TWI799189B - Improved speed change mechanism - Google Patents

Abstract

本創作包括相平行的傳動軸和換檔凸輪軸，以及相連結的複合行星齒輪組、兩同步組件、離合組及兩離合致動組。其中，兩同步組件結合於換檔凸輪軸，且能由換檔凸輪軸控制、沿著換檔凸輪軸活動，進而控制傳動軸和複合行星齒輪組的連結與否。離合組設有兩離合組件，兩離合致動組結合換檔凸輪軸及離合組，且能由換檔凸輪軸控制兩離合組件沿著傳動軸活動，進而控制複合行星齒輪組。本創作沿著相平行的傳動軸和換檔凸輪軸來控制換檔，能減小變速機構的體積，解決現有變速裝置體積大的問題，提供一種結構簡潔、緊湊、體積小且節能的改良型變速機構。The creation includes parallel propshafts and shift camshafts, as well as a connected compound planetary gear set, two synchronizing assemblies, a clutch set and two clutch actuation sets. Wherein, the two synchronous components are combined with the shift camshaft, and can be controlled by the shift camshaft, move along the shift camshaft, and then control whether the transmission shaft and the compound planetary gear set are connected or not. The clutch group is provided with two clutch components, the two clutch actuation groups are combined with the shift camshaft and the clutch group, and the shift camshaft can control the two clutch components to move along the transmission shaft, thereby controlling the compound planetary gear set. This invention controls gear shifting along the parallel transmission shaft and shifting camshaft, which can reduce the volume of the speed change mechanism, solve the problem of large volume of the existing speed change device, and provide an improved type with simple structure, compact size, small volume and energy saving. speed change mechanism.

Description

改良型變速機構Improved speed change mechanism

本創作係涉及一種變速裝置，尤其是指一種體積小、結構簡潔，還能減少耗能的改良型變速機構。 The invention relates to a speed change device, in particular to an improved speed change mechanism with small volume, simple structure and reduced energy consumption.

在車輛行駛的過程中，會需要不同的動力來因應不同的路況。例如，在車輛爬坡時就需要轉速較低的低速檔；而在平坦的道路上行駛時，就需要轉速高的高速檔。因此，為了得到不同的動力，車輛需要裝配變速裝置與驅動裝置配合，來變換不同的檔位。 During the driving process of the vehicle, different power is required to cope with different road conditions. For example, when the vehicle is climbing a hill, a low speed gear with a low speed is required; when driving on a flat road, a high speed gear with a high speed is required. Therefore, in order to obtain different power, the vehicle needs to be equipped with a speed change device to cooperate with the drive device to change different gear positions.

一種現有的變速裝置包括有輸入軸、輸出軸及中間軸之外，還包括有與排檔桿相連結的數個排檔軸，排檔軸的數量係因應檔位的數量來設置。其中，輸入軸、輸出軸，以及中間軸設有相嚙合的多數個齒輪。各排檔軸則設有套置於輸出軸的同步器。使用者操作排檔桿來選擇對應不同檔位的排檔軸，且以排檔軸上所設的同步器來連結輸出軸與中間軸，藉此來輸出不同的動力。 A conventional speed change device includes, besides an input shaft, an output shaft and an intermediate shaft, several gear shafts connected with a gear lever. The number of gear shafts is set according to the number of gear positions. Wherein, the input shaft, the output shaft, and the intermediate shaft are provided with a plurality of meshing gears. Each gear shaft is provided with a synchronizer sleeved on the output shaft. The user operates the gear lever to select the gear shaft corresponding to different gear positions, and uses the synchronizer provided on the gear shaft to connect the output shaft and the intermediate shaft, thereby outputting different powers.

然而，現有的變速裝置除了輸入軸、輸出軸及中間軸，還需要因應檔位的數量來設置排檔軸。因此，現有的變速裝置在結構上較為不緊密，且體積大而不適用於裝設空間較小的車輛。除此之外，現有的自動變速裝置多採用電子液壓控制系統來進行檔位的切換，為了維持電子液壓控制系統正常地持續運作，需要持續地耗費能量維持一定的液壓，而有耗能的問題。由此可知，現有的變速裝置在結構上實有進步與改良的空間。 However, in addition to the input shaft, the output shaft and the intermediate shaft, the existing transmission device also needs to set a gear shaft according to the number of gear positions. Therefore, the existing transmission device is less compact in structure, and has a large volume and is not suitable for vehicles with small installation space. In addition, the existing automatic transmission devices mostly use the electronic hydraulic control system to switch gears. In order to maintain the normal and continuous operation of the electronic hydraulic control system, it is necessary to continuously consume energy to maintain a certain hydraulic pressure, and there is a problem of energy consumption. . It can be seen from this that the existing transmission device has room for progress and improvement in structure.

為了解決現有變速裝置體積大而不適用於體積小之車輛的問題。本創作提供一種改良型變速機構，其結構精簡、緊湊且又採用電子配合機構的型式來控制換檔，無須持續維持液壓，而只有在換檔時才需要耗能，因而能達到縮小體積和減少耗能的目的。 In order to solve the problem that the existing speed change device has a large volume and is not suitable for vehicles with small volume. This creation provides an improved transmission mechanism, which has a simplified and compact structure and uses an electronic coordination mechanism to control gear shifting. It does not need to maintain hydraulic pressure continuously, but only consumes energy when shifting gears. purpose of energy consumption.

本創作解決技術問題所提出的改良型變速機構，其包括：一傳動軸，其係能受驅動而旋轉；一換檔凸輪軸，其與該傳動軸相平行且能受驅動而旋轉，該換檔凸輪軸包括有一軸體及兩同步凸輪槽，各該同步凸輪槽環設於該軸體，且兩該同步凸輪槽間隔地設置；一複合行星齒輪組，其能與該傳動軸相連結且能受該傳動軸驅動而作動；兩同步組件，兩該同步組件能與該複合行星齒輪組相連結且分別結合於兩該同步凸輪槽，兩該同步組件能分別受兩該同步凸輪槽所驅動而沿著該換檔凸輪軸往復活動；一離合組，其包括有一中央導引座及兩離合組件；該中央導引座係用於固結於一離合器轂且包括有一套管部及兩離合凸輪段；該套管部呈圓管狀、包括有一軸向，以及於該套管部之軸向上位置相對的兩端，且該套管部同軸地套設於該傳動軸；各該離合凸輪段環設於該套管部的外周面且包括有一推抵曲面，兩該離合凸輪段的推抵曲面分別朝向該套管部的兩端；各該離合組件包括有多數個離合件，各該離合件與該套管部同軸設置、能沿著該套管部的軸向往復活動且與該複合行星齒輪組相連結；以及兩離合致動組，各該離合致動組包括有一驅動齒輪及一致動件；該驅動齒輪結合於該換檔凸輪軸且能隨著該換檔凸輪軸旋轉； 該致動件呈環狀、能轉動地套設於該套管部，且包括有與該驅動齒輪相嚙合的一致動環齒輪，該致動環齒輪的側面間隔地環設有多數個致動抵部；兩該離合致動組之兩致動件的兩致動環齒輪分別以所設的致動抵部抵靠於兩該離合凸輪段，兩該致動環齒輪能受兩該離合凸輪段所推抵，而使兩該致動件於沿著該套管部活動、推抵兩該離合組件。 The improved transmission mechanism proposed by this invention to solve technical problems includes: a transmission shaft, which can be driven to rotate; a shift camshaft, which is parallel to the transmission shaft and can be driven to rotate. The gear camshaft includes a shaft body and two synchronous cam grooves, each of the synchronous cam groove rings is set on the shaft body, and the two synchronous cam grooves are arranged at intervals; a compound planetary gear set, which can be connected with the transmission shaft and Can be driven by the transmission shaft; two synchronous components, the two synchronous components can be connected with the compound planetary gear set and respectively combined with the two synchronous cam slots, and the two synchronous components can be respectively driven by the two synchronous cam slots And move back and forth along the shift camshaft; a clutch group, which includes a central guide seat and two clutch assemblies; the central guide seat is used to be fixed on a clutch hub and includes a sleeve part and two clutch assemblies Cam segment; the sleeve portion is in the shape of a circular tube, including an axial direction, and two ends opposite to the axial direction of the sleeve portion, and the sleeve portion is coaxially sleeved on the transmission shaft; each of the clutch cam segments The ring is arranged on the outer peripheral surface of the sleeve part and includes a push-off curved surface, and the push-off curved surfaces of the two clutch cam segments are respectively facing the two ends of the sleeve part; each clutch assembly includes a plurality of clutch parts, and each clutch The component is arranged coaxially with the casing part, can reciprocate along the axial direction of the casing part and is connected with the compound planetary gear set; and two clutch actuation groups, each of which includes a driving gear and a consistent moving part; the drive gear is combined with the shift camshaft and can rotate with the shift camshaft; The actuating member is ring-shaped, rotatably sheathed on the sleeve part, and includes an actuating ring gear meshed with the driving gear. The side of the actuating ring gear is provided with a plurality of actuating Reach portion; the two actuation ring gears of the two actuating parts of the two clutch actuation groups respectively abut against the two clutch cam sections with the set actuation actuation portions, and the two actuation ring gears can be supported by the two clutch cams Pushed by the section, so that the two actuators move along the sleeve part and push against the two clutch components.

所述之改良型變速機構，其中各所述之離合凸輪段的推抵曲面間隔地設有多數個離合致動區，各該離合致動區包括有多數個致動凸部。 In the above-mentioned improved speed change mechanism, a plurality of clutch actuation areas are arranged at intervals on the pushing curved surface of each of the clutch cam segments, and each clutch actuation area includes a plurality of actuation protrusions.

所述之改良型變速機構，其中各所述之離合致動區包括有兩致動凸部，以及位於兩該致動凸部間的限制凹部。 In said improved speed change mechanism, each said clutch actuating area includes two actuating protrusions, and a limiting recess located between the two actuating protrusions.

所述之改良型變速機構，其中各所述之致動件包括有一抵靠環及多數個緩衝彈性件；該抵靠環同軸地與該致動件的致動環齒輪藉由多數個定位件相結合；該多數個緩衝彈性件介於該致動環齒輪與該抵靠環之間、分別套置於該多數個定位件，且各該緩衝彈性件的兩端分別抵靠於該致動環齒輪與該抵靠環。 Said improved transmission mechanism, wherein each said actuating member includes an abutment ring and a plurality of buffer elastic members; the abutment ring is coaxial with the actuating ring gear of the actuating member through a plurality of positioning members Combined; the plurality of buffer elastic members are interposed between the actuating ring gear and the abutment ring, respectively sleeved on the plurality of positioning members, and the two ends of each of the buffer elastic members respectively abut against the actuating ring The ring gear comes with this abutment ring.

所述之改良型變速機構，其中所述之中央導引座包括有兩輔助導溝，兩該輔助導溝分別靠近該中央導引座之套管部的兩端，各該輔助導溝凹設於該套管部的外周面且波浪起伏地環繞該套管部；各所述致動件的致動環齒輪於於內周緣間隔地環設有多數個導引凸部，兩所述致動件之兩致動環齒輪分別以所設的導引凸部插置於該套管部的兩輔助導溝。 Said improved speed change mechanism, wherein said central guide seat includes two auxiliary guide grooves, the two auxiliary guide grooves are respectively close to the two ends of the bushing part of the central guide seat, and each of the auxiliary guide grooves is recessed On the outer peripheral surface of the casing part, the casing part is undulatingly surrounded; the actuating ring gear of each actuating member is provided with a plurality of guiding convex parts at intervals on the inner peripheral edge, and the two actuating parts The two actuating ring gears of the component are respectively inserted into the two auxiliary guide grooves of the sleeve part with the set guide protrusions.

所述之改良型變速機構，其中各所述之離合件包括有同軸設置的一卡制環及一摩擦環；該摩擦環的兩平面粗糙，且其外徑小於該卡制環的外徑。 Said improved transmission mechanism, wherein each of said clutch parts includes a snap ring and a friction ring arranged coaxially; the two planes of the friction ring are rough, and its outer diameter is smaller than that of the snap ring.

所述之改良型變速機構，其中各所述之離合件包括有一波形彈簧；該離合件的波形彈簧與該離合件的卡制環和摩擦環同軸設置；各所述離合組件的多數個離合件以所設的波形彈簧相抵靠。 Said improved transmission mechanism, wherein each of said clutch parts includes a wave spring; the wave spring of said clutch part is arranged coaxially with the snap ring and friction ring of said clutch part; Against each other with the provided wave spring.

所述之改良型變速機構，其包括有一駐車組，所述之駐車組包括有一駐車凸輪及一駐車爪；該駐車凸輪結合於所述換檔凸輪軸的軸體且能推抵該駐車爪，使該駐車爪與所述複合行星齒輪組所設之輸出環齒輪的駐車卡制口相卡制。 The improved transmission mechanism includes a parking group, the parking group includes a parking cam and a parking pawl; the parking cam is combined with the shaft body of the shift camshaft and can push against the parking pawl, The parking pawl is locked with the parking locking opening of the output ring gear provided by the compound planetary gear set.

所述之改良型變速機構，其包括有一驅動組，該驅動組包括有一馬達、一蝸桿、一蝸輪及一驅動齒輪；該蝸桿結合於該馬達的馬達軸而能受該馬達所驅動；該蝸輪和該驅動齒輪同軸地設置且能同步旋轉，該蝸輪與該蝸桿相嚙合；所述換檔凸輪軸包括有同軸地設於所述軸體的一從動齒輪，該驅動齒輪與該從動齒輪相嚙合。 The improved transmission mechanism includes a driving group, the driving group includes a motor, a worm, a worm gear and a driving gear; the worm is combined with the motor shaft of the motor and can be driven by the motor; the worm gear Set coaxially with the driving gear and can rotate synchronously, the worm gear is meshed with the worm; the shift camshaft includes a driven gear coaxially arranged on the shaft body, the driving gear and the driven gear Mesh.

本創作的技術手段可獲得的功效增進在於： The effect enhancement that the technical means of this creation can obtain is:

1.本創作設有相平行的傳動軸和換檔凸輪軸，兩同步組件結合於換檔凸輪軸，且能由換檔凸輪軸控制、沿著換檔凸輪軸活動，進而控制傳動軸和複合行星齒輪組是否連結。兩離合致動組結合換檔凸輪軸及離合組，且能由換檔凸輪軸控制兩離合組件沿著傳動軸活動，進而控制複合行星齒輪組。本創作沿著相平行的傳動軸和換檔凸輪軸來控制換檔，能減小體積又無須耗費能量持續維持液壓，使本創作的結構更為簡潔、更為緊湊也更為節能。 1. This creation is equipped with a parallel transmission shaft and shift camshaft, and the two synchronous components are combined with the shift camshaft, and can be controlled by the shift camshaft, move along the shift camshaft, and then control the transmission shaft and compound Whether the planetary gear set is connected. The two clutch actuating groups are combined with the shift camshaft and the clutch group, and the shift camshaft can control the two clutch assemblies to move along the transmission shaft, thereby controlling the compound planetary gear set. This creation controls gear shifting along the parallel transmission shaft and gear shift camshaft, which can reduce the volume without consuming energy to maintain hydraulic pressure continuously, making the structure of this creation simpler, more compact and more energy-saving.

2.本創作之各致動件的致動環齒輪與抵靠環之間設有多數個緩衝彈性件，能夠在致動件推抵離合組件時提供緩衝及預壓，確保離合組件動作時抵靠環抵靠多數個離合件提供一預壓夾緊功能，避免多數個離合件的卡制環和摩擦環產生滑差。 2. There are many cushioning elastic parts between the actuating ring gear and the abutting ring of each actuating part of this invention, which can provide buffer and preload when the actuating part pushes against the clutch assembly, ensuring that the clutch assembly is in contact with the clutch assembly when it moves. The backing ring provides a preload clamping function against the plurality of clutch parts, so as to avoid slipping between the locking ring and the friction ring of the plurality of clutch parts.

3.本創作之各致動件的致動環齒輪設有導引凸部，且各致動件的致動環齒輪以所設的導引凸部插置於該套管部的輔助導溝，使各致動件能穩定且平順地相對中央導引座的套管部旋轉及活動，使離合致動組精確驅使離合組件往復作動。 3. The actuation ring gears of each actuator in this invention are provided with guide protrusions, and the actuation ring gears of each actuator are inserted into the auxiliary guide groove of the casing part with the provided guide protrusions , so that each actuator can stably and smoothly rotate and move relative to the sleeve part of the central guide seat, so that the clutch actuator group can accurately drive the clutch assembly to reciprocate.

4.本創作之離合組件的各離合件設有波形彈簧；離合組件未作動時，離合組件的多數個離合件以所設的波形彈簧相抵靠。各離合件所設的波形彈簧強制使相鄰兩離合件的卡制環與摩擦環脫離，而能避免離合組件無預期地作動。 4. Each clutch part of the clutch assembly of this invention is provided with a wave spring; when the clutch assembly is not actuated, the plurality of clutch parts of the clutch assembly lean against each other with the provided wave springs. The wave springs provided on each clutch part forcibly disengage the clamping rings and friction rings of two adjacent clutch parts, so as to prevent the clutch assembly from actuating unexpectedly.

5.本創作的驅動組係利用馬達驅動蝸桿，進而帶動蝸輪、驅動齒輪和從動齒輪旋轉，能夠利用蝸桿與蝸輪之間的自鎖特性，使本創作在不同的檔位都無需耗費能量來達到鎖定的功能。 5. The driving group of this creation uses a motor to drive the worm, and then drives the worm gear, driving gear and driven gear to rotate. It can use the self-locking characteristics between the worm and the worm gear, so that this creation does not need to consume energy to operate in different gears. to achieve the locked function.

10:傳動軸 10: Drive shaft

11:輸入件 11: Input piece

111:輸入端 111: input terminal

12:行星架傳動件 12:Planet carrier transmission parts

121:卡掣齒輪部 121: Buckle gear part

122:行星架卡掣段 122:Planet carrier locking section

13:小太陽齒輪傳動件 13: Small sun gear transmission part

131:小太陽齒輪卡掣段 131:Small sun gear locking section

14:連接件 14:Connector

141:卡掣齒部 141: locking teeth

142:容槽 142: storage tank

15:單向離合器 15: One-way clutch

16:大太陽齒輪傳動件 16: Big sun gear transmission part

161:大太陽齒輪卡合部 161: large sun gear engaging part

162:卡掣部 162: locking part

163:離合卡制溝 163: Clutch card groove

17:連結件 17: link

20:換檔凸輪軸 20: Shift camshaft

21:軸體 21: Shaft body

22A:第一同步凸輪槽 22A: The first synchronous cam groove

22B:第二同步凸輪槽 22B: Second synchronous cam groove

23:從動齒輪 23: driven gear

24:齒輪卡掣段 24: gear locking section

30:複合行星齒輪組 30: compound planetary gear set

31:行星架 31:Planet carrier

311:傳動件卡掣部 311: The locking part of the transmission part

312:卡制齒部 312: clamping gear

32:大太陽齒輪 32: Big sun gear

321:傳動件卡合部 321: The engaging part of the transmission part

33:小太陽齒輪 33:Small sun gear

34:短軸行星齒輪 34: Minor axis planetary gear

35:長軸行星齒輪 35:Long shaft planetary gear

36:輸出環齒輪 36: Output ring gear

361:駐車卡制口 361: Parking card opening

40A:第一同步組件 40A: first synchronization component

40B:第二同步組件 40B: second synchronization component

41:從動軸套 41: Driven bushing

411:導引件 411: guide

42A:套環 42A: Collar

42B:套環 42B: Collar

421:卡制溝 421: card groove

43A:連動臂 43A: link arm

43B:連動臂 43B: link arm

44:第一傳動件 44: The first transmission member

45:第二傳動件 45: Second transmission member

50:離合組 50: clutch group

51:中央導引座 51: Central guide seat

511:套管部 511: Casing Department

512:法蘭部 512: flange part

513A:第一輔助導溝 513A: The first auxiliary guide ditch

513B:第二輔助導溝 513B: Second auxiliary guide ditch

514A:第一離合凸輪段 514A: The first clutch cam section

514B:第二離合凸輪段 514B: Second clutch cam section

515:離合致動區 515: Clutch actuation area

516:致動凸部 516: actuation protrusion

517:限制凹部 517: Limit recess

52A:第一離合組件 52A: The first clutch assembly

52B:第二離合組件 52B: Second clutch assembly

521:離合件 521: Clutch

522:卡制環 522: clamping ring

523:摩擦環 523: friction ring

524:波形彈簧 524: wave spring

525:卡制凸部 525: card convex part

60A:第一離合致動組 60A: The first clutch actuation group

60B:第二離合致動組 60B: The second clutch actuation group

61:驅動齒輪 61: Drive gear

62:致動件 62: Actuator

621:致動環齒輪 621:Actuation ring gear

622:抵靠環 622: abutment ring

623:緩衝彈性件 623: Buffer elastic parts

624:致動抵部 624: Actuation Arrival

625:導引凸部 625: Guiding convex part

626:定位件 626: Positioner

70:駐車組 70:Parking group

71:駐車凸輪 71: Parking cam

711:推抵部 711: pushing department

72:駐車爪 72:Park pawl

721:卡制勾 721: card system hook

80:驅動組 80: drive group

81:馬達 81: motor

82:蝸桿 82: Worm

83:蝸輪 83: worm gear

84:驅動齒輪 84: Drive gear

圖1係本創作較佳實施例的外觀立體圖。 Fig. 1 is the perspective view of the appearance of the preferred embodiment of the invention.

圖2係本創作較佳實施例的局部剖面立體圖。 Fig. 2 is a partially cutaway perspective view of a preferred embodiment of the invention.

圖3係本創作較佳實施例的另一視角之局部剖面立體圖。 Fig. 3 is a partial sectional perspective view of another viewing angle of a preferred embodiment of the invention.

圖4係本創作較佳實施例之局部的元件分解圖。 Fig. 4 is an exploded view of parts of the preferred embodiment of the invention.

圖5係本創作較佳實施例之分解的局部剖面立體圖。 Fig. 5 is an exploded partial sectional perspective view of a preferred embodiment of the invention.

圖6係本創作較佳實施例之分解的局部剖面立體圖。 Fig. 6 is an exploded partial sectional perspective view of a preferred embodiment of the invention.

圖7係本創作之換檔凸輪軸的外觀立體圖。 Fig. 7 is the appearance perspective view of the shift camshaft of this creation.

圖8係本創作較佳實施例N檔時之側視的局部剖面圖。 Fig. 8 is the partial cross-sectional view of the side view when the preferred embodiment of the present invention is in N gear.

圖9係本創作較佳實施例之複合行星齒輪組的元件分解圖。 Fig. 9 is an exploded view of the compound planetary gear set of the preferred embodiment of the present invention.

圖10係本創作較佳實施例之中央導引座的外觀立體圖。 Fig. 10 is the external perspective view of the central guide seat of the preferred embodiment of the invention.

圖11係本創作較佳實施例之離合件的外觀立體圖。 Fig. 11 is the external perspective view of the clutch part of the preferred embodiment of the present invention.

圖12係本創作較佳實施例之致動件的外觀立體圖。 Fig. 12 is a perspective view of the appearance of the actuator of the preferred embodiment of the invention.

圖13係本創作較佳實施例之駐車組的平面示意圖。 Fig. 13 is the schematic plan view of the parking group of the preferred embodiment of the present invention.

圖14係本創作較佳實施例P檔時之側視的局部剖面圖。 Fig. 14 is the partial sectional view of the side view when the P file of the preferred embodiment of the creation.

圖15係本創作較佳實施例R檔時之側視的局部剖面圖。 Fig. 15 is the partial sectional view of the side view when the R file of the preferred embodiment of the creation.

圖16係本創作較佳實施例D1檔時之側視的局部剖面圖。 Fig. 16 is the partial sectional view of the side view when the preferred embodiment D1 file of this creation.

圖17係本創作較佳實施例D2檔時之側視的局部剖面圖。 Fig. 17 is the partial sectional view of the side view when the D2 file of the preferred embodiment of the creation.

圖18係本創作較佳實施例D3檔時之側視的局部剖面圖。 Fig. 18 is the partial sectional view of the side view when the preferred embodiment D3 file of this creation.

圖19係本創作較佳實施例D4檔時之側視的局部剖面圖。 Fig. 19 is the partial sectional view of the side view when the D4 file of the preferred embodiment of the creation.

為能詳細瞭解本創作的技術特徵及實用功效，並可依照發明內容來實現，玆進一步以如圖式所示的較佳實施例，詳細說明如後： In order to understand the technical characteristics and practical effects of this creation in detail, and to realize it according to the content of the invention, the preferred embodiment shown in the figure is further described in detail as follows:

如圖1至圖3所示，本創作之改良型變速機構的較佳實施例包括有一傳動軸10、一換檔凸輪軸20、一複合行星齒輪組30、一第一同步組件40A、一第二同步組件40B、一離合組50、一第一離合致動組60A、一第二離合致動組60B及一駐車組70。進一步地，如圖1、圖3及圖5所示，本創作的改良型變速機構還包括有與該換檔凸輪軸20相連結的一驅動組80，該驅動組80係用於驅動該換檔凸輪軸20旋轉。 As shown in Figures 1 to 3, the preferred embodiment of the improved speed change mechanism of the present invention includes a transmission shaft 10, a shift camshaft 20, a compound planetary gear set 30, a first synchronous assembly 40A, a first Two synchronization components 40B, a clutch group 50 , a first clutch actuation group 60A, a second clutch actuation group 60B and a parking group 70 . Further, as shown in Fig. 1, Fig. 3 and Fig. 5, the improved transmission mechanism of the present invention also includes a driving group 80 connected with the shift camshaft 20, and the driving group 80 is used to drive the shifting camshaft 20. The gear camshaft 20 rotates.

如圖1至圖3所示，該傳動軸10與該換檔凸輪軸20平行地間隔設置；兩該同步組件40A、40B與該傳動軸10與該換檔凸輪軸20相連結，且能使該複合行星齒輪組30能與該傳動軸10和該換檔凸輪軸20相連結，且兩該同步組件40A、40B能沿著該換檔凸輪軸20往復活動，使該換檔凸輪軸20能藉由兩該同步組件40A、40B控制該傳動軸10是否連結該複合行星齒輪組30，使該複合行星齒輪組30能受該傳動軸10所驅動；該離合組50與該複合行星齒輪組30相連結，兩該離合致動組60A、60B與該傳動軸10與該換檔凸輪軸20相連結，且能使該複合行星齒輪組30能與該傳動軸10和該換檔凸輪軸20相連結；當該驅動組80驅動該 換檔凸輪軸20旋轉時，該換檔凸輪軸20能藉由兩該離合致動組60A、60B控制該複合行星齒輪組30的輸出。藉由以上的配置，讓本創作能沿著相平行設置的該傳動軸10和該換檔凸輪軸20來換檔。 As shown in Figures 1 to 3, the transmission shaft 10 and the shift camshaft 20 are spaced apart in parallel; The compound planetary gear set 30 can be connected with the transmission shaft 10 and the shift camshaft 20, and the two synchronous assemblies 40A, 40B can reciprocate along the shift camshaft 20, so that the shift camshaft 20 can Whether the transmission shaft 10 is connected to the compound planetary gear set 30 is controlled by the two synchronization components 40A, 40B, so that the compound planetary gear set 30 can be driven by the transmission shaft 10; the clutch set 50 and the compound planetary gear set 30 The two clutch actuating groups 60A, 60B are connected with the transmission shaft 10 and the shift camshaft 20, and the compound planetary gear set 30 can be connected with the transmission shaft 10 and the shift camshaft 20. link; when the drive group 80 drives the When the shift camshaft 20 rotates, the shift camshaft 20 can control the output of the compound planetary gear set 30 through the two clutch actuating groups 60A, 60B. Through the above configuration, the present invention can shift gears along the transmission shaft 10 and the shift camshaft 20 arranged in parallel.

如圖3至圖6，以及圖8所示，該傳動軸10包括有一軸向，以及同軸設置的一輸入件11、一行星架傳動件12、一小太陽齒輪傳動件13、一連接件14、一單向離合器15、一大太陽齒輪傳動件16及一連結件17；其中，該輸入件11具有與一動力源(圖未示)相連結的一輸入端111。該行星架傳動件12同軸地穿置於該輸入件11且能相對該輸入件11旋轉，該行星架傳動件12包括有一卡掣齒輪部121和一行星架卡掣段122；該卡掣齒輪部121設於該行星架傳動件12的一端，該行星架卡掣段122設於該行星架傳動件12的另一端。如圖4所示，該小太陽齒輪傳動件13套設於該行星架傳動件12並呈管狀且包括有一小太陽齒輪卡掣段131。該連接件14呈環狀且套置於該小太陽齒輪傳動件13，且該連接件14包括有位置相對的一卡掣齒部141及一容槽142；該單向離合器15套置於該小太陽齒輪傳動件13且容置於該容槽142。 As shown in Figures 3 to 6 and Figure 8, the transmission shaft 10 includes an axial and coaxially arranged input member 11, a planet carrier transmission member 12, a small sun gear transmission member 13, and a connecting member 14 , a one-way clutch 15, a large sun gear transmission member 16 and a connecting member 17; wherein, the input member 11 has an input end 111 connected to a power source (not shown). The planet carrier transmission member 12 is coaxially worn on the input member 11 and can rotate relative to the input member 11. The planet carrier transmission member 12 includes a locking gear portion 121 and a planet carrier locking segment 122; the locking gear The portion 121 is disposed at one end of the planetary carrier transmission member 12 , and the planetary carrier locking section 122 is disposed at the other end of the planetary carrier transmission member 12 . As shown in FIG. 4 , the small sun gear transmission member 13 is sheathed on the planetary carrier transmission member 12 and has a tubular shape and includes a small sun gear locking section 131 . The connecting member 14 is ring-shaped and sleeved on the small sun gear transmission member 13, and the connecting member 14 includes a locking tooth portion 141 and a receiving groove 142 opposite to each other; the one-way clutch 15 is sleeved on the small sun gear transmission member 13. The small sun gear transmission member 13 is accommodated in the container 142 .

如圖5、圖6及圖8所示，該大太陽齒輪傳動件16呈圓罩狀且套置於該小太陽齒輪傳動件13，該大太陽齒輪傳動件16包括有一大太陽齒輪卡合部161、一卡掣部162及多數個離合卡制溝163；其中，該大太陽齒輪卡合部161位於該大太陽齒輪傳動件16的前端，該卡掣部162位於該大太陽齒輪傳動件16的內部，該多數個離合卡制溝163環設於該大太陽齒輪傳動件16的外周面，各該離合卡制溝163與該傳動軸10的軸向平行。如圖6及圖8所示，該連結件17同軸地設於該大太陽齒輪傳動件16的內部且與該輸入件11相連結。 As shown in Figure 5, Figure 6 and Figure 8, the large sun gear transmission part 16 is in the shape of a dome and is sleeved on the small sun gear transmission part 13, and the large sun gear transmission part 16 includes a large sun gear engaging part 161. A locking part 162 and a plurality of clutch locking grooves 163; wherein, the large sun gear engaging part 161 is located at the front end of the large sun gear transmission part 16, and the locking part 162 is located at the large sun gear transmission part 16 Inside, the plurality of clutch locking grooves 163 are arranged around the outer peripheral surface of the large sun gear transmission member 16 , and each of the clutch locking grooves 163 is parallel to the axial direction of the transmission shaft 10 . As shown in FIG. 6 and FIG. 8 , the connecting member 17 is coaxially disposed inside the large sun gear transmission member 16 and connected with the input member 11 .

如圖6至圖8所示，該換檔凸輪軸20包括有一軸體21、一第一同步凸輪槽22A、一第二同步凸輪槽22B、一從動齒輪23及一齒輪卡掣段24。其中，該第一同步凸輪槽22A、該第二同步凸輪槽22B以不同的形式而波浪起伏地 環設於該軸體21且相間隔；該齒輪卡掣段24位於該軸體21的中間段；該從動齒輪23和該軸體21同軸設置；該第一同步凸輪槽22A、該第二同步凸輪槽22B和該從動齒輪23位於該軸體21的一端且靠近該輸入件11的輸入端111。 As shown in FIGS. 6 to 8 , the shift camshaft 20 includes a shaft body 21 , a first synchronous cam slot 22A, a second synchronous cam slot 22B, a driven gear 23 and a gear engagement section 24 . Wherein, the first synchronous cam groove 22A and the second synchronous cam groove 22B are undulating in different forms The ring is arranged on the shaft body 21 and spaced apart; the gear locking section 24 is located in the middle section of the shaft body 21; the driven gear 23 is coaxially arranged with the shaft body 21; the first synchronous cam groove 22A, the second The synchronous cam slot 22B and the driven gear 23 are located at one end of the shaft body 21 and close to the input end 111 of the input member 11 .

如圖3、圖9、圖14及圖15所示，該複合行星齒輪組30環設於該傳動軸10且遠離該輸入件11的輸入端111，該複合行星齒輪組30包括有一行星架31、一大太陽齒輪32、一小太陽齒輪33、三短軸行星齒輪34、三長軸行星齒輪35及一輸出環齒輪36。其中，該大太陽齒輪32、該小太陽齒輪33、各該短軸行星齒輪34，以及各該長軸行星齒輪35都設於該行星架31內。該行星架31包括有一傳動件卡掣部311及一卡制齒部312。該傳動件卡掣部311呈管狀，該行星架31以所設的傳動件卡掣部311套置於如圖4所示的該行星架傳動件12，且該傳動件卡掣部311與該行星架傳動件12的行星架卡掣段122相卡掣；該卡制齒部312設於該行星架31的外周面。該大太陽齒輪32能轉動地套置於該行星架傳動件12，該大太陽齒輪32包括有一傳動件卡合部321，該傳動件卡合部321與該大太陽齒輪傳動件16的大太陽齒輪卡合部161相卡合。該小太陽齒輪33的外徑小於該大太陽齒輪32的外徑且內周面環設有多數個齒，該小太陽齒輪33套置於如圖4所示的該小太陽齒輪傳動件13上且與該小太陽齒輪卡掣段131相卡掣。 As shown in Fig. 3, Fig. 9, Fig. 14 and Fig. 15, the compound planetary gear set 30 is arranged around the transmission shaft 10 and away from the input end 111 of the input member 11, and the compound planetary gear set 30 includes a planet carrier 31 , a large sun gear 32, a small sun gear 33, three minor axis planetary gears 34, three major axis planetary gears 35 and an output ring gear 36. Wherein, the large sun gear 32 , the small sun gear 33 , each of the short-axis planetary gears 34 , and each of the long-axis planetary gears 35 are all arranged in the planet carrier 31 . The planetary carrier 31 includes a locking portion 311 of a transmission member and a locking tooth portion 312 . The transmission member engaging portion 311 is tubular, and the planet carrier 31 is sleeved on the planet carrier transmission member 12 as shown in FIG. The planet carrier locking section 122 of the planet carrier transmission member 12 is locked in phase; the locking tooth portion 312 is disposed on the outer peripheral surface of the planet carrier 31 . The large sun gear 32 is rotatably placed on the planet carrier transmission member 12. The large sun gear 32 includes a transmission member engaging portion 321, and the transmission member engaging portion 321 is connected to the large sun of the large sun gear transmission member 16. The gear engaging portion 161 is engaged with each other. The outer diameter of the small sun gear 33 is smaller than the outer diameter of the large sun gear 32 and the inner peripheral surface is provided with a plurality of teeth. The small sun gear 33 is sleeved on the small sun gear transmission member 13 as shown in FIG. 4 And engage with the engaging section 131 of the small sun gear.

如圖3、圖9及圖14所示，三該短軸行星齒輪34環繞該小太陽齒輪33且各該短軸行星齒輪34與該小太陽齒輪33相嚙合。各該長軸行星齒輪35的長度大於各該短軸行星齒輪34的長度，三該長軸行星齒輪35環繞該大太陽齒輪32及三該短軸行星齒輪34；各該長軸行星齒輪35與該大太陽齒輪32相嚙合，且三該長軸行星齒輪35分別與三該短軸行星齒輪34相嚙合。該輸出環齒輪36呈圓罩狀並套置於三該長軸行星齒輪35且與三該長軸行星齒輪35相嚙合，該輸出環齒輪36的外周面環設有多數個駐車卡制口361。 As shown in FIG. 3 , FIG. 9 and FIG. 14 , the three short-axis planetary gears 34 surround the small sun gear 33 and each of the short-axis planetary gears 34 meshes with the small sun gear 33 . The length of each of the major axis planetary gears 35 is greater than the length of each of the minor axis planetary gears 34, and the three major axis planetary gears 35 surround the large sun gear 32 and the three minor axis planetary gears 34; each of the major axis planetary gears 35 and The large sun gear 32 is meshed, and the three long-axis planetary gears 35 are respectively meshed with the three short-axis planetary gears 34 . The output ring gear 36 is in the shape of a dome and is sleeved on the three long-axis planetary gears 35 and meshed with the three long-axis planetary gears 35 . The outer peripheral surface of the output ring gear 36 is provided with a plurality of parking locking ports 361 .

如圖1、圖5及圖6所示，各該同步組件40A/40B包括有一從動軸套41、一套環42A/42B及一連動臂43A/43B；其中，該從動軸套41套置於該換檔凸輪軸20且能沿著該換檔凸輪軸20往復活動，該從動軸套41包括有一導引件411，該導引件411用於插置於該換檔凸輪軸20的其中一同步凸輪槽22A/22B，且該導引件411能沿著波浪起伏的所述同步凸輪槽22A/22B活動。該套環42A/42B套置於該輸入件11且能沿著該傳動軸10的軸向往復活動，該套環42A/42B於外周緣環設有一卡制溝421。該連動臂43A/43B包括有位置相對的兩端，該連動臂43A/43B的一端固結於該從動軸套41，該連動臂43A/43B的另一端嵌置於該套環42A/42B的卡制溝421，使該套環42A/42B能相對該連動臂43A/43B旋轉。當該換檔凸輪軸20旋轉時，該導引件411沿著所述同步凸輪槽22A/22B活動，該從動軸套41便能以該連動臂43A/43B帶動該套環42A/42B，使該套環42A/42B沿著該傳動軸10的軸向往復活動。 As shown in Figure 1, Figure 5 and Figure 6, each of the synchronous components 40A/40B includes a driven shaft sleeve 41, a set of rings 42A/42B and a link arm 43A/43B; wherein, the driven shaft sleeve 41 sets Placed on the shift camshaft 20 and capable of reciprocating along the shift camshaft 20 , the driven sleeve 41 includes a guide 411 for being inserted into the shift camshaft 20 One of the synchronous cam grooves 22A/22B, and the guide 411 can move along the undulating synchronous cam grooves 22A/22B. The collar 42A/42B is sleeved on the input member 11 and can reciprocate along the axial direction of the transmission shaft 10 . The collar 42A/42B is provided with a clamping groove 421 on the outer peripheral ring. The linkage arm 43A/43B includes two opposite ends, one end of the linkage arm 43A/43B is fixed to the driven shaft sleeve 41, and the other end of the linkage arm 43A/43B is embedded in the collar 42A/42B. The retaining groove 421 enables the collar 42A/42B to rotate relative to the linkage arm 43A/43B. When the shift camshaft 20 rotates, the guide member 411 moves along the synchronous cam groove 22A/22B, and the driven sleeve 41 can drive the collar 42A/42B with the linkage arm 43A/43B, The collar 42A/42B is reciprocated along the axial direction of the transmission shaft 10 .

如圖2、圖3及圖5所示，該第一同步組件40A進一步包括有呈環狀的一第一傳動件44，該第一同步組件40A的套環42A與該第一傳動件44以多數個連接桿相連結，該第一傳動件44同軸地設於該輸入件11的內部且同軸地套設於該行星架傳動件12，且該第一傳動件44能沿著該傳動軸10的軸向往復活動；其中，該第一傳動件44的外周緣與該輸入件11的內周緣相卡掣。該第一傳動件44的內周緣能與該行星架傳動件12的卡掣齒輪部121相卡掣；進一步，該第一傳動件44的內周緣也能與該連接件14的卡掣齒部141相卡掣。 As shown in Fig. 2, Fig. 3 and Fig. 5, the first synchronizing assembly 40A further includes a ring-shaped first transmission member 44, and the collar 42A of the first synchronizing assembly 40A is connected to the first transmission member 44 with A plurality of connecting rods are connected, the first transmission member 44 is coaxially arranged inside the input member 11 and coaxially sleeved on the planet carrier transmission member 12, and the first transmission member 44 can move along the transmission shaft 10 The axial reciprocating movement; wherein, the outer peripheral edge of the first transmission member 44 is engaged with the inner peripheral edge of the input member 11 . The inner peripheral edge of the first transmission member 44 can engage with the engagement gear portion 121 of the planet carrier transmission member 12; 141 Phase locking.

如圖2、圖3、圖5及圖6所示，該第二同步組件40B進一步包括有呈環狀的一第二傳動件45，該第二同步組件40B的套環42B與該第二傳動件45以多數個連接桿相連結，該第二傳動件45同軸地設於該大太陽齒輪傳動件16的內部、同軸地套設於該連結件17、與該連結件17相卡掣且同軸地環繞該小太陽齒輪傳動件13，且該第二傳動件45能沿著該傳動軸10的軸向往復活動；該第二 傳動件45的內周面環設有多數個齒，該第二傳動件45於內周面所設的多數個齒能與該大太陽齒輪傳動件16的卡掣部162相卡掣。 As shown in Fig. 2, Fig. 3, Fig. 5 and Fig. 6, the second synchronous assembly 40B further includes a ring-shaped second transmission member 45, and the collar 42B of the second synchronous assembly 40B is connected with the second transmission 45 is connected by a plurality of connecting rods, and the second transmission member 45 is coaxially arranged inside the large sun gear transmission member 16, coaxially sleeved on the connecting member 17, locked and coaxial with the connecting member 17 ground around the small sun gear transmission member 13, and the second transmission member 45 can reciprocate along the axial direction of the transmission shaft 10; the second The inner peripheral surface of the transmission member 45 is provided with a plurality of teeth, and the plurality of teeth provided on the inner peripheral surface of the second transmission member 45 can engage with the engagement portion 162 of the large sun gear transmission member 16 .

如圖1、圖3、圖10及圖14所示，該離合組50包括有一中央導引座51、一第一離合組件52A和一第二離合組件52B。該中央導引座51包括有一套管部511、一法蘭部512、一第一輔助導溝513A、一第二輔助導溝513B、一第一離合凸輪段514A及一第二離合凸輪段514B。如圖10所示，該套管部511呈圓管狀且包括有一軸向，以及在該套管部511之軸向上位置相對的兩端，該套管部511同軸地套設於該傳動軸10。該法蘭部512環設於該套管部511的外周面且位於該套管部511之中間段，該中央導引座51係以該法蘭部512與一離合器轂相結合。兩該輔助導溝513A、513B分別靠近該套管部511的兩端，兩該輔助導溝513A、513B凹設於該套管部511的外周面且以不同的形式而波浪起伏地環繞該套管部511。兩該離合凸輪段514A、514B以不同的形式而波浪起伏地環設於該套管部511的外周面，且各該離合凸輪段514A/514B包括有呈波浪狀的一推抵曲面，各該離合凸輪段514A/514B的推抵曲面間隔地設有多數個離合致動區515，各該離合致動區515包括有兩致動凸部516及一位於兩該致動凸部516間的限制凹部517；兩該離合凸輪段514A、514B介於兩該輔助導溝513A、513B之間且受該法蘭部512所區隔，兩該離合凸輪段514A、514B的推抵曲面分別朝向該套管部511的兩端。 As shown in FIG. 1 , FIG. 3 , FIG. 10 and FIG. 14 , the clutch assembly 50 includes a central guide seat 51 , a first clutch assembly 52A and a second clutch assembly 52B. The central guide seat 51 includes a sleeve portion 511, a flange portion 512, a first auxiliary guide groove 513A, a second auxiliary guide groove 513B, a first clutch cam section 514A, and a second clutch cam section 514B. . As shown in FIG. 10 , the sleeve portion 511 is in the shape of a circular tube and includes an axial direction, and opposite ends of the sleeve portion 511 in the axial direction. The sleeve portion 511 is coaxially sleeved on the transmission shaft 10 . The flange portion 512 is disposed around the outer peripheral surface of the sleeve portion 511 and is located in the middle section of the sleeve portion 511 . The central guide seat 51 is combined with a clutch hub through the flange portion 512 . The two auxiliary guide grooves 513A, 513B are respectively close to the two ends of the sleeve portion 511, and the two auxiliary guide grooves 513A, 513B are recessed on the outer peripheral surface of the sleeve portion 511 and surround the sleeve in different forms undulating. pipe part 511 . The two clutch cam segments 514A, 514B are undulatingly arranged on the outer peripheral surface of the sleeve portion 511 in different forms, and each of the clutch cam segments 514A/514B includes a wavy pushing curved surface, each of which The push-off curved surface of the clutch cam segment 514A/514B is provided with a plurality of clutch actuation areas 515 at intervals, and each of the clutch actuation areas 515 includes two actuation protrusions 516 and a restriction between the two actuation protrusions 516. Recess 517; the two clutch cam segments 514A, 514B are located between the two auxiliary guide grooves 513A, 513B and are separated by the flange portion 512, and the pushing curved surfaces of the two clutch cam segments 514A, 514B are respectively facing the set both ends of the pipe portion 511.

如圖1、圖3、圖9、圖11及圖14所示，各該離合組件52A/52B包括有多數個離合件521。如圖11所示，各該離合件521包括有同軸設置的一卡制環522、一摩擦環523及一波形彈簧524。該卡制環522的外周緣間隔地環設有多數個卡制凸部，該摩擦環523的兩平面粗糙、其內周緣間隔地環設有多數個卡制凸部525，且其外徑小於該卡制環522的外徑。該波形彈簧524環繞該摩擦環523。該多數個離合件521與該套管部511同軸設置，且該多數個離合件521能沿 著該套管部511的軸向往復活動。當各該離合組件52A/52B未作動時，其多數個離合件521以所設的波形彈簧524相抵靠；當各該離合組件52A/52B作動時，其多數個離合件521所設的波形彈簧524被壓縮，且以所設的摩擦環523相抵靠。 As shown in FIG. 1 , FIG. 3 , FIG. 9 , FIG. 11 and FIG. 14 , each clutch assembly 52A/52B includes a plurality of clutch parts 521 . As shown in FIG. 11 , each clutch member 521 includes a locking ring 522 , a friction ring 523 and a wave spring 524 coaxially disposed. The outer peripheral edge of the clamping ring 522 is provided with a plurality of clamping protrusions at intervals, the two planes of the friction ring 523 are rough, and the inner circumference of the friction ring 523 is provided with a plurality of clamping protrusions 525 at intervals, and its outer diameter is less than The outer diameter of the clamping ring 522 . The wave spring 524 surrounds the friction ring 523 . The plurality of clutch parts 521 are arranged coaxially with the sleeve part 511, and the plurality of clutch parts 521 can be The axial reciprocating movement of the sleeve part 511 is controlled. When each of the clutch assemblies 52A/52B was not actuated, its plurality of clutch parts 521 abutted against the set wave springs 524; 524 is compressed and abuts against the provided friction ring 523 .

如圖3、圖6、圖11及圖14所示，該第一離合組件52A的各離合件521，以其摩擦環523設於內周緣的多數個卡制凸部525與該大太陽齒輪傳動件16的多數個離合卡制溝163相卡制，使該第一離合組件52A藉由該大太陽齒輪傳動件16與該複合行星齒輪組30的大太陽齒輪32相連結、且能控制該大太陽齒輪32是否能旋轉。該第二離合組件52B的各離合件521，同樣以其摩擦環523設於內周緣的多數個卡制凸部525與該複合行星齒輪組30之行星架31的卡制齒部312相卡制、藉此與該複合行星齒輪組30相連結，且能控制該複合行星齒輪組30之行星架31是否能旋轉。 As shown in Fig. 3, Fig. 6, Fig. 11 and Fig. 14, each clutch part 521 of the first clutch assembly 52A, with its friction ring 523 arranged on a plurality of clamping protrusions 525 on the inner peripheral edge and the big sun gear transmission The plurality of clutch locking grooves 163 of the part 16 are locked, so that the first clutch assembly 52A is connected with the big sun gear 32 of the compound planetary gear set 30 through the big sun gear transmission part 16, and can control the big sun gear 32 of the compound planetary gear set. Whether the sun gear 32 can rotate. Each clutch part 521 of the second clutch assembly 52B is similarly locked by the locking teeth 312 of the planetary carrier 31 of the planetary carrier 31 of the compound planetary gear set 30 with its friction ring 523 disposed on the plurality of locking protrusions 525 on the inner peripheral edge. , thereby being connected with the compound planetary gear set 30 and controlling whether the planetary carrier 31 of the compound planetary gear set 30 can rotate.

如圖3、圖12及圖14所示，各該離合致動組60A/60B包括有一驅動齒輪61及一致動件62。圖3、圖7及圖14所示，該驅動齒輪61呈環狀，該驅動齒輪61的內周緣環設有多數個齒；該驅動齒輪61套置於該換檔凸輪軸20的齒輪卡掣段24，且驅動齒輪61以內周緣所設的多數個齒與該齒輪卡掣段24相卡掣。在本創作的較佳實施例中，兩該離合致動組60A、60B的驅動齒輪61同軸地相固結，且一起與該齒輪卡掣段24相卡掣。 As shown in FIG. 3 , FIG. 12 and FIG. 14 , each of the clutch actuating groups 60A/60B includes a driving gear 61 and an actuating member 62 . As shown in Fig. 3, Fig. 7 and Fig. 14, the driving gear 61 is annular, and the inner peripheral ring of the driving gear 61 is provided with a plurality of teeth; Section 24, and a plurality of teeth provided on the inner periphery of the drive gear 61 are engaged with the gear engagement section 24. In a preferred embodiment of the present invention, the driving gears 61 of the two clutch actuating groups 60A, 60B are fixed coaxially, and are locked together with the gear locking section 24 .

如圖3、圖10、圖12及圖14所示，各該致動件62呈環狀且能轉動地套設於該套管部511，各該致動件62包括有一致動環齒輪621、一抵靠環622及多數個緩衝彈性件623。該致動環齒輪621呈環狀，該致動環齒輪621於側面間隔地環設有三致動抵部624，以及於內周緣間隔地環設有三導引凸部625，各該導引凸部625徑向地突設於該致動環齒輪621的內周緣。該抵靠環622同軸地與該致動環齒輪621相結合。該多數個緩衝彈性件623介於該致動環齒輪621與該抵靠環622之間；在本創作的較佳實施例中，各該緩衝彈性件623係為一壓縮 彈簧，且各該緩衝彈性件623的兩端分別抵靠於該致動環齒輪621與該抵靠環622。本創作的各該緩衝彈性件623不限定為壓縮彈簧，只要各該緩衝彈性件623能彈性地支撐該致動環齒輪621與該抵靠環622，即為本創作所欲保護的標的。在本創作的較佳實施例中，各該致動件62的致動環齒輪621和抵靠環622係藉由多數個定位件626相結合，該多數個緩衝彈性件623分別套置於該多數個定位件626，各該緩衝彈性件623同時抵靠該致動環齒輪621和該抵靠環622、維持該致動環齒輪621與該抵靠環622之間的距離，且對相對應的一該離合組件52A/52B產生預壓的效果。再者，該多數個緩衝彈性件623藉由該多數個定位件626所導引，而能穩定地抵靠該致動環齒輪621和該抵靠環622。 As shown in Figure 3, Figure 10, Figure 12 and Figure 14, each of the actuators 62 is ring-shaped and rotatably sleeved on the sleeve part 511, and each of the actuators 62 includes an actuating ring gear 621 1. An abutment ring 622 and a plurality of cushioning elastic parts 623 . The actuating ring gear 621 is ring-shaped. The actuating ring gear 621 is provided with three actuating abutments 624 at intervals on the side, and three guide protrusions 625 are provided at intervals on the inner periphery. 625 radially protrudes from the inner periphery of the actuating ring gear 621 . The abutment ring 622 is coaxially combined with the actuation ring gear 621 . The plurality of buffer elastic members 623 are interposed between the actuating ring gear 621 and the abutment ring 622; in a preferred embodiment of this invention, each of the buffer elastic members 623 is a compressed spring, and the two ends of each buffer elastic member 623 abut against the actuating ring gear 621 and the abutting ring 622 respectively. The buffer elastic members 623 of the present invention are not limited to compression springs, as long as each of the buffer elastic members 623 can elastically support the actuating ring gear 621 and the abutment ring 622 , it is the object to be protected by the present invention. In a preferred embodiment of the present invention, the actuating ring gear 621 and the abutment ring 622 of each actuating member 62 are combined by a plurality of positioning members 626, and the plurality of buffering elastic members 623 are respectively sleeved on the actuating member 62. A plurality of positioning members 626, each of the buffer elastic members 623 abuts against the actuation ring gear 621 and the abutment ring 622 at the same time, maintains the distance between the actuation ring gear 621 and the abutment ring 622, and corresponds to One of the clutch assemblies 52A/52B produces a preload effect. Furthermore, the plurality of buffer elastic elements 623 are guided by the plurality of positioning elements 626 to stably abut against the actuating ring gear 621 and the abutment ring 622 .

如圖3、圖10、圖12及圖14所示，兩該離合致動組60A、60B的兩致動件62能轉動地套設於該套管部511且能沿著該套管部511往復活動，兩該致動件62的兩致動環齒輪621與固結於該換檔凸輪軸20的兩該驅動齒輪61相嚙合，兩該致動件62以所設的致動環齒輪621抵靠於固結於所述離合器轂的該中央導引座51。具體而言，兩該致動環齒輪621分別以所設的致動抵部624抵靠於該中央導引座51之兩離合凸輪段514A、514B的兩推抵曲面；且兩該致動環齒輪621分別以所設的導引凸部625插置於該套管部511的兩輔助導溝513A、513B。 As shown in Fig. 3, Fig. 10, Fig. 12 and Fig. 14, the two actuating members 62 of the two clutch actuating groups 60A, 60B are rotatably sleeved on the sleeve part 511 and can move along the sleeve part 511. Reciprocating, the two actuating ring gears 621 of the two actuating parts 62 are meshed with the two driving gears 61 fixed on the shift camshaft 20, and the two actuating parts 62 are connected with the set actuating ring gears 621 It rests against the central guide seat 51 fixed to the clutch hub. Specifically, the two actuating ring gears 621 abut against the two abutting curved surfaces of the two clutch cam sections 514A, 514B of the central guide seat 51 with the provided actuating abutting portions 624 respectively; and the two actuating rings The gears 621 are respectively inserted into the two auxiliary guide grooves 513A, 513B of the sleeve portion 511 with the provided guiding protrusions 625 .

當該換檔凸輪軸20旋轉時，其帶動兩該離合致動組60A、60B的兩驅動齒輪61旋轉。兩該離合致動組60A、60B的兩致動件62，其與兩該驅動齒輪61相嚙合的兩致動環齒輪621再被帶動而相對該套管部511旋轉。兩該離合致動組60A、60B的兩致動件62，其旋轉的兩致動環齒輪621能受兩該離合凸輪段514A、514B的推抵曲面所推抵而於沿著該套管部511(亦即該傳動軸10的軸向)活動，使兩該致動件62能分別朝向該套管部511的兩端活動。而兩該致動環齒輪621的導引凸部625能分別沿著兩該輔助導溝513A、513B活動，使兩該致動件 62能沿著該套管部511往復活動，幫助兩該致動環齒輪621能平穩地相對該套管部511旋轉。 When the shift camshaft 20 rotates, it drives the two driving gears 61 of the two clutch actuating groups 60A, 60B to rotate. The two actuating members 62 of the two clutch actuating groups 60A, 60B are driven by the two actuating ring gears 621 meshing with the two driving gears 61 to rotate relative to the sleeve portion 511 . The two actuating members 62 of the two clutch actuating groups 60A, 60B, the rotating two actuating ring gears 621 can be pushed by the pushing curved surfaces of the two clutch cam segments 514A, 514B and move along the casing portion. 511 (that is, the axial direction of the transmission shaft 10 ) is movable, so that the two actuators 62 can move toward the two ends of the sleeve portion 511 respectively. And the guide protrusions 625 of the two actuating ring gears 621 can move respectively along the two auxiliary guide grooves 513A, 513B, so that the two actuating parts 62 can reciprocate along the sleeve portion 511 to help the two actuating ring gears 621 to rotate relatively to the sleeve portion 511 smoothly.

如圖2、圖3、圖13及圖14所示，該駐車組70包括有一駐車凸輪71及一駐車爪72。其中，該駐車凸輪71結合於該換檔凸輪軸20的軸體21上而遠離兩該同步組件40A、40B且包括有一推抵部711。該駐車爪72能樞擺且包括有能卡制於該輸出環齒輪36之任一駐車卡制口361的一卡制勾721。 As shown in FIG. 2 , FIG. 3 , FIG. 13 and FIG. 14 , the parking set 70 includes a parking cam 71 and a parking claw 72 . Wherein, the parking cam 71 is combined with the shaft body 21 of the shift camshaft 20 and is away from the two synchronizing components 40A, 40B and includes a pushing portion 711 . The parking pawl 72 can pivot and includes a locking hook 721 that can be locked in any parking locking opening 361 of the output ring gear 36 .

如圖1、圖3及圖5所示，該驅動組80包括有一馬達81、一蝸桿82、一蝸輪83及一驅動齒輪84；該蝸桿82結合於該馬達81的馬達軸而能受該馬達81所驅動；該蝸輪83和該驅動齒輪84同軸地設置且能同步旋轉，該蝸輪83與該蝸桿82相嚙合；該驅動齒輪84與該換檔凸輪軸20的從動齒輪23相嚙合。本創作係利用該馬達81驅動該蝸桿82，進而帶動該蝸輪83、該驅動齒輪84和該從動齒輪23旋轉，能夠利用該蝸桿82與該蝸輪83之間的自鎖特性，使本創作在不同的檔位都無需耗費能量來達到鎖定的功能。 As shown in Fig. 1, Fig. 3 and Fig. 5, the driving group 80 includes a motor 81, a worm 82, a worm wheel 83 and a driving gear 84; Driven by 81; the worm gear 83 and the driving gear 84 are coaxially arranged and can rotate synchronously, the worm gear 83 is meshed with the worm 82; the driving gear 84 is meshed with the driven gear 23 of the shift camshaft 20. This creation system utilizes this motor 81 to drive this worm screw 82, and then drives this worm wheel 83, this driving gear 84 and this driven gear 23 to rotate, can utilize the self-locking characteristic between this worm screw 82 and this worm wheel 83, makes this creation in Different gears do not need to consume energy to achieve the locking function.

以下介紹本創作的N檔、P檔、R檔、D1檔、D2檔、D3檔及D4檔的作動與配置。 The following introduces the action and configuration of the N file, P file, R file, D1 file, D2 file, D3 file and D4 file of this creation.

黑色圓點：作動黑色線段：未作動

Black dot: Action Black line segment: No action

N檔： N files:

請參看圖8所示的N檔配置，再配合參看圖4、圖6及圖9，該傳動軸10之大太陽齒輪傳動件16的大太陽齒輪卡合部161與該複合行星齒輪組30之大太陽齒輪32的傳動件卡合部321相卡合、該大太陽齒輪傳動件16與該大太陽齒輪32相連結；兩該同步組件40A、40B、兩該離合組件52A、52B、兩該離合致動組60A、60B，以及該駐車組70均未作動。該第一同步組件40A的第一傳動件44介於該行星架傳動件12的卡掣齒輪部121以及該連接件14的卡掣齒部141之間；因此，該第一傳動件44僅與該輸入件11相卡掣，而未與該卡掣齒輪部121或該卡掣齒部141相卡掣；該第二同步組件40B的第二傳動件45也未與該大太陽齒輪傳動件16的卡掣部162相卡掣。 Please refer to the N gear configuration shown in Fig. 8, and then refer to Fig. 4, Fig. 6 and Fig. 9, the large sun gear engaging part 161 of the large sun gear transmission part 16 of the transmission shaft 10 and the compound planetary gear set 30 The transmission part engagement part 321 of the large sun gear 32 is engaged, and the large sun gear transmission part 16 is connected with the large sun gear 32; the two synchronous assemblies 40A, 40B, the two clutch assemblies 52A, 52B, the two clutch assemblies The actuating groups 60A, 60B and the parking group 70 are not actuated. The first transmission member 44 of the first synchronous assembly 40A is between the engagement gear portion 121 of the planet carrier transmission member 12 and the engagement tooth portion 141 of the connecting member 14; therefore, the first transmission member 44 is only connected to The input member 11 is locked in phase, but not locked with the locking gear part 121 or the locking tooth part 141; the second transmission part 45 of the second synchronous assembly 40B is not connected with the large sun gear transmission part 16 The locking portion 162 is locked in phase.

雖然該大太陽齒輪傳動件16與該大太陽齒輪32相連結，但由於兩該同步組件40A/40B均未作動，該傳動軸10未與該複合行星齒輪組30相連結，因此該傳動軸10的動力無法傳遞至該複合行星齒輪組30而無法輸出。 Although the large sun gear transmission member 16 is connected with the large sun gear 32, since the two synchronous assemblies 40A/40B are not actuated, the transmission shaft 10 is not connected with the compound planetary gear set 30, so the transmission shaft 10 The power cannot be transmitted to the compound planetary gear set 30 and cannot be output.

請再參看圖8、圖10及圖12，各該離合致動組60A/60B的致動件62，以所設的致動環齒輪621抵靠於固結於所述離合器轂的該中央導引座51；各該離合致動組60A/60B的致動件62，以所設的致動抵部624抵靠於相對應之一離合凸輪段514A/514B的推抵曲面。在N檔時，該致動環齒輪621的致動抵部624抵靠於該推抵曲面的凹設之處，而非抵靠於該推抵曲面的離合致動區515。兩該離合致動組60A、60B的兩致動件62抵靠於固定的該中央導引座51，卻未分別推抵兩該離合組件52A、52B。兩該離合組件52A、52B的離合件521未被兩該致動件62所壓抵而未作動；因此，與該第一離合組件52A相連結的該大太陽齒輪 32，以及與該第二離合組件52B相連結的該行星架31未被兩該離合組件52A、52B鎖定。 Please refer to Fig. 8, Fig. 10 and Fig. 12, the actuating member 62 of each of the clutch actuating groups 60A/60B leans against the central guide fixed to the clutch hub with the provided actuating ring gear 621. The guiding seat 51 ; the actuating member 62 of each clutch actuating group 60A/ 60B abuts against the abutting curved surface of a corresponding one of the clutch cam segments 514A/ 514B with the provided actuating abutting portion 624 . In gear N, the actuating abutting portion 624 of the actuating ring gear 621 abuts against the concave portion of the pushing curved surface instead of abutting against the clutch actuating area 515 of the pushing curved surface. The two actuating members 62 of the two clutch actuating groups 60A, 60B abut against the fixed central guide seat 51 , but do not push against the two clutch assemblies 52A, 52B respectively. The clutch parts 521 of the two clutch assemblies 52A, 52B are not pressed against by the two actuating parts 62 and are not actuated; therefore, the large sun gear connected with the first clutch assembly 52A 32, and the planet carrier 31 connected to the second clutch assembly 52B is not locked by the two clutch assemblies 52A, 52B.

P檔： P file:

請參看如圖14所示的P檔配置，再配合參看圖3及圖13，本創作的P檔配置與N檔配置相似；該大太陽齒輪傳動件16與該大太陽齒輪32相連結，兩該同步組件40A、40B及兩該離合組件52A、52B均未作動。本創作的P檔配置與N檔配置的差別在於：在P檔時，該換檔凸輪軸20被驅動而旋轉，結合於該換檔凸輪軸20的該駐車凸輪71以所設的推抵部711推抵該駐車爪72，使該駐車爪72以所設的卡制勾721卡制於該複合行星齒輪組30之輸出環齒輪36的其中一駐車卡制口361，使該輸出環齒輪36無法旋轉。與N檔相比，本創作的P檔配置除了該傳動軸10的動力無法傳遞至該複合行星齒輪組30而無法輸出；該駐車組70進一步作動、卡制該輸出環齒輪36。 Please refer to the P file configuration as shown in Figure 14, and refer to Fig. 3 and Fig. 13 again, the P file configuration of this creation is similar to the N file configuration; The synchronizing components 40A, 40B and the two clutch components 52A, 52B are not actuated. The difference between the P gear configuration and the N gear configuration of this creation is that: in the P gear, the gear shift camshaft 20 is driven to rotate, and the parking cam 71 combined with the gear shift camshaft 20 is connected with the set pushing part. 711 pushes against the parking pawl 72, so that the parking pawl 72 is clamped on one of the parking clamping openings 361 of the output ring gear 36 of the compound planetary gear set 30 with the provided locking hook 721, so that the output ring gear 36 Cannot rotate. Compared with the N gear, the P gear configuration of the invention can not be output except that the power of the transmission shaft 10 cannot be transmitted to the compound planetary gear set 30; the parking set 70 further actuates and blocks the output ring gear 36.

R檔： R files:

如圖15所示的R檔配置，該大太陽齒輪傳動件16與該大太陽齒輪32相連結。當該換檔凸輪軸20旋轉，該駐車組70未作動，該第一同步組件40A的第一傳動件44未與該卡掣齒輪部121或該卡掣齒部141相卡掣。 In the R gear configuration shown in FIG. 15 , the large sun gear transmission member 16 is connected with the large sun gear 32 . When the shift camshaft 20 rotates, the parking group 70 is not activated, and the first transmission member 44 of the first synchronizing assembly 40A is not engaged with the engaging gear portion 121 or the engaging tooth portion 141 .

如圖5、圖6及圖15所示，該換檔凸輪軸20的第二同步凸輪槽22B驅動該第二同步組件40B朝向圖15的右側作動，該第二同步組件40B的第二傳動件45與該大太陽齒輪傳動件16的卡掣部162相卡掣，使該第二同步組件40B與該複合行星齒輪組30的大太陽齒輪32相連結。 As shown in Fig. 5, Fig. 6 and Fig. 15, the second synchronous cam groove 22B of the shift camshaft 20 drives the second synchronous assembly 40B to move toward the right side of Fig. 15, and the second transmission member of the second synchronous assembly 40B 45 engages with the engaging portion 162 of the large sun gear transmission member 16 to connect the second synchronizing assembly 40B with the large sun gear 32 of the compound planetary gear set 30 .

如圖3、圖10、圖12及圖15所示，兩該離合致動組60A、60B的驅動齒輪61和致動件62被該換檔凸輪軸20驅動而旋轉；其中，該第一離合致動組60A的致動件62抵靠於該第一離合凸輪段514A之推抵曲面的凹設處，而未驅使該第一離合組件52A作動。該第二離合致動組60B的致動件62被該第二離合凸 輪段514B之推抵曲面的離合致動區515所推抵，該第二離合致動組60B的致動件62朝向圖15的右側推抵、擠壓該第二離合組件52B的離合件521，該第二離合組件52B作動且卡制該複合行星齒輪組30的行星架31，使該行星架31無法旋轉。 As shown in Fig. 3, Fig. 10, Fig. 12 and Fig. 15, the driving gear 61 and the actuator 62 of the two clutch actuating groups 60A, 60B are driven to rotate by the shift camshaft 20; wherein, the first clutch The actuating member 62 of the coupling actuating group 60A abuts against the recess of the pushing surface of the first clutch cam section 514A, and does not drive the first clutch assembly 52A to actuate. The actuating member 62 of the second clutch actuating group 60B is driven by the second clutch protrusion Pushed by the clutch actuating area 515 of the pushing curved surface of the wheel segment 514B, the actuating member 62 of the second clutch actuating group 60B pushes and squeezes the clutch member 521 of the second clutch assembly 52B toward the right side of FIG. 15 , the second clutch assembly 52B actuates and blocks the planetary carrier 31 of the compound planetary gear set 30 , so that the planetary carrier 31 cannot rotate.

如圖3、圖9及圖15所示，由於該大太陽齒輪傳動件16與該大太陽齒輪32相連結；該第二同步組件40B的第二傳動件45與該複合行星齒輪組30的大太陽齒輪傳動件16相連結；且該第二離合組件52B作動，使該行星架31無法旋轉；該傳動軸10的輸入件11順時針地旋轉作動時，該大太陽齒輪32順時針地旋轉，所述的長軸行星齒輪35逆時針旋轉且帶動該輸出環齒輪36逆時針旋轉，使裝設有本創作的車輛能進行倒車。 As shown in Fig. 3, Fig. 9 and Fig. 15, since the large sun gear transmission member 16 is connected with the large sun gear 32; the second transmission member 45 of the second synchronous assembly 40B and the large The sun gear transmission member 16 is connected; and the second clutch assembly 52B is actuated so that the planet carrier 31 cannot rotate; when the input member 11 of the transmission shaft 10 rotates clockwise, the large sun gear 32 rotates clockwise, The long-axis planetary gear 35 rotates counterclockwise and drives the output ring gear 36 to rotate counterclockwise, so that the vehicle equipped with the present invention can be reversed.

D₁檔： D ₁ file:

如圖16所示的本創作D₁檔配置，該大太陽齒輪傳動件16與該大太陽齒輪32相連結。 As shown in FIG. 16 , the present creation D ₁ gear configuration, the large sun gear transmission member 16 is connected with the large sun gear 32 .

如圖5、圖6及圖16所示，當該換檔凸輪軸20旋轉，該駐車組70未作動、該輸出環齒輪36能夠進行輸出，該第二同步組件40B的第二傳動件45未與該大太陽齒輪傳動件16的卡掣部162相卡掣、該第二同步組件40B未與該複合行星齒輪組30相連結。該第一同步組件40A朝向圖16的右側作動，該第一同步組件40A的第一傳動件44與該連接件14相卡掣。該第一離合組件52A未作動；而該第二離合組件52B作動，與該第二離合組件52B相連結的該行星架31被鎖定。 As shown in Fig. 5, Fig. 6 and Fig. 16, when the shift camshaft 20 rotates, the parking group 70 is not actuated, the output ring gear 36 can output, and the second transmission member 45 of the second synchronous assembly 40B is not Engages with the engagement portion 162 of the large sun gear transmission member 16 , and the second synchronous assembly 40B is not connected with the compound planetary gear set 30 . The first synchronizing assembly 40A moves toward the right side of FIG. 16 , and the first transmission member 44 of the first synchronizing assembly 40A engages with the connecting member 14 . The first clutch assembly 52A is not activated; while the second clutch assembly 52B is activated, and the planet carrier 31 connected to the second clutch assembly 52B is locked.

如圖3、圖9及圖16所示，該傳動軸10的輸入件11順時針地旋轉作動時，該傳動軸10提供的動力經由該第一同步組件40A的第一傳動件44、該連接件14、該單向離合器15、該小太陽齒輪傳動件13傳動至該小太陽齒輪33、帶動該小太陽齒輪33順時針旋轉，使裝設有本創作的車輛能前進。 As shown in Figure 3, Figure 9 and Figure 16, when the input member 11 of the transmission shaft 10 rotates clockwise, the power provided by the transmission shaft 10 passes through the first transmission member 44 of the first synchronous assembly 40A, the connection Part 14, the one-way clutch 15, the small sun gear transmission part 13 are transmitted to the small sun gear 33, and the small sun gear 33 is driven to rotate clockwise, so that the vehicle equipped with the present invention can advance.

如圖3、圖9及圖16所示，該小太陽齒輪33帶動三該短軸行星齒輪34逆時針旋轉，三該長軸行星齒輪35順時針旋轉，該輸出環齒輪36順時針旋轉。同樣地，當該傳動軸10減速時，該小太陽齒輪33的轉速大於該傳動軸10的輸入件11，該單向離合器15鬆開該小太陽齒輪傳動件13，達到無引擎煞車的效果。 As shown in FIG. 3 , FIG. 9 and FIG. 16 , the small sun gear 33 drives the three short-axis planetary gears 34 to rotate counterclockwise, the three long-axis planetary gears 35 to rotate clockwise, and the output ring gear 36 to rotate clockwise. Similarly, when the transmission shaft 10 decelerates, the rotation speed of the small sun gear 33 is greater than the input member 11 of the transmission shaft 10, and the one-way clutch 15 releases the small sun gear transmission member 13 to achieve the effect of no engine braking.

D₂檔： D ₂ files:

如圖17所示的本創作D₂檔配置，該大太陽齒輪傳動件16與該大太陽齒輪32相連結。當該換檔凸輪軸20旋轉，該駐車組70未作動，使該輸出環齒輪36能夠旋轉且進行輸出動力。 As shown in FIG. 17 , in the D ₂ gear configuration of the present invention, the large sun gear transmission member 16 is connected with the large sun gear 32 . When the gear shift camshaft 20 rotates, the parking set 70 is inactive, so that the output ring gear 36 can rotate and output power.

如圖10、圖12及圖17所示，兩該離合致動組60A、60B的驅動齒輪61和致動件62被該換檔凸輪軸20驅動而旋轉；其中，該第一離合致動組60A的致動件62抵靠於該第一離合凸輪段514A之推抵曲面的離合致動區515而作動，並進而驅使該第一離合組件52A卡制該大太陽齒輪傳動件16、鎖定該大太陽齒輪32。該第二離合致動組60B的致動件62被該第二離合凸輪段514B之推抵曲面的凹設處而未驅使該第二離合組件52B作動，使該行星架31能旋轉。 As shown in Figure 10, Figure 12 and Figure 17, the drive gear 61 and the actuator 62 of the two clutch actuation groups 60A, 60B are driven to rotate by the shift camshaft 20; wherein, the first clutch actuation group The actuating member 62 of 60A abuts against the clutch actuating area 515 of the pushing curved surface of the first clutch cam section 514A to actuate, and then drives the first clutch assembly 52A to clamp the large sun gear transmission member 16 and lock the Big sun gear 32. The actuating member 62 of the second clutch actuating group 60B is pushed against the recess of the curved surface by the second clutch cam segment 514B and does not drive the second clutch assembly 52B, so that the planetary carrier 31 can rotate.

如圖5、圖6及圖17所示，該換檔凸輪軸20的第一同步凸輪槽22A驅動該第一同步組件40A朝向圖17的右側作動，該第一同步組件40A的第一傳動件44與該連接件14相卡掣。 As shown in Fig. 5, Fig. 6 and Fig. 17, the first synchronous cam groove 22A of the shift camshaft 20 drives the first synchronous assembly 40A to move toward the right side of Fig. 17, the first transmission member of the first synchronous assembly 40A 44 is engaged with the connector 14.

如圖5、圖6及圖17所示，該換檔凸輪軸20的第二同步凸輪槽22B驅動該第二同步組件40B朝向圖17的左側作動，該第二同步組件40B的第二傳動件45與該大太陽齒輪傳動件16相脫離。 As shown in Fig. 5, Fig. 6 and Fig. 17, the second synchronous cam groove 22B of the shift camshaft 20 drives the second synchronous assembly 40B to move toward the left side of Fig. 17, the second transmission member of the second synchronous assembly 40B 45 is disengaged from this large sun gear transmission member 16.

如圖3、圖9及圖17所示，該複合行星齒輪組30改與該第一同步組件40A相連結，該傳動軸10的輸入件11順時針地旋轉作動時，經由該第一同步組件40A的第一傳動件44帶動該連接件14順時針轉動，該連接件14之容槽142 內的該單向離合器15夾制該小太陽齒輪傳動件13且帶動該小太陽齒輪傳動件13順時針轉動，該小太陽齒輪傳動件13帶動相卡掣的該小太陽齒輪33順時針旋轉。 As shown in Fig. 3, Fig. 9 and Fig. 17, the compound planetary gear set 30 is connected to the first synchronous assembly 40A, and when the input member 11 of the transmission shaft 10 rotates clockwise, it passes through the first synchronous assembly The first transmission part 44 of 40A drives this connecting part 14 to rotate clockwise, and the accommodation groove 142 of this connecting part 14 The inner one-way clutch 15 clamps the small sun gear transmission part 13 and drives the small sun gear transmission part 13 to rotate clockwise, and the small sun gear transmission part 13 drives the phase locked small sun gear 33 to rotate clockwise.

如圖3、圖9及圖17所示，該小太陽齒輪33帶動三該短軸行星齒輪34逆時針旋轉，三該長軸行星齒輪35順時針旋轉，該輸出環齒輪36順時針旋轉，使裝設有本創作的車輛能前進。 As shown in Figure 3, Figure 9 and Figure 17, the small sun gear 33 drives the three short-axis planetary gears 34 to rotate counterclockwise, the three long-axis planetary gears 35 to rotate clockwise, and the output ring gear 36 to rotate clockwise, so that The vehicle equipped with this creation can advance.

當該傳動軸10進行減速時，由於該小太陽齒輪33的轉速大於該傳動軸10的輸入件11，該單向離合器15鬆開該小太陽齒輪傳動件13，達到無引擎煞車的效果。 When the transmission shaft 10 is decelerating, since the rotation speed of the small sun gear 33 is greater than the input member 11 of the transmission shaft 10, the one-way clutch 15 releases the small sun gear transmission member 13, thereby achieving the effect of no engine braking.

D₃檔： D ₃ files:

如圖18所示的本創作D₃檔配置，該大太陽齒輪傳動件16與該大太陽齒輪32相連結。 As shown in FIG. 18 , the _third gear configuration of D in the present invention, the large sun gear transmission member 16 is connected with the large sun gear 32 .

如圖5、圖6及圖18所示，該換檔凸輪軸20旋轉，該駐車組70未作動、該輸出環齒輪36能夠進行輸出；兩該同步組件40A、40B朝向圖18的右側作動，該第一同步組件40A的第一傳動件44與該連接件14相卡掣，該第一同步組件40A與該複合行星齒輪組30的小太陽齒輪33相連結，該第二同步組件40B的第二傳動件45與該複合行星齒輪組30的大太陽齒輪32相連結。 As shown in Fig. 5, Fig. 6 and Fig. 18, the shift camshaft 20 rotates, the parking group 70 is not actuated, and the output ring gear 36 can output; The first transmission member 44 of the first synchronous assembly 40A is engaged with the connecting member 14, the first synchronous assembly 40A is connected with the small sun gear 33 of the compound planetary gear set 30, the second synchronous assembly 40B is The second transmission member 45 is connected with the large sun gear 32 of the compound planetary gear set 30 .

如圖10、圖12及圖18所示，兩該離合致動組60A、60B的致動件62分別抵靠於兩該離合凸輪段514A、514B之推抵曲面的凹設處，而未驅使兩該離合組件52A、52B作動，使該大太陽齒輪32和該行星架31未被鎖定且能夠旋轉。 As shown in Fig. 10, Fig. 12 and Fig. 18, the actuating parts 62 of the two clutch actuating groups 60A, 60B respectively abut against the recesses of the pushing curved surfaces of the two clutch cam sections 514A, 514B, without driving The two clutch assemblies 52A, 52B are actuated, so that the large sun gear 32 and the planet carrier 31 are not locked and can rotate.

如圖3、圖9及圖18所示，該傳動軸10的輸入件11順時針地旋轉。該傳動軸10提供的動力經由該第一同步組件40A的第一傳動件44、該連接件14、該單向離合器15、該小太陽齒輪傳動件13傳遞至該小太陽齒輪33、帶動 該小太陽齒輪33順時針旋轉。該傳動軸10提供的動力也經由該第二同步組件40B的第二傳動件45、該大太陽齒輪傳動件16傳遞至該大太陽齒輪32、帶動該大太陽齒輪32順時針旋轉。 As shown in FIG. 3 , FIG. 9 and FIG. 18 , the input member 11 of the transmission shaft 10 rotates clockwise. The power provided by the transmission shaft 10 is transmitted to the small sun gear 33 through the first transmission member 44 of the first synchronous assembly 40A, the connecting member 14, the one-way clutch 15, and the small sun gear transmission member 13, driving The small sun gear 33 rotates clockwise. The power provided by the transmission shaft 10 is also transmitted to the large sun gear 32 via the second transmission member 45 of the second synchronous assembly 40B and the large sun gear transmission member 16 , driving the large sun gear 32 to rotate clockwise.

如圖3、圖9及圖18所示，順時針旋轉的該小太陽齒輪33及順時針旋轉的大太陽齒輪32分別藉由所述短軸行星齒輪34及所述該長軸行星齒輪35分別帶動該輸出環齒輪36及該行星架31順時針旋轉。減速時，該傳動軸10提供的動力經由該大太陽齒輪32順轉而達到有引擎煞車的效果。 As shown in Fig. 3, Fig. 9 and Fig. 18, the small sun gear 33 rotating clockwise and the large sun gear 32 rotating clockwise are respectively driven by the short-axis planetary gear 34 and the long-axis planetary gear 35 respectively. Drive the output ring gear 36 and the planet carrier 31 to rotate clockwise. When decelerating, the power provided by the transmission shaft 10 rotates clockwise through the large sun gear 32 to achieve the effect of engine braking.

D₄檔： D ₄ files:

如圖19所示的本創作D₄檔配置，請配合參看圖5及圖6，該大太陽齒輪傳動件16與該大太陽齒輪32相連結。該換檔凸輪軸20旋轉，該駐車組70未作動、該輸出環齒輪36能夠進行輸出；兩該同步組件40A、40B朝向圖19的左側作動，該第一同步組件40A的第一傳動件44與該行星架傳動件12的卡掣齒輪部121相卡掣；該第二同步組件40B的第二傳動件45與該大太陽齒輪傳動件16相離脫而未與該大太陽齒輪32相連結。該第一離合組件52A作動，使該大太陽齒輪32被鎖定。 As shown in Figure 19, the creation D ₄ gear configuration, please refer to Figure 5 and Figure 6, the big sun gear transmission part 16 is connected with the big sun gear 32. The shift camshaft 20 rotates, the parking group 70 is not activated, and the output ring gear 36 can output; the two synchronous assemblies 40A, 40B move toward the left side of FIG. 19 , and the first transmission member 44 of the first synchronous assembly 40A Engaged with the locking gear part 121 of the planet carrier transmission member 12; the second transmission member 45 of the second synchronization assembly 40B is separated from the large sun gear transmission member 16 and is not connected with the large sun gear 32 . The first clutch assembly 52A is actuated to lock the large sun gear 32 .

如圖3、圖9及圖19所示，該傳動軸10的輸入件11順時針地旋轉作動時，該第一傳動件44帶動該行星架傳動件12順時針旋轉，該行星架31與該行星架傳動件12相卡掣且被該行星架傳動件12帶動而順時針旋轉，三該長軸行星齒輪35繞該大太陽齒輪32順時針地旋轉，且該輸出環齒輪36順時針旋轉。當該傳動軸10減速時，該行星架31隨之減速，達到有引擎煞車的效果。 As shown in Figure 3, Figure 9 and Figure 19, when the input member 11 of the transmission shaft 10 rotates clockwise, the first transmission member 44 drives the planetary carrier transmission member 12 to rotate clockwise, and the planetary carrier 31 and the The planet carrier transmission member 12 is locked in phase and is driven by the planet carrier transmission member 12 to rotate clockwise. The three long-axis planetary gears 35 rotate clockwise around the large sun gear 32 and the output ring gear 36 rotates clockwise. When the transmission shaft 10 decelerates, the planetary carrier 31 decelerates accordingly to achieve the effect of engine braking.

10:傳動軸 10: Drive shaft

11:輸入件 11: Input piece

111:輸入端 111: input terminal

12:行星架傳動件 12:Planet carrier transmission parts

13:小太陽齒輪傳動件 13: Small sun gear transmission part

14:連接件 14:Connector

15:單向離合器 15: One-way clutch

20:換檔凸輪軸 20: Shift camshaft

23:從動齒輪 23: driven gear

30:複合行星齒輪組 30: compound planetary gear set

31:行星架 31:Planet carrier

32:大太陽齒輪 32: Big sun gear

33:小太陽齒輪 33:Small sun gear

34:短軸行星齒輪 34: Minor axis planetary gear

35:長軸行星齒輪 35:Long shaft planetary gear

36:輸出環齒輪 36: Output ring gear

361:駐車卡制口 361: Parking card opening

40A:第一同步組件 40A: first synchronization component

40B:第二同步組件 40B: second synchronization component

44:第一傳動件 44: The first transmission member

45:第二傳動件 45: Second transmission member

50:離合組 50: clutch group

51:中央導引座 51: Central guide seat

52A:第一離合組件 52A: The first clutch assembly

52B:第二離合組件 52B: Second clutch assembly

521:離合件 521: Clutch

60A:第一離合致動組 60A: The first clutch actuation group

60B:第二離合致動組 60B: The second clutch actuation group

61:驅動齒輪 61: Drive gear

70:駐車組 70:Parking group

71:駐車凸輪 71: Parking cam

72:駐車爪 72:Park pawl

721:卡制勾 721: card system hook

80:驅動組 80: drive group

81:馬達 81: motor

82:蝸桿 82: Worm

Claims (10)

一種改良型變速機構，其包括有：一傳動軸，其係能受驅動而旋轉；一換檔凸輪軸，其與該傳動軸相平行且能受驅動而旋轉，該換檔凸輪軸包括有一軸體及兩同步凸輪槽，各該同步凸輪槽環設於該軸體，且兩該同步凸輪槽間隔地設置；一複合行星齒輪組，其能與該傳動軸相連結且能受該傳動軸驅動而作動；兩同步組件，兩該同步組件能與該複合行星齒輪組相連結且分別結合於兩該同步凸輪槽，兩該同步組件能分別受兩該同步凸輪槽所驅動而沿著該換檔凸輪軸往復活動；一離合組，其包括有一中央導引座及兩離合組件；該中央導引座係用於固結於一離合器轂且包括有一套管部及兩離合凸輪段；該套管部呈圓管狀、包括有一軸向，以及於該套管部之軸向上位置相對的兩端，且該套管部同軸地套設於該傳動軸；各該離合凸輪段環設於該套管部的外周面且包括有一推抵曲面，兩該離合凸輪段的推抵曲面分別朝向該套管部的兩端；各該離合組件包括有多數個離合件，各該離合件與該套管部同軸設置、能沿著該套管部的軸向往復活動且與該複合行星齒輪組相連結；以及兩離合致動組，各該離合致動組包括有一驅動齒輪及一致動件；該驅動齒輪結合於該換檔凸輪軸且能隨著該換檔凸輪軸旋轉；該致動件呈環狀、能轉動地套設於該套管部，且包括有與該驅動齒輪相嚙合的一致動環齒輪，該致動環齒輪的側面間隔地環設有多數個致動抵部； 兩該離合致動組之兩致動件的兩致動環齒輪分別以所設的致動抵部抵靠於兩該離合凸輪段，兩該致動環齒輪能受兩該離合凸輪段所推抵，而使兩該致動件於沿著該套管部活動、推抵兩該離合組件。 An improved transmission mechanism, which includes: a transmission shaft, which can be driven to rotate; a shift camshaft, which is parallel to the transmission shaft and can be driven to rotate, and the shift camshaft includes a shaft Body and two synchronous cam grooves, each synchronous cam groove ring is set on the shaft body, and the two synchronous cam grooves are arranged at intervals; a compound planetary gear set, which can be connected with the transmission shaft and can be driven by the transmission shaft and actuate; two synchronous components, the two synchronous components can be connected with the compound planetary gear set and respectively combined with the two synchronous cam slots, and the two synchronous components can be driven by the two synchronous cam slots to shift along the gear The camshaft reciprocates; a clutch group, which includes a central guide seat and two clutch assemblies; the central guide seat is used to be fixed on a clutch hub and includes a sleeve part and two clutch cam segments; the sleeve The part is in the shape of a circular tube, including an axial direction, and two ends opposite to the axial direction of the sleeve part, and the sleeve part is coaxially sleeved on the transmission shaft; each of the clutch cam segments is arranged on the sleeve The outer peripheral surface of the part and includes a push-off curved surface, and the push-off curved surfaces of the two clutch cam segments are respectively facing the two ends of the sleeve part; each of the clutch assemblies includes a plurality of clutch parts, each of the clutch parts and the sleeve part Coaxially arranged, able to reciprocate along the axial direction of the casing part and connected with the compound planetary gear set; and two clutch actuation groups, each of which includes a driving gear and an actuating member; the driving gear Combined with the shift camshaft and capable of rotating with the shift camshaft; the actuating member is ring-shaped, rotatably sleeved on the sleeve part, and includes an actuating ring meshing with the drive gear A gear, the side of the actuating ring gear is provided with a plurality of actuating contact parts at intervals; The two actuating ring gears of the two actuating members of the two clutch actuating groups are respectively abutted against the two clutch cam segments with the provided actuating contact parts, and the two actuating ring gears can be pushed by the two clutch cam segments Resist, so that the two actuators move along the bushing and push against the two clutch assemblies. 如請求項1所述之改良型變速機構，其中各所述離合凸輪段的推抵曲面間隔地設有多數個離合致動區，各該離合致動區包括有多數個致動凸部。 The improved speed change mechanism according to claim 1, wherein the pushing curved surface of each clutch cam section is provided with a plurality of clutch actuation areas at intervals, and each clutch actuation area includes a plurality of actuation protrusions. 如請求項2所述之改良型變速機構，其中各所述離合致動區包括有兩致動凸部，以及位於兩該致動凸部間的限制凹部。 The improved speed change mechanism according to claim 2, wherein each clutch actuation area includes two actuation protrusions, and a limiting recess located between the two actuation protrusions. 如請求項2所述之改良型變速機構，其中各所述致動件包括有一抵靠環及多數個緩衝彈性件；該抵靠環同軸地與該致動件的致動環齒輪藉由多數個定位件相結合；該多數個緩衝彈性件介於該致動環齒輪與該抵靠環之間、分別套置於該多數個定位件，且各該緩衝彈性件的兩端分別抵靠於該致動環齒輪與該抵靠環。 The improved transmission mechanism as described in claim 2, wherein each said actuator includes an abutment ring and a plurality of buffer elastic members; the abutment ring is coaxial with the actuating ring gear of the actuating member through a plurality of The plurality of positioning parts are combined; the plurality of buffer elastic parts are interposed between the actuation ring gear and the abutment ring, respectively sleeved in the plurality of positioning parts, and the two ends of each of the buffer elastic parts are respectively against the two ends of the buffer elastic parts. The actuation ring gear and the abutment ring. 如請求項4所述之改良型變速機構，其中所述的中央導引座包括有兩輔助導溝，兩該輔助導溝分別靠近該中央導引座之套管部的兩端，各該輔助導溝凹設於該套管部的外周面且波浪起伏地環繞該套管部；各所述致動件的致動環齒輪於於內周緣間隔地環設有多數個導引凸部，兩所述致動件之兩致動環齒輪分別以所設的導引凸部插置於該套管部的兩輔助導溝。 The improved transmission mechanism as described in claim 4, wherein the central guide seat includes two auxiliary guide grooves, and the two auxiliary guide grooves are respectively close to the two ends of the sleeve part of the central guide seat, and each of the auxiliary guide grooves The guide groove is recessed on the outer peripheral surface of the casing part and surrounds the casing part undulatingly; the actuating ring gear of each said actuating member is provided with a plurality of guiding convex parts at intervals on the inner peripheral edge, and the two sides The two actuating ring gears of the actuating member are respectively inserted into the two auxiliary guiding grooves of the casing part with the provided guiding protrusions. 如請求項1所述之改良型變速機構，其中各所述致動件包括有一抵靠環及多數個緩衝彈性件；該抵靠環同軸地與該致動件的致動環齒輪相結合；該多數個緩衝彈性件介於該致動環齒輪與該抵靠環之間，且各該緩衝彈性件的兩端分別抵靠於該致動環齒輪與該抵靠環。 The improved speed change mechanism as described in Claim 1, wherein each said actuating member includes an abutment ring and a plurality of cushioning elastic members; the abutting ring is coaxially combined with the actuating ring gear of the actuating member; The plurality of cushioning elastic pieces are interposed between the actuating ring gear and the abutment ring, and two ends of each of the buffering elastic pieces abut against the actuating ring gear and the abutting ring respectively. 如請求項2、4或6中任一項所述之改良型變速機構，其中各所述離合件包括有同軸設置的一卡制環及一摩擦環；該摩擦環的兩平面粗糙，且其外徑小於該卡制環的外徑。 The improved transmission mechanism as described in any one of claim 2, 4 or 6, wherein each of the clutch members includes a snap ring and a friction ring coaxially arranged; the two planes of the friction ring are rough, and the The outer diameter is smaller than the outer diameter of the clamping ring. 如請求項7所述之改良型變速機構，其中各所述離合件包括有一波形彈簧；該離合件的波形彈簧與該離合件的卡制環和摩擦環同軸設置；各所述離合組件的多數個離合件以所設的波形彈簧相抵靠。 The improved transmission mechanism as described in claim 7, wherein each of the clutch parts includes a wave spring; the wave spring of the clutch part is coaxially arranged with the snap ring and the friction ring of the clutch part; most of the clutch components The two clutch parts lean against each other with the set wave spring. 如請求項1所述之改良型變速機構，其包括有一駐車組，所述的駐車組包括有一駐車凸輪及一駐車爪；該駐車凸輪結合於所述換檔凸輪軸的軸體且能推抵該駐車爪，使該駐車爪與所述複合行星齒輪組相卡制。 The improved transmission mechanism as described in claim 1, which includes a parking group, the parking group includes a parking cam and a parking pawl; the parking cam is combined with the shaft of the shift camshaft and can be pushed against The parking pawl is used to clamp the parking pawl to the compound planetary gear set. 如請求項1所述之改良型變速機構，其包括有一驅動組，該驅動組包括有一馬達、一蝸桿、一蝸輪及一驅動齒輪；該蝸桿結合於該馬達的馬達軸而能受該馬達所驅動；該蝸輪和該驅動齒輪同軸地設置且能同步旋轉，該蝸輪與該蝸桿相嚙合；所述換檔凸輪軸包括有同軸地設於所述軸體的一從動齒輪，該驅動齒輪與該從動齒輪相嚙合。The improved transmission mechanism as described in claim 1, which includes a driving group, the driving group includes a motor, a worm, a worm wheel and a driving gear; the worm is combined with the motor shaft of the motor and can be controlled by the motor drive; the worm gear and the drive gear are coaxially arranged and can rotate synchronously, the worm gear is meshed with the worm; the shift camshaft includes a driven gear coaxially arranged on the shaft body, the drive gear and The driven gear meshes.

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