性與能源浪 費，但是同樣地一簡單的行星齒輪系僅能提供兩個比率。 並且，其需要很多的推力軸承，這是造成噪音與磨損的原 因。 該軸向位移需要操作於負載之下的齒條，其具有”污 ‘染”該力偶與分別由齒推力和離心飛行重量所提供的速度訊 號。 在該習知行星齒輪系的一個傳動比率與另外一個傳動 比率之間的切換牽涉到該齒輪系的所有元件，並且在該作 動元件之間需要一相對複雜的一致性（同時性）。雖然， 5 本紙張尺度適用中_家標準（CNS)A4規格（ χ 297公餐） (請先閱讀背面之注意事項再填寫本頁) 訂---------蜂 530015 A7 —--------~一 _BZ___ 五、發明說明（）） ^ 〜 一個行星齒輪係理論上能夠提供相當多數的傳動比率，伯 是實用上其無法提供超過兩個以上的比率，並且必須考鹰 到從一個比率轉換到另外一個比率的複雜切換程序。、〜 【發明目的】A7 530015 __________B7_______ V. Description of the Invention (Field of Invention) This invention relates to a transmission device for ground vehicles, especially for automobiles. The present invention relates more specifically to transmissions that can be automated and / or capable of providing numerous transmission ratios in a relatively simple structure. [Background of the invention] [Related prior art descriptions] Almost all automatic transmissions use differential mechanisms or more particularly planetary gear trains, where selective coupling devices such as brakes, clutches and / or one-way clutches allow changing Transmission ratio provided by each basic gear train. Traditionally, a planetary gear train provides one or two other ratios, one of which is a direct drive that can be obtained by combining a clutch with the other two intermeshing rotating elements of the gear train. It is customary to provide more than two ratios of planetary gear trains, but they usually contain so-called "complex" planetary gear trains, that is, planetary gear trains with more than three intermeshing rotating elements, and their actual This corresponds to at least two basic planetary gear trains. Because of the need to provide a large number of different transmission ratios for current automatic transmissions, such as five or even six, its formation usually requires the design of an automatic transmission that includes four or even five planetary gear trains. Such transmissions are bulky, expensive, difficult to handle, and poorly described in terms of dynamic efficiency. And 'the majority of planetary gear trains cause particularly complicated and expensive self-reporting (please read the precautions on the back before filling this page) -------- Order · -------- This paper size Applicable to China National Standard (CNS) A4 specification (210 X 297 public love) A7 530015 __B7____ 5. Description of the invention (>) Dynamic control. EP-Α-0 683 877 discloses an automatic transmission device, in which the automatic control is relatively simple due to the use of the axial thrust of the helical teeth. At the same time, the measurement of the transmission force couple and an action proportional to this force couple power. When the planetary gear train is operated as a reduction gear, this force is maintained in a disengaged state, and a direct drive clutch is mounted between the input element and the output element of the planetary gear train. Simultaneously, the third element of the gear train is held in a stationary state by a one-way clutch (flywheel) when the engine power couple is driven, and when the engine power couple is reversed (engine braking operation) by An auxiliary brake is actuated by a hydraulic pressure. When the rotation speed is high enough to allow such flying weights to overcome the axial tooth thrust ', the engagement of the direct drive clutch occurs under the effect of centrifugal flying weights. The amount of hydraulic power is also used to influence the automatic behavior of the transmission. In other words, it can change the "natural" balance between the tooth thrust and the centrifugal power. With this conventional device, the control allows less complexity and energy waste, but again a simple planetary gear train can only provide two ratios. In addition, it requires a lot of thrust bearings, which is the cause of noise and wear. This axial displacement requires a rack operating under a load, which has a "dirty" stain and a speed signal provided by the tooth thrust and the centrifugal flight weight, respectively. Switching between one transmission ratio and another transmission ratio of the conventional planetary gear train involves all the elements of the gear train and requires a relatively complex consistency (simultaneity) between the moving elements. Although, 5 paper sizes are applicable to the Chinese standard (CNS) A4 specification (χ 297 meals) (Please read the precautions on the back before filling this page) Order --------- Bee 530015 A7 —- ------- ~ 一 _BZ___ V. Description of the invention ()) ^ ~ A planetary gear train can theoretically provide a considerable number of transmission ratios. In practice, it cannot provide more than two ratios, and must Examine the Eagle to a complex switching procedure from one ratio to another. , ~ [Objective of the Invention]

此發明的目的之一在於提供一傳動裝置，其中在芦動 裝置中需要從一比率切換至另一比率所需要的裝置被g 地簡單化。 V 此發明的另一目的在於提供一傳動裝置，其中一簡單 的差動機構，也就是說僅以三個互相嚙合元件，即能夠提 供多於兩個的傳動比率。 本發明的更一目的在於提供一傳動裝置，其允許以十 分簡單的結構和一強化的機械效率來提供無數個比率。 【發明槪要】 根據本發明的一第一樣態，一傳動裝置，其中一差動 機構包含： -一外殻元件； -一輸入旋轉連接元件和一輸出旋轉連接元件； . -三個旋轉元件，其相對於該外殻元件係可旋轉地， 並彼此相互嚙合； -在該元件之間有兩個摩擦耦合裝置； -一單向離合器，其禁止該等旋轉元件的一第一元件 相對於該等元件的一第二元件的單一方向的相對旋轉； 6 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注音？事項再填寫本頁) 訂---------蜂 A7 530015 五、發明說明（十） -該耦合裝置的作動裝置； 其特徵在於： -該等選擇性耦合裝置的一第一裝置係機械地平行於 單向離合器； -該等選擇性耦合裝置的一第二裝置係可操作地安裝 於該等元件的該第一元件與一第三元件之間； -該兩個摩擦耦合裝置係由一介於兩個穩定狀態之間 的反向器控制裝置所協調，在該兩個穩定狀態中的每一個 狀態，該等耦合裝置的其中一個裝置係嚙合的，而另外一 個係釋放的。 使用此裝置，該差動機構的第一旋轉元件係牽涉到所 有耦合改變之中，而此等耦合改變對於改變該傳動比率是 需要的。該第一旋轉元件係： 1) 不是藉著該第一選擇性耦合裝置而被使得跟第二元 件（例如，外殻）來加速旋轉，並且藉著平行安裝於此第 一耦合裝置的單向離合器，針對一力偶方向來旋轉， 2) 就是藉著該第二選擇性耦合裝置而被使得跟第三元 件（例如，該等旋轉連接元件的其中一個，並在一尙更精 確的範例中，該輸入旋轉連接元件）來加速旋轉。 構成該傳動裝置的其它元件因此變得更爲簡單些。該 等摩擦耦合裝置能以一特別有利的方式被空間地聚集而彼 此靠近在一起。該等作動裝置更簡單了，因爲每個摩擦耦 合裝置具有一部分，該部分跟著第一旋轉元件快速旋轉， 因此其不再需要在以不同速度旋轉的元件之間傳送力量。 7 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) I---111 訂—— II----/' A7 530015 五、發明說明（< ) 該反向器控制裝置，特別地以該第一旋轉元件被連接以作 爲普通旋轉之用，可在其兩個穩定狀態之間穿過一在該處 兩個摩擦耦合裝置係同時脫離的漂浮位置。這並不是一項 缺點，因爲該單向離合器同時實現了相對於第一選擇性耦 合裝置的嚙合作用的情況。爲了達到此目的，該單向離合 器以平行於耦合裝置被安裝，該耦合裝置被嚙合以提供兩 個傳動比率的較低比率操作之用，並且由該單向離合器所 禁止的方向將產生一更低的傳動比率。 造成該差動機構的第一旋轉元件與反向器控制裝置成 爲一體並以其齒被做成螺旋狀的齒推力來貢獻該反向器控 制裝置的作動係特別有利的。 在此方式之中，該結構係簡單的且可靠的，且該齒推 力不需要交替就被傳送到反向器控制裝置處。該反向器控 制裝置較佳地被當作具有兩個相對面的每個相對面能夠緊 迫該第一和第二摩擦耦合裝置的各別一個的一簡單壓力元 件來應用。 一般而言，商業上可使用的單向離合器不允許相對的 軸向位移。雖然在該第一與第二元件之間提供有單向離合 器，爲了使該第一旋轉元件能夠軸向移動，較佳地與介於 .該第一旋轉元件與第二元件之間的單向離合器機械地串連 一裝置以提供普通旋轉與軸向位移性之用。 此用於普通旋轉的耦合係較佳地操作地安裝於該第一 和第二元件的其中之一元件和一單向離合器支撐之間。其 機械地以平行於該單向離合器方式提供一軸向不可滑動的 8 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） "' --------------------訂---------線 (請先閱讀背面之注意事項再填寫本頁) A7 530015 五、發明說明（k ) 軸承於單向離合器支撐與該第一和第二元件的另外一個元 件之間。因此，該單向離合器係完美地被保護以免於任何 軸向應力。 另一方面，爲了避免在具有軸向可滑動性的普通旋轉 裝置中的不正常摩擦，較佳地以獨立於具有軸向可滑動性 的普通旋轉裝置，該第一旋轉元件被導引來作軸向滑動。 用於普通旋轉的該裝置可被安裝於第一元件和單向離 合器支撐之間。因此，該支撐以與第一旋轉元件的同樣速 度來旋轉，另一方面與該第二元件（特別是外殻元件）被 軸向加速。該支撐於是被適用於攜帶另外一個作動裝置， 例如，彈簧，其能因此軸向地推進該第一旋轉元件，而不 需要插入任何軸向推力軸承。 一尙更作動裝置能包含一附屬於該第一旋轉元件處的 液壓推動元件，該液壓推動元件係與該第一旋轉元件同軸 並能同時提供該第一旋轉元件可滑動的引導。結果，所有 需要於比率改變的作動可藉由該第一旋轉元件和附屬其上 的反向器控制裝置的位移在多數個控制力量和不需要透過 軸向推力軸承的控制力量的傳動之下來獨立實行。 爲了一行星齒輪系中的兩傳動比率的選擇，一個基本 .上被聚合於該差動機構的旋轉元件的其中一元件上的耦合 和控制的基本結構已經被敘述了。本發明同時包含了將另 外一個此類基本結構提供於該差動機構的旋轉元件的另外 一個元件之上。該差動機構的第三旋轉元件可被例如地永 遠連接於該輸入和輸出旋轉連接元件的其中一個元件之上 9 本紙張尺度適用中國國家標準（CNS)A4規格（21〇 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) i I I I I I I 訂---------. A7 530015 五、發明說明（1 ) ，譬如說該輸出元件之上。所以，本發明提供一具有四個 不同操作狀態的行星齒輪系。 如果一同樣的旋轉連接兀件，例如該輸入元件，被處 理以便相關於該兩個並不與一單向離合器平行的摩擦耦合 裝置，則該四個操作狀態中的相對於上述兩個摩擦耦合裝 置被脫離的例子的其中一狀態爲一空檔狀態，該空檔狀態 對於允許該交通工具在交通工具引擎軸尙在旋轉時保持靜 止是很有用的。如果其它兩個選擇性耦合裝置爲阻擋該差 動機構和隨其的輸出連接元件的制動器，則一停泊制動能 功能被同時達成。爲了從此空擋狀態切換到相對於一傳動 比率的其它三個狀態的其中一個狀態，僅需要改變兩個反 向器控制裝置的其中一個反向器控制裝置的狀態，這可以 一高到足以確保該交通工具的漸進啓動的漸進性來完成。 因此，其以一單一簡單行星齒輪系提供一同時間具有三個 傳動比率、一空檔狀態和一能夠允許省卻傳統上提供於一 汽車之中的引擎和傳動裝置之間的離合器或力耦轉換器的 漸進式啓動裝置。 根據本發明的另外一個樣態，其能夠在該傳動裝中使 用以剛剛所敘述的方式來控制的兩個差動機構。該等差動 機構中的一個機構的各種狀態的其中一個狀態可爲一逆向 運轉比率。較佳地，該逆向運轉比率係被提供於位於更下 游的差動機構之中。 甚至以一單一簡單差動機構’將如所看到地，其能夠 提供一若干比率的向前驅動與一逆向驅動。 10 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) 訂---------線· A7 530015 ____B7___ 五、發明說明（g ) 根據此發明的更一樣態，其提供一傳動裝置，其中一 傳動機構包含： -一輸入旋轉連接元件和一輸出旋轉連接元件； -至少兩個相對於該外殼元件爲可旋轉的並且至少非 直接相互嚙合的旋轉元件； -至少一在脫離時能在該傳動機構中提供一空檔狀態 和在嚙合狀態中提供一介於該兩個連接元件之間的動力傳 送關係的摩擦耦合； -作動該摩擦耦合裝置的作動裝置，該作動裝置包含 1) 兩個不相容的作動裝置，該兩個不相容的作動裝置 的至少其中之一係可控制的； 2) 該兩個相互嚙合的旋轉元件的至少其中之一的一軸 向可移動性，和將該相互嚙合旋轉元件的一軸向齒推力傳 送給該摩擦耦合裝置的一壓力元件的傳動裝置。 本發明的此樣態提供了一免卻該傳統輸入離合器或輸 入耦合轉換器的可能性。一提供在該傳動機構中的摩擦親 合裝置係可操作於提供一其中從該主移動器到將被驅動的 例如一交通工具的輪子的負載的該動力傳送流動途徑被中 .斷於該傳動機構之中的空檔狀態。 並且，在該傳動中的齒輪齒所產生的軸向齒推力被當 作該摩擦耦合裝置的一作動力量來使用。如果該齒推力係 位於相對於摩擦耦合裝置的嚙合方向上時，則其結果是該 需要嚙合該摩擦耦合裝置的額外力量的減少。特別是，此 11 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ' *- (請先閱讀背面之注意事項再填寫本頁) i I I I---訂--------- *5^ A7 530015 五、發明說明（) 額外力量係由該例如一液壓致動器的可控制致動器所產生 。當該可控制致動器被減弱能量時’該離合器的脫離作用 能藉由一其強度足夠反作用於該齒壓力的彈簧來執行。當 該傳動裝置起初係處於空檔狀態，同時該交通工具先前已 經正在被啓動著，則此一類型裝置能夠執行該交通工具的 漸進式啓動。該可控制式致動器係可控制地被增加能量來 執行該交通工具的漸進與平順的啓動。例如’該交通工具 的加速可被偵測到，並比較於一需求値。此項比較的結果 爲該可控制致動器和/或該引擎的動力和/或r.p.m.(轉速） 的增加能量水準的調整基礎。 其同時能安裝該傳動機構，使得該齒推力的方向相反 於該可控制致動器所產生的力量的方向。該啓動作用於是 到某個程度地係自我調整的，因爲該交通工具的一非常高 的加速度產生該齒壓力的一增加，此增加傾向依次多少地 脫離該離合器，也就是，減少該離合器中的握緊。此解決 方案的缺點爲：由該致動器產生以用於嚙合該摩擦耦合裝 置的力量太高，因爲其必須克服該齒推力進而嚙合該離合 器。 根據此發明的一更進一步樣態，其提供一傳動裝置， .其中一傳動機構包含： -一輸入旋轉連接元件和一輸出旋轉連接元件； -至少兩個相對於該外殼元件爲可旋轉的並且至少非 直接相互嚙合的旋轉元件； _至少兩摩擦耦合裝置，每個摩擦耦合裝置當處於一 12 本紙張^度適用中國國家標準（CNS)A4規格（210 X 297公爱) --一 -- (請先閱讀背面之注意事項再填寫本頁) ---I---訂---------' A7 530015 五、發明說明（Μ ) 嚼合狀態時能以一^各別的傳動比率在該兩連接元件之間提 供一各別的動力傳送關係； -用於作動該摩擦耦合裝置的不相容作動裝置，該作 動裝置包含至少一可控制不相容作動裝： -其中，當兩摩擦耦合裝置係處於一彼此脫離狀態時 ，在該傳動機構中實現一空檔狀態。 該兩摩擦耦合裝置允許選擇該兩傳動比率中的其中一 個比率。當該兩摩擦耦合裝置係彼此脫離時，一空檔狀態 實現於該傳動機構之中，並允許該交通工具的引擎不需要 交通工具的驅動輪子的任何相對旋轉下旋轉。一個非常簡 單的結構被提供於該三操作狀態之間的選擇。 較佳地，一第四狀態可被提供，其中該兩摩擦耦合裝 置係彼此嚙合著。此一類第四狀態在大多數情況下係一直 接驅動狀態。 根據本發明的一另更進一步樣態，其提供一傳動裝置 ，其中一差動機構包含： -一外殻元件； -一輸入旋轉連接元件和一輸出旋轉連接元件； -兩個其相對於該外殼元件爲可旋轉的同軸嚙合元件 ,，其包含： •一太陽輪；和 •一冠狀輪； -一支撐若干個與該太陽輪和冠狀輪相嚙合的行星齒 輪的行星齒輪架元件； 13 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁)One of the objects of the present invention is to provide a transmission device in which a device required to switch from one ratio to another ratio in a moving device is simplified. V Another object of this invention is to provide a transmission device in which a simple differential mechanism, that is, with only three interengaging elements, can provide more than two transmission ratios. A further object of the present invention is to provide a transmission device which allows to provide countless ratios with a very simple structure and an enhanced mechanical efficiency. [Inventive summary] According to a first aspect of the present invention, a transmission device in which a differential mechanism includes:-a housing element;-an input rotary connection element and an output rotary connection element;-three rotations Element, which is rotatably relative to the housing element and engages with each other;-there are two frictional coupling devices between the element;-a one-way clutch that prohibits a first element of the rotating elements from opposing Relative rotation in one direction of a second component of these components; 6 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the note on the back? Matters before filling out this page) Order --------- Bee A7 530015 V. Description of the invention (ten)-Actuating device of the coupling device; It is characterized by:-A first device of the selective coupling device is mechanically parallel to the single device To the clutch;-a second device of the selective coupling devices is operatively installed between the first element and a third element of the elements;-the two friction coupling devices are Steady state The inverter control device coordinates that in each of the two stable states, one of the coupling devices is engaged and the other is released. With this device, the first rotating element of the differential mechanism is involved in all coupling changes, and these coupling changes are needed to change the transmission ratio. The first rotating element system: 1) is not accelerated by a second element (for example, a housing) through the first selective coupling device, and is unidirectionally mounted in parallel with the first coupling device The clutch rotates in the direction of a force couple. 2) The second selective coupling device is used to make the third component (for example, one of the rotational connection elements), and in a more precise example, This input rotates the connection element) to accelerate rotation. The other elements that make up the transmission are therefore simpler. Such friction coupling devices can be spaced together and brought close together in a particularly advantageous manner. Such actuating devices are simpler because each friction coupling device has a portion that rotates rapidly with the first rotating element, so it no longer needs to transfer power between elements rotating at different speeds. 7 This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) I --- 111 Order—— II ---- / 'A7 530015 5. Description of the invention (<) The inverter control device, in particular, the first rotating element is connected for ordinary rotation, and can pass between its two stable states, one at the two frictions there. The coupling device is a floating position that is simultaneously disengaged. This is not a disadvantage, since the one-way clutch simultaneously realizes the engagement with respect to the first selective coupling device. To achieve this, the one-way clutch is installed parallel to the coupling device, which is engaged to provide a lower ratio operation of two transmission ratios, and the direction prohibited by the one-way clutch will produce a more Low transmission ratio. It is particularly advantageous for the first rotating element that causes the differential mechanism to be integrated with the inverter control device and to contribute to the actuation system of the inverter control device with its teeth being helical tooth thrust. In this way, the structure is simple and reliable, and the tooth thrust is transmitted to the inverter control device without the need to alternate. The inverter control device is preferably applied as a simple pressure element having two opposite surfaces each capable of pressing the respective one of the first and second friction coupling devices. Generally speaking, commercially available one-way clutches do not allow relative axial displacement. Although a one-way clutch is provided between the first and second elements, in order to enable the first rotating element to move axially, it is preferably a one-way interposed between the first rotating element and the second element. The clutch is mechanically connected in series with a device to provide ordinary rotation and axial displacement. This coupling for normal rotation is preferably operatively mounted between one of the first and second elements and a one-way clutch support. It mechanically provides an axially non-sliding 8 papers parallel to the one-way clutch. The paper size applies to Chinese National Standard (CNS) A4 (210 X 297 mm) " '--------- ----------- Order --------- line (please read the precautions on the back before filling this page) A7 530015 V. Description of the invention (k) Bearing is supported by one-way clutch Between the first and second elements. Therefore, the one-way clutch system is perfectly protected from any axial stress. On the other hand, in order to avoid abnormal friction in an ordinary rotating device having axial slidability, it is preferable to use the first rotating element as a guide independent of an ordinary rotating device having axial slidability. Axial sliding. The device for ordinary rotation can be mounted between the first element and the one-way clutch support. Therefore, the support rotates at the same speed as the first rotating element, and on the other hand, is accelerated axially with the second element (especially the housing element). The support is then adapted to carry another actuating device, such as a spring, which can therefore advance the first rotating element axially without the need to insert any axial thrust bearing. The first actuator can include a hydraulic pushing element attached to the first rotating element, the hydraulic pushing element is coaxial with the first rotating element and can simultaneously provide slidable guidance of the first rotating element. As a result, all the actions required to change the ratio can be independent by the displacement of the first rotating element and the inverter control device attached thereto under the transmission of a plurality of control forces and control forces that do not need to pass through the axial thrust bearing Implemented. For the selection of two transmission ratios in a planetary gear train, a basic structure of coupling and control on one of the elements that are aggregated into the rotating elements of the differential mechanism has been described. The present invention also includes providing another such basic structure on the other element of the rotating element of the differential mechanism. The third rotating element of the differential mechanism can be permanently connected to one of the input and output rotating connecting elements, for example. 9 This paper size applies to the Chinese National Standard (CNS) A4 specification (21 × 297 mm). (Please read the precautions on the back before filling this page) i IIIIII Order ---------. A7 530015 V. Description of the invention (1), for example, on the output element. Therefore, the present invention provides a planetary gear train having four different operating states. If an identical rotary connection element, such as the input element, is processed so as to relate to the two friction coupling devices that are not parallel to a one-way clutch, then the four operating states are frictionally coupled relative to the two One of the examples of the device being disengaged is a neutral state, which is useful for allowing the vehicle to remain stationary while the vehicle engine shaft is rotating. If the other two selective coupling devices are brakes that block the differential mechanism and its output connecting element, a parking brake energy function is achieved at the same time. In order to switch from this neutral state to one of the other three states relative to a transmission ratio, it is only necessary to change the state of one of the two inverter control devices, which can be high enough to ensure that The gradual nature of the gradual start of the vehicle is done. Therefore, it is provided in a single simple planetary gear train at the same time with three transmission ratios, a neutral state, and a clutch or force coupling converter that can allow the traditionally provided engine and transmission in an automobile to be dispensed with. Progressive starter. According to another aspect of the present invention, it is possible to use two differential mechanisms controlled in the manner just described in the transmission. One of the states of one of the differential mechanisms may be a reverse operating ratio. Preferably, the reverse operating ratio is provided in a differential mechanism located further downstream. Even a single simple differential mechanism 'will, as can be seen, be able to provide a number of forward drive and reverse drive ratios. 10 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) Order --------- line · A7 530015 ____B7___ V. Description of the invention (g) According to a more general aspect of the invention, it provides a transmission device, wherein a transmission mechanism comprises:-an input rotary connection element and an output rotary connection element;-at least two are rotatable relative to the housing element And at least non-directly meshing rotating elements;-at least one frictional coupling capable of providing a neutral state in the transmission mechanism when disengaged and a power transmission relationship between the two connecting elements in the engaged state -An actuating device for actuating the friction coupling device, the actuating device comprising 1) two incompatible actuating devices, at least one of the two incompatible actuating devices is controllable; 2) the two An axial movability of at least one of the intermeshing rotating elements, and a transmission of an axial tooth thrust of the intermeshing rotating element to a pressure element of the friction coupling device Device. This aspect of the invention provides the possibility to dispense with the conventional input clutch or input coupling converter. A friction affinity device provided in the transmission mechanism is operable to provide the power transmission flow path in which a load from the main mover to, for example, a wheel of a vehicle to be driven is interrupted. Neutral status in the organization. And, the axial tooth thrust generated by the gear teeth in the transmission is used as a power amount of the friction coupling device. If the tooth thrust is located in the meshing direction with respect to the friction coupling device, the result is a reduction in the extra force required to mesh the friction coupling device. In particular, these 11 paper sizes are in accordance with China National Standard (CNS) A4 (210 X 297 mm) '*-(Please read the precautions on the back before filling this page) i II I --- Order --- ------ * 5 ^ A7 530015 V. Description of the invention () The extra power is generated by the controllable actuator such as a hydraulic actuator. When the controllable actuator is weakened 'the disengagement of the clutch can be performed by a spring which is strong enough to counteract the tooth pressure. When the transmission is initially in a neutral state and the vehicle has been previously started, this type of device can perform a gradual start of the vehicle. The controllable actuator system is controllably increased in energy to perform a gradual and smooth start of the vehicle. For example, ‘the vehicle ’s acceleration can be detected and compared to a demand 値. The result of this comparison is the basis for the adjustment of the energy level of the controllable actuator and / or the engine and / or r.p.m. (rotational speed). It can also install the transmission mechanism so that the direction of the tooth thrust is opposite to the direction of the force generated by the controllable actuator. The starting action is self-adjusting to a certain extent because a very high acceleration of the vehicle produces an increase in the tooth pressure, and this increase tends to disengage the clutch in order, that is, reduce the clutch in the clutch. Hold tight. The disadvantage of this solution is that the force generated by the actuator for engaging the friction coupling is too high because it must overcome the tooth thrust to engage the clutch. According to a further aspect of the invention, a transmission device is provided, wherein a transmission mechanism comprises:-an input rotary connection element and an output rotary connection element;-at least two are rotatable relative to the housing element and Rotating elements that are at least indirectly meshed with each other; _ At least two friction coupling devices, each friction coupling device should be on a 12-sheet paper, applicable to China National Standard (CNS) A4 (210 X 297 public love) ----- (Please read the precautions on the back before filling this page) --- I --- Order --------- 'A7 530015 V. Description of the invention (M) It can be divided into one when the state is chewed. The transmission ratio provides a separate power transmission relationship between the two connecting elements;-an incompatible actuator for actuating the friction coupling device, the actuator including at least one controllable incompatible actuator:-wherein When the two friction coupling devices are in a disengaged state, a neutral state is realized in the transmission mechanism. The two friction couplings allow selection of one of the two transmission ratios. When the two friction coupling devices are disengaged from each other, a neutral state is realized in the transmission mechanism, and the engine of the vehicle is allowed to rotate without any relative rotation of the driving wheels of the vehicle. A very simple structure is provided to choose between the three operating states. Preferably, a fourth state may be provided, wherein the two friction coupling devices are engaged with each other. This type of fourth state is in most cases always a driving state. According to a further aspect of the present invention, it provides a transmission device, wherein a differential mechanism includes:-a housing element;-an input rotary connection element and an output rotary connection element;-two relative to the The housing element is a rotatable coaxial meshing element, which includes: a sun gear; and a crown wheel; a planet gear carrier element supporting a plurality of planetary gears meshing with the sun gear and the crown wheel; Paper size applies Chinese National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page)

^1 n n n i^i imm n 一 口、I ϋ I— 1 1 I n I 530015 A7 B7 ---------^ 五、發明說明（I丨） -該行星齒輪架與輸出旋轉連接元件之間的連接裝置 -該等同軸嚙合元件、外殼元件和輸入連接元件之間 的選擇性耦合裝置； 其特徵在於該選擇性耦合裝置包含： -一用於選擇性地耦合該太陽輪於輸入連接元件和外 殻元件之上的第一聚合結構； -一用於選擇性地耦合該冠狀輪於輸入連接元件和外 殻元件之上的第二聚合結構； 因此提供： -一低比率，當該太陽輪被連接到輸入連接元件且該 冠狀輪被連接到外殻元件時； -一中間比率，當該太陽輪被連接到外殻元件且該冠 狀輪被連接到輸入連接元件時； -一直接驅動比率，當該太陽輪和冠狀輪同時被連接 到輸入連接元件時。 一非常簡單結構被提供給一具有至少低至三個嚙合輪 數目的三速傳動機構。 在幾乎無附加複雜性之下，當兩模組各別地將該輸入 ，連接元件從太陽輪和從冠狀輪切離時，更提供了一空檔狀 態。 根據此發明的更另一樣態，其提供一傳動裝置，包含 -一提供一低比率、一中間比率和一上比率的三速機 14 (請先閱讀背面之注意事項再填寫本頁) 訂---------線· 本紙張尺度適用中國國家標準（CNS)A4規格（21〇 X 297公釐） A7 530015 ____Β7____ 五、發明說明（A ) 構，其中該低比率與中間比率之間的一第一比率間隙至少 約爲該中間比率與上比率之間的一第二比率間隙的平方； -一與該三速機構串連安裝並提供一較低和較高比率 的兩速機構，該兩速機構在較低和較高比率之間具有一中 間於該第一和第二比率間隙的第三比率間隙， 其中藉由下列的組合提供六種排檔： -第一排檔：低比率和較低比率； -第二排檔：低比率和較高比率； -第三排檔：中間比率和較低比率； -第四排檔：上比率和較低比率； -第五排檔：中間比率和較高比率； -第六排檔：高比率和較高比率。 此一類具有前述比率間隙分佈的六速機構可爲定義於 本發明先前樣態的類型。 本發明的其它特徵與優點將從下列相關於非限制性範 例的說明中顯現出來。 【圖式簡單說明】 圖1和圖2係相對於依據本發明的傳動裝置的第一和 .第二具體實施例的軸向橫剖面示意圖。 圖3係依據本發明的傳動裝置的第三具體實施例的軸 向橫剖面的一略微更詳細的半視圖。 圖4係沿著依據本發明的傳動裝置的兩平行軸所做成 的剖面圖’其形式爲相對於每個軸分離成兩部分的兩半視 15 $氏張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 一 (請先閱讀背面之注意事項再填寫本頁) --------訂---------線· 530015 A7 _B7__ 五、發明說明（6 ) 圖。 圖5係一相似於圖2但僅表示一部分的修飾具體實施 例視圖。 圖6係一相似於圖2但表示另一修飾的具體實施例視 圖。 圖7和圖8係本發明的兩更具體實施例的示意圖。 圖9係相對於圖8該兩比率機構的修飾具體實施例的 右半部。 圖10係本發明的另一具體實施例的一示意圖。 圖11係圖10該具體實施例的右半部的一具體實施例 的槪略視圖。 圖12係依據本發明的傳動裝置的另一更具體實施例 的一示意圖。 【元件符號說明】 (請先閱讀背面之注意事項再填寫本頁) --------訂---------線 1 動機構 2 外殻元件 3 輸入旋轉連接元件 4 輸出旋轉連接元件、輸出軸 5, 6, 7 行星齒輪系 5 太陽輪旋轉元件 6 旋轉冠狀元件、冠狀輪 7 行星齒輪架旋轉元件 8 單向離合器、自由輪 16 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 _ B7 五、發明說明（斗） 9 第一摩擦耦合裝置 、制動器 10 第二摩擦耦合機構 、離合器 14 彈簧裝置 21 定子軸 22 環狀室 23 外殻元件部分 24 室 26 軸襯 27 活塞 28 爪形離合器 29 作動元件 31 輸入軸、管狀軸、 定子軸、引擎軸 32 鐘狀元件 35 太陽輪 41 輸出軸、管狀軸 42 齒輪齒、輸出齒 43 輸出齒輪 44 爪形離合器 45 中間連接元件、中間輸出元件 46 凸緣 51 支撐 52, 53 齒條 54 軸承 61 導引桿 17 (請先閱讀背面之注意事項再填寫本頁)^ 1 nnni ^ i imm n One mouth, I ϋ I— 1 1 I n I 530015 A7 B7 --------- ^ V. Description of the invention (I 丨)-The planetary gear carrier and the output rotary connection element Connection device-a selective coupling device between the coaxial engaging element, the housing element and the input connection element; characterized in that the selective coupling device comprises:-a selective coupling for the sun gear to the input connection element A first polymer structure above the housing element;-a second polymer structure for selectively coupling the crown wheel above the input connection element and the housing element; thus providing:-a low ratio when the sun When the wheel is connected to the input connection element and the crown wheel is connected to the housing element;-an intermediate ratio when the sun wheel is connected to the housing element and the crown wheel is connected to the input connection element;-a direct drive Ratio when the sun and crown wheels are connected to the input connection element at the same time. A very simple structure is provided for a three-speed transmission mechanism with a number of at least three meshing wheels. With almost no additional complexity, the two modules provide a neutral state when the input and connection elements are cut off separately from the sun gear and the crown wheel. According to yet another aspect of this invention, it provides a transmission device including-a three-speed machine 14 providing a low ratio, an intermediate ratio and an upper ratio 14 (please read the precautions on the back before filling this page) order- -------- Line · This paper size applies to China National Standard (CNS) A4 specification (21 × X 297 mm) A7 530015 ____ Β7 ____ V. Description of invention (A), where the low ratio and the middle ratio A first ratio gap between at least about the square of a second ratio gap between the intermediate ratio and the upper ratio;-a two-speed mechanism installed in series with the three-speed mechanism and providing a lower and higher ratio The two-speed mechanism has a third ratio gap between the first and second ratio gaps between the lower and higher ratios, wherein six gears are provided by the following combination:-First gear: low ratio And lower ratio;-second gear: low ratio and higher ratio;-third gear: middle ratio and lower ratio;-fourth gear: upper ratio and lower ratio;-fifth gear: middle ratio and lower ratio High ratio;-sixth gear: high ratio and comparison Ratio. This type of six-speed mechanism with the aforementioned ratio gap distribution may be the type defined in the previous aspect of the present invention. Other features and advantages of the present invention will appear from the following description relating to non-limiting examples. [Brief description of the drawings] Figures 1 and 2 are schematic axial cross-sectional views of the first and second specific embodiments relative to the transmission device according to the present invention. Fig. 3 is a slightly more detailed half view of an axial cross section of a third embodiment of a transmission device according to the present invention. Fig. 4 is a cross-sectional view taken along two parallel axes of a transmission device according to the present invention, which is in the form of two halves that are separated into two parts with respect to each axis. A4 specifications (210 X 297 mm) I (Please read the precautions on the back before filling out this page) -------- Order --------- line 530015 A7 _B7__ V. Description of the invention (6) Figure. Fig. 5 is a view of a modified embodiment similar to Fig. 2 but showing only a part of the modification. Fig. 6 is a view of a specific embodiment similar to Fig. 2 but showing another modification. 7 and 8 are schematic diagrams of two more specific embodiments of the present invention. FIG. 9 is a right half of a modified embodiment of the two-ratio mechanism with respect to FIG. 8. FIG. FIG. 10 is a schematic diagram of another embodiment of the present invention. Fig. 11 is a schematic view of a specific embodiment of the right half of the specific embodiment of Fig. 10; Fig. 12 is a schematic diagram of another more specific embodiment of the transmission device according to the present invention. [Description of component symbols] (Please read the precautions on the back before filling this page) -------- Order --------- Wire 1 Actuating Mechanism 2 Housing Element 3 Input Rotary Connection Element 4 Output rotary connection element, output shaft 5, 6, 7 planetary gear train 5 Sun gear rotation element 6 Rotation crown element, crown wheel 7 Planet gear carrier rotation element 8 One-way clutch, free wheel 16 ) A4 size (210 X 297 mm) 530015 A7 _ B7 V. Description of the invention (bucket) 9 First friction coupling device, brake 10 Second friction coupling mechanism, clutch 14 Spring device 21 Stator shaft 22 Annular chamber 23 Housing Element 24 Chamber 26 Bushing 27 Piston 28 Claw clutch 29 Actuating element 31 Input shaft, tubular shaft, stator shaft, engine shaft 32 Bell-shaped element 35 Sun gear 41 Output shaft, tubular shaft 42 Gear teeth, Output teeth 43 Output gear 44 Claw clutch 45 Intermediate connecting element, intermediate output element 46 Flange 51 Support 52, 53 Rack 54 Bearing 61 Guide rod 17 (Please read the back first Note to fill out this page)

* I 訂---------線· 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 _B7 五、發明說明（6 ) 62 凸緣 63 軸襯 64 液體室 65 爪形離合器齒 71 轉軸 72 行星輪 73 爪形離合器裝置 81 中間副齒輪 82 副齒輪 83 中間偏心階梯副齒輪 84 第二齒組 86 籠子 87, 88, 89 圓環 91 爪形離合器 92 爪形離合器 93 耦合元件 94 圓環 96, 97 爪形離合器 97, 98, 99 逆向驅動連接 98 中間輸出元件、中間逆向驅動元件 99 副齒輪 101 交通工具引擎 102 輸入離合器 111 反向器控制裝置、壓力元件 18 (請先閱讀背面之注意事項再填寫本頁) -------- 訂---------線 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 B7 五、發明說明（山） 112 113 114 116 117 118 131 141 142 181 181 182 182 183 184 186 208 209 209 210 211 212 213 214 壓迫面 壓迫面 彈簧 液壓致動器 活塞 彈簧 輸入軸 軸向推力軸承 推力軸承 逆向驅動連接 中間副齒輪 齒輪齒 逆向驅動連接 彈簧 圓環 爪狀離合器 單向離合器、自由輪 制動器 離合器 離合器 反向器控制元件 壓迫面 壓迫面 彈簧 (請先閱讀背面之注意事項再填寫本頁) 訂---------線· 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 B7 五、發明說明（^ ) 216 217 251 252, 253 254 255 256 301 302 303 304 308 309 310 311 312 313 314 316 317,318,319,320 322 330 333 334 液壓致動器 活塞 單向離合器支撐 齒條 不可滑動軸承 爪形離合器 爪形離合器齒 第一傳動機構 第二差動機構 逆向驅動機構、分離單位 輸出連接元件 單向離合器 制動器 離合器 反向器控制元件 壓迫面 壓迫面 彈簧 液壓致動器 致動器 液壓室 輸入連接元件 軸承 輸入齒輪 (請先閱讀背面之注意事項再填寫本頁) ^4--------訂--------—線· 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 B7 五、發明說明（ 336 軸 350 太陽輪元件 352, 353 齒條 354 軸承 360 冠狀輪元件、第二機構冠狀輪 361 爪形離合器系統 362 爪形離合器 365 軸承 370 行星齒輪架 371 偏心轉軸 372 行星齒輪 373 爪（形）離合器系統 374 軸襯狀控制元件 376 稱合園 402 雙速副軸機構、第二機構 408 單向離合器、自由輪 410 推進器副齒輪 411 接收器副齒輪 413 離合器 414 彈簧裝置 416 致動器 420 推進器副齒輪 411,421,422 接收器副齒輪 423 摩擦離合器 21 (請先閱讀背面之注意事項再填寫本頁) 訂---------線- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） A7 530015 _______B7 五、發明說明Μ ) 425 齒推力 426 液壓致動器 442 推力軸承 482 逆向推進器副齒輪 483 中間副齒輪 484 逆向接收器副齒輪 【較佳實施例的詳細說明】 在圖1所表示的範例當中，該傳動裝置基本上包含一 差動機構1，其包含： 一外殼元件2，其僅部分代表和包含一相對抗平移和 旋轉而靜止並沿著該機構的主X軸延伸的定子軸21 ; 一輸入旋轉連接元件3 ’其係被防止相對於該外殼元 件2的平移，並包含一超過該定子軸21而順著該主軸X 延伸的輸入軸31，該輸入軸31其目的在於直接或間接地 連接交通工具的一驅動引擎軸； 一其目的在於至少間接地被連接到該交通工具的輸出 旋轉連接元件4，其包含一沿著軸X被安裝並具有繞著該 定子軸21而做相對旋轉的可能性的管狀軸31 ; . 一沿著軸X繞著該定子軸21安裝且能夠相對於後者 繞著軸X旋轉的太陽輪旋轉元件5 ; 一可旋轉地繞著該軸X裝載並繞著太陽輪元件5和定 子軸21安裝的旋轉冠狀元件6，該輸入連接元件3具有一 鐘狀元件32，靠著該鐘狀元件32使得該冠狀輪6與輸入 22 本紙張尺度適用中國國家標準（CNS)A4規格（21Q x 297公爱） 一 (請先閱讀背面之注意事項再填寫本頁) 訂---------線. A7 530015 五、發明說明（/ ) 軸31 —起被加速； 一與該輸出軸41形成一體並攜帶著若干規則分佈於 軸X四周且相對於主軸X偏心的轉軸71的行星齒輪架旋 轉元件7,在上面的該等行星齒輪係可自由地在上面旋轉 並且同時與太陽輪元件5和冠狀輪元件6相嚙合，藉此與 它們形成一彳了星齒輪系； 一僅象徵性被代表並避免該太陽輪元件5以相反於輸 入軸31之旋轉方向相對於外殻元件2來旋轉的單向離合器 8 ° 如果該傳動裝置限制於剛才所敘述的機構，則其僅將 當作一減速齒輪來操作，並且僅有如果施加於該輸入軸31 上面的力耦係一引發運動的力耦，方能成立。在此一類似 例子當中，該行星齒輪架7自輸出軸41所承受的負載具有 停止轉軸71的傾向，使得施加於該冠狀輪6上面的引發運 動力耦傾向於造成太陽輪元件5的逆旋轉。但是此一傾向 被該單向離合器8所防止，使得該太陽輪元件5被停止且 該行星齒輪架7以一中間於太陽輪5零速度和冠狀輪6相 對於輸入軸31速度的速度來旋轉。 如果施加於該引擎軸31的力耦係負的，也就是當該 .交通工具操作的引擎具有一制動時，該交通工具的輪子f頃 向於，透過該輸出軸4，造成該行星齒輪架7的旋轉快於 連接於輸入軸31的冠狀輪6的旋轉，並且此傾向於造成該 太陽輪5的旋轉更快速於行星齒輪架7的旋轉，此現象之 發生並不被該單向離合器8所防止。此錯誤操作必須被避 23 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁)* I order --------- line · This paper size applies to China National Standard (CNS) A4 specification (210 X 297 mm) 530015 A7 _B7 V. Description of the invention (6) 62 Flange 63 Bushing 64 Liquid chamber 65 Claw clutch teeth 71 Rotary shaft 72 Planetary gear 73 Claw clutch device 81 Intermediate gear 82 Sub gear 83 Intermediate eccentric stepped gear 84 Second tooth set 86 Cage 87, 88, 89 Ring 91 Claw clutch 92 Claw Clutch 93 coupling element 94 ring 96, 97 claw clutch 97, 98, 99 reverse drive connection 98 intermediate output element, intermediate reverse drive element 99 auxiliary gear 101 vehicle engine 102 input clutch 111 reverser control device, pressure element 18 (Please read the precautions on the back before filling this page) -------- Order --------- The size of thread paper is applicable to China National Standard (CNS) A4 (210 X 297) 530015 A7 B7 V. Description of the invention (mountain) 112 113 114 116 117 118 131 141 142 181 181 182 182 182 183 184 186 208 209 209 210 211 212 213 214 to Thrust bearing thrust bearing reverse drive connection intermediate counter gear gear teeth reverse drive connection spring ring claw clutch one-way clutch, free wheel brake clutch clutch reverser control element pressing surface pressing surface spring (please read the precautions on the back before filling (This page) Order --------- Line · This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) 530015 A7 B7 V. Description of the invention (^) 216 217 251 252, 253 254 255 256 301 302 303 304 308 309 310 311 312 313 314 316 317,318,319,320 322 330 333 334 Hydraulic actuator piston one-way clutch support rack non-sliding bearing claw clutch claw clutch teeth first transmission mechanism second differential mechanism Reverse drive mechanism, separation unit output connection element one-way clutch brake clutch reverser control element pressing surface pressing surface spring hydraulic actuator actuator hydraulic chamber input connection element bearing input gear (please read the precautions on the back before filling in this Page) ^ 4 -------- Order ---------- Line · This paper size applies to Chinese national standards CNS) A4 specification (210 X 297 mm) 530015 A7 B7 V. Description of the invention (336 shaft 350 sun gear element 352, 353 rack 354 bearing 360 crown wheel element, second mechanism crown wheel 361 claw clutch system 362 claw shape Clutch 365 Bearing 370 Planetary gear carrier 371 Eccentric shaft 372 Planetary gear 373 Claw (shape) clutch system 374 Bushing-like control element 376 Weighing park 402 Two-speed countershaft mechanism, second mechanism 408 One-way clutch, free wheel 410 thruster Pinion 411 Receiver Pinion 413 Clutch 414 Spring device 416 Actuator 420 Thruster pinion 411,421,422 Receiver pinion 423 Friction clutch 21 (Please read the precautions on the back before filling this page) Order ------ --- Line- This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) A7 530015 _______B7 V. Description of invention) 425 Tooth thrust 426 Hydraulic actuator 442 Thrust bearing 482 Reverse thruster auxiliary gear 483 Intermediate gear 484 Reverse receiver gear [Detailed description of the preferred embodiment] The example shown in Figure 1 In the transmission, the transmission basically includes a differential mechanism 1 including: a housing element 2 which only partially represents and includes a stator shaft 21 that is relatively resistant to translation and rotation and is stationary along the main X axis of the mechanism An input rotary connection element 3 'which is prevented from translation relative to the housing element 2 and includes an input shaft 31 which extends beyond the stator shaft 21 and extends along the main shaft X, the purpose of which is to directly or A drive engine shaft of a vehicle indirectly connected; a purpose of which is to be connected at least indirectly to the output rotary connection element 4 of the vehicle, which includes a shaft X mounted along the shaft X and having a structure around the stator shaft 21 Tubular shaft 31 with the possibility of relative rotation;-a sun gear rotating element 5 mounted around the stator shaft 21 along the axis X and capable of rotating relative to the latter around the axis X; a rotatable load around the axis X A rotating crown-shaped element 6 mounted around the sun gear element 5 and the stator shaft 21. The input connection element 3 has a bell-shaped element 32, and the crown-shaped element 6 and the input 22 are supported by the bell-shaped element 32. National Standard (CNS) A4 Specification (21Q x 297 Public Love) One (Please read the precautions on the back before filling out this page) Order --------- Line. A7 530015 V. Description of Invention (/) Shaft 31 — is accelerated; a planetary gear carrier rotating element 7 that is integrated with the output shaft 41 and carries a number of rotating shafts 71 that are regularly distributed around the axis X and eccentric with respect to the main shaft X, and the planetary gear trains above may be Rotate freely on top and mesh with the sun gear element 5 and the crown gear element 6 at the same time, thereby forming a star gear train with them; a symbolic representation is only avoided and the sun gear element 5 is prevented from being opposite to the input shaft One-way clutch with 31 rotation direction relative to housing element 2 8 ° If the transmission is limited to the mechanism just described, it will only operate as a reduction gear and only if applied to the input The force coupling above the shaft 31 is a force coupling that causes motion. In a similar example, the load on the planetary gear carrier 7 from the output shaft 41 has a tendency to stop the rotating shaft 71, so that the induced motion force coupling applied on the crown wheel 6 tends to cause the reverse rotation of the sun gear element 5. . However, this tendency is prevented by the one-way clutch 8 so that the sun gear element 5 is stopped and the planetary gear carrier 7 rotates at a speed intermediate to the zero speed of the sun gear 5 and the speed of the crown wheel 6 relative to the speed of the input shaft 31 . If the force coupling applied to the engine shaft 31 is negative, that is, when the engine operated by the vehicle has a brake, the wheel f of the vehicle is oriented through the output shaft 4 to cause the planetary gear carrier. The rotation of 7 is faster than the rotation of the crown wheel 6 connected to the input shaft 31, and this tends to cause the rotation of the sun gear 5 to be faster than that of the planetary gear carrier 7. This phenomenon is not caused by the one-way clutch 8 Prevented. This wrong operation must be avoided

· I ------訂---------線. A7 530015 五、發明說明（“） 免，並將造成該引擎不需要制動該交通工具即恢復空轉。 因此，其在該太陽輪元件5和外殻元件2之間提供一係機 械地平行於該單向離合器8的第一摩擦耦合裝置_或制動器 9。當耦合時，該制動器9使得該太陽輪5相對外殼元件2 係靜止的’並且因此允3午該傳動裝置當施加於輸入軸31的 力耦係負時被當作一減速齒輪來操作，當該力偶是正時， 以相同的方式來操作。該制動器9可以一剛好足夠被使用 於牽涉到遠弱於尖峰引發運動的力耦的力耦的制動操作的 方式來設計尺寸。 由於一第二摩擦耦合機構或離合器_1〇能夠選擇性地 耦合以使用於該行星齒輪系的三個旋轉元件5, 6, 7的其中 兩個元件的旋轉，使得該整個行星齒輪系當作繞著軸X的 一單一部分來旋轉，所以該傳動裝置更加允許一直接驅動 比率的實現。此自動地藉著該自由輪8而成爲可能，但需 要脫離該制動器9。 根據此發明的一項重要特徵，該第二摩擦耦合裝置1〇 係相關於同樣的旋轉兀件，也就是在該代表性範例中係相 關於太陽輪元件5，就像該其它已經說明的耦合裝置，亦 即該単向離合拖^ 8和弟一^親合裝置9。 更特別地，在該代表性範例當中，該第二摩擦耦合裝 置係操作地安裝於該太陽輪元件5和輸入連接裝置3之間 〇 在上文中其已經解釋：該第二摩擦鍋合裝置1〇的嚙 合需要脫離該第一摩擦耦合裝置9。相反地，該制動器 (請先閱讀背面之注意事項再填寫本頁) -------訂----I--- *5^ · 9 24 A7 530015 五、發明說明（) 的嚙合需要脫離離合器10。爲達成此目的，根據本發明的 一項更重要特徵，一單一控制元件111當作介於兩穩定狀 態之間的一反向器來操作，在每個穩定狀態之中，該摩擦 耦合裝置9, 10中的各別一裝置係嚙合的而另外一個裝置 係各別地脫離的。在所示範的例子當中，該反向器控制裝 置111係一軸向可移動的壓力元件。當被朝圖1的右方推 進時，該壓力元件111嚙合制動器9並脫離離合器10。當 被朝圖1的左方推進時，該壓力元件111脫離制動器9並 嚙合離合器10。此兩個穩定狀態之間的切換係由一軸向傳 動動作所執行。 該壓力元件111係與太陽輪元件5形成一體，因此以 相同於後者的旋轉速度來旋轉。因爲兩摩擦耦合裝置9和 10同時具有以一機構1的各別另一元件來選擇性地連接太 陽輪5的功能，所以該壓力元件111與太陽輪元件5的形 成一體的連接允許壓力元件111實現了以一具有兩相對壓 迫面的普通壓力元件來成形，亦即一壓迫面112使用於制 動器9扁碟的疊置而一壓迫面113使用於離合器10扁碟的 疊置。 一般而言，市場中可供應的該等單向離合器需要被安 ,裝於兩個彼此係相對軸向靜止的元件之間。因此，當將該 太陽輪元件5的軸向可移動性考慮進去時，則該單向離合 器8不能直接地安裝於太陽輪元件5和外殻元件2之間。 依據這個理由’其提供一在其外周邊軸向轉輪52上嚙合著 該太陽輪元件5的相對軸向齒條53的支撐51，藉此該太 (請先閱讀背面之注音？事項再填寫本頁} --------訂---------線· 25 530015 A7 ____ Β7 五、發明說明（A ) 陽輪5係相對於支撐51爲可滑動的，同時被耦合以作爲普 通一起旋轉之用。藉著一介於該支撐51和定子軸21之間 的軸向不可滑動軸承54的安裝，使得該支撐51係相對於 外殻元件2爲軸向靜止的。該單向離合器8同樣地平行於 軸承54被安裝於支撐51和定子軸21之間。 爲了對兩摩擦耦合裝置9和10進行反向控制，該反 向器控制裝置111受到下列三作動裝置的斜調性動作： -一包含已經如所述地在該反向器控制裝置Π1和太 陽輪元件5之間形成一體連接的第一作動裝置。由於此形 成一體的連接，使得該反向器控制裝置111受到由於其齒 的螺旋形狀因而發生於太陽輪元件5之中軸向推力作用。 此推力係由該等齒所傳動的力耦的量度； -一包含至少一個例如BELLEVILLE墊圈堆疊並插入 軸向靜止支撐51和太陽輪元件5之間的彈簧114的第二作 動裝置； -該第三作動裝置係一包含一成形於外殻元件2之中 的環狀室22和與反向器控制元件111形成一體並具有一圍 繞軸X的圓環形狀的活塞117的液壓致動器116。該活塞 Π7於是在與外殻元件2形成一體的室22之中繞著軸X旋 圖1以箭頭F1和F2表不該太陽輪兀件5所受到的齒 推力的兩個可能方向。針對該等齒的傾斜的一特定方向， 當施加於該輸入軸31上面的力偶係引發運動的，則該軸向 推力出現在一相對應的特定方向上，而當該施加於輸入軸 26 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) -------訂---------· 530015 A7 _ B7_ 五、發明說明（>iV ) 31上的力偶係爲負時（引擎制動操作），則該軸向推力出 現在相反方向上。 假設該齒推力的方向是向右的，當該力偶係引發運動 的，則該操作係如下的： -在啓動期間，該等彈簧114將制動器9保持嚙合而 將離合器10保持脫離：該傳動裝置當作一減速齒輪來操作 。在一引發運動的力偶傳動期間，由於被加到彈簧Π4的 力量上，該齒軸向推力F1加強了離合器9的嚙合； -爲了切換到該上傳動比率，一合適的液體壓力被提 供給該制動器116以克服彈簧114的力量或任何的力量F1 ，. -爲了造成該裝置從直接驅動比率切換回到減速壓力 ，其僅需要以所需的漸進性釋放該位於致動器116室22之 中的壓力。 在引擎制動的期間，該齒推力係被逆轉的同時所取的 一相對低數値係不足夠克服彈簧114力量。因此’該裝置 正常地係當作一減速齒輪來操作，除非如果一合適的液體 壓力被施加於室22之中。在兩個操作狀態之間的轉換期間 ，亦即在該控制元件111的兩穩定狀態之間’其存在一其 ，中兩個摩擦裝置皆不嚙合的中間狀態。假設施加於該輸入 軸31的力偶係引發運動的，則兩個耦合裝置9和10的同 時脫離並不是一個問題，因爲該太陽輪元件5保持被單向 離合器8所限制著，使得該操作以減速模式來發生。如果 相反地施加於輸入軸31的力偶係負的，則其存在一理論上 27 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ------------r装--------訂---------線 (請先閱讀背面之注意事項再填寫本頁) 530015 A7 B7 五、發明說明（Λ ) (請先閱讀背面之注意事項再填寫本頁) 危險一該太陽輪元件5的旋轉速度將增加，並且輸入軸31 的速度將減少，另一方面該輸出軸41將加速。但實際上， 如果考慮施加於軸41的負載的慣性（該交通工具的質量） 、施加於軸31的負力偶的低數値和此狀態的短期限，則此 效應係微小的。 當施加於該輸入軸31的力偶係引發運動的，其同時 可能選擇該等齒的螺旋狀角度，使得該齒推力發生於方向 F2之上。在此一'倩況之下，該彈簧114必須在此可實際地 需要對抗齒推力F2的所有的狀況下有力到足以保持該裝置 於減速的操作之中。爲達到此目的，其並不需要該等彈簧 提供一太大的多餘力量，只要該離合器10被釋放就足夠了 ，甚至於如果該制動器9僅是微弱地嚙合著，因爲該離合 器8單向係執行保持太陽輪元件5靜止的功能。在該引擎 制動操作期間，該制動器9係較緊地被嚙合著，因爲該齒 推力被逆轉並採行方向F1。 針對該直接驅動操作，該室22被輸入一高到足以能 有力地嚙合離合器10的壓力。 如圖1中的幻線所示，其可能以安裝於該支撐51和 反向器控制元件111之間的彈簧118來替代彈簧114，使 .得不再作用於相反於致動器116的方向上，而是作用於與 後者相同的方向上。在一此類例子當中，並且如果如所示 的無其它作動裝置被提供，則其需要選擇該齒推力係位於 方向F1之上，當施加於該輸入軸31的力耦係引發運動的 。當該齒推力克服彈賛118和任何致動器116中占優勢的 28 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公楚） " " A7 530015 五、發明說明（八） 壓力的反推力時，該操作發生於減速模式之中。 當該齒推力F1充分地減弱時和/或當一充分高的壓力 或一補充壓力被施加於致動器Π6的室之中時，切換到直 接驅動的操作於是發生。該引擎制動操作需要地發生於直 接驅動之中，因爲所有的該作動力量在當時係朝向圖1的 左邊被引導。 更其它種組合係可能的，例如，藉由使得該致動器以 相反於彈簧118的方向來操作。在一此類情況之中，該等 彈簧118傾向於提升直接驅動操作，並且該致動器可被增 加能量以提升引擎制動操作。當施加於該輸入軸31的力親 係引發運動的，則其於是有利於選擇該方向F1給齒推力使 用。爲了該引擎的制動操作，該齒推力被逆轉並提升直接 驅動操作，但此能被選擇性地被一合適的液體壓力所反作 用。 將僅就不同於圖1之處來說明圖2中的範例。 圖1表示一將所有控制和耦合元件強制地且實用地聚 集於該行星齒輪系的該等旋轉元件的一單一旋轉元件（亦 即太陽輪5)之上的所謂”聚集的”控制結構的執行。此結 構提供了在該行星齒輪系的至少一其它旋轉元件上執行其 .它控制和其它選擇性耦合的可能性，以提供更進一步地傳 動比率。在圖2的該範例之中，一第二作動和控制結構被 聚集於該行星齒輪系5, 6, 7的冠狀輪6之上。 在此具體實施例當中，除了該太陽輪元件5可被選擇 性地連接於輸入連接元件3或外殼元件2，該冠狀輪6會g 29 I紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ~ " (請先閱讀背面之注意事項再填寫本頁) i ------訂---------- A7 530015 ___B7 ___―一一 五、發明說明（>1 ) 被選擇性地連接於輸入連接元件3和外殻元件2 ’該外殼 元件2的另外部分23現在被表示出來。該冠狀輪6的聚集 控制和耦合結構係非常相似於太陽輪元件5所說明的。更 明確地，一反向器控制元件211係與冠狀輪6形成一體’ 並與後者一起軸向地可移動。元件211包含一用於可選擇 性地嚙合操作地安裝於冠狀輪6和外殼部分23之間的制動 器209的壓迫面212和一用於選擇性定嚙合可操作地安裝 於冠狀輪6和輸入連接元件3之間的離合器210的相對的 壓迫面213。該外殻元件2的部分23以一隨同冠狀輪6被 加快並可在該室中滑動的活塞217來定義一液壓致動器 216的一室24。由於齒條252，253，一支撐251被耦合以 便於與該冠狀輪6作普通旋轉但是相對於冠狀輪6可軸向 地滑動。在該支撐251與外殻元件部分23之間’其提供一 平行於一禁止該冠狀輪6.相對於外殼元件2以相反於輸入 軸31的正常旋轉方向而旋轉的單向離合器208的軸向不可 滑動軸承254。軸向安裝於該支撐251與活塞217之間的 彈簧214以一相反於可充滿於室24之中的液體壓力的方向 來軸向地推動該冠狀輪6。 根據圖2的該傳動裝置相對於反向器控制元件1Π和 .211的穩定狀態的四個可能組合具有四個主要操作狀態的 能力： -如果元件111朝向圖2的右邊係處於其穩定狀態且 元件211朝向圖2的左邊係處於其穩定的狀態，則兩個離 合器10和210係脫離的。該結果爲一空檔狀態，因爲該輸 30 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂---------線· A7 530015 五、發明說明（d ) 入連接元件3係脫離行星齒輪系的所有旋轉元件； -從此空檔情況啓動，藉著使控制元件111移動到其 其它穩定狀態，另一方面藉著制動器209和/或由自由輪 208，該冠狀輪6被保持靜止，以提供一第一傳動比率。相 對於該輸出軸41相對於輸入軸31的一低旋轉速度，一第 一減速比率被實現； -藉著同時或幾乎同時改變兩個反向器控制元件111， 211的穩定狀態，使其嚙合制動器9和離合器210，另一方 面，脫離離合器10和制動器209，以形成一第二傳動比率 。此再一次地形成眉1的一相對於一保持低於該輸入軸31 速度的輸出軸41速度的減速模式操作，但是其減速比相關 於圖2所已經說明的該第一傳動比率的情況中的減速要來 的溫和； -該第四狀態係一直接驅動狀態，其可藉著保持該冠 狀輪6的控制元件211處於造成離合器210嚙合的狀態和 使得該控制元件111移動進入其使得離合器1〇嚙合的狀態 來獲得。該輸入連接元件3因此同時地以太陽輪元件5和 冠狀輪6被加快，此實現了該傳動裝置中的直接驅動。 該太陽輪元件5具有螺旋齒，同時該冠狀輪6亦具有 .螺旋齒，因此，該相關於冠狀輪6的聚集控制和稱合結構 同樣地受到包含三個力-一齒推力、一彈性力和一被液壓 裝置所選擇性施加的力的綜合（協調）作用。 並且，如同以參考圖1所解釋的，此三個力量方向的 不同組合係可能的。在圖2中所表示的範例當中，該相關 31 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) ----訂---------線 A7 530015 五、發明說明Μ ) 於冠狀輪6的聚集控制和作動結構已經相對於相關於太陽 輪元件5的聚集控制和作動結構被逆轉’因爲在操作當中 ，在該冠狀輪6中和在太陽輪元件5中的齒推力總是相等 和相對的。因此，在此非限制的範例當中，該各種作動力 量的組合方向對兩聚集結構係相同的。 其可注意的是:雖然在一單一簡單的行星齒輪系中提 供了四個操作狀態，但是沒有牽涉到控制和耦合，例如， 該行星齒輪架7和輸出軸41，並且針對在具有不同速度的 旋轉元件之間的傳動推力，沒有推力軸承的需要。 如同圖1中的範例所示，該等液壓活塞以相距與它們 形成一體並同時一起提供相關行星齒輪系元件軸向導引服 務的相關旋轉元件相對地較大的距離被定位。因此，該齒 條52, 53和252, 253並沒有導引功能，並因而並不產生將 傾向於改變由齒推力所產生的力偶信號的顯著摩擦。 針對該等作動力量，更特別地在被說明以當作圖1的 聚集結構的範例的四個可能組合之中的一合適選擇，將允 許最小化該液壓作動所需要的能量，並因而最小化該傳動 機構操作本質上所必須的動力消耗。 在圖2的該第一和第二減小比率之間的轉換期間，其 .存在一危險一一短暫情況的出現，其將相對應於空檔或者 相對於一直接驅動。藉由該等室22和24的每個室中的液 體壓力的一合適控制並藉著將兩個控制元件111和211合 適地同步動作，上述情況將可避免。例如，針對從第一到 第二比率的切換，其能夠以離合器210的嚙合開始來漸進 32 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --訂---------線· 530015 A7 _____B7___ 五、發明說明（p ) 地使得冠狀輪6旋轉，直到該輸出軸41和輸入軸31之間 的速度比率相對應於第二減低比率爲止，並且僅有在此階 段才開始釋放離合器10，另一方面，持續地增加離合器 21〇的縮緊，使得由於兩程序的一相互補償，該傳動比率 於是保持實質上地固定，並等於該第二減低比率，直到該 比率改變程序的完成爲止。其因此顯示出本發明允許，以 一相當簡單的方式，將四個摩擦耦合裝置的狀態的實質上 同時改變同步化。 在該空檔的狀態當中，彈簧114和214保持制動器9 和209於嚙合的狀態中，使得該整個行星齒輪系和隨其的 輸出軸41不能轉動，因此，獲得一停車制動。在此狀態之 中，例如藉著該交通工具引擎的啓動，其可能造成該輸入 軸31的移動，然後藉著漸進地應用室22之中的一液體壓 力來漸進地嚙合離合器10並引入該交通工具的一漸進的啓 動，來漸進地啓動該交通工具。因此，圖2的該傳動傳動 裝置允許傳統上被塞入一交通工具的引擎與齒輪箱之間的 離合器或力偶轉換器的裝置。 圖3的該傳動裝置將僅就與圖2的不同點來說明。 在圖3範例當中，該傳動裝置包含兩個串連安裝的差 ,動機構，即，在下列從該輸入連接元件3到輸出連接裝置 4的順序，一基本上相似於圖2的第一機構301和一將詳 細說明如下的第二差動機構302。 機構301不同於圖2的地方在於：該定子軸21係管 狀的並圍繞著輸入軸31，假設該交通工具係位於圖3的左 33 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂---------· 530015 A7 _B7_____ 五、發明說明（W ) 邊，而非位於圖的右邊(圖2的情況）。 該機構301的各種元件可從它們與圖2中相同的元件 編號來辨識。然而，與該冠狀輪6形成一體的活塞217被 一與外殻元件2形成一體的活塞27所替代，其係形成定義 該相對應編號元件爲64的液體室的冠狀輪的元件6 °該等 彈簧214不再承載於活塞之上，而是被繞著與冠狀元件6 形成一體的導引桿61而被安裝，並且穿過被提供有合適鏜 (穿孔）的該支撐251而可滑動地延伸。該等彈簧214係 安裝於支撐的一背面和桿61的一凸緣62之間。針對一較 佳的滑動導引功能，該冠狀元件6與一軸襯63被提供於一 內鏜之上，以便在現在不僅代表該第一機構301的輸出軸 同時代表第二機構302的輸入軸的管狀軸41的外周邊面上 滑動。軸41因此被附著於機構302的一輸入連接元件330 處。 機構302包含一包含一太陽輪元件350、一冠狀元件 360和一行星齒輪架370的簡單的行星齒輪系。該冠狀元 .件360與輸出元件4形成一體並藉著相對於屬於外殻元件 2的一軸襯26的軸承365而軸向靜止。該輸出元件4包含 與主軸X同軸安裝的齒輪齒42。該齒輪齒42將與一並沒 有顯示並沿著一平行於軸X的軸而被支撐的副齒輪相嚙合 。該行星齒輪架元件370攜帶上面有可被旋轉安裝的行星 齒輪372的偏心轉軸371，該行星齒輪372與太陽輪元件 35〇的齒和冠狀輪元件360的齒相嚙合。 該太陽輪元件350係相關於一聚集耦合和控制結構’ 34 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) ------— —訂-------I I . A7 530015 ___E7__ 五、發明說明（β) 該結構包含選擇性地將太陽輪元件350與外殻元件2連接 一起的制動器309，一選擇性地將該太陽輪元件350與輸 入連接元件330連接一起的離合器310，一包含與太陽輪 元件350形成一體並包含一嚙合制動器309於其兩穩定狀 態的其中一狀態之中的壓迫面312和一嚙合離合器310於 其兩穩定狀態的另一狀態之中的相反被導引的壓迫面313 的壓力元件的反向器控制元件311。該太陽輪元件350以 外殻2定義將太陽輪元件350朝著相對於當供給時的離合 器310嚙合而制動器309脫離的穩定狀態推進而安置的一 液壓致動器316的一室322。 根據相關於機構301的該太陽輪元件5的聚集結構的 一不同點，該單向離合器308以平行於離合器310而不再 平行於制動器309地被安裝。該單向離合器308防止太陽 輪元件350旋轉快於輸入連接元件330。然而，該單向離 器308的安裝方式其本身係相似於已經說明的方式：該單 向離合器308係與一介於輸入連接元件330和支撐351之 間的一軸向不可滑動的軸承354相平行地被安裝。該輸入 連接元件其本身藉著一以圖形編號333被表示的軸承333 相對於外殼元件2被軸向地限制行動。該支撐351藉著齒 .條352, 353被耦合於太陽輪元件350以作普通的旋轉。彈 簧314被安裝於支撐351和太陽輪元件350之間用於以相 反於液壓室322中壓力所定義的方向推進太陽輪元件350 。該行星齒輪系的齒型係螺旋狀的，因此，如上文中所說 明的所有聚集結構，太陽輪元件350受到一包含該齒推力 35 才、紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ' ~ (請先閱讀背面之注意事項再填寫本頁) --------訂--------I · 530015 A7 ___B7_____ 五、發明說明（0 ) 、彈簧314彈性力和室322中的液體壓迫力等三個力量組 合的作用。 該機構302更包含一包含一攜帶耦合齒376的控制元 件374的爪（形）離合器系統373。該控制元件374在標 示爲”N”的空檔位置、一其中該行星齒輪架370與第二機 構302的輸入連接元件330相耦合以爲普通旋轉的向前驅 動位置”D”，和一其中該行星齒輪架370與輸入連接元件 330脫離耦合並和與外殻元件形成一體的軸襯26相耦合的 逆向驅動位置”R”等三位置之間係可移動的。該控制元件 374係一可移動地被塞入定子軸21和定子軸襯26之間的 管子。 現在將說明當該爪形離合器係位於允許兩不同向前驅 動比率的”D”位置當中的該第二機構302的操作 當該離合器310被嚙合時，該輸入連接元件330同時 藉離合器310與太陽輪元件350和藉著爪形離合器373的 耦合齒376與行星齒輪架370相連接以爲普通旋轉。該機 構302於是操作於一直接驅動模式。當該離合器310被釋 放且制動器309被嚙合時，該太陽輪元件350被外殼元件 2所阻擋，並且該輸入連接元件330單獨地驅動行星齒輪 ‘架370。結果’該行星齒輪372滾轉於太陽輪35的四周齒 之上，並使得該冠狀輪360轉得比行星齒輪架370要來得 快。該機構302於是操作於一過驅動模式。 在此兩穩定狀態間的轉換期間，該冠狀元件360傾向 於被施加於輸出元件4處的負載所遲滯，結果，該太陽輪 36 本紙張尺度適用中國國家標準(CNS)A4規格（210 X 297公复) '" (請先閱讀背面之注意事項再填寫本頁) --------訂-------- A7 530015 ___ B7 _ 五、發明說明（讨） 元件350有旋轉快於於包含有行星齒輪架370和輸入連接 元件330的組件的傾向。 (請先閱讀背面之注意事項再填寫本頁) 當該爪形離合器373係位於”R”位置時，該行星齒輪 架370被禁止旋轉，結果，該行星齒輪被當作太陽輪350 和冠狀輪360之間移動逆向裝置來操作。在這情況之下， 離合器310必須以一位於室322之中對抗彈簧314的合適 的液體壓力來被嚙合，使得由輸入連接元件330所引入的 動作能被該太陽輪元件350所傳動。該移動逆向以一減速 來發生，因爲該冠狀元件360的直徑大於太陽輪元件350 的齒的直徑。 .藉著該等嚙合元件不同直徑之間的一合適比率選擇， 圖3該等嚙合元件的一選擇提供一大略的槪念，圖3的該 傳動機構提供當爪形離合器裝置係位於” D”位置時被合適 分配的六個向前驅動比率。 此六個比率如下所述： -針對該第一全體比率，該機構301以其第一減速比 率（該最減速比率）來操作，且該第二機構302以其較低 (直接驅動）模式來操作； -針對該第二全體比率，該機構302切入過驅動狀餘 .之中，而該機構301則保持於強烈減速操作之中； -針對該第三整體比率，該機構301以其第二比率（ 中等減速）來操作，而該機構302以其直接驅動模式來操 作； -該第四比率係一遍佈整個傳動的直接驅動； 37 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） A7 530015 五、發明說明（β ) -該第五比率當該機構301以其第二比率（中等減速 )來操作而機構302以過驅動模式來操作時被獲得’和 -在該第六比率當中，該機構301以直接驅動模式而 機構302以過驅動模式來操作； -針對該逆向驅動，以該爪形離合器373位於該”R”位 置，一方便的比率當該機構301係位於其第二比率操作（ 中等減速）時可被獲得。 釋放該輸出元件4中所造成的該爪形離合器373的 ”N”位置係一有用於例如以手推動該交通工具或拖吊該交 通工具的狀態，其事實上雖然缺乏該機構301的增能效果 ，但是在機構301中的一制動條件可被實現。此使該停車 制動功能無效的可能性的結果來自該機構301係位於該爪 形離合系統相對於引擎與交通工具輪子之間的動力流動通 路上游處。 圖3的傳動機構在其僅以兩個簡單行星齒輪系、只有 三個液壓位置和六個摩擦耦合裝置之下提供六個比率和一 逆向的功能是値得令人注意的。並且，該液壓作動器僅供 應一補充力量，並且它們的能量消耗因而被減低。在該六 個摩擦耦合當中，其中總是有三個位於嚙合的狀態，其因 .而在該傳動中不產生任何殘餘的摩擦。 其中該第一機構301的三個比率在一基本行星齒輪系 中可被獲得的方式在第一和第二比率之間產生一個大於第 二和直接驅動比率之間的比率間隙的比率間隙。更明確地 說，該第一比率間隙係實質上相等於超過第二間隙的平方 38 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂---------線· A7 530015 五、發明說明（祚） ，並仍更明確地說，係約該第二比率間隙的一立方。例如 ，該等比率爲1:4.2, 1:1.4和1:1，則獲得該第一和第二比 率之間的第一比率間隙爲4.2/1.4=3.00，該第二和直接驅動 比率間的一第二比率間隙爲1.4/1 = 1.4。該在第二機構中的 過驅動比率被選擇，使得其値介於該第一機構中的第一和 第二比率間隙的中間，亦即，約1.8，所以得到的該過驅動 比率約爲1 : 1.8。 圖4的範例將僅就其與圖3的不同之處來加以說明。 在圖4的範例之中，該等機構301和302基本上與圖3的 機構相同，但是它們沿著彼此平行並相隔開的軸XI和X2 來安裝。該機構301的輸出元件41攜帶一嚙合著一機構 302輸入齒輪334的輸出齒輪43，此輸入齒輪334與該輸 入連接元件330係形成一體的。在該機構302當中，其不 在存在該輸入軸31，同時亦不存在定子軸31，所以，該輸 入連接元件330以一攜帶有一齒輪334的軸336來佔據中 央位置，並被該爪形離合器的該軸襯狀控制元件374所圍 繞著。 由於下列的事實，該圖4的雙軸裝置簡單地被實現： 該兩個機構301, 302係僅以一單一旋轉連接（該第一機構 ，的輸出軸41與第二機構輸入連接元件330的連接）來彼此 地連接在一起，並允許一特別短的設計。其因而可能構成 ，例如，一橫過來安裝於該交通工具之中並相關於一六速 自動傳動的直列式六缸引擎。藉著將一離合器或力偶轉換 器合適地安裝於該引擎與傳動裝置之間的可能性，該低軸 39 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) ------— 丨訂--------. A7 530015 __B7____ 五、發明說明（vl ) 向空間需求被更進一步地增強。 圖5的該範例僅就其與圖2的不同處加以說明之。 該行星齒輪架7不再剛硬地連接到輸出軸41處。其 在該機構中引進一爪形離合器裝置73，該裝置73包含： -一爪形離合器44，其被提供一作動元件29，並與該 輸出軸41連接以爲普通旋轉之用，然後在一”N”(空檔)位 置、一以”D”（向前驅動）表示並執行行星齒輪架7和輸 出軸41之間普通旋轉耦合的位置和一執行該冠狀輪6和輸 出輪41之間的耦合的”R”（逆向）位置等三位置之間可軸 向地移動。針對此目的，該冠狀輪6被提供爪形離合器齒 65 ； -一被安裝於該定子軸21之上以禁止旋轉移動但可與 爪形離合器44 一起平移移動的爪形離合器28。當該爪形 離合器44係位於R位置時，該爪形離合器28將行星齒輪 架7耦合於定子軸21，因而同時耦合於外殼2 ; -一在該爪形離合器44上可自由旋轉的並與其連接以 作爲普通平移的爪形離合器255。該爪形離合器255係永 久地與提供於除了在D位置上不再透過在此位置同時與爪 形離合器齒65相嚙合的爪形離合器255而與冠狀輪6相連 ，接的支撐251之上的爪形離合器齒256相嚙合。 在向前驅動當中，該操作與在圖2當中的操作相同。 在逆向操作當中，制動器209和離合器10 (圖2)係被嚙 合的，該轉軸71被爪形離合器28所阻擋，並且該等行星 輪72被當作在連接於輸入的太陽輪元件5和連接於輸出並 40 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂---------線· 530015 A7 ___ B7 _ 五、發明說明（β ) 允許由於與單向離合器支撐251相脫離而逆向旋轉的冠狀 輪ό之間的移動逆向裝置來操作。在該太陽輪5和冠狀輪 6之間的減速係令人滿意地高。 其因而以一單一簡單的行星齒輪系實現一個具有三個 向前驅動比率、一逆向驅動、一空檔和一漸進性的啓動裝 置的交通工具的一自動傳動的該整體性。針對從向則驅動 切換至逆向驅動，一^爪形離合益系統通吊係令人滿思的’ 因爲此一類切換通常發生於當該交通工具係停止的，也就 是一個其中牽涉到該爪形離合器切換的所有零件皆靜止的 狀況，甚至於該引擎轉動該輸入軸31 ° .在該逆向驅動模式當中，該冠狀輪6係旋轉的，同時 該支撐251係靜止的。因此，一軸向推力軸承141已經被 塞入該彈簧214和冠狀輪元件6之間。 圖6的該具體實施例將僅就其與圖2之不同處加以說 明之。該等彈賛114和214已經被除去並以一^塞入太陽輪 5和冠狀輪6之間以供推進它們於每一個與圖2中彈簧114 和214所促進方向所相同的相互相反方向上亦即用於反作 於該各別液壓作動器的單一彈簧裝置14所替代。因爲該太 陽輪5和冠狀輪6的旋轉速度除了在直接驅動模式之外是 .不同的，所以一推力軸承142已經被塞入該彈簧裝置14和 太陽輪5和冠狀輪6元件的其中之一元件之間，例如，在 所表示的範例當中，該其中之一元件爲太陽輪5。 在圖6的該具體實施例的第一和第二比率的每一個比 率當中，該等液壓致動器的其中一個係被增加能量的並透 41 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂--------- *5^ · 530015 B7 五、發明說明（4) 過彈簧裝置14和推力軸承142將另外一個致動器的活褰推 向後。 在直接驅動操作當中，兩個液壓致動器被增加能囊# 該彈簧裝置14作一最大的壓縮，另一方面，如同圖2的_ 具體實施例所示，嚙合該離合器10和210。 在一未顯示的修飾具體實施例當中，該彈簧14和推 力軸承142組件可被一減少能量以用於直接驅動操作的補 充液壓致動器所替代。 圖7的該具體實施例將就其與圖4之不同點說明之。 已經被使用於前述圖式的元件編號在圖7中係相對於相同 或非常相似元件的編號。 圖7的該具體實施例包含一大體上相似於圖4的第二 機構302但具有下列主要的不同點： -該機構302的輸入連接元件330係與行星齒輪架370 和傳動裝置輸入軸131形成一體的； -在該傳動裝置之中，該逆向驅動裝置不再包含於第 二機構302之中，而是形成一將於後文說明的分離單位 303 ； -該第一機構302係安裝於沿著傳動裝置的輸入軸 ‘和輸出齒42之間的動力流動途徑的第一機構301的上游處 ;和 -該第二差動機構302的冠狀輪元件360係與一包含 透過一中間副齒輪81驅動第一傳動機構301的被嚙合著的 輸入旋轉連接元件3的齒輪齒的輸出連接元件304形成一 42 請先聞讀背面Μ漆意事頊再填寫本頁) -------訂--------- 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） A7 530015 _____B7____ 五、發明說明（V ) 體。 (請先閱讀背面之注意事項再填寫本頁) 該第一機構301大抵相似於圖6，但具有下列不同點 :透過一具有可移動於一將行星齒輪架7連接於輸出連接 元件4以供一起普通旋轉之用的”D”位置和一其中行星齒 輪架7和輸出連接元件4被如所示彼此分離的”R，N”位置 之間的爪形離合器44的一爪形離合器系統，其輸出旋轉連 接元件4被連接至行星齒輪架7處。 該第一機構301的輸出連接元件4被提供嚙合著一其 上該輸出齒42係一體成形的且可旋轉地被安裝於傳動裝置 輸入軸131之上的中間輸出元件45的齒輪齒的齒輪齒。因 此，該整個傳動裝置的輸入（軸131)和輸出（齒42)係 同軸的。這是有利的，因爲其允許自由地繞著一交通工具 的發動機隔間中的輸入和輸出共同軸X3視可提供的空間 地放置該傳動裝置。 該逆向驅動機構303係繞著幾何軸X3被安裝，爲得 是要選擇性地繞過該第一機構301。該逆向驅動機構303 包含一選擇性地將第二機構冠狀輪360和其形成一體的輸 出連接元件304與一可自由地繞著輸入軸131旋轉的副齒 輪82相連接以供普通旋轉之用的爪形離合器系統361。該 ,副齒輪82嚙合一依次地嚙合該中間輸出元件45的一第三 齒組84的中間偏心階梯副齒輪83。 該裝置爲使得在直接驅動當中，由於該第二機構302 的輸出連接元件304和第一機構301的輸入連接元件3之 間的中間副齒輪81的緣故，該輸出齒42的移動方向係相 43 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） A7 530015 五、發明說明（V ) 反於輸入軸131的移動方向，然而，該輸出齒42和輸入軸 131在逆向驅動模式中具有相同的旋轉方向。該爪形離合 器系統361的爪形離合器362如圖7中所示地在一”N，D，， 位置之間係可移動的，在該”N，D”位置當中，該第二機構 3〇2的輸出元件304係與副齒輪82相脫離的，而在一”R” 位置當中，它們係彼此連接在一起的。該等爪形離合器44 和362係聯合地被驅動，使得當爪形離器44係位於該 ”RN”位置時，另外一方面爪形離合器362係位於”R”位置 ’該逆向驅動狀態被實現，當爪形離合器44係位於”D”位 置，另一方面爪形離合器362係位於”N，D”位置，則該向 前驅動被實現，而當爪形離合器44係位於”R，N”位置且爪 形離合器362位於”N，D”位置，則一空檔狀態被實現。在 該向前驅動位置當中，當該致動器116和216被減少能量 時’該第一機構301執行一制動功能，反之，當該空檔被 實現時，該輸出齒42係可自由地移動。因此，該傳動裝置 的輸入軸131可形成一體地與一引擎1〇1的一引擎軸相連 接’而不需要插入任何輸入離合器或耦合轉換器。 圖8的該具體實施例僅就其與圖7的不同之點加以說 明之。 . 第二機構302與圖7的第二機構相似，除了其輸出連 接元件304不再可連接於一逆向驅動機構，不用透過圖7 的該中間副齒輪81，直接嚙合於該第一機構301的輸入連 接元件3的齒輪齒。 該第一機構301係相同於圖7的第一機構，除了該行 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁} -------I — ^ . I I-----· A7 530015 ____B7___ 五、發明說明（θ ) 星齒輪架7係永遠地連接於第一機構301的輸出元件4。 並且，不選擇性地將該冠狀輪6與外殻元件2相結合 ，該離合器209和單向離合器208組件將冠狀輪6與一可 繞著第一傳動機構301的軸X4旋轉的籠子86相連接.。 該輸出元件4和籠子86被提供與可繞著輸入軸131 旋轉並與其同軸的各別圓環87, 88形成一體的相對應齒嚙 合的各別的齒輪齒。一靜止的圓環89係與外殻元件2形成 一體並與圓環87和88軸向地排成一直線並安裝在它們之 間。該三個圓環87，88和89係可繞著一中間連接元件45 的管狀軸和在此管狀軸的兩個嚙合著的凸緣46之間旋轉。 一第一爪形離合器91選擇性地與用於直接驅動的傳動裝置 的輸出齒42或與該靜止的圓環89相耦合以供圓環87作普 通旋轉，爲了要使該行星齒輪架7不能移動，以作爲逆向 驅動之用。一第二爪形離合器選擇性地與該輸出齒42或靜 止圓環89相連接以供該第二圓環88作普通旋轉之用，爲 了要將該籠子86與輸出齒連接以爲逆向驅動之用或者連接 於外殼2以爲直接驅動之用。兩個爪形離合器91，92藉由 一耦合元件93被同步化。 圖9的該具體實施例將僅就其與圖8不同之處予以說 .明之。 該第二差動機構301以一雙速副軸機構402來替代， 該機構402同時執行來自軸X3動力的傳送，沿著該軸X3 輸入軸131延伸於並未顯示的第一差動機構301的平行軸 X4之上，更特別地，從該傳動裝置的輸入軸131延伸至第 45 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁)I ------ order --------- line.  A7 530015 V. Description of the invention (") Free and will cause the engine to resume idling without braking the vehicle. Therefore, it provides a series of mechanically parallel to the sun gear element 5 and the housing element 2. The first friction coupling device of the one-way clutch 8 or the brake 9. When coupled, the brake 9 makes the sun gear 5 stationary relative to the housing element 2 and therefore allows the transmission device to be applied to the input shaft 31 at 3 o'clock. When the coupling is negative, it is operated as a reduction gear. When the coupling is positive, it is operated in the same way. The brake 9 can be used just enough to involve a force coupling that is far weaker than the peak-induced motion. The dimensions are designed in a way that the braking operation is coupled. Because a second friction coupling mechanism or clutch_110 can be selectively coupled for use of two of the three rotating elements 5, 6, 7 of the planetary gear train. Rotation makes the entire planetary gear train rotate as a single part around the axis X, so the transmission device more allows the realization of a direct drive ratio. This is automatically achieved by the free wheel 8 becomes possible, but needs to be disengaged from the brake 9. According to an important feature of the invention, the second friction coupling device 10 is related to the same rotating element, that is, to the sun in this representative example. The wheel element 5 is like the other coupling device already described, that is, the head clutch ^ 8 and the brother ^ affinity device 9. More specifically, in the representative example, the second friction coupling device is Operatively installed between the sun gear element 5 and the input connection device 3 As explained above, the engagement of the second friction clutch device 10 needs to be disengaged from the first friction coupling device 9. Instead, the brake (Please read the precautions on the back before filling this page) ------- Order ---- I --- * 5 ^ · 9 24 A7 530015 V. Description of the invention () The engagement of () needs to be disengaged from the clutch 10. To achieve this, according to a more important feature of the invention, a single control element 111 operates as an inverter between two stable states. In each stable state, the friction coupling device 9 Each of the 10 devices is engaged The other device is separately disengaged. In the illustrated example, the inverter control device 111 is an axially movable pressure element. When pushed toward the right side of FIG. 1, the pressure element 111 engages The brake 9 is disengaged from the clutch 10. When pushed to the left of Fig. 1, the pressure element 111 disengages from the brake 9 and engages the clutch 10. The switching between these two stable states is performed by an axial transmission action. The pressure element 111 is integrated with the sun gear element 5 and therefore rotates at the same rotational speed as the latter. Because the two friction coupling devices 9 and 10 simultaneously have the other elements of a mechanism 1 selectively connected to the sun gear 5 function, so the integral connection of the pressure element 111 and the sun gear element 5 allows the pressure element 111 to be formed with a common pressure element having two opposing pressing surfaces, that is, a pressing surface 112 is used for the brake 9 flat The discs are stacked and a pressing surface 113 is used to stack the flat discs of the clutch 10. Generally speaking, the one-way clutches available in the market need to be installed between two components that are relatively axially stationary with respect to each other. Therefore, when the axial movability of the sun gear element 5 is taken into consideration, the one-way clutch 8 cannot be directly installed between the sun gear element 5 and the housing element 2. For this reason, it provides a support 51 that engages the relative axial rack 53 of the sun gear element 5 on the axial peripheral wheel 52 of its outer periphery, so that it is too (please read the note on the back? This page} -------- Order --------- line · 25 530015 A7 ____ Β7 V. Description of the invention (A) The sun gear 5 series is slidable relative to the support 51 and is simultaneously Coupling for common rotation together. By mounting an axial non-sliding bearing 54 between the support 51 and the stator shaft 21, the support 51 is axially stationary relative to the housing element 2. The The one-way clutch 8 is also installed parallel to the bearing 54 between the support 51 and the stator shaft 21. In order to perform reverse control of the two friction coupling devices 9 and 10, the inverter control device 111 is inclined by the following three actuators Tonal action:-A first actuating device comprising an integral connection which has been formed between the inverter control device Π1 and the sun gear element 5 as described. Due to this forming an integral connection, the inverter control device 111 suffers from the sun gear due to the spiral shape of its teeth The axial thrust acts in 5. This thrust is a measure of the force coupling transmitted by the teeth;-a spring 114 comprising at least one BELLEVILLE washer stacked and inserted between the axial static support 51 and the spring 114 of the sun gear element 5 A second actuating device; the third actuating device comprises a ring-shaped chamber 22 formed in the housing element 2 and a piston integrated with the inverter control element 111 and having a circular ring shape around the axis X The hydraulic actuator 116 of 117. The piston Π7 is then rotated around the axis X in the chamber 22 integrated with the housing element 2 and the arrows F1 and F2 indicate the tooth thrust of the sun gear 5 There are two possible directions. For a specific direction of the inclination of the teeth, when the force coupling applied to the input shaft 31 causes motion, the axial thrust appears in a corresponding specific direction, and when the Applied to the input shaft 26 This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before filling this page) ------- Order ----- ---- · 530015 A7 _ B7_ V. Description of the invention (& iV) 31 When the system is negative (engine braking operation), the axial thrust appears in the opposite direction. Assuming that the direction of the thrust of the tooth is right, when the force couple causes motion, the operation is as follows:-at start During this time, the springs 114 keep the brake 9 engaged and keep the clutch 10 disengaged: the transmission is operated as a reduction gear. During a motion-inducing force couple transmission, the teeth are added to the force of the spring Π4 during the transmission Axial thrust F1 strengthens the engagement of the clutch 9;-In order to switch to the upper transmission ratio, a suitable hydraulic pressure is provided to the brake 116 to overcome the force of the spring 114 or any force F1,  -In order to cause the device to switch from the direct drive ratio back to the deceleration pressure, it only needs to release the pressure located in the chamber 116 of the actuator 116 with the required gradualness. During the engine braking, a relatively low number of gears taken while the tooth thrust is reversed is not sufficient to overcome the force of the spring 114. Therefore, the device is normally operated as a reduction gear unless a suitable liquid pressure is applied to the chamber 22. During the transition between the two operating states, that is, between the two stable states of the control element 111, there is an intermediate state in which both friction devices are not engaged. Assuming that the force coupling applied to the input shaft 31 causes motion, the simultaneous disengagement of the two coupling devices 9 and 10 is not a problem, because the sun gear element 5 remains restricted by the one-way clutch 8 so that the operation is decelerated Pattern to happen. If the force couple applied to the input shaft 31 on the contrary is negative, then there exists a theoretical 27 paper size applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) ---------- --r installed -------- order --------- line (please read the precautions on the back before filling this page) 530015 A7 B7 V. Description of the invention (Λ) (Please read first Note on the back, fill in this page again) Danger-The rotation speed of the sun gear element 5 will increase, and the speed of the input shaft 31 will decrease, on the other hand, the output shaft 41 will accelerate. However, in reality, if the inertia of the load applied to the shaft 41 (the mass of the vehicle), the low number of the negative force couple applied to the shaft 31, and the short period of this state are considered, the effect is small. When the force couple applied to the input shaft 31 causes motion, it may also select the helical angle of the teeth, so that the tooth thrust occurs in the direction F2. Under this condition, the spring 114 must be strong enough to keep the device in decelerating operation under all conditions where it may actually be necessary to oppose the tooth thrust F2. In order to achieve this, it does not require the springs to provide a large excess force, as long as the clutch 10 is released, even if the brake 9 is only weakly engaged because the clutch 8 is unidirectional The function of keeping the sun gear element 5 stationary is performed. During the engine braking operation, the brake 9 is engaged more tightly because the tooth thrust is reversed and adopts the direction F1. For this direct drive operation, the chamber 22 is input with a pressure high enough to forcefully engage the clutch 10. As shown by the magic line in Figure 1, it may be replaced by a spring 118 installed between the support 51 and the inverter control element 111, so that. It no longer acts in the direction opposite to the actuator 116, but in the same direction as the latter. In one such example, and if no other actuator is provided as shown, it is necessary to select the tooth thrust system above the direction F1 when the force coupling applied to the input shaft 31 causes motion. When the thrust of the tooth overcomes the predominant 28 of the Zanzan 118 and any of the actuators 116, the paper size applies to the Chinese National Standard (CNS) A4 specification (210 X 297). &Quot; " A7 530015 ) When the pressure is reversed, the operation occurs in the deceleration mode. When the tooth thrust F1 is sufficiently weakened and / or when a sufficiently high pressure or a supplementary pressure is applied to the chamber of the actuator Π6, the operation of switching to the direct drive then takes place. This engine braking operation needs to take place in the direct drive, because all of this power is guided at the time towards the left of FIG. 1. Still other combinations are possible, for example, by having the actuator operate in a direction opposite to the spring 118. In one such case, the springs 118 tend to boost direct drive operation, and the actuator can be augmented with energy to boost engine braking operation. When the force applied to the input shaft 31 is relative to cause motion, it is advantageous to select the direction F1 to use for tooth thrust. For the braking operation of the engine, the tooth thrust is reversed and lifted for direct drive operation, but this can be selectively reversed by an appropriate fluid pressure. The example in FIG. 2 will be explained only in terms of differences from FIG. 1. Figure 1 shows the implementation of a so-called "aggregated" control structure that forcibly and practically gathers all control and coupling elements on a single rotating element (ie, sun gear 5) of the rotating elements of the planetary gear train. . This structure provides execution on at least one other rotating element of the planetary gear train. It controls the possibility of selective coupling to provide further transmission ratios. In the example of Fig. 2, a second actuation and control structure is gathered on the crown wheels 6 of the planetary gear trains 5, 6, 7. In this specific embodiment, in addition to the sun gear element 5 may be selectively connected to the input connection element 3 or the housing element 2, the crown wheel 6 will be g 29 I paper size applicable to China National Standard (CNS) A4 specifications (210 X 297 mm) ~ " (Please read the notes on the back before filling out this page) i ------ Order ---------- A7 530015 ___B7 ___― One-fifth, description of the invention (≫ 1) The input connection element 3 and the housing element 2 are selectively connected. The other part 23 of the housing element 2 is now shown. The gathering control and coupling structure of the crown wheel 6 is very similar to that described for the sun wheel element 5. More specifically, an inverter control element 211 is integrated with the crown wheel 6 and is axially movable with the latter. Element 211 includes a pressing surface 212 for selectively engaging and operatively mounting the brake 209 between the crown wheel 6 and the housing portion 23, and a selective fixed engagement and operatively mounting on the crown wheel 6 and the input connection The opposing pressing surfaces 213 of the clutch 210 between the elements 3. The part 23 of the housing element 2 defines a chamber 24 of a hydraulic actuator 216 with a piston 217 which is accelerated with the crown wheel 6 and can slide in the chamber. Due to the racks 252, 253, a support 251 is coupled to facilitate normal rotation with the crown wheel 6 but is slidable axially relative to the crown wheel 6. Between the support 251 and the housing element portion 23, it provides a parallel to a prohibited crown wheel 6. The axial non-sliding bearing 254 of the one-way clutch 208 which rotates with respect to the housing element 2 in a direction opposite to the normal rotation direction of the input shaft 31. A spring 214 axially mounted between the support 251 and the piston 217 pushes the crown wheel 6 axially in a direction opposite to the pressure of the liquid that can be filled in the chamber 24. This transmission according to FIG. 2 is relative to the inverter control elements 1Π and. The four possible combinations of the steady state of 211 have the capability of four main operating states:-if element 111 is in its stable state towards the right side of Fig. 2 and element 211 is in its steady state towards the left side of Fig. 2 then two Clutches 10 and 210 are disengaged. The result is in a neutral state, because the paper size of this paper is applicable to the Chinese National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) ------ --Order --------- line · A7 530015 V. Description of the invention (d) The connecting elements 3 are all the rotating elements that are separated from the planetary gear train;-Start from this neutral condition, by making the control element 111 Moving to its other stable state, on the other hand, by means of the brake 209 and / or by the free wheel 208, the crown wheel 6 is kept stationary to provide a first transmission ratio. A low speed of rotation relative to the output shaft 41 relative to the input shaft 31, a first reduction ratio is achieved;-by changing the steady state of the two inverter control elements 111, 211 at the same time or almost at the same time, making them mesh The brake 9 and the clutch 210, on the other hand, are disengaged from the clutch 10 and the brake 209 to form a second transmission ratio. This once again forms a deceleration mode operation of the eyebrow 1 relative to an output shaft 41 speed that is kept below the speed of the input shaft 31, but its reduction ratio is related to the case of the first transmission ratio already explained in FIG. 2 The gentleness of the deceleration to come;-the fourth state is a direct drive state, which can keep the control element 211 of the crown wheel 6 in a state that causes the clutch 210 to engage and move the control element 111 into it so that the clutch 1 〇The state of engagement is obtained. The input connection element 3 is therefore accelerated simultaneously with the sun gear element 5 and the crown wheel 6, which enables a direct drive in the transmission. The sun gear element 5 has helical teeth, and the crown wheel 6 also has. Spiral teeth, therefore, the aggregate control and scaling structure related to the crown wheel 6 is similarly subjected to a combined (coordinated) action including three forces-a tooth thrust, an elastic force, and a force selectively applied by the hydraulic device . And, as explained with reference to Fig. 1, different combinations of these three directions of force are possible. In the example shown in Figure 2, the relevant 31 paper sizes are applicable to the Chinese National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling out this page) ---- Order --------- Line A7 530015 V. Description of the invention M) The aggregation control and actuation structure on the crown wheel 6 has been reversed relative to the aggregation control and actuation structure on the sun wheel element 5 because it is in operation The tooth thrust in the crown wheel 6 and in the sun gear element 5 is always equal and opposite. Therefore, in this non-limiting example, the combination direction of the various working forces is the same for the two aggregate structures. It can be noted that although four operating states are provided in a single simple planetary gear train, there is no control and coupling involved, for example, the planetary gear carrier 7 and the output shaft 41, and the There is no need for thrust bearings for transmission thrust between rotating elements. As shown in the example in Figure 1, the hydraulic pistons are positioned relatively large distances from the associated rotating elements that are integral with them and simultaneously provide the related planetary gear train element axial guidance services. Therefore, the racks 52, 53 and 252, 253 do not have a guiding function and therefore do not generate significant friction that would tend to change the force couple signals generated by the tooth thrust. A suitable choice for such working forces, more particularly among the four possible combinations illustrated as an example of the aggregate structure of Fig. 1, would allow to minimize the energy required for the hydraulic actuation, and thus minimize The power consumption necessary for the operation of the transmission mechanism is essential. During the transition between the first and second reduction ratios of Figure 2, which. There is a danger—a transient condition that will correspond to neutral or to a direct drive. With a proper control of the liquid pressure in each of these chambers 22 and 24 and by appropriately synchronizing the two control elements 111 and 211, the above situation can be avoided. For example, for the switch from the first to the second ratio, it can be progressively started with the engagement of the clutch 210. This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) (Please read the note on the back first) Please fill in this page again) --Order --------- line · 530015 A7 _____B7___ V. Description of the invention (p) Rotate the crown wheel 6 until the speed between the output shaft 41 and the input shaft 31 The ratio corresponds to the second reduction ratio, and the clutch 10 is only released at this stage. On the other hand, the tightening of the clutch 21 is continuously increased, so that the transmission ratio is maintained due to the mutual compensation of the two programs. It is substantially fixed and equal to the second reduction ratio until the completion of the ratio change procedure. It therefore shows that the invention allows, in a relatively simple manner, to synchronize substantially simultaneous changes in the state of the four friction coupling devices. In the neutral state, the springs 114 and 214 keep the brakes 9 and 209 in an engaged state, so that the entire planetary gear train and the output shaft 41 therewith cannot rotate, and therefore, a parking brake is obtained. In this state, for example, by starting the vehicle engine, it may cause the input shaft 31 to move, and then gradually apply a fluid pressure in the chamber 22 to gradually engage the clutch 10 and introduce the traffic. A gradual start of the tool comes to start the vehicle gradually. Therefore, the transmission device of Fig. 2 allows a device that is conventionally tucked into a clutch or power coupler between an engine and a gearbox of a vehicle. The transmission device of FIG. 3 will be described only in terms of differences from FIG. 2. In the example of FIG. 3, the transmission device includes two differentially mounted differential mechanisms, that is, in the following sequence from the input connection element 3 to the output connection device 4, a mechanism substantially similar to the first mechanism of FIG. 2 301 and a second differential mechanism 302 will be described in detail below. The mechanism 301 differs from FIG. 2 in that the stator shaft 21 is tubular and surrounds the input shaft 31. It is assumed that the vehicle is located on the left 33 of FIG. 3. The paper size is applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) (Please read the notes on the back before filling out this page) -------- Order --------- · 530015 A7 _B7_____ 5. The description of the invention (W) side, not Located on the right side of the figure (case of Figure 2). The various components of the mechanism 301 can be identified from their same component numbers as in FIG. However, the piston 217 integrated with the crown wheel 6 is replaced by a piston 27 integrated with the housing element 2, which is the element forming the crown wheel defining the liquid chamber of the corresponding numbered element 64. The spring 214 is no longer carried on the piston, but is mounted around a guide rod 61 integral with the crown element 6 and slidably extends through this support 251 provided with a suitable bore (perforation). . The springs 214 are mounted between a back surface of the support and a flange 62 of the rod 61. For a better sliding guide function, the crown element 6 and a bushing 63 are provided on an inner boring, so that not only the output shaft of the first mechanism 301 but also the input shaft of the second mechanism 302 The tubular shaft 41 slides on the outer peripheral surface. The shaft 41 is thus attached to an input connection element 330 of the mechanism 302. The mechanism 302 includes a simple planetary gear train including a sun gear element 350, a crown element 360, and a planetary carrier 370. The coronal element. The piece 360 is integrated with the output element 4 and is axially stationary by a bearing 365 with respect to a bushing 26 belonging to the housing element 2. The output element 4 includes gear teeth 42 mounted coaxially with the main shaft X. The gear teeth 42 will mesh with a pinion gear not shown and supported along an axis parallel to the axis X. The planetary carrier element 370 carries an eccentric shaft 371 having a planetary gear 372 rotatably mounted thereon, and the planetary gear 372 meshes with the teeth of the sun gear element 350 and the teeth of the crown wheel element 360. The sun gear element 350 is related to a cluster coupling and control structure. 34 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page)- ------ --Order ------- II.  A7 530015 ___E7__ 5. Description of the invention (β) The structure includes a brake 309 that selectively connects the sun gear element 350 and the housing element 2 together, and a structure that selectively connects the sun gear element 350 and the input connection element 330 together. Clutch 310 includes a pressing surface 312 that is integral with the sun gear element 350 and includes an engaging brake 309 in one of its two stable states, and an engaging clutch 310 in the other of its two stable states. An inverter control element 311 of the pressure element which is directed against the pressure surface 313. The sun gear element 350 defines, as the housing 2, a chamber 322 of a hydraulic actuator 316 disposed to advance the sun gear element 350 toward a steady state in which the clutch 310 is engaged and the brake 309 is disengaged when supplied. The one-way clutch 308 is installed parallel to the clutch 310 and no longer parallel to the brake 309 according to a different point of the gathering structure of the sun gear element 5 with respect to the mechanism 301. This one-way clutch 308 prevents the sun gear element 350 from rotating faster than the input connection element 330. However, the way of installing the one-way clutch 308 is similar to that already described: the one-way clutch 308 is parallel to an axially non-sliding bearing 354 between the input connection element 330 and the support 351 Ground is installed. The input connection element itself is axially restricted with respect to the housing element 2 by a bearing 333 indicated by a figure number 333. The support 351 is by teeth. The bars 352, 353 are coupled to the sun gear element 350 for normal rotation. A spring 314 is mounted between the support 351 and the sun gear element 350 for advancing the sun gear element 350 in a direction opposite to that defined by the pressure in the hydraulic chamber 322. The planetary gear train has a helical shape. Therefore, as with all the aggregate structures explained above, the sun gear element 350 is subjected to a tooth thrust of 35, and the paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) '~ (Please read the precautions on the back before filling this page) -------- Order -------- I · 530015 A7 ___B7_____ V. Description of the invention (0), spring The combination of the three forces of 314 elastic force and liquid compression force in the chamber 322. The mechanism 302 further includes a claw (shaped) clutch system 373 including a control element 374 carrying a coupling tooth 376. The control element 374 is in a neutral position labeled "N", one in which the planetary gear carrier 370 is coupled to the input connection element 330 of the second mechanism 302 as a forward driving position "D" for ordinary rotation, and one of the The planetary gear carrier 370 is displaceable from the reverse driving position "R", which is decoupled from the input connection element 330 and coupled with the bushing 26 which is integrated with the housing element, and the like. The control element 374 is a tube which is movably inserted between the stator shaft 21 and the stator bushing 26. The operation of the second mechanism 302 when the claw clutch is in a "D" position allowing two different forward drive ratios will now be explained. When the clutch 310 is engaged, the input connection element 330 simultaneously borrows the clutch 310 with the sun. The wheel element 350 and the coupling teeth 376 via the dog clutch 373 are connected to the planetary carrier 370 for normal rotation. The mechanism 302 then operates in a direct drive mode. When the clutch 310 is released and the brake 309 is engaged, the sun gear element 350 is blocked by the housing element 2 and the input connection element 330 individually drives the planetary gear ′ carrier 370. As a result, the planetary gear 372 rolls over the surrounding teeth of the sun gear 35 and makes the crown wheel 360 rotate faster than the planetary gear carrier 370. The mechanism 302 then operates in an overdrive mode. During the transition between these two stable states, the crown element 360 tends to be retarded by the load applied to the output element 4. As a result, the sun wheel 36 paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297) (Public reply) '" (Please read the precautions on the back before filling this page) -------- Order -------- A7 530015 ___ B7 _ V. Description of the Invention (Discussion) Element 350 There is a tendency to rotate faster than an assembly including the planetary carrier 370 and the input connection element 330. (Please read the precautions on the back before filling this page) When the claw clutch 373 is in the "R" position, the planetary gear carrier 370 is prohibited from rotating. As a result, the planetary gear is used as the sun gear 350 and crown Move the reverse device between 360 to operate. In this case, the clutch 310 must be engaged with a suitable fluid pressure against the spring 314 in the chamber 322 so that the action introduced by the input connection element 330 can be transmitted by the sun gear element 350. The reverse movement occurs with a deceleration because the diameter of the crown member 360 is larger than the diameter of the teeth of the sun gear member 350. . By selecting a suitable ratio between the different diameters of the meshing elements, a selection of the meshing elements in FIG. 3 provides a rough idea, and the transmission mechanism in FIG. 3 provides when the claw clutch device is located in the “D” position. The six forward drive ratios are appropriately assigned. The six ratios are as follows:-For the first overall ratio, the mechanism 301 operates with its first deceleration ratio (the deceleration ratio), and the second mechanism 302 operates with its lower (direct drive) mode Operation;-For the second overall ratio, the mechanism 302 cuts into overdrive status. While the mechanism 301 remains in a strong deceleration operation;-for the third overall ratio, the mechanism 301 operates at its second ratio (moderate deceleration), while the mechanism 302 operates in its direct drive mode -The fourth ratio is a direct drive throughout the entire transmission; 37 This paper size applies to Chinese National Standard (CNS) A4 (210 X 297 mm) A7 530015 V. Description of the invention (β)-The fifth ratio is The mechanism 301 is obtained when it operates at its second ratio (moderate deceleration) and the mechanism 302 is operated in an overdrive mode 'and-in this sixth ratio, the mechanism 301 is in a direct drive mode and the mechanism 302 is in an overdrive mode To operate;-for the reverse drive, with the claw clutch 373 in the "R" position, a convenient ratio can be obtained when the mechanism 301 is in its second ratio operation (moderate deceleration). The “N” position of the claw clutch 373 caused by the release of the output element 4 is in a state for, for example, pushing the vehicle by hand or towing the vehicle, which actually lacks the energization of the mechanism 301 Effect, but a braking condition in the mechanism 301 can be achieved. The result of this possibility of invalidating the parking brake function is that the mechanism 301 is located upstream of the power flow path of the claw clutch system relative to the engine and vehicle wheels. The transmission mechanism of Fig. 3 is remarkable because it provides six ratios and one reverse in only two simple planetary gear trains, only three hydraulic positions, and six friction couplings. Moreover, the hydraulic actuators are only used to supplement the power, and their energy consumption is thereby reduced. Of the six frictional couplings, three of them are always in the meshing state due to. No residual friction is generated in this transmission. The manner in which the three ratios of the first mechanism 301 are available in a basic planetary gear train creates a ratio gap between the first and second ratios that is greater than the ratio gap between the second and direct drive ratios. More specifically, the first ratio gap is substantially equal to the square of the second gap 38. The paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before (Fill in this page) -------- Order --------- Line · A7 530015 V. Description of the Invention (祚), and still more specifically, about one second of the second ratio gap cube. For example, these ratios are 1: 4. 2, 1: 1. 4 and 1: 1, then the first ratio gap between the first and second ratios is 4. 2/1. 4 = 3. 00, a second ratio gap between the second and direct drive ratios is 1. 4/1 = 1. 4. The overdrive ratio in the second mechanism is selected such that it lies between the first and second ratio gaps in the first mechanism, that is, about 1. 8, so the obtained overdrive ratio is about 1: 1. 8. The example of FIG. 4 will be described only in terms of differences from FIG. 3. In the example of Fig. 4, these mechanisms 301 and 302 are basically the same as those of Fig. 3, but they are mounted along axes XI and X2 which are parallel and spaced apart from each other. The output element 41 of the mechanism 301 carries an output gear 43 meshing with an input gear 334 of a mechanism 302, and the input gear 334 is integrally formed with the input connection element 330. In the mechanism 302, there is no input shaft 31 and no stator shaft 31. Therefore, the input connection element 330 occupies a central position with a shaft 336 carrying a gear 334, and is occupied by the claw clutch. The bush-like control element 374 is surrounded. The biaxial device of FIG. 4 is simply implemented due to the following facts: The two mechanisms 301, 302 are connected in a single rotation only (the output shaft 41 of the first mechanism, the input mechanism 41 of the second mechanism, Connection) to connect to each other and allow for a particularly short design. It may thus constitute, for example, an in-line six-cylinder engine mounted across the vehicle and associated with a six-speed automatic transmission. By the possibility of a clutch or a power coupler being properly installed between the engine and the transmission, the low shaft 39 paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) (please first (Read the notes on the back and fill out this page) -------- 丨 Order --------.  A7 530015 __B7____ 5. Description of the Invention (vl) The demand for space has been further enhanced. The example of FIG. 5 only illustrates the differences from FIG. 2. The planetary carrier 7 is no longer rigidly connected to the output shaft 41. It introduces a claw clutch device 73 in the mechanism, which device comprises:-a claw clutch 44 which is provided with an actuating element 29 and is connected to the output shaft 41 for ordinary rotation, and then in a " N "(neutral) position, a position indicated by" D "(forward drive) and performing ordinary rotational coupling between the planetary carrier 7 and the output shaft 41, and a position between the crown wheel 6 and the output wheel 41 The three positions, such as the coupled "R" (reverse) position, can move axially. For this purpose, the crown wheel 6 is provided with claw clutch teeth 65;-a claw clutch 28 which is mounted on the stator shaft 21 to prevent rotational movement but which can be moved in translation with the claw clutch 44. When the claw clutch 44 is in the R position, the claw clutch 28 couples the planetary gear carrier 7 to the stator shaft 21, and is therefore coupled to the housing 2 at the same time;-a freely rotatable on the claw clutch 44 and connected to it Connected as a normal translation claw clutch 255. The claw clutch 255 is permanently connected to the crown wheel 6 provided on the support 251 except that the claw clutch 255 which is no longer in engagement with the claw clutch teeth 65 at this position in the D position is connected. The dog clutch teeth 256 are engaged. In forward driving, this operation is the same as that in FIG. 2. During reverse operation, the brake 209 and the clutch 10 (Fig. 2) are engaged, the shaft 71 is blocked by the claw clutch 28, and the planetary gears 72 are regarded as being connected to the input sun gear element 5 and connected At the output, 40 paper sizes are applicable to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) -------- Order ----- ---- Line · 530015 A7 ___ B7 _ 5. Description of the invention (β) Allows operation by moving the reverse device between the crown wheels which rotates in the reverse direction due to disengagement from the one-way clutch support 251. The speed reduction system between the sun gear 5 and the crown wheel 6 is satisfactorily high. It thus achieves the integrity of an automatic transmission of a vehicle with three forward drive ratios, a reverse drive, a neutral and a gradual starter with a single simple planetary gear train. Regarding the switch from the direction drive to the reverse drive, the ^ claw-shaped clutch system is a thought-provoking 'because this type of switching usually occurs when the vehicle system is stopped, that is, one of which involves the claw shape. All parts of the clutch switch are stationary, even when the engine rotates the input shaft 31 °. In the reverse driving mode, the crown wheel 6 is rotated, while the support 251 is stationary. Therefore, an axial thrust bearing 141 has been inserted between the spring 214 and the crown wheel element 6. The specific embodiment of FIG. 6 will be described only in terms of differences from FIG. 2. The bombs 114 and 214 have been removed and are inserted between the sun wheel 5 and the crown wheel 6 by a square for advancing them in each of the opposite directions which are the same as the directions promoted by the springs 114 and 214 in FIG. 2 That is, a single spring device 14 for counteracting the respective hydraulic actuator is replaced. Because the rotation speed of the sun wheel 5 and the crown wheel 6 is in addition to the direct drive mode. Different, so a thrust bearing 142 has been inserted between the spring device 14 and one of the elements of the sun gear 5 and the crown wheel 6, for example, in the example shown, the one of the elements is the sun gear 5. In each of the first and second ratios of the specific embodiment of FIG. 6, one of the hydraulic actuators is increased in energy and is transparent. 41 This paper size applies to the Chinese National Standard (CNS) A4 specification. (210 X 297 mm) (Please read the notes on the back before filling in this page) -------- Order --------- * 5 ^ · 530015 B7 V. Description of the invention (4 ) Pass the spring device 14 and thrust bearing 142 to push the flap of the other actuator backward. During the direct drive operation, two hydraulic actuators are added. The spring device 14 makes a maximum compression, on the other hand, as shown in the embodiment of FIG. 2, the clutches 10 and 210 are engaged. In a modified embodiment not shown, the spring 14 and thrust bearing 142 assembly may be replaced by a supplemental hydraulic actuator that reduces energy for direct drive operation. The specific embodiment of FIG. 7 will be described in terms of differences from FIG. 4. The component numbers that have been used in the aforementioned drawings are relative to the same or very similar components in FIG. 7. The specific embodiment of FIG. 7 contains a second mechanism 302 substantially similar to the second mechanism 302 of FIG. 4 but with the following main differences:-The input connection element 330 of the mechanism 302 is formed with the planetary gear carrier 370 and the transmission input shaft 131 Integrated;-in the transmission device, the reverse drive device is no longer included in the second mechanism 302, but forms a separate unit 303 which will be described later;-the first mechanism 302 is installed along the Upstream of the first mechanism 301 that faces the power flow path between the input shaft 'and the output teeth 42 of the transmission; and-the crown wheel element 360 of the second differential mechanism 302 and The output connection element 304 that drives the gear teeth of the input rotation connection element 3 that is engaged with the first transmission mechanism 301 forms a 42. Please read the M paint on the back first, and then fill out this page) ------- Order --------- This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) A7 530015 _____B7____ 5. The description of the invention (V). (Please read the precautions on the back before filling out this page) The first mechanism 301 is similar to that in Figure 6 but has the following differences: a planetary carrier 7 is connected to the output connection element 4 through A claw clutch system for a claw clutch 44 between a "D" position for ordinary rotation and a "R, N" position in which the planetary carrier 7 and the output connection element 4 are separated from each other as shown, The output rotary connection element 4 is connected to the planetary gear carrier 7. The output connecting element 4 of the first mechanism 301 is provided with a gear tooth that engages a gear tooth of the intermediate output element 45 integrally formed on the output tooth 42 and integrally rotatably mounted on the input shaft 131 of the transmission device. . Therefore, the input (shaft 131) and output (tooth 42) of the entire transmission are coaxial. This is advantageous because it allows the transmission to be placed freely around the input and output common axis X3 in the engine compartment of a vehicle, depending on the space available. The reverse drive mechanism 303 is mounted around the geometric axis X3 so as to selectively bypass the first mechanism 301. The reverse drive mechanism 303 includes an output connecting element 304 that selectively connects the second mechanism crown wheel 360 and an integral unit thereof with an auxiliary gear 82 that can freely rotate about the input shaft 131 for ordinary rotation. Claw clutch system 361. Accordingly, the secondary gear 82 meshes with an intermediate eccentric stepped secondary gear 83 that sequentially meshes with a third tooth set 84 of the intermediate output element 45. This device is such that during direct drive, the movement direction of the output tooth 42 is phase 43 due to the intermediate auxiliary gear 81 between the output connection element 304 of the second mechanism 302 and the input connection element 3 of the first mechanism 301. This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) A7 530015 V. Description of the invention (V) is opposite to the moving direction of the input shaft 131, however, the output teeth 42 and the input shaft 131 are driven in the reverse The modes have the same direction of rotation. The claw clutch 362 of the claw clutch system 361 is movable between a “N, D,” position as shown in FIG. 7, and in the “N, D” position, the second mechanism 3 The output element 304 of 2 is disengaged from the auxiliary gear 82, and in an "R" position, they are connected to each other. The claw clutches 44 and 362 are jointly driven so that when the claws are disengaged When the clutch 44 is in the "RN" position, on the other hand, the claw clutch 362 is in the "R" position. This reverse driving state is realized. When the claw clutch 44 is in the "D" position, on the other hand If the 362 series is in the "N, D" position, the forward drive is realized, and when the claw clutch 44 is in the "R, N" position and the claw clutch 362 is in the "N, D" position, a neutral state Realized. In the forward drive position, when the actuators 116 and 216 are reduced in energy, the first mechanism 301 performs a braking function, and conversely, when the neutral is implemented, the output tooth 42 is enabled. Freely move. Therefore, the input shaft 131 of the transmission device can be shaped Integrally with an engine shaft connected to an engine 1〇1 contact 'without the need to insert any input clutch or coupler converter. The particular embodiment of FIG. 8 embodiment only in respect of them Description 7 differs from the point of FIG.  The second mechanism 302 is similar to the second mechanism of FIG. 7, except that its output connection element 304 can no longer be connected to a reverse driving mechanism, and does not need to directly mesh with the input of the first mechanism 301 through the intermediate auxiliary gear 81 of FIG. 7. Gear teeth of the connecting element 3. The first institution 301 is the same as the first institution in FIG. 7, except that the paper size of this bank applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before filling this page} ------- I — ^.  I I ----- · A7 530015 ____B7___ 5. Explanation of the invention (θ) The star gear carrier 7 is permanently connected to the output element 4 of the first mechanism 301. Furthermore, the crown wheel 6 is not selectively combined with the housing element 2. The clutch 209 and the one-way clutch 208 assembly phase the crown wheel 6 with a cage 86 that can rotate about the axis X4 of the first transmission mechanism 301. connection. . The output element 4 and the cage 86 are provided with respective gear teeth engaged with corresponding teeth that are rotatable about the input shaft 131 and are formed integrally with the respective rings 87, 88 coaxial with the same. A stationary ring 89 is formed integrally with the housing element 2 and is axially aligned with the rings 87 and 88 and mounted between them. The three rings 87, 88 and 89 are rotatable between a tubular shaft of an intermediate connecting element 45 and two engaging flanges 46 of the tubular shaft. A first claw clutch 91 is selectively coupled to the output teeth 42 of a direct drive transmission or to the stationary ring 89 for normal rotation of the ring 87. In order to prevent the planetary gear carrier 7 from Move for reverse drive. A second claw clutch is selectively connected to the output tooth 42 or the stationary ring 89 for ordinary rotation of the second ring 88. In order to connect the cage 86 to the output tooth for reverse driving Alternatively, it is connected to the casing 2 for direct driving. The two claw clutches 91, 92 are synchronized by a coupling element 93. The specific embodiment of FIG. 9 will be described only in terms of differences from FIG. 8. Mingzhi. The second differential mechanism 301 is replaced by a two-speed countershaft mechanism 402. The mechanism 402 simultaneously executes power transmission from the axis X3, and extends along the axis X3 input shaft 131 to the first differential mechanism 301 not shown. Above the parallel axis X4, and more specifically, from the input shaft 131 of the transmission to the 45th paper standard applicable to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back first (Fill in this page again)

I I I 1 I I I 訂·1111---I 530015 A7 ___ B7___ 五、發明說明（θ ) 一差動機構301的輸入連接元件3處。 該機構402包含兩個不同直徑的並可旋轉地安裝於輸 入軸131之上且嚙合於與輸入軸連接元件3形成一體的各 別接收器副齒輪411，422的推進器副齒輪410, 420。該等 推進器副齒輪410的較小一個係藉著當一致動器416被增 加能量時即被嚙合的離合器413相平行地被安裝的單向離 合器408選擇性地耦合於輸入軸131。 具有較大直徑的推進器副齒輪420係可滑動地被安裝 於輸入軸131之上並與其選擇性的被耦合以爲普通旋轉之 用，當一摩擦離合器423被嚙合時。當從輸入軸131傳送 一可引發運動的力偶至輸入連接兀件3之時，藉由一液壓 致動器426以相對於由推進器副齒輪420所施加的齒推力 425的方向軸向推動推進器副齒輪420，則離合器423的嚙 合動作可被引發。其在該推進器副齒輪410和420之間與 一推力軸承442相串連地提供一彈簧裝置414。 圖9的該具體實施例的操作如下： 當該等致動器416和426沒有任何一個被增加能量且 一可引發運動的力偶被施加於輸入軸131之時，單向離合 器408驅動推進器副齒輪410，該副齒輪410以該兩個傳 .動比率的較低一個比率依序地驅動輸入連接元件3。該致 動器416可被增加能量以維持同樣的傳動比率，如果施加 於輸入軸131之上的力偶變成負値（引擎制動操作）。 當該致動器416被減少能量而致動器426被增加能量 以嚙合離合器423之時，該機構402被切進其較高的傳動 46 本紙i尺度適用中國國家標準（CNS)A4規格（210 X 297公爱) 一 (請先閲讀背面之注意事項再填寫本頁) 訂---------線- A7 530015 _B7_____ 五、發明說明（4) 比率。此造成該輸入軸131的一較低的旋轉速度，另外一 方面，由輸入連接元件3的旋轉速度所決定的推進器副齒 輪410的旋轉速度保持不變，如同單向離合器或自由輪 408所允許的一般。 圖10的該具體實施例將就其與前述具體實施例不同 之處加以說明之。 該第一機構301和第二機構402係沿著一同樣幾何軸 X5被串連地連接。該交通工具引擎101係透過一輸入離合 器102連接於第一機構301的輸入連接元件3。該第一機 構301基本上係相似於圖6，除了該輸出元件係一管狀軸 41同時形成該第二機構402的輸入連接元件。該第二機構 402係相同於圖9，除了其輸入連接元件，如已經所述地， 係一管狀軸，第一機構301的定子軸21穿過該管狀軸而延 伸。 並不剛硬地連接於該輸入連接元件3，該第二機構 402的兩個接收器副齒輪411和421被剛硬地連接於一藉 由一爪形離合器96選擇性地連接於輸出齒42的圓環94。 另外一個爪形離合器97選擇性地將該等輸出齒42連接於 一形成一體地包含一副齒輪99的中間逆向驅動元件98。 >一中間副齒輪181嚙合副齒輪99並嚙合提供於第一機構 301的輸入連接元件3之上的齒輪齒182。 該中間輸出元件98、輸出齒42、圓環94以及接收器 副齒輪411和421沿著一平行於第一和第二機構301，402 的軸X5的共同軸X6而延伸。 47 本紙張尺度適用中國國家標準（CNS)A4規格（21〇 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) -------訂---------線- A7 530015 五、發明說明（β ) 爪形離合器96和97被一彈簧183所推送而分開，藉 此，在兩個離合器的該其它位置上，由透過接收器副齒輪 411或421的其中之一所帶來的向前驅動運動中和由透過 該中間逆向驅動連接元件98所帶來的逆向驅動運動中，該 等兩個輸出齒42被從分開。從此狀態開始，將爪狀離合器 96推向保持於靜止狀態的爪狀離合器97，該向前驅動模式 被建立，相反地，將爪狀離合器97推向保持於靜止狀態的 爪狀離合器96，該逆向驅動模式被建立。 在該逆向驅動模式當中，第一機構301和第二機構 302兩者皆被迴繞。 .因此允許該交通工具在逆向驅動中漸進地啓動將需要 該輸入離合器102。 圖11的該範例將僅就其與圖10的不同處加以說明之 〇 介於該第一機構輸入和輸出齒42之間的逆向驅動連 接182, 181，99, 98, 97係完全地被刪除，且該等輸出齒42 被剛硬地連接於接收器副齒輪411和421，和連接於一逆 向接收器副齒輪484。一中間副齒輪483嚙合於該逆向接 收器副齒輪484並嚙合於一被安裝以自由地繞著第二機構 J02中的管狀軸41旋轉的逆向推進器副齒輪482。 不再被安裝於該推進器副齒輪410和第二機構的輸入 連接元件之間，該單向離合器408現在被安裝於推進器副 齒輪410和一圓環184之間。一爪狀離合器180選擇性地 將該管狀軸41與圓環184連接以便直接驅動，或者與該逆 48 本紙張尺度適时關家鮮（CNS)A4規格（210 X 297公爱)' -- (請先閱讀背面之注意事項再填寫本頁) --------訂--------- . A7 530015 ______B7______ 五、發明說明（一） 向驅動器副齒輪482連接以爲逆向驅動之用。因爲動力經 由該第一機構301流動以作爲向前驅動或逆向驅動之用， 所以此具體實施例在該引擎101和第一機構301的輸入連 接元件3之間並不需要任何輸入離合器102 (圖10)。 圖12的該具體實施例將就其與圖8之不同處加以說 明之。 該第一機構301已經被修飾，使得每一個摩擦耦合裝 置9, 10, 209, 210被一僅以箭頭表示的特定的致動器317, 318, 319, 320所控制。該太陽輪元件5和冠狀輪元件6在 軸方向係靜止的。針對這個理由，其不再需要以平行於該 單向離合器8, 208的方式提供軸承。 該彈簧裝置被免除。 在此具體實施例當中，該可提供的齒輪比率與圖8中 的相同。然而，該等被需要以便實現每個齒輪比率的離合 器嚙合係由增加各個相對的液壓致動器的能量來決定。 該第二機構302並沒有作超過圖8的同機構的修飾， 但使得太陽輪元件350軸向地不可滑動、取消彈簧314並 針對每個摩擦耦合裝置309和310提供一特定的致動器而 非提供一共同的致動器316等等，則可以相同於該第一機 ,構301的精神來修飾第二機構302。 當然，本發明並不僅限制於所表示和所說明的具體實 施例。 所已經代表的作動力量之外的作動力量可以被牽涉進 來，例如，當該旋轉速度增加藉由離心飛行重量以一較高 49 (請先閱讀背面之注意事項再填寫本頁) -------訂---------一 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 530015 A7 _B7__ 五、發明說明（训） 傳動比率來增強操作所產生的力量，或其它以一相反於該 第一液壓力量的第二液壓力量來能夠以一個或其它方向來 確實地影響一聚集的作動或控制結構的操作狀態。 其已經在圖2和由其所衍生的具體實施例當中看到， 雖然在一單一簡單齒輪系上安裝兩個聚集控制和耦合結構 ，但是該差動機構（在該行星齒輪架的範例當中）的旋轉 元件的其中之一完全保持此類結構的豁免。其於是能考慮 提供一相關於該行星齒輪架的第三聚集結構。 本發明與具有至少四旋轉元件的複雜差動機構係可相 容的。其於是可能增加該聚集的耦合與控制結構的數目。 (請先閱讀背面之注意事項再填寫本頁) 訂---------線. 50 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐）I I I 1 I I I Order · 1111 --- I 530015 A7 ___ B7___ V. Description of the invention (θ) There are 3 input connection elements of the differential mechanism 301. The mechanism 402 includes two propeller gears 410, 420 of different diameters rotatably mounted on the input shaft 131 and meshing with respective receiver gears 411, 422 integrated with the input shaft connecting member 3. The smaller one of the thruster pinion gears 410 is selectively coupled to the input shaft 131 by a one-way clutch 408 which is installed in parallel with the clutch 413 which is engaged when the actuator 416 is energized. A thruster gear 420 having a larger diameter is slidably mounted on the input shaft 131 and is selectively coupled thereto for ordinary rotation when a friction clutch 423 is engaged. When a motion-inducing force couple is transmitted from the input shaft 131 to the input connecting element 3, a hydraulic actuator 426 is pushed axially in a direction relative to the tooth thrust 425 applied by the thruster pinion 420 Gear 420, the meshing action of the clutch 423 can be triggered. It provides a spring device 414 in series between the thruster pinions 410 and 420 and a thrust bearing 442. The operation of the specific embodiment of FIG. 9 is as follows: When none of the actuators 416 and 426 is increased in energy and a motion-inducing force couple is applied to the input shaft 131, the one-way clutch 408 drives the propeller pair The gear 410 drives the input connection element 3 in sequence at a lower ratio of the two transmission ratios. The actuator 416 can be increased in energy to maintain the same transmission ratio if the force couple applied to the input shaft 131 becomes negative 値 (engine braking operation). When the actuator 416 is reduced in energy and the actuator 426 is increased in energy to engage the clutch 423, the mechanism 402 is cut into its higher transmission 46 This paper i-size applies the Chinese National Standard (CNS) A4 specification (210 X 297 public love) I (Please read the precautions on the back before filling this page) Order --------- Line-A7 530015 _B7_____ 5. Description of the invention (4) Ratio. This results in a lower rotation speed of the input shaft 131. On the other hand, the rotation speed of the propeller gear 410, which is determined by the rotation speed of the input connection element 3, remains unchanged, as is the case with the one-way clutch or freewheel 408. Allowed in general. The specific embodiment of Fig. 10 will be described in terms of differences from the foregoing specific embodiment. The first mechanism 301 and the second mechanism 402 are connected in series along a same geometric axis X5. The vehicle engine 101 is connected to the input connection element 3 of the first mechanism 301 through an input clutch 102. The first mechanism 301 is basically similar to FIG. 6 except that the output element is a tubular shaft 41 and simultaneously forms the input connection element of the second mechanism 402. The second mechanism 402 is the same as that of FIG. 9, except that its input connection element is, as already described, a tubular shaft, and the stator shaft 21 of the first mechanism 301 extends through the tubular shaft. Not rigidly connected to the input connection element 3, the two receiver pinions 411 and 421 of the second mechanism 402 are rigidly connected to a selectively connected output tooth 42 by a claw clutch 96 Of the ring 94. Another dog clutch 97 selectively connects the output teeth 42 to an intermediate reverse driving element 98 which integrally includes a sub-gear 99. > An intermediate auxiliary gear 181 engages the auxiliary gear 99 and engages gear teeth 182 provided on the input connection member 3 of the first mechanism 301. The intermediate output element 98, the output tooth 42, the ring 94, and the receiver pinions 411 and 421 extend along a common axis X6 parallel to the axis X5 of the first and second mechanisms 301, 402. 47 This paper size applies to China National Standard (CNS) A4 (21〇X 297 mm) (Please read the precautions on the back before filling this page) ------- Order -------- -Line- A7 530015 V. Description of the invention (β) The claw clutches 96 and 97 are separated by being pushed by a spring 183, whereby the other positions of the two clutches are transmitted by the receiver sub gear 411 or 421. The two output teeth 42 are separated from each other in the forward drive motion brought by one of them and the reverse drive motion brought by the intermediate reverse drive connection element 98. From this state, the forward driving mode is established by pushing the dog clutch 96 toward the dog clutch 97 held in a stationary state, and conversely, pushing the dog clutch 97 toward the dog clutch 96 held in a stationary state, the A reverse drive mode is established. In this reverse driving mode, both the first mechanism 301 and the second mechanism 302 are wrapped. The input clutch 102 will therefore be required to allow the vehicle to start progressively in reverse drive. The example of FIG. 11 will only be described in terms of differences from FIG. 10. The reverse drive connection 182, 181, 99, 98, 97 between the input and output teeth 42 of the first mechanism is completely deleted. The output teeth 42 are rigidly connected to the receiver paired gears 411 and 421, and connected to a reverse receiver paired gear 484. An intermediate sub-gear 483 meshes with the reverse receiver sub-gear 484 and meshes with a reverse-thruster sub-gear 482 installed to rotate freely around the tubular shaft 41 in the second mechanism J02. No longer mounted between the thruster pinion 410 and the input connection element of the second mechanism, the one-way clutch 408 is now mounted between the thruster pinion 410 and a ring 184. A claw-shaped clutch 180 selectively connects the tubular shaft 41 with the ring 184 for direct driving, or with the inverse 48 paper size in time (CNS) A4 size (210 X 297 public love) '- (Please read the precautions on the back before filling this page) -------- Order ---------. A7 530015 ______B7______ V. Description of the invention (1) Connect to the auxiliary gear 482 of the driver for reverse For driving. Because power flows through the first mechanism 301 for forward driving or reverse driving, this specific embodiment does not require any input clutch 102 between the engine 101 and the input connection element 3 of the first mechanism 301 (FIG. 10). The specific embodiment of Fig. 12 will be described in terms of differences from Fig. 8. The first mechanism 301 has been modified so that each friction coupling device 9, 10, 209, 210 is controlled by a specific actuator 317, 318, 319, 320, which is indicated only by an arrow. The sun gear element 5 and the crown gear element 6 are stationary in the axial direction. For this reason, it is no longer necessary to provide bearings in a manner parallel to the one-way clutches 8,208. The spring device is dispensed with. In this specific embodiment, the available gear ratio is the same as that in FIG. However, the clutches required to achieve each gear ratio are determined by increasing the energy of each opposing hydraulic actuator. The second mechanism 302 is not modified more than the same mechanism of FIG. 8, but makes the sun gear element 350 axially non-slidable, eliminates the spring 314 and provides a specific actuator for each of the friction coupling devices 309 and 310. Instead of providing a common actuator 316, etc., the second mechanism 302 can be modified in the same spirit as the first mechanism 301. Of course, the invention is not limited to the specific embodiments shown and described. The amount of working force other than the amount of working force that has been represented can be involved, for example, when the rotation speed is increased by the centrifugal flight weight to a higher 49 (please read the precautions on the back before filling this page) ---- --- Order --------- A paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 530015 A7 _B7__ V. Description of the invention (training) Transmission ratio to enhance operation Or a second hydraulic force opposite to the first hydraulic force to be able to positively affect the operating state of an aggregated actuation or control structure in one or other directions. It has been seen in FIG. 2 and the specific embodiments derived from it. Although two aggregate control and coupling structures are installed on a single simple gear train, the differential mechanism (in the example of the planetary gear carrier) One of the rotating elements completely maintains the exemption of such structures. It can then be considered to provide a third gathering structure associated with the planetary carrier. The present invention is compatible with complex differential mechanisms having at least four rotating elements. It is then possible to increase the number of the coupled coupling and control structures. (Please read the precautions on the back before filling this page) Order --------- line. 50 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm)

Claims (1)

530015 A8 B8 C8 D8 iM 申請專利範圍 禱克I 1·-種傳動裝置，其中一差動機構（1，301，302)係包含 (請先閱讀背面之注意事項再塡寫本頁) 一外殼元件(2); 一輸入旋轉連接元件（3, 303)和一輸出旋轉連接元件 (4); 三個旋轉元件(5, 6, 7; 350, 360, 370)，其相對於該外 殼元件(2)係可旋轉地，並彼此相互嚙合； 南個摩擦耦合裝置(9, 10; 209, 210; 309, 310)介於該 元件之間； 一單向離合器（8; 208; 308)，其禁止該等旋轉元件的 一第一元件（5, 350)相對於該等元件的一第二元件（2, 330) 的單一方向的相對旋轉； 作動裝置（114, 116; 214, 216; 314, 316)，其用於該耦 合裝置； 線 其特徵在於： 該等選擇性耦合裝置的一第一裝置(9; 209; 310)係機 械地平行於單向離合器(8; 208; 308); 該等選擇性耦合裝置的一第二裝置（1〇; 21〇; 3〇9)係可 ί呆作地，安裝於該等兀件的該第一元件(5; 350)與一第三元件 (3; 2)之間； 該兩個摩擦耦合裝置係由一介於兩個穩定狀態之間的 反向器控制裝置（11; 211; Ml)所協調..，在該兩個穩定狀態 中的每-個狀態，該等親合魏的其中〜個 ，而另外一個係釋放的。 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公箸) 530015 、ν:Φ''丨ί，'Α8 '7 υ Β8 } r：lf λ ί C8 ι. D8 - -- —— ...... - —κ χ_ 六、申請專利範圍 (請先閲讀背面之注意事項再塡寫本頁) 2·如申請專利申請專利範圍第1項之裝置，其特徵在 於：該反向器控制裝置係一可在兩終端位置之間移動的普 通壓力元件（11; 211; 311)，該兩終端位置的每一個位置相 對於該等穩定狀態的其中一穩定狀態，且該普通壓力元件 (Π; 211; 311)上面被作動裝置所作動。 3·如申請專利申請專利範圍第1項之裝置，其特徵在 於：該反向器控制裝置係與第一元件(5; 6; 350)形成一體。 4·如申請專利申請專利範圍第1項之裝置，其特徵在 於：包含在該第一旋轉兀件(5; 350)與第二元見(2; 330)之 間機械式串連的單向離合器(8; 208; 308)，~具有軸向可移 動性以作爲普通旋轉之用的裝置（52, 53; 252, 253; 352, 353) 〇 線 5·如申請專利申請專利範圍第4項之裝置，其特徵在 於：該第一旋轉元件(5, 350)被導引以獨立於作爲普通旋轉 之用的裝置(52, 53; 252, 253; 352, 353)來軸向滑動。 6.如申請專利申請專利範圍第4項之裝置，其特徵在 於：該作爲普通旋轉之用的裝置（ 52, 53; 252, 253; 352, 353)係可操作地被裝置在第一和第二元件的其中之一元件 與一單向離合器支撐(51; 251; 351)之間，並且一軸向不可 滑動的軸承(54; 254; 354)與單向離合器(8; 208; 308)機械地 相平行被提供於單向離合器支撐和該第一和第二元件的其 中另外一個元件之間。 7·如申請專利申請專利範圍第1項之裝置，其特徵在 _2____ 本紙張尺度適用中國國家標準(CNS)A4规格(210 X 297公釐） 53〇〇15 ί(7 !f^(〇 n(L A8 B8 C8 D8 六 、申請專利範函 於：該作動裝置包含一在一齒反應推力（Fl，F2)作用下該第 /元件(5; 6; 350)的軸向可移動性。 8·如申請專利申請專利範圍第7項之裝置，其特徵在 於：該等作動裝置包含兩不相容致動器（114, 116; 214, 216; 314, 316)，其中一致動器具有一與該齒推力同方向的動作 的功能。 9·如申請專利申請專利範圍第8項之裝置，其特徵在 於：該等不相容致動器的其中一致動器係至少爲一彈簧 (114; 214; 314)。 10·如申請專利範圍第9項之裝置，其特徵在於：該至 少一彈簧作用在一相反於齒推力的方向上。 11.如申請專利範圍第8項到第10項的其中一項之裝 置’其特徵在於··該具有與齒推力同方向動作功能的不相 容致動器係一可控制的致動器，較佳地係一液壓致動器 (Π6; 216; 316)。 I2·如申請專利範圍第1項到第10項的其中一項之裝 置，其特徵在於：該第一元件係該差動機構（1; 302)的一太 陽輪（5; 350)。 13·如申請專利範圍第1項到第1〇項的其中一項之裝 置’其特徵在於：該第二元件係外殼元件(2)。 I4·如申請專利範圍第1項到第10項的宜中一項之裝 置’其特徵在於：其提供一軸向穿過該第\元件(5· 35〇)屬 於形成第二元件的外殼元件(2)的定子軸(21)。 15 ·如申師專利朝;圍弟14項之裝置’其特徵在於：該 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐) (請先閲讀背面之注意事項再塡寫本頁) -一口 線 530015530015 A8 B8 C8 D8 iM Patent application scope Ig1 ·-a kind of transmission device, one of the differential mechanism (1,301,302) contains (please read the precautions on the back before writing this page) a housing element (2); one input rotary connection element (3, 303) and one output rotary connection element (4); three rotary elements (5, 6, 7; 350, 360, 370), which are opposite to the housing element (2 ) Is rotatably and meshes with each other; South friction coupling device (9, 10; 209, 210; 309, 310) is between the elements; a one-way clutch (8; 208; 308), which prohibits Unidirectional relative rotation of a first element (5, 350) of the rotating elements relative to a second element (2, 330) of the elements; an actuator (114, 116; 214, 216; 314, 316) ), Which is used for the coupling device; the line is characterized by: a first device (9; 209; 310) of the selective coupling devices is mechanically parallel to the one-way clutch (8; 208; 308); etc. A second device (10; 21〇; 309) of the selective coupling device is a first component (5; 350) which can be installed on the components in a dwelling manner. Between a third element (3; 2); the two friction coupling devices are coordinated by an inverter control device (11; 211; Ml) between two stable states. Each of the stable states, ~~ of these affinity Wei, and the other is released. This paper size applies to China National Standard (CNS) A4 specifications (210 X 297 male) 530015, ν: Φ '' 丨 ί, 'Α8' 7 υ Β8} r: lf λ ί C8 ι. D8--—— ...-κ χ_ VI. Scope of patent application (please read the precautions on the back before writing this page) 2. If the device of the scope of patent application for item 1 of the patent application is characterized by: The control device is an ordinary pressure element (11; 211; 311) that can be moved between two end positions. Each position of the two end positions is relative to one of the stable states, and the ordinary pressure element (Π; 211; 311) was actuated by an actuating device. 3. The device according to item 1 of the scope of patent application, characterized in that the inverter control device is integrated with the first element (5; 6; 350). 4. The device according to item 1 of the scope of patent application for patent application, characterized in that it includes a unidirectional mechanical serial connection between the first rotating element (5; 350) and the second element (2; 330) Clutch (8; 208; 308), ~ A device with axial mobility for ordinary rotation (52, 53; 252, 253; 352, 353) 〇 Line 5: If the scope of patent application is 4 The device is characterized in that the first rotating element (5, 350) is guided to slide axially independently of the device (52, 53; 252, 253; 352, 353) for ordinary rotation. 6. The device according to item 4 of the scope of patent application for patent application, characterized in that the device (52, 53; 252, 253; 352, 353) for ordinary rotation is operatively installed in the first and the second One of the two components is between a one-way clutch support (51; 251; 351) and an axial non-sliding bearing (54; 254; 354) and a one-way clutch (8; 208; 308). The ground phase is provided in parallel between the one-way clutch support and the other of the first and second elements. 7 · If the device under the scope of patent application for the application for patent application is characterized by _2____ This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 53 〇15 ί (7! F ^ (〇 n (L A8 B8 C8 D8 VI. Patent application letter is in: The actuating device includes an axial movability of the first element (5; 6; 350) under the action of a one-tooth reaction thrust (Fl, F2). 8. The device according to item 7 of the scope of patent application, characterized in that the actuating devices include two incompatible actuators (114, 116; 214, 216; 314, 316), in which the actuator has an The tooth thrust functions in the same direction. 9. The device of claim 8 in the scope of patent application, characterized in that the actuator of these incompatible actuators is at least a spring (114; 214 314). 10. The device according to item 9 of the scope of patent application, characterized in that the at least one spring acts in a direction opposite to the thrust of the tooth. 11. One of the items 8 to 10 of the scope of patent application The device of one item is characterized in that it has the function of acting in the same direction as the tooth thrust. The capacity actuator is a controllable actuator, preferably a hydraulic actuator (Π6; 216; 316). I2. If the device is one of the items 1 to 10 of the scope of patent application, It is characterized in that: the first element is a sun gear (5; 350) of the differential mechanism (1; 302). 13. If the device of one of the items 1 to 10 of the scope of patent application is applied, its It is characterized in that the second element is a housing element (2). I4. The device according to one of the first to tenth of the scope of patent application 'is characterized in that it provides an axial penetration through the first element (5.35) The stator shaft (21) that belongs to the casing element (2) forming the second element. 15 · As claimed in the patent application; the device of the 14th item is characterized in that the paper size is applicable to the country of China Standard (CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before transcribing this page)-Yikou Line 530015 .....、申請專利範厂圍 疋子軸（21)係管狀的並圍繞著一以第三元件（3)被加快的軸 (31)。 (請先閲讀背面之注意事項再塡寫本頁) 16.如申請專利範圍第I4項之裝置，其特徵在於：該 定子軸（21)被一以其它連接元件（4)被加快的管（41)所圍繞 〇 如申請專利範圍第1項到第10項其中一項之裝置 ’其特徵在於：該第三元件係該等連接元件(3; 330)的其中 〜個元件。 18. 如申請專利範圍第17項之裝置，其特徵在於··該 裝置包含一選擇性的爪形離合器裝置以作爲下列功能之用 在一向前驅動位置，將該差動機構的三個互相嚙合元 件的所剩餘一個元件連接於其它連接元件，並將該第二元 件至少選擇性地連接至外殼元件。 線」 在一逆向驅動位置，將該差動機構的該剩餘元件連接 至外殼元件，並將該第二元件連接至其它連接元件。 19. 如申請專利範圍第18項之裝置，其特徵在於：該 裝置包含一第三摩擦耦合裝置(210; 10)，靠著該裝置(210; 1〇)該第三元件（3)係選擇性地連接至該等元件的一第四個 兀件處，該第四個元件係由除了第一元件(5; 6)之外的該等 旋轉元件(6; 5)的其中之一個旋轉元件所形成的。 20·如申請專利範圍第19項之裝置，其特徵在於：該 裝置包含： 在該第四元件（6; 5)和該等元件的另外一個元件（2)之 - —~ _ 4_ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015....., the patent application plant surrounds the sprocket shaft (21) which is tubular and surrounds a shaft (31) which is accelerated by a third element (3). (Please read the precautions on the back before writing this page) 16. If the device in the scope of patent application No. I4, it is characterized in that the stator shaft (21) is accelerated by a tube with other connecting elements (4) ( 41) The device 'around one of items 1 to 10 of the scope of patent application' is characterized in that the third element is one of the connecting elements (3; 330). 18. The device according to item 17 of the scope of patent application, characterized in that the device includes a selective claw clutch device for the following functions in a forward drive position, engaging three of the differential mechanisms with each other The remaining one of the elements is connected to the other connection elements, and the second element is at least selectively connected to the housing element. In a reverse driving position, the remaining element of the differential mechanism is connected to the housing element, and the second element is connected to other connecting elements. 19. The device according to item 18 of the scope of patent application, characterized in that the device includes a third friction coupling device (210; 10), and the third element (3) is selected by relying on the device (210; 10). To a fourth element of the elements, the fourth element being one of the rotating elements (6; 5) other than the first element (5; 6) Formed. 20 · The device according to item 19 of the scope of patent application, characterized in that the device includes: in the fourth element (6; 5) and another element (2) of these elements--~ _ 4_ This paper size Applicable to China National Standard (CNS) A4 (210 X 297 mm) 530015 、申請專利範圍 間，一與一桌一單向離合器(208; 8)相平行的第四摩擦親合 裝置(209; 9);和 (請先閲讀背面之注意事項再塡寫本頁) 一第一反向器控制裝置(211; 11)，其協調位於兩穩定 狀態之間的該第三和第四耦合裝置，在每個穩定狀態當中 ，各別地，該第三和第四耦合裝置的其中一個裝置係被嚙 合著，而另外一個係不被嚙合著。 21·如申g靑專利範圍第9項之裝置，其特徵在於：該彈 簧係可操作地被安裝於兩個反向器控制裝置之間。 22·如申請專利範圍第20項之裝置，其特徵在於：該 作動裝置包含一可操作地被安裝於該兩反向器控制裝置之 間的可控制致動器。 線 23. 如申請專利範圍第20項之裝置，其特徵在於：該 第二反向器控制裝置(211; 11)係受到該第四元件(6; 5)的一 齒反應推力所作用，該第四元件(6; 5)係被安裝以作爲在齒 推力作用下位移之用。 24. 如申請專利範圍第19項之裝置，其特徵在於：該 其它元件，藉由第四耦合裝置，能被連接至該第四元件以 最爲旋轉之用，係該第二元件(2)。 25. 如申請專利範圍第19項之裝置，其特徵在於：該 等連接裝置(3)的其中一個裝置係適用於與一引擎軸相耦合 ，而不需要插入任何的啓動離合器。 26·如申請專利範圍第1項到第1〇項的其中一項之裝 置，其特徵在於：該等連接裝置(41)的其中一個連接裝置 本紙張尺度適用中國國家標準(CNS)A4規格(210 X 297公釐) 530015 頜 C8 ^ V (〇 fi ： _ D8 — 六、申請專利範圍 係連接到一提供至少兩比率的機構(302)。 27.如申gra專利範圍弟26項之裝置，其特徵在於：該 兩比率機構將一運動從一差動機構軸傳送至一第二平行軸 〇 28·如申請專利範圍第27項之裝置，其特徵在於該兩 比率機構包含： 兩旋轉地被安裝於一第一連接軸之上刻有齒的輪； 一具有兩副齒輪剛硬地安裝其上並具有不同直徑的第 二連接軸； 一以該第一軸選擇性地親合該等刻有齒的輪的其中一 輪的離合器； 一以第一軸耦合其它刻有齒的輪的單向離合器，當該 離合器不被作用時； 一與該單向離合器相平行的輔助離合器。 29. 如申請專利範圍第28項之裝置，其特徵在於：該 相關於一離合器刻有齒的輪具有軸向移動的可能性，使得 其齒反應參加該離合器的作動。 30. 如申請專利範圍第27項之裝置，其特徵在於：包 含一逆向驅動裝置，其曾經被一爪形離合器所作動，並選 擇性地繞過該差動機構和兩個比率機構。 31·如申請專利範圍第27項之裝置，其特徵在於：包 ；含一逆向驅動裝置，其曾經被一爪形離合器所作動，並選 擇性地繞過介於該差動機構的軸和該第二平行軸之間的兩 比率機構。 (請先閱讀背面之注意事項再塡寫本頁) 0 線！ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐）Between the scope of patent application, a fourth friction affinity device (209; 9) parallel to a table and one-way clutch (208; 8); and (Please read the precautions on the back before writing this page) A first inverter control device (211; 11) that coordinates the third and fourth coupling devices located between two stable states. In each stable state, the third and fourth coupling devices are individually One of the devices is engaged while the other is not engaged. 21. The device according to item 9 of the patent application, characterized in that the spring system is operatively installed between two inverter control devices. 22. The device according to claim 20, wherein the actuating device includes a controllable actuator operatively installed between the two inverter control devices. Line 23. The device according to item 20 of the scope of patent application, characterized in that the second inverter control device (211; 11) is subject to a tooth response thrust of the fourth element (6; 5), the The fourth element (6; 5) is installed for displacement under the action of tooth thrust. 24. The device according to item 19 of the scope of patent application, characterized in that the other element, through a fourth coupling device, can be connected to the fourth element for the most rotating use, and is the second element (2) . 25. The device according to item 19 of the patent application is characterized in that one of the connecting devices (3) is suitable for coupling with an engine shaft without inserting any starting clutch. 26. The device according to one of the items 1 to 10 of the scope of patent application, characterized in that one of the connecting devices (41) is connected to the Chinese paper standard (CNS) A4 ( 210 X 297 mm) 530015 Jaw C8 ^ V (〇fi: _ D8 — VI. The scope of patent application is connected to a mechanism that provides at least two ratios (302). It is characterized in that the two-ratio mechanism transmits a motion from a differential mechanism shaft to a second parallel axis. 28. The device according to item 27 of the patent application is characterized in that the two-ratio mechanism includes: A wheel with teeth engraved on a first connecting shaft; a second connecting shaft having two pairs of gears rigidly mounted thereon and having different diameters; a first shaft selectively engaging the cuts A clutch of one of the toothed wheels; a one-way clutch that couples other toothed wheels with the first shaft when the clutch is not activated; an auxiliary clutch that is parallel to the one-way clutch. 29. Such as Patent application scope The device according to item 28 is characterized in that the wheel engraved with teeth of a clutch has the possibility of axial movement, so that its teeth react to participate in the actuation of the clutch. It is characterized by including a reverse drive device that was once actuated by a claw clutch and selectively bypassing the differential mechanism and two ratio mechanisms. 31. The device according to item 27 of the scope of patent application is characterized by : Package; Contains a reverse drive that was once actuated by a claw clutch and selectively bypasses the two ratio mechanism between the axis of the differential mechanism and the second parallel axis. (Please read first (Notes on the back are reproduced on this page) 0 lines! This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) 六、申請專利範圍 ^ 32·如申請專利範圍第26項之裝置，其特徵在於：該 機構具有至少兩比率並且該等差動機構係沿著兩個不同的 平行軸(XI，X2)而安裝。 八33·如申請專利範圍第32項之裝置，其特徵在於：包 含一補充的連接元件，其與該兩比率機構同軸並與該差動 機構的連接元件相耦合，而另外一個連接元件則與該兩比 率機構相耦合，因此，該傳動裝置的輸入與輸出係同軸的 〇 34.如申g靑專利範圍第33項之裝置，其特徵在於：一 逆向驅動機構被安裝於該兩比率機構和該補充的連接元件 之間，逆向控制裝置被提供以作爲選擇性地作動該逆向驅 動裝置並聯合地解除該差動機構的作動。 35·如申請專利範圍第33項之裝置，其特徵在於：該 差動機構和該補充連接元件藉由選擇性爪形離合器裝置而 連接在一起，該爪形離合器使得該差動機構不是以若干向 則驅動比率ί呆作，就是以一逆向驅動比率來操作。 36·如申請專利範圍第32項之裝置，其特徵在於：該 機構具有至少兩比率(302)並且更提供一逆向驅動比率。 37. 如申請專利範圍第1項到第9項的其中一項之裝置 ，其特徵在於：其有一第一和一第二差動機構，該第二差 動機構係被連接至該第一機構的其中一個_接機構。申^ 專利 _ 38. 如申請專利範圍第37項之裝置，其特徵在於：在 該第二機構當中，該第二元件(330)係一連接元件，而該第 (請先閲讀背面之：/i意事項再填寫本頁) 二叮： 線' 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015 "屮々 i D8 六、申請專利範圍 (請先閲讀背面之注意事項再塡寫本頁) 三元件係一外殼元件（2)，該第二差動機構（302)的三個旋轉 元件所剩下的一個旋轉元件（360)被連接至該其它連接元件 (4)處。 39. 如申請專利範圍第38項之裝置，其特徵在於：該 第二機構的該第二元件係與第一機構(301)連接在一起的元 件。 40. 如申請專利範圍第38項之裝置，其特徵在於：該 第二機構(302)的該其它旋轉元件（370)係選擇性地可連接於 該連接元件（330)處，以便提供一直接向前驅動比率、選擇 性地一不同的向前驅動比率，或連接於該外殼元件（2)，以 便提供一逆向驅動比率。 41. 如申請專利範圍第38項之裝置，其特徵在於：該 兩比率機構係相對於穿過該傳動裝置的動力流動方向被放 置於該差動機構的上游處。 42. 如申請專利範圍第1項到第9項的其中一項之裝置 ，其特徵在於：該第二元件（330)係一連接元件，而第三元 件係一外殼元件（2)，該三個旋轉元件所剩下的旋轉元件 (360)被連接到其它的連接元件(4)處。 43. 如申請專利範圍第42項之裝置，其特徵在於：該 第二元件係爲該輸入連接元件（330)。 44. 如申請專利範圍第38項之裝置，其特徵在於：形 • 成該第二元件的連接元件（330)係更選擇性地可連接至該等 旋轉元件（370)的另外一個旋轉元件處。 45. 如申請專利範圍第38項之裝置，其特徵在於：該 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015 、 i 六、申請專利範圍 (請先閲讀背面之注意事項再塡寫本頁) 三個旋轉元件的所剩下的一旋轉元件係選擇性地被連接至 一逆向驅動裝置處。 46. 如申請專利範圍第42項之裝置，其特徵在於：該 其它的旋轉元件（370)係選擇性地可連接於連接元件（330)， 以便提供一直接向前驅動比率，和選擇性地提供一不同的 向前驅動比率，或連接於該外殼元件(2)，以便提供一逆向 驅動比率。 47. 如申請專利範圍第38項之裝置，其特徵在於：該 不同的向前驅動比率係一過驅動比率。 48. —種傳動裝置，其中一傳動機構包含： 一輸入旋轉連接元件（3)和一輸出旋轉連接元件(4) 至少兩個相對於該外殼元件爲可旋轉的並且至少非直 接相互嚙合的旋轉元件； 至少一在脫離時能在該傳動機構中提供一空檔狀態和 在嚙合狀態中提供一介於該兩個連接元件之間的動力傳送 關係的摩擦耦合裝置； 作動該摩擦耦合裝置的作動裝置，該作動裝置包含： 1) 兩個不相容的作動裝置，該兩個不相容的作動裝置 的至少其中之一係可控制的； 2) 該兩個相互嚙合的旋轉元件的至少其中之一的一軸 ^向可移動性，和將該相互嚙合旋轉元件的一軸向齒推力傳 送給該摩擦耦合裝置的一壓力元件的傳動裝置。 49. 如申請專利範圍第48項之裝置，其特徵在於：該 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015 ^(L· rf A8 B8 C8 D8 Θ二岑二二』《>ί ~ - _ ^ .. ________ 六、 :推=傳動裝置係一介於該等相互嚙合的旋轉元件的其中 個方疋轉元件和該壓力元件之間形成一體的連接。 5〇.如申請專利範圍第48項之裝置，意特徵在於：該 =!不相容裝置係被安裝，以便在-™ 力勺期間，反作用於該齒推力。 5ι.如申請專利範圍第48項之裝置，其特徵在於：該 ~Ί?工制的不相容裝置係被安裝，以便於在〜可引發運動的 動力的傳送期間，以相同於該齒推力的方向來作用。 52.如申請專利範圍第48項之裝置，其中，該作動裝 置包含一反作用於該可控制的不相容裝置的彈簧。 53·如申請專利範圍第48項之裝置，其特徵在於：該 輸入連接元件係永遠地被連接至一主移動器（1〇1)。 54·如申請專利範圍第48項之裝置，其特徵在於：該 壓力兀件（113)屬於一形成一體地攜帶另外〜個摩擦親合裝 置（9)的另外一個壓力元件（112)的一反向器控制元件（111) ’該反向器控制元件可在兩個終端位置之間移動，在每〜 個終端位置當中，各別地，該等親合裝置的一裝置係位於 嚙合狀態，而另外一個裝置則位於未嚙合狀態。 55. 如申請專利範圍第54項之裝置，其特徵在於：該 等摩擦耦合裝置的其中一個裝置係一與一操作地被安裝於 該傳動機構的兩元件之間的單向離合器相平行機械地被安: 裝的輔助稱合裝置。 56. 如申請專利範圍弟49項到第54項的其中一項之 裝置，其特徵在於：該至少一摩擦耦合裝置包含兩個此類 —10 (請先閲讀背面之注意事項再填寫本頁) 、一二口 線 本紙張尺度適用中國國家標準（CNS)A4規格(21〇 x 297公釐）6. The scope of patent application ^ 32. The device according to item 26 of the patent application scope is characterized in that the mechanism has at least two ratios and the differential mechanisms are installed along two different parallel axes (XI, X2) . 833. The device according to item 32 of the scope of patent application, characterized in that it includes a supplementary connection element coaxial with the two ratio mechanisms and coupled with the connection element of the differential mechanism, and the other connection element is The two ratio mechanisms are coupled. Therefore, the input and output of the transmission device are coaxial. The device of item 33 of the patent scope of claim g, characterized in that a reverse drive mechanism is installed on the two ratio mechanisms and Between the supplementary connecting elements, a reverse control device is provided to selectively actuate the reverse drive device and jointly deactivate the differential mechanism. 35. The device according to item 33 of the application for a patent, characterized in that the differential mechanism and the supplementary connecting element are connected together by a selective claw clutch device, which makes the differential mechanism not The direction-driven ratio is idle, which is to operate with a reverse-driven ratio. 36. The device according to item 32 of the scope of patent application, characterized in that the mechanism has at least two ratios (302) and further provides a reverse driving ratio. 37. The device according to any one of claims 1 to 9 of the scope of patent application, characterized in that it has a first and a second differential mechanism, and the second differential mechanism is connected to the first mechanism One of the _ access agencies. Applying for a patent _ 38. If the device in the 37th scope of the patent application is applied, it is characterized in that: in the second mechanism, the second element (330) is a connection element, and the (please read the first: / (I will fill in this page on the matter of interest) Erding: Line 'This paper size is applicable to China National Standard (CNS) A4 (210 X 297 mm) 530015 " 屮 々 i D8 VI. Patent Application Scope (Please read the Note that this page is rewritten) The three elements are a housing element (2), and the remaining one rotation element (360) of the three rotation elements of the second differential mechanism (302) is connected to the other connection element ( 4) place. 39. The device of claim 38, characterized in that the second component of the second mechanism is a component connected to the first mechanism (301). 40. The device of claim 38, characterized in that the other rotating element (370) of the second mechanism (302) is selectively connectable to the connecting element (330) so as to provide a direct Forward drive ratio, optionally a different forward drive ratio, or connected to the housing element (2) to provide a reverse drive ratio. 41. The device of claim 38, wherein the two ratio mechanism is placed upstream of the differential mechanism with respect to the direction of power flow through the transmission. 42. The device according to any one of claims 1 to 9 of the scope of patent application, characterized in that the second element (330) is a connection element, and the third element is a housing element (2), the three The remaining rotating elements (360) of each rotating element are connected to other connecting elements (4). 43. The device of claim 42 in the scope of patent application, characterized in that the second element is the input connection element (330). 44. The device in the scope of patent application No. 38 is characterized in that: the connecting element (330) forming the second element is more selectively connectable to another rotating element of the rotating elements (370) . 45. If the device of the scope of patent application is item 38, it is characterized in that the size of this paper is applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 530015, i 6. The scope of patent application (please read the back page first) (Note again on this page) The remaining one of the three rotating elements is selectively connected to a reverse drive. 46. The device according to item 42 of the patent application, characterized in that the other rotating element (370) is selectively connectable to the connecting element (330) so as to provide a direct forward driving ratio, and selectively A different forward drive ratio is provided or connected to the housing element (2) to provide a reverse drive ratio. 47. The device according to item 38 of the patent application is characterized in that the different forward drive ratio is an overdrive ratio. 48. A transmission device, wherein a transmission mechanism includes: an input rotary connection element (3) and an output rotary connection element (4) at least two rotations which are rotatable with respect to the housing element and at least indirectly mesh with each other Element; at least one friction coupling device capable of providing a neutral state in the transmission mechanism when disengaged and a power transmission relationship between the two connecting elements in an engaged state; an actuating device for actuating the friction coupling device The actuating device includes: 1) two incompatible actuating devices, at least one of the two incompatible actuating devices is controllable; 2) at least one of the two intermeshing rotating elements A one-axis axial movability, and a transmission for transmitting an axial tooth thrust of the intermeshing rotating element to a pressure element of the friction coupling device. 49. For the device in the scope of application for patent No. 48, it is characterized in that the paper size is applicable to Chinese National Standard (CNS) A4 (210 X 297 mm) 530015 ^ (L · rf A8 B8 C8 D8 Θ 二 cen 二Two "" > ί ~-_ ^ .. ________ VI: Push = Transmission is an integral connection between one of the square rotation elements and the pressure element between these intermeshing rotation elements. 5 If the device of the scope of patent application 48, the meaning is that the =! Incompatible device is installed so as to react to the tooth thrust during the-™ force spoon. 5ι. The device is characterized in that the incompatible work system is installed so as to act in the same direction as the thrust of the tooth during the transmission of the power that can cause motion. 52. If a patent is applied for The device of the scope item 48, wherein the actuating device includes a spring that reacts on the controllable incompatible device. 53. The device of the scope of the patent application item 48 is characterized in that the input connection element is forever Connected to a master 54. The device according to item 48 of the scope of patent application, characterized in that the pressure element (113) belongs to another pressure which integrally carries another ~ friction affinity device (9) An inverter control element (111) of the element (112) 'The inverter control element can be moved between two end positions, and in each of the end positions, individually, one of the affinity devices The device is in the engaged state and the other device is in the non-engaged state. 55. The device of the scope of application for patent No. 54 is characterized in that one of the friction coupling devices is operatively installed in one and one The one-way clutch between the two elements of the transmission mechanism is mechanically installed in parallel: an auxiliary closing device is installed. 56. For example, the device of one of the 49th to 54th patent applications, which is characterized by: The at least one friction coupling device contains two of these—10 (please read the precautions on the back before filling this page), and one or two lines. The paper size is applicable to the Chinese National Standard (CNS) A4 specification (21 × x297 mm). ) 530015 之摩擦耦合裝置。 (請先閲讀背面之注意事項再填寫本頁) 57·如申__嶋56項之赌，浦徵在於··該 麵此類摩擦親合裝置係可操作地安裝在該等連接元件的 :、中兀件和s亥互相嚙合旋轉元件的各別一元件之間，當 該兩個此類摩擦耦合裝置係同時處於未嚙合的狀態時，該 空檔狀態於是形成。 58·如申請專利範圍第57項之裝置，其中，兩個摩擦 耦口裝置被安裝於該等互相嚙合旋轉元件的該各別的一元 件和該輸入與輸出連接元件的同樣一元件之間。 59·如申請專利範圍第58項之裝置，其中，該同樣一 連接元件係該輸入連接元件。 線-」 6〇·如申請專利範圍第57項之裝置，其中，當兩個摩 擦耦合裝置係位於被嚙合的狀態當中，一更進一步的傳動 比率被提供。 61. 如申請專利範圍第6〇項之裝置，其中，該更進一 步的傳動比率係一直接驅動傳動比率，其中，動力透過該 等互相嚙合的旋轉元件被傳送，因此，在直接驅動期間， 齒推力被保持著。 62. 如申請專利範圍第56項之裝置，其特徵在於··該 兩個摩擦耦合裝置的每一個裝置的壓力元件（113, 213)係屬 '於一各別的反向器控制元件（111，211)，該反向器控制元件 (111，211)形成一體地攜帶一各別的其它摩擦耦合裝置(9)的 另外一個壓力元件（112)，每一個反向器控制元件在兩個極 ---u------一 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 六、申請專利範圍+ (請先閱讀背面之注意事項再塡寫本頁) 端位置係爲可移動的’在每個極端位置當中，該等耦[合裝 置的一各別的一個耦合裝置係位於嚙合狀態，而另外一個 則位於未嚙合狀態。 63. 如申請專利範圍第55項之裝置，其特徵在於包含 :一機械地與該單向離合器(8)相串連並以軸向可滑動性作 爲普通旋轉的裝置，在該單向離合器和兩元件之間，安裝 有輔助性耦合裝置並且該軸向可滑動性產生效果。 64. 如申請專利範圍第63項之裝置，其特徵在於：該 等作爲普通旋轉之用的裝置(52, 53; 252, 253; 352, 353)係 可操作地安裝於兩元件的其中一元件和一單向離合器支撐 (51; 251; 351)之間，並且其在該單向離合器支撐與該兩元 件的另外一個元件之間，以機械地平行該單向離合器（8; 208; 308)提供一輔助的不可滑動的軸承(54; 254; 354)。 65. 如申請專利範圍第64項之裝置，其特徵在於：該 等不相容裝置的其中一裝置安裝在該支撐之上。 66. 如申請專利範圍第48項到第54項的其中一項之 裝置，其特徵在於包含：一與該傳動機構相串連並提供至 少兩比率的第二機構。 67. 如申請專利範圍第68項之裝置’其特徵在於：該 第二機構包含逆向驅動裝置。 68. 如申請專利範圍第48項到第54項的其中〜項之 裝置，其特徵在於包含：一與該傳動機構相串連並具有逆 向驅動裝置的逆向驅動機構。 ____12_________^_ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐）530015 friction coupling device. (Please read the precautions on the back before filling out this page) 57 · If you apply for __ 嶋 56, Pu Zheng lies in: · This type of friction affinity device is operatively installed on these connecting elements: The neutral state and the middle element and the respective elements of the meshing rotation element are formed when the two such friction coupling devices are in an unmeshed state at the same time. 58. The device according to claim 57 in which two friction coupling devices are installed between the respective one of the intermeshing rotating elements and the same one of the input and output connecting elements. 59. The device according to claim 58 in which the same connection element is the input connection element. Line- "6〇 · As in the 57th patent application, a further transmission ratio is provided when the two frictional coupling devices are in the engaged state. 61. As for the device in the scope of patent application No. 60, wherein the further transmission ratio is a direct drive transmission ratio, wherein power is transmitted through the intermeshing rotating elements, therefore, during the direct drive, the tooth The thrust is maintained. 62. The device in the 56th scope of the patent application is characterized in that the pressure element (113, 213) of each of the two friction coupling devices belongs to a separate inverter control element (111 211), the inverter control element (111, 211) forms another pressure element (112) integrally carrying a respective other friction coupling device (9), each inverter control element is in two poles --- u ------ A paper size is applicable to China National Standard (CNS) A4 specification (210 X 297 mm) 6. Scope of patent application + (Please read the precautions on the back before writing this page) The end position is movable. In each extreme position, one of the coupling devices is in the engaged state and the other is in the unengaged state. 63. The device of the scope of application for patent No. 55 is characterized by comprising: a device mechanically connected in series with the one-way clutch (8) and using axial slidability as a normal rotation. Between the two elements, an auxiliary coupling device is installed and the axial slidability produces an effect. 64. The device in the scope of patent application No. 63 is characterized in that the devices (52, 53; 252, 253; 352, 353) used for ordinary rotation are operatively mounted on one of the two components And a one-way clutch support (51; 251; 351) and between the one-way clutch support and the other element of the two elements to mechanically parallel the one-way clutch (8; 208; 308) Provide an auxiliary non-sliding bearing (54; 254; 354). 65. The device according to item 64 of the patent application is characterized in that one of the incompatible devices is mounted on the support. 66. The device according to any one of claims 48 to 54 of the scope of patent application, characterized in that it comprises a second mechanism connected in series with the transmission mechanism and providing at least two ratios. 67. The device of claim 68, characterized in that the second mechanism includes a reverse drive device. 68. The device of any one of items 48 to 54 of the scope of application for a patent, characterized in that it comprises a reverse drive mechanism which is connected in series with the drive mechanism and has a reverse drive device. ____ 12 _________ ^ _ This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) 530015 69·如申請專利範圍第48項之裝置，其特徵在於：一 逆向驅動機構係可操作的以迴繞该弟一*機構，g亥逆向驅動 機構係與該傳動機構成連續。 7〇·如申請專利範圍第48項到第54項的其中一項之 裝置，其中： 該輸入連接裝置係永遠地連接該主移動器以便同時旋 轉； 該空檔狀態係一停車制動狀態； 該輸出旋轉元件係與一透過爪形離合器裝置將被驅動 的負載相連接。 71·如申請專利範圔第70項之裝置，其中該爪形離合 器裝置具有下列三狀態的功能： '-向前驅動和停車狀態； 一允許該負載自由旋轉的空檔狀態； 一逆向驅動狀態。 72·—種傳動裝置，其中一差動機構（1)包含： 一外殼元件(2); 一輸入旋轉連接元件(3)和一輸出旋轉連接元件(4); 兩個其相對於該外殼元件爲可旋轉的同軸嚙合(5, 6)元 件，其包含： 一太陽輪(5);和 一冠狀輪(6); 一支撐若干個與該太陽輪（5)和冠狀輪（6)相嚙合的行 星齒輪(72)的行星齒輪架元件(7); (請先閲讀背面之注意事項再塡寫本頁) 11 線 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015 :韶 ί〇 SI i ........—丨— ~ , ---—___ 六、申請專利範圍 該行星齒輪架(7)與輸出旋轉連接元件之間的連接裝置 y 該等同軸嚙合元件、外殼元件和輸入連接元件之間的 選擇性耦合裝置； 其特徵在於該選擇性耦合裝置包含： 一用於選擇性地耦合該太陽輪(5)於輸入連接元件和外 殼元件(2)之上的第一聚合結構； 一用於選擇性地耦合該冠狀輪(6)於輸入連接元件和外 殼元件之上的第二聚合結構； 因此提供： 一低比率，當該太陽輪被連接到輸入連接元件且該冠 狀輪被連接到外殼元件時； 一中間比率，當該太陽輪（5)被連接到外殼元件（2)且 g亥冠狀輪(6)被連接到輸入連接元件時； 一直接驅動比率，當該太陽輪（5)和冠狀輪同時被 連接到輸入連接元件時。 73.如申請專利範圍第72項之裝置，其特徵在於： 當該太陽輪(5)和冠狀輪(6)兩者被連接到外殼元件時，其提 供一空檔狀態。 74·如申請專利範圍第72項之裝置，其特徵在於：該 聚集結構的至少一結構包含： ； 在該相對應的同軸嚙合元件和外殼元件之間，一機械 地與一單向離合器(8)相平行的第一摩擦耦合裝置(9); 在該同軸嚙合元件和該輸入連接元件之間，操作地安 ----—__— 14_ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公爱） ----- (請先閲讀背面之注意事項再塡寫本頁) 釋 、1T.· 線530015 69. The device according to item 48 of the scope of patent application, characterized in that: a reverse drive mechanism is operable to rewind the brother * mechanism, and the ghai reverse drive mechanism is continuous with the drive. 70. The device according to any one of the 48th to 54th of the scope of patent application, wherein: the input connection device is permanently connected to the main mover for simultaneous rotation; the neutral state is a parking brake state; the The output rotation element is connected to a load to be driven through a claw clutch device. 71. The device according to item 70 of the patent application, wherein the claw clutch device has the functions of the following three states: '-forward driving and parking state; a neutral state allowing the load to rotate freely; a reverse driving state . 72 · —A transmission device, wherein a differential mechanism (1) includes: a housing element (2); an input rotary connection element (3) and an output rotary connection element (4); two opposite to the housing element Is a rotatable coaxial meshing (5, 6) element, which includes: a sun gear (5); and a crown wheel (6); a support for a plurality of meshing with the sun gear (5) and the crown wheel (6) Planetary carrier element (7) of the planetary gear (72); (Please read the precautions on the back before writing this page) 11 The size of the paper is applicable to China National Standard (CNS) A4 (210 X 297 mm) 530015: 邵 ί〇SI i ..............——————, ---——___ VI. Scope of patent application The connecting device between the planetary gear carrier (7) and the output rotation connecting element y etc. A selective coupling device between a coaxial engaging element, a housing element and an input connection element; characterized in that the selective coupling device comprises: a selective coupling device for selectively coupling the sun gear (5) to the input connection element and the housing element (2 ) Above the first polymer structure; a for selectively coupling the crown wheel (6) to the input A second polymeric structure above the connection element and the housing element; thus providing: a low ratio when the sun gear is connected to the input connection element and the crown wheel is connected to the housing element; an intermediate ratio when the sun gear ( 5) When connected to the housing element (2) and the g-crown wheel (6) is connected to the input connection element; a direct drive ratio when the sun wheel (5) and the crown wheel are connected to the input connection element at the same time. 73. The device of claim 72, characterized in that: when both the sun wheel (5) and the crown wheel (6) are connected to the housing element, it provides a neutral state. 74. The device according to item 72 of the scope of patent application, characterized in that at least one structure of the gathering structure includes :; between the corresponding coaxial engaging element and the housing element, a mechanical and a one-way clutch (8 ) The first friction coupling device (9) parallel to each other; between the coaxial engaging element and the input connecting element, the operation ground safety ---- ___ 14_ This paper size applies to China National Standard (CNS) A4 specifications ( 210 X 297 public love) ----- (Please read the precautions on the back before writing this page) Explanation, 1T. · Line 六、—申請專利範圍 530015 裝一第二摩擦耦合裝置（10)。 75. 如申請專利範圍第74項之裝置，其特徵在於：該 第一和第二摩擦耦合裝置由一介於雨穩定狀態之間的一反 向器控制裝置（11; 211; 311)所協調，在每一個穩定狀態當 中’各別地，該聚集結構的耦合裝置的其中一裝置係嚙合 著，而另外一個則未嚙合。 76. 如申請專利範圍第75項之裝置，其特徵在於：該 反向器控制裝置係一可在兩終端位置之間移動的普通壓力 兀件（11; 211; 3 11 )，該兩終端位置的每一個位置相對於該 等穩定狀態的其中一穩定狀態，且該普通壓力元件（11; 211; 311)上面被作動裝置所作動。 77·如申請專利範圍第75之裝置，其特徵在於：該反 向器控制裝置係與相對應的同軸嚙合元件(5; 6; 35〇)形成一 n 〇 5 78·如申請專利範圍第72項到第77項的其中一項之 裝置，其特徵在於：該等連接元件(6)的其中一元件係被連 接於一兩比率機構。 79.如申g靑專利範圍第78項之裝置，其特徵在於：該 兩比率的其中一個較低比率爲一直接驅動(74)。 80·如申請專利範圍第78項之裝置，其特徵在於：該 兩比率的其中一個較高比率爲一過驅動(75)。 81_如申請專利範圍第78項之裝置，其特徵在於提供 具有下列組合的六種排檔： 第一排檔：低比率和較低比率； _______ ________ 1S . 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐)'' -- (請先閲讀背面之注意事項再塡寫本頁) '1T: 線 1 ^^广….... .. /\S r, ΐ ν'--*· Γΐ- i C8 tki。/.! \i/u 5.:? ·Ί . D8 ： "ίίΠΏ 六¥平胥’專利:範请 第二排檔：低比率和較高比率； 第三排檔：中間比率和較低比率； (請先閲讀背面之注意事項再填寫本頁) 第四排檔：直接驅動和較低比率； 第五排檔：中間比率和較高比率； 第六排檔：直接驅動和較高比率。 82. 如申請專利範圍第72項到第77項的其中一項之 裝置，其特徵在於：行星齒輪架和輸出連接元件之間的連 接裝置包含一爪形離合器(44, 28; 91)，藉著該爪形離合器 (44, 28; 91)，該行星齒輪架能從該輸出連接元件(4; 42)處 脫離並連接到該外殼元件(2)處，另外一個爪形離合器(255; 92)允許從其相對應的聚集結構處釋放該等同軸嚙合元件 (6)的其中一元件，然後將其連接到該輸出連接元件(4; 42) ，以便提供一逆向驅動狀態。 83. —種傳動裝置，其包含： 一提供一低比率、一中間比率和一上比率的三速機構 ，其中該低比率與中間比率之間的一第一比率間隙至少約 爲該中間比率與上比率之間的一第二比率間隙的平方； 一與該二速機構串連安裝並提供一較低和較商比率的 兩速機構，該兩速機構在較低和較高比率之間具有一中間 於該第一和第二比率間隙的第三比率間隙， 其中藉由下列的組合提供六種排檔： J 第一排檔：低比率和較低比率； 第二排檔：低比率和較高比率； 第三排檔：中間比率和較低比率； ___ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） 530015 充 A8 B8 C8 D8 、申請專利範圍 第四排檔：上比率和較低比率； (請先閲讀背面之注意事項再填寫本頁) 第五排檔：中間比率和較高比率； 第六排檔：局比率和較局比率。 84. 如申請專利範圍第83項之裝置，其中，該三速機 構包含一行星齒輪系，其具有： 一外殼元件； 一輸入旋轉連接兀件； 一輸出旋轉連接元件； 一太陽輪； 一冠狀輪！ 一連接於該輸出旋轉連接元件並支撐著與該太陽輪和 冠狀輪相嚙合著的若干行星輪的行星齒輪架，並且其中， 藉著該作爲普通旋轉的太陽輪與輸入旋轉連接元件的 相連接，和該冠狀輪與外殼元件的相連接，該低比率被建 立起來； 藉著將該作爲普通旋轉的冠狀輪與該輸入旋轉連接元 件的相連接，和該太陽輪與外殼元件的相連接，該中間比 率被建立起來； 藉著將該作爲普通旋轉之用的冠狀輪和太陽輪與該輸 入旋轉連接元件相連接，該上比率被建立起來。 85. —種傳動裝置，其中一傳動機構包含： 一輸入旋轉連接元件(3)和一輸出旋轉連接元件(4); 至少兩個相對於該外殼元件爲可旋轉的並且至少非直 接相互嚙合的旋轉元件； _17_ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 297公釐） A86. Application scope 530015 A second friction coupling device (10) is installed. 75. The device according to item 74 of the scope of patent application, characterized in that the first and second friction coupling devices are coordinated by an inverter control device (11; 211; 311) between the rain steady state, In each stable state 'respectively, one of the coupling means of the gathering structure is engaged and the other is not engaged. 76. The device in the scope of patent application No. 75, characterized in that the inverter control device is a common pressure element (11; 211; 3 11) that can be moved between two terminal positions, and the two terminal positions Each position of is relative to one of the stable states, and the ordinary pressure element (11; 211; 311) is actuated by an actuating device. 77. The device according to the scope of patent application 75, characterized in that the inverter control device is formed with a corresponding coaxial meshing element (5; 6; 35〇). The device according to any one of items 77 to 77, wherein one of the connecting elements (6) is connected to a one-to-two ratio mechanism. 79. The device of claim 78, characterized in that one of the lower ratios is a direct drive (74). 80. The device according to item 78 of the scope of patent application, characterized in that one of the two ratios is a higher drive ratio (75). 81_ The device according to item 78 of the scope of patent application is characterized by providing six types of gears with the following combinations: The first gear: low ratio and low ratio; _______ ________ 1S. This paper standard applies to Chinese National Standard (CNS) A4 Specifications (210 X 297 mm) ''-(Please read the notes on the back before writing this page) '1T: 线 1 ^^ 广… .... .. / \ S r, ΐ ν'- -* · Γΐ- i C8 tki. /.! \ i / u 5.:? · Ί. D8: " ίίΠΏ 六 ¥ 平 胥 'Patent: Fan please second gear: low ratio and higher ratio; third gear: middle ratio and lower ratio; (Please read the notes on the back before filling out this page.) Fourth gear: direct drive and lower ratio; fifth gear: middle and higher ratio; sixth gear: direct drive and higher ratio. 82. The device according to one of the items 72 to 77 of the scope of patent application, characterized in that the connecting device between the planetary gear carrier and the output connecting element includes a claw clutch (44, 28; 91). With the claw clutch (44, 28; 91), the planetary gear carrier can be disengaged from the output connection element (4; 42) and connected to the housing element (2), and another claw clutch (255; 92 ) Allows one of the coaxial engaging elements (6) to be released from its corresponding gathering structure, and then connected to the output connecting element (4; 42) to provide a reverse driving state. 83. A transmission device comprising: a three-speed mechanism providing a low ratio, an intermediate ratio, and an upper ratio, wherein a first ratio gap between the low ratio and the intermediate ratio is at least about the intermediate ratio and The square of a second ratio gap between upper ratios; a two-speed mechanism installed in series with the two-speed mechanism and providing a lower and more competitive ratio, the two-speed mechanism having between the lower and higher ratios A third ratio gap between the first and second ratio gaps, in which six gears are provided by the following combination: J first gear: low ratio and lower ratio; second gear: low ratio and higher ratio The third gear: the middle ratio and the lower ratio; ___ This paper size is applicable to the Chinese National Standard (CNS) A4 specification (210 X 297 mm) 530015 A8 B8 C8 D8, the patent application scope fourth gear: upper ratio and comparison Low ratio; (Please read the notes on the back before filling out this page) Fifth gear: intermediate ratio and higher ratio; sixth gear: ratio of rounds and ratio of rounds. 84. The device as claimed in claim 83, wherein the three-speed mechanism includes a planetary gear train having: a housing element; an input rotary connection element; an output rotary connection element; a sun gear; a crown wheel! A planetary gear carrier connected to the output rotary connection element and supporting a plurality of planetary gears meshing with the sun gear and the crown wheel, and wherein the sun gear as a normal rotation is connected with the input rotary connection element And the connection between the crown wheel and the casing element, the low ratio is established; by connecting the crown wheel as a normal rotation with the input rotation connection element, and the connection between the sun wheel and the casing element, The intermediate ratio is established; the upper ratio is established by connecting the crown wheel and the sun wheel for ordinary rotation with the input rotation connection element. 85. A transmission device, wherein a transmission mechanism includes: an input rotary connection element (3) and an output rotary connection element (4); at least two are rotatable relative to the housing element and at least indirectly mesh with each other Rotating element; _17_ This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) A8 六、申請專利範圍 530015 至少兩摩擦耦合裝置，每個摩擦耦合裝置當處於一嚙 合狀態時能以一各別的傳動比率在該兩連接元件之間提供 一各別的動力傳送關係； ^ 用於作動該摩擦耦合裝置的不相容作動裝置，該作動 裝置包含至少一可控制不相容作動裝： 其中，當兩摩擦耦合裝置係處於一彼此脫離狀態 時，在該傳動機構中實現一空檔狀態。 86. 如申請專利範圍第85項之裝置，其中，兩個摩擦 耦合裝置被安裝於該等互相嚙合旋轉元件的該各別的一元 件和g亥輸入與輸出連接兀件的同樣—^元件之間。 87. 如申請專利範圍第86項之裝置，其中，該同樣一 連接兀件係該輸入連接兀件。 88·如申請專利範圍第85項之裝置，其中，當兩個摩 擦耦合裝置係位於被嚙合的狀態當中，一更進一步的傳動 比率被提供。 89·如申請專利範圍第88項之裝置，其中，該更進一 步的傳動比率係一直接驅動傳動比率，其中，動力透過該 等互相嚙合的旋轉元件被傳送，因此，在直接驅動期間， 齒推力被保持著。 9〇·如申請專利範圍第85項之裝置，其特徵在於：該 其它摩擦耦合裝置的至少一摩擦耦合裝置係一與一操作地 ^被安裝於該傳動機構的兩元件之間的單向離合器相平行機 械地被安裝的輔助的耦合裝置。 91.如申請專利範圍第90項之裝置，其特徵在於包含 ______________ 度適用中國國家標準（CNS)A4規格(210 X 297公釐) ^ ' (請先閱讀背面之注意事項再塡寫本頁)Sixth, the scope of application for patents 530015 At least two friction coupling devices, each friction coupling device can provide a separate power transmission relationship between the two connecting elements with a respective transmission ratio when in an engaged state; ^ used for An incompatible actuation device for actuating the friction coupling device, the actuation device includes at least one controllable incompatible actuation device: wherein when the two friction coupling devices are in a disengaged state from each other, a neutral position is achieved in the transmission mechanism status. 86. As for the device under the scope of patent application No. 85, in which two friction coupling devices are installed on the respective one of the intermeshing rotating elements and the same input-output connecting element of the helical input-output element. between. 87. The device according to item 86 of the application, wherein the same connection element is the input connection element. 88. The device as claimed in claim 85, wherein, when the two frictional coupling devices are in the engaged state, a further transmission ratio is provided. 89. The device according to item 88 of the scope of patent application, wherein the further transmission ratio is a direct drive transmission ratio, in which power is transmitted through the intermeshing rotating elements. Therefore, during direct driving, the tooth thrust Be kept. 90. The device according to item 85 of the scope of patent application, characterized in that at least one friction coupling device of the other friction coupling device is a one-way clutch operatively installed between two elements of the transmission mechanism. Auxiliary couplings installed mechanically in parallel. 91. The device under the scope of patent application of item 90 is characterized in that it contains ______________ degrees applicable to China National Standard (CNS) A4 specifications (210 X 297 mm) ^ '(Please read the precautions on the back before writing this page ) 530015 •一機械地與該單向離合器（8)相串連並以軸向可滑動性作 爲普通旋轉的裝置’在該單向離合器和兩元件之間，安裝 有輔助性耦合裝置並且該軸向可滑動性產生效果。 92.如申請專利範圍第91項之裝置，其特徵在於：該 等作爲普通旋轉之用的裝置(5;2, 53; 252, M3; 3U，353)係 可操作地安裝於兩元件的其中一元件和一單向離合器支撐 (51; 251; 351)之間’並且其在該單向離合器支撐與該兩元 件的另外一個元件之間，以機械地平行該單向離合器（8; 208; 308)提供一輔助的不可滑動的軸承(54; 254; 354)。 93·如申請專利範圍第92項之裝置，其特徵在於：該 等不相容裝置的其中一裝置安裝在該支撐之上。 94·如申請專利範圍第85項到第93項的其中一項之 裝置’其特徵在於包含：一與該傳動機構相串連並提供至 少兩比率的第二機構。 95·如申請專利範圍第94項之裝置，其特徵在於：該 第二機構包含逆向驅動裝置。 96. 如申請專利範圍第85項到第93項的其中一項之 裝置，其特徵在於包含：一與該傳動機構相串連並具有逆 向驅動裝置的逆向驅動機構。 97. 如申請專利範圍第96項之裝置，其特徵在於：一 逆向驅動機構係可操作的以迴繞該第二機構，該逆向驅動 ^機構係與該傳動機構成連續。 98. 如申g靑專利範圍第85項到第93項的其中一項之 裝置，其中： ------------ 1Q___ 本紙張尺度適用中國國家標準（CNS)A4規格(210 X 2^7公釐) -- (請先閲讀背面之注意事項再塡寫本頁) 、言 線 530015 MM- A8 B8 C8 D8 申請專利範圍 該輸入連接裝置係永遠地連接該主移動器以便同時旋 (請先閲讀背面之注意事項再塡寫本頁) 轉； 該空檔狀態係一停車制動狀態； 該輸出旋轉元件係與一透過爪形離合器裝置將被驅動 的負載相連接。 99.如申請專利範圍第98項之裝置，其中該爪形離合 器裝置具有下列三狀態的功能： 一向前驅動和停車狀態； 一允許該負載自由旋轉的空檔狀態； 一逆向驅動狀態。 20 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐）530015 • A device that is mechanically connected in series with the one-way clutch (8) and uses axial slidability as a normal rotation. 'Auxiliary coupling device is installed between the one-way clutch and the two elements and the axial direction Slippery effect. 92. The device according to item 91 of the scope of patent application, characterized in that these devices for ordinary rotation (5; 2, 53; 252, M3; 3U, 353) are operatively installed in the two elements Between an element and a one-way clutch support (51; 251; 351) 'and between the one-way clutch support and the other element of the two elements to mechanically parallel the one-way clutch (8; 208; 308) Provide an auxiliary non-sliding bearing (54; 254; 354). 93. The device according to item 92 of the scope of patent application, characterized in that one of the incompatible devices is mounted on the support. 94. The device of one of the items 85 to 93 of the scope of patent application 'is characterized by including a second mechanism connected in series with the transmission mechanism and providing at least two ratios. 95. The device according to claim 94, wherein the second mechanism includes a reverse drive device. 96. The device according to any one of claims 85 to 93 of the scope of patent application, characterized in that it comprises a reverse drive mechanism which is connected in series with the drive mechanism and has a reverse drive device. 97. The device according to the scope of application for patent item 96 is characterized in that: a reverse drive mechanism is operable to wind the second mechanism, and the reverse drive mechanism is continuous with the drive. 98. If you apply for one of the items in the 85th to 93rd patent scope, where: ------------ 1Q___ This paper size applies to China National Standard (CNS) A4 specifications ( 210 X 2 ^ 7 mm)-(Please read the precautions on the back before writing this page), speech line 530015 MM- A8 B8 C8 D8 patent application scope The input connection device is always connected to the main mover in order to Rotate at the same time (please read the precautions on the back before writing this page). The neutral state is a parking brake state. The output rotation element is connected to a load to be driven through a claw clutch device. 99. The device according to item 98 of the patent application scope, wherein the claw clutch device has the functions of the following three states: a forward driving and parking state; a neutral state allowing the load to freely rotate; a reverse driving state. 20 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm)
TW090128455A 2000-11-17 2001-11-16 Transmission devices, for ground vehicles and more particularly for motors-cars TW530015B (en)

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EA003825B1 (en) 2003-10-30
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WO2002040900A9 (en) 2002-09-19
CA2407598A1 (en) 2002-05-23
PL360256A1 (en) 2004-09-06
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MXPA02010721A (en) 2003-05-14
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AR031466A1 (en) 2003-09-24
BR0107665A (en) 2002-11-12
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AU2002237222A1 (en) 2002-05-27
KR20020070482A (en) 2002-09-09

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