JP6343925B2 - Dual clutch transmission - Google Patents

Dual clutch transmission Download PDF

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JP6343925B2
JP6343925B2 JP2013262499A JP2013262499A JP6343925B2 JP 6343925 B2 JP6343925 B2 JP 6343925B2 JP 2013262499 A JP2013262499 A JP 2013262499A JP 2013262499 A JP2013262499 A JP 2013262499A JP 6343925 B2 JP6343925 B2 JP 6343925B2
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gear train
gear
shaft
input shaft
output shaft
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JP2015117793A (en
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将 尾▲崎▼
将 尾▲崎▼
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Isuzu Motors Ltd
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Isuzu Motors Ltd
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    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0933—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with coaxial countershafts
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H3/097—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts the input and output shafts being aligned on the same axis

Description

本発明は、デュアルクラッチ式変速機に関する。   The present invention relates to a dual clutch transmission.

従来、駆動源からの動力を断接する第１クラッチを有する第１入力軸と、駆動源からの動力を断接する第２クラッチを有する第２入力軸と、出力軸及び副軸に設けられた複数の変速用ギヤ列とを備え、第１クラッチ及び第２クラッチを交互に切り替えることで変速を行うデュアルクラッチ式変速機が知られている（例えば、特許文献１参照）。   2. Description of the Related Art Conventionally, a first input shaft having a first clutch for connecting / disconnecting power from a drive source, a second input shaft having a second clutch for connecting / disconnecting power from a drive source, and a plurality of output shafts and auxiliary shafts. There is known a dual-clutch transmission that has a gear train for shifting and that performs shifting by alternately switching a first clutch and a second clutch (see, for example, Patent Document 1).

特開２０１０−５３１４１７号公報JP 2010-531417 A

従来型のデュアルクラッチ式変速機の一例を図１３に示す。このデュアルクラッチ式変速機では、第１入力軸１１０及び第２入力軸１２０にそれぞれ設けられた２個のプライマリギヤ列１３０，１４０と、出力軸２００及び副軸２１０に設けられた３個の変速用ギヤ列２２０，２３０，２４０とを備え、５速時に第１入力軸１１０と出力軸２００とを直結し、６速時にプライマリギヤ列１４０を変速用ギヤ列として再利用することで、前進６段の変速を実現させている。   An example of a conventional dual clutch transmission is shown in FIG. In this dual clutch transmission, two primary gear trains 130 and 140 provided on the first input shaft 110 and the second input shaft 120, respectively, and three shifts provided on the output shaft 200 and the sub shaft 210 are provided. The first input shaft 110 and the output shaft 200 are directly connected at the fifth speed, and the primary gear train 140 is reused as the gear train for shifting at the sixth speed. The stage shift is realized.

しかしながら、このような従来型のデュアルクラッチ式変速機でさらなる増段を実現させるためには、変速用ギヤ列及び、シンクロ機構の追加が必要となり、装置全体の大型化や重量増加、コストの上昇等を招く課題がある。   However, in order to realize a further step increase in such a conventional dual clutch transmission, it is necessary to add a gear train for shifting and a synchro mechanism, which increases the size, weight, and cost of the entire device. There is a problem that invites.

本発明の目的は、大型化や重量増加を抑制しつつ、変速段数を効果的に増加することができるデュアルクラッチ式変速機を提供することにある。   An object of the present invention is to provide a dual clutch transmission that can effectively increase the number of shift stages while suppressing an increase in size and weight.

上述の目的を達成するため、本発明のデュアルクラッチ式変速機は、駆動源からの動力を断接する第１クラッチを有する第１入力軸と、前記駆動源からの動力を断接する第２クラッチを有すると共に前記第１入力軸が回転自在に挿通された第２入力軸と、前記第１入力軸と同軸に配置された出力軸と、前記第１入力軸、前記第２入力軸及び、前記出力軸と平行に配置された副軸と、前記第１入力軸と前記副軸とに回転自在に設けられた第１ギヤ列、前記出力軸と前記副軸とに回転自在に設けられた第２ギヤ列、前記第１ギヤ列と前記第２ギヤ列とを前記第１入力軸に選択的に同期させる第１同期機構、前記第１ギヤ列と前記第２ギヤ列とを前記副軸に選択的に同期させる第２同期機構及び、前記第２ギヤ列を前記出力軸に選択的に同期させる第３同期機構を有する第１スプリッタ変速部と、前記第２入力軸又は前記副軸の一方に回転自在に設けられた第３ギヤ列、前記第１入力軸又は前記副軸の一方に回転自在に設けられた第４ギヤ列及び、前記第３ギヤ列と前記第４ギヤ列とを前記第２入力軸又は前記副軸に選択的に同期させる第４同期機構を有する第２スプリッタ変速部とを備えることを特徴とする。   In order to achieve the above-described object, a dual clutch transmission of the present invention includes a first input shaft having a first clutch for connecting / disconnecting power from a drive source and a second clutch for connecting / disconnecting power from the drive source. A second input shaft rotatably inserted in the first input shaft, an output shaft arranged coaxially with the first input shaft, the first input shaft, the second input shaft, and the output A secondary shaft disposed in parallel with the shaft, a first gear train rotatably provided on the first input shaft and the secondary shaft, and a second gear rotatably provided on the output shaft and the secondary shaft. A first synchronization mechanism that selectively synchronizes the gear train, the first gear train and the second gear train with the first input shaft, and the first gear train and the second gear train are selected as the auxiliary shaft. A second synchronizing mechanism that synchronizes automatically and the second gear train is selectively synchronized with the output shaft A first splitter transmission having a three-synchronization mechanism; a third gear train rotatably provided on one of the second input shaft or the sub-shaft; and rotatable on one of the first input shaft or the sub-shaft. A fourth gear train provided, and a second splitter transmission having a fourth synchronization mechanism for selectively synchronizing the third gear train and the fourth gear train to the second input shaft or the sub shaft. It is characterized by providing.

また、前記第１ギヤ列及び前記第２ギヤ列の副軸側のギヤが互いに一体形成されることが好ましい。   Moreover, it is preferable that the gears on the sub-shaft side of the first gear train and the second gear train are integrally formed with each other.

また、所定の低速段において、前記第１同期機構で前記第２入力ギヤ列と前記第１入力軸とを同期させると共に、前記第５同期機構で前記第５ギヤ列と前記出力軸とを同期させて、前記第２入力ギヤ列及び前記第５ギヤ列のギヤ比を用いて減速を行い、所定の高速段において、前記第１同期機構で前記第１入力ギヤ列と前記第１入力軸とを同期させると共に、前記第３同期機構で前記第２入力ギヤ列と前記出力軸とを同期させて、前記第１入力軸及び前記出力軸を直結するものであってもよい。   Further, at a predetermined low speed stage, the first synchronization mechanism synchronizes the second input gear train and the first input shaft, and the fifth synchronization mechanism synchronizes the fifth gear train and the output shaft. The first input gear train and the first input shaft are decelerated using the gear ratios of the second input gear train and the fifth gear train, and the first synchronizing mechanism is used for the predetermined high speed stage. And the second input gear train and the output shaft may be synchronized by the third synchronization mechanism to directly connect the first input shaft and the output shaft.

本発明のデュアルクラッチ式変速機によれば、大型化や重量増加を抑制しつつ、変速段数を効果的に増加することができる。   According to the dual clutch transmission of the present invention, it is possible to effectively increase the number of shift stages while suppressing an increase in size and weight.

本発明の一実施形態に係るデュアルクラッチ式変速機を示す模式的なスケルトン図である。1 is a schematic skeleton diagram showing a dual clutch transmission according to an embodiment of the present invention. 他の実施形態に係るデュアルクラッチ式変速機の一例を示す模式的なスケルトン図である。It is a typical skeleton figure which shows an example of the dual clutch type transmission which concerns on other embodiment. 図１に示すデュアルクラッチ式変速機の１速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 1st speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の２速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 2nd speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の３速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 3rd speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の４速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 4th speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の５速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 5th speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の６速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 6th speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の７速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 7th speed of the dual clutch transmission shown in FIG. 図１に示すデュアルクラッチ式変速機の８速時の動力伝達経路を示す図である。It is a figure which shows the power transmission path | route at the time of the 8th speed of the dual clutch transmission shown in FIG. 他の実施形態に係るデュアルクラッチ式変速機の一例を示す模式的なスケルトン図である。It is a typical skeleton figure which shows an example of the dual clutch type transmission which concerns on other embodiment. 他の実施形態に係るデュアルクラッチ式変速機の一例を示す模式的なスケルトン図である。It is a typical skeleton figure which shows an example of the dual clutch type transmission which concerns on other embodiment. 従来型のデュアルクラッチ式変速機の一例を示す模式的なスケルトン図である。It is a typical skeleton diagram showing an example of a conventional dual clutch transmission.

以下、添付図面に基づいて、本発明の一実施形態に係るデュアルクラッチ式変速機を説明する。同一の部品には同一の符号を付してあり、それらの名称および機能も同じである。したがって、それらについての詳細な説明は繰返さない。   Hereinafter, a dual clutch transmission according to an embodiment of the present invention will be described with reference to the accompanying drawings. The same parts are denoted by the same reference numerals, and their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

図１に示すように、第１入力軸１１の入力側端には、第１クラッチ１０が設けられている。第２入力軸１３の入力側端には、第２クラッチ１２が設けられている。また、第２入力軸１３には、軸方向に貫通する中空軸が形成されると共に、この中空軸には第１入力軸１１が相対回転自在に挿通されている。   As shown in FIG. 1, a first clutch 10 is provided at the input side end of the first input shaft 11. A second clutch 12 is provided at the input side end of the second input shaft 13. The second input shaft 13 is formed with a hollow shaft penetrating in the axial direction, and the first input shaft 11 is inserted into the hollow shaft so as to be relatively rotatable.

出力軸１４は、第１入力軸１１と同軸上に間隔を隔てて配置されている。副軸１５は、入力軸１１，１３及び、出力軸１４と間隔を隔てて平行に配置されている。   The output shaft 14 is arranged coaxially with the first input shaft 11 and spaced apart. The auxiliary shaft 15 is disposed in parallel with the input shafts 11 and 13 and the output shaft 14 with a space therebetween.

第１クラッチ１０は、エンジン２のクランクシャフト３に固定された第１プレッシャプレート１０Ａと、第１入力軸１１の入力側端に固定された第１クラッチディスク１０Ｂとを備えている。第１プレッシャプレート１０Ａが移動して第１クラッチディスク１０Ｂに圧接すると、エンジン２の動力は第１クラッチ１０を介して第１入力軸１１に伝達される。   The first clutch 10 includes a first pressure plate 10A fixed to the crankshaft 3 of the engine 2 and a first clutch disk 10B fixed to the input side end of the first input shaft 11. When the first pressure plate 10 </ b> A moves and presses against the first clutch disk 10 </ b> B, the power of the engine 2 is transmitted to the first input shaft 11 via the first clutch 10.

第２クラッチ１２は、エンジン２のクランクシャフト３に固定された第２プレッシャプレート１２Ａと、第２入力軸１３の入力側端に固定された第２クラッチディスク１２Ｂとを備えている。第２プレッシャプレート１２Ａが移動して第２クラッチディスク１２Ｂに圧接すると、エンジン２の動力は第２クラッチ１２を介して第２入力軸１３に伝達される。   The second clutch 12 includes a second pressure plate 12A fixed to the crankshaft 3 of the engine 2 and a second clutch disk 12B fixed to the input side end of the second input shaft 13. When the second pressure plate 12A moves and comes into pressure contact with the second clutch disk 12B, the power of the engine 2 is transmitted to the second input shaft 13 via the second clutch 12.

第１スプリッタ変速部２０は、第１高速ギヤ列２１と、第１低速ギヤ列２２と、第１シンクロ機構２３と、第２シンクロ機構２４と、第３シンクロ機構２５とを備えている。   The first splitter transmission 20 includes a first high speed gear train 21, a first low speed gear train 22, a first sync mechanism 23, a second sync mechanism 24, and a third sync mechanism 25.

第１高速ギヤ列２１は、本発明の第１ギヤ列の一例であって、第１入力軸１１に相対回転自在に設けられた第１入力軸ギヤ２１Ａと、副軸１５に相対回転自在に設けられて第１入力軸ギヤ２１Ａと常時噛合する第１副軸ギヤ２１Ｂとを有する。   The first high-speed gear train 21 is an example of the first gear train of the present invention. The first high-speed gear train 21 is relatively rotatable with respect to the first input shaft gear 21 </ b> A provided on the first input shaft 11 and relatively rotatable with respect to the auxiliary shaft 15. A first countershaft gear 21B that is provided and always meshes with the first input shaft gear 21A.

第１低速ギヤ列２２は、本発明の第２ギヤ列の一例であって、出力軸１４に相対回転自在に設けられた第１出力軸ギヤ２２Ａと、副軸１５に相対回転自在に設けられて第１出力軸ギヤ２２Ａと常時噛合する第２副軸ギヤ２２Ｂとを有する。第２副軸ギヤ２２Ｂは、第１副軸ギヤ２１Ｂと一体形成されており、その中空軸内には副軸１５が挿通されている。   The first low speed gear train 22 is an example of the second gear train of the present invention, and is provided on the output shaft 14 so as to be relatively rotatable and on the auxiliary shaft 15 so as to be relatively rotatable. And a second countershaft gear 22B that always meshes with the first output shaft gear 22A. The second countershaft gear 22B is formed integrally with the first countershaft gear 21B, and the countershaft 15 is inserted into the hollow shaft.

第１シンクロ機構２３は、第１入力軸１１の出力側端に固定されたシンクロハブ２３Ａと、シンクロハブ２３Ａに回転不能且つ軸方向に移動可能に設けられた第１スリーブ２３Ｂと、第１入力軸ギヤ２１Ａに固定されたドグギヤ２３Ｃと、第１出力軸ギヤ２２Ａに固定されたドグギヤ２３Ｄとを備えている。   The first sync mechanism 23 includes a sync hub 23A fixed to the output side end of the first input shaft 11, a first sleeve 23B provided on the sync hub 23A so as not to be rotatable and movable in the axial direction, and a first input. A dog gear 23C fixed to the shaft gear 21A and a dog gear 23D fixed to the first output shaft gear 22A are provided.

第１スリーブ２３Ｂが第１入力軸ギヤ２１Ａ側に移動してドグギヤ２３Ｃと係合すると、第１入力軸ギヤ２１Ａと第１入力軸１１とが同期される。一方、第１スリーブ２３Ｂが第１出力軸ギヤ２２Ａ側に移動してドグギヤ２３Ｄと係合すると、第１出力軸ギヤ２２Ａと第１入力軸１１とが同期される。すなわち、第１シンクロ機構２３によって、第１入力軸ギヤ２１Ａ及び第１出力軸ギヤ２２Ａが第１入力軸１１と選択的に同期可能に構成されている。   When the first sleeve 23B moves to the first input shaft gear 21A side and engages with the dog gear 23C, the first input shaft gear 21A and the first input shaft 11 are synchronized. On the other hand, when the first sleeve 23B moves to the first output shaft gear 22A side and engages with the dog gear 23D, the first output shaft gear 22A and the first input shaft 11 are synchronized. In other words, the first sync mechanism 23 is configured so that the first input shaft gear 21 </ b> A and the first output shaft gear 22 </ b> A can be selectively synchronized with the first input shaft 11.

第２シンクロ機構２４は、第１副軸ギヤ２１Ｂよりも入力側の副軸１５に固定されたシンクロハブ２４Ａと、シンクロハブ２４Ａに回転不能且つ軸方向に移動可能に設けられた第２スリーブ２４Ｂと、第１副軸ギヤ２１Ｂに固定されたドグギヤ２４Ｃとを備えている。すなわち、第２スリーブ２４Ｂが第１副軸ギヤ２１Ｂ側に移動してドグギヤ２４Ｃと係合すると、一体形成された第１副軸ギヤ２１Ｂ及び第２副軸ギヤ２２Ｂが副軸１５と同期するように構成されている。   The second sync mechanism 24 includes a sync hub 24A fixed to the counter shaft 15 on the input side of the first counter shaft gear 21B, and a second sleeve 24B provided on the sync hub 24A so as not to be rotatable and movable in the axial direction. And a dog gear 24C fixed to the first countershaft gear 21B. That is, when the second sleeve 24B moves toward the first countershaft gear 21B and engages with the dog gear 24C, the integrally formed first countershaft gear 21B and second countershaft gear 22B are synchronized with the countershaft 15. It is configured.

第３シンクロ機構２５は、第１出力軸ギヤ２２Ａよりも出力側の出力軸１４に固定されたシンクロハブ２５Ａと、シンクロハブ２５Ａに回転不能且つ軸方向に移動可能に設けられた第３スリーブ２５Ｂと、第１出力軸ギヤ２２Ａに固定されたドグギヤ２５Ｃとを備えている。すなわち、第３スリーブ２４Ｂが第１出力軸ギヤ２２Ａ側に移動してドグギヤ２５Ｃと係合すると、第１出力軸ギヤ２２Ａが出力軸１４と同期するように構成されている。   The third sync mechanism 25 includes a sync hub 25A that is fixed to the output shaft 14 on the output side of the first output shaft gear 22A, and a third sleeve 25B that is provided on the sync hub 25A so as not to rotate but to move in the axial direction. And a dog gear 25C fixed to the first output shaft gear 22A. That is, the first output shaft gear 22A is configured to synchronize with the output shaft 14 when the third sleeve 24B moves to the first output shaft gear 22A side and engages with the dog gear 25C.

第２スプリッタ変速部３０は、第２高速ギヤ列３１と、第２低速ギヤ列３２と、第４シンクロ機構３３とを備えている。   The second splitter transmission unit 30 includes a second high speed gear train 31, a second low speed gear train 32, and a fourth sync mechanism 33.

第２高速ギヤ列３１は、本発明の第３ギヤ列の一例であって、第２入力軸１３に相対回転自在に設けられた第２入力軸ギヤ３１Ａと、副軸１５に固定されて第３入力軸ギヤ３１Ａと常時噛合する第３副軸ギヤ３１Ｂとを有する。   The second high-speed gear train 31 is an example of a third gear train according to the present invention, and is fixed to the second input shaft gear 31 </ b> A provided on the second input shaft 13 so as to be rotatable relative to the second input shaft 13 and the second shaft 15. And a third countershaft gear 31B that always meshes with the three input shaft gear 31A.

第２低速ギヤ列３２は、本発明の第４ギヤ列の一例であって、第１入力軸１１に相対回転自在に設けられた第３入力軸ギヤ３２Ａと、副軸１５に固定されて第４入力軸ギヤ３２Ａと常時噛合する第４副軸ギヤ３２Ｂとを有する。   The second low-speed gear train 32 is an example of a fourth gear train according to the present invention, and is fixed to the first input shaft 11 and a third input shaft gear 32 </ b> A that is relatively rotatable with the first input shaft 11. It has a fourth countershaft gear 32B that always meshes with the four input shaft gear 32A.

第４シンクロ機構３３は、第２入力軸１３の出力側端に固定されたシンクロハブ３３Ａと、シンクロハブ３３Ａに回転不能且つ軸方向に移動可能に設けられた第４スリーブ３３Ａと、第２入力軸ギヤ３１Ａに固定されたドグギヤ３３Ｃと、第３入力軸ギヤ３２Ａに固定されたドグギヤ３３Ｄとを備えている。   The fourth synchronization mechanism 33 includes a synchronization hub 33A fixed to the output side end of the second input shaft 13, a fourth sleeve 33A provided on the synchronization hub 33A so as not to rotate and to be movable in the axial direction, and a second input. A dog gear 33C fixed to the shaft gear 31A and a dog gear 33D fixed to the third input shaft gear 32A are provided.

第４スリーブ３３Ｂが第２入力軸ギヤ３１Ａ側に移動してドグギヤ３３Ｃと係合すると、第２入力軸ギヤ３１Ａと第２入力軸１３とが同期される。一方、第４スリーブ３３Ｂが第３入力軸ギヤ３２Ａ側に移動してドグギヤ３３Ｄと係合すると、第３入力軸ギヤ３２Ａと第２入力軸１３とが同期される。すなわち、第４シンクロ機構３３によって、第２入力軸ギヤ３１Ａ及び第３入力軸ギヤ３２Ａが第２入力軸１３と選択的に同期可能に構成されている。   When the fourth sleeve 33B moves to the second input shaft gear 31A side and engages with the dog gear 33C, the second input shaft gear 31A and the second input shaft 13 are synchronized. On the other hand, when the fourth sleeve 33B moves to the third input shaft gear 32A side and engages with the dog gear 33D, the third input shaft gear 32A and the second input shaft 13 are synchronized. That is, the fourth sync mechanism 33 is configured so that the second input shaft gear 31 </ b> A and the third input shaft gear 32 </ b> A can be selectively synchronized with the second input shaft 13.

なお、図２に示すように、第４シンクロ機構３３を副軸１５側に設けて構成してもよい。この場合は、第２入力軸ギヤ３１Ａ及び第３入力軸ギヤ３２Ａを第２入力軸１３に固定すると共に、第３副軸ギヤ３１Ｂ及び第４副軸ギヤ３２Ｂを副軸１５に相対回転自在に設ければよい。   In addition, as shown in FIG. 2, you may comprise the 4th synchro mechanism 33 in the subshaft 15 side. In this case, the second input shaft gear 31A and the third input shaft gear 32A are fixed to the second input shaft 13, and the third countershaft gear 31B and the fourth countershaft gear 32B are relatively rotatable with respect to the subshaft 15. What is necessary is just to provide.

低速段用ギヤ列４０は、出力軸１４に相対回転自在に設けられた第２出力軸ギヤ４０Ａと、副軸１５に固定されて第２出力軸ギヤ４０Ａと常時噛合する第５副軸ギヤ４０Ｂとを有する。   The low-speed stage gear train 40 includes a second output shaft gear 40A that is rotatably provided on the output shaft 14 and a fifth countershaft gear 40B that is fixed to the countershaft 15 and constantly meshes with the second output shaft gear 40A. And have.

リバース用ギヤ列５０は、出力軸１４に相対回転自在に設けられた第３出力軸ギヤ５０Ａと、副軸１５に固定されて第３出力軸ギヤ５０Ａと常時噛合する第６副軸ギヤ５０Ｂと、第６副軸ギヤ５０Ｂと常時噛合するアイドラギヤ５０Ｃとを有する。   The reverse gear train 50 includes a third output shaft gear 50A that is rotatably provided on the output shaft 14, and a sixth countershaft gear 50B that is fixed to the countershaft 15 and constantly meshes with the third output shaft gear 50A. The idler gear 50C always meshes with the sixth countershaft gear 50B.

第５シンクロ機構６０は、第２出力軸ギヤ４０Ａと第３出力軸ギヤ５０Ａとの間の出力軸１４に固定されたシンクロハブ６０Ａと、シンクロハブ６０Ａに回転不能且つ軸方向に移動可能に設けられた第５スリーブ６０Ｂと、第２出力軸ギヤ４０Ａに固定されたドグギヤ６０Ｃと、第３出力軸ギヤ５０Ａに固定されたドグギヤ６０Ｄとを備えている。   The fifth sync mechanism 60 is provided with a sync hub 60A fixed to the output shaft 14 between the second output shaft gear 40A and the third output shaft gear 50A, and provided in the sync hub 60A so as not to be rotatable and movable in the axial direction. The fifth sleeve 60B, a dog gear 60C fixed to the second output shaft gear 40A, and a dog gear 60D fixed to the third output shaft gear 50A are provided.

第５スリーブ６０Ｂが第２出力軸ギヤ４０Ａ側に移動してドグギヤ６０Ｃと係合すると、第２出力軸ギヤ４０Ａと出力軸１４とが同期される。一方、第５スリーブ６０Ｂが第３出力軸ギヤ５０Ａ側に移動してドグギヤ６０Ｄと係合すると、第１出力軸ギヤ２２Ａと出力軸１４とが同期される。すなわち、第５シンクロ機構６０によって、第２出力軸ギヤ４０Ａ及び第３出力軸ギヤ５０Ａが出力軸１４と選択的に同期可能に構成されている。   When the fifth sleeve 60B moves to the second output shaft gear 40A side and engages with the dog gear 60C, the second output shaft gear 40A and the output shaft 14 are synchronized. On the other hand, when the fifth sleeve 60B moves to the third output shaft gear 50A side and engages with the dog gear 60D, the first output shaft gear 22A and the output shaft 14 are synchronized. In other words, the second output shaft gear 40 </ b> A and the third output shaft gear 50 </ b> A are configured to be selectively synchronized with the output shaft 14 by the fifth synchronization mechanism 60.

次に、本実施形態のデュアルクラッチ式変速機による各前進段の動力伝達経路を図３〜１０に基づいて説明する。   Next, the power transmission path of each forward gear by the dual clutch transmission of this embodiment will be described with reference to FIGS.

図３は、１速時の動力伝達経路を示している。１速の場合は、第１クラッチ１０が選択されると共に、第１シンクロ機構２３によって第１出力軸ギヤ２２Ａと第１入力軸１１とが連結される。さらに、第２シンクロ機構２４によって第１副軸ギヤ２１Ｂと副軸１５とが連結されると共に、第５シンクロ機構６０によって第２出力軸ギヤ４０Ａと出力軸１４とが連結される。すなわち、エンジン２の動力は、第１クラッチ１０から第１入力軸１１、第１低速ギヤ列２２、第１副軸ギヤ２１Ｂ、副軸１５及び、低速段用ギヤ列４０を介して出力軸１４に伝達される。   FIG. 3 shows a power transmission path at the first speed. In the case of the first speed, the first clutch 10 is selected, and the first output shaft gear 22 </ b> A and the first input shaft 11 are connected by the first sync mechanism 23. Furthermore, the first countershaft gear 21B and the countershaft 15 are connected by the second synchro mechanism 24, and the second output shaft gear 40A and the output shaft 14 are connected by the fifth synchro mechanism 60. That is, the power of the engine 2 is output from the first clutch 10 through the first input shaft 11, the first low speed gear train 22, the first countershaft gear 21 </ b> B, the subshaft 15, and the low speed gear train 40. Is transmitted to.

図４は、２速時の動力伝達経路を示している。２速の場合は、１速の状態から第４シンクロ機構３３によって第３入力軸ギヤ３２Ａと第２入力軸１３とを連結すると共に、第１クラッチ１０を第２クラッチ１２に切り替えることで実現される。すなわち、エンジン２の動力は、第２クラッチ１２から第２入力軸１３、第２低速ギヤ列３２、副軸１５及び、低速段用ギヤ列４０を介して出力軸１４に伝達される。   FIG. 4 shows a power transmission path at the second speed. In the case of the second speed, the third input shaft gear 32A and the second input shaft 13 are connected by the fourth sync mechanism 33 from the first speed state, and the first clutch 10 is switched to the second clutch 12. The That is, the power of the engine 2 is transmitted from the second clutch 12 to the output shaft 14 via the second input shaft 13, the second low speed gear train 32, the auxiliary shaft 15, and the low speed gear train 40.

図５は、３速時の動力伝達経路を示している。３速の場合は、２速の状態で第１シンクロ機構２３によって第１入力軸ギヤ２１Ａと第１入力軸１１とを連結すると共に、第２シンクロ機構２４によって第１副軸ギヤ２１Ｂと副軸１５とを連結し、第２クラッチ１２から第１クラッチ１０に切り替えることで実現される。すなわち、エンジン２の動力は、第１クラッチ１０から第１入力軸１１、第１高速ギヤ列２１、副軸１５及び、低速段用ギヤ列４０を介して出力軸１４に伝達される。   FIG. 5 shows a power transmission path at the third speed. In the case of the third speed, the first input shaft gear 21A and the first input shaft 11 are connected by the first sync mechanism 23 in the second speed state, and the first counter shaft gear 21B and the counter shaft are connected by the second sync mechanism 24. 15 is connected and switched from the second clutch 12 to the first clutch 10. That is, the power of the engine 2 is transmitted from the first clutch 10 to the output shaft 14 via the first input shaft 11, the first high speed gear train 21, the auxiliary shaft 15, and the low speed gear train 40.

図６は、４速時の動力伝達経路を示している。４速の場合は、３速の状態から第４シンクロ機構３３によって第２入力軸ギヤ３１Ａと第２入力軸１３とを連結すると共に、第１クラッチ１０を第２クラッチ１２に切り替えることで実現される。すなわち、エンジン２の動力は、第２クラッチ１２から第２入力軸１３、第２高速ギヤ列３１、副軸１５及び、低速段用ギヤ列４０を介して出力軸１４に伝達される。   FIG. 6 shows a power transmission path at the fourth speed. The fourth speed is realized by connecting the second input shaft gear 31A and the second input shaft 13 from the third speed state by the fourth synchronization mechanism 33 and switching the first clutch 10 to the second clutch 12. The That is, the power of the engine 2 is transmitted from the second clutch 12 to the output shaft 14 via the second input shaft 13, the second high speed gear train 31, the auxiliary shaft 15, and the low speed gear train 40.

図７は、５速時の動力伝達経路を示している。５速の場合は、４速の状態から第１シンクロ機構２３によって第１出力軸ギヤ２２Ａと第１入力軸１１とを連結すると共に、第３シンクロ機構２５によって第１出力軸ギヤ２２Ａと出力軸１４とを連結し（第１入力軸１１と出力軸１４とを直結）、第２クラッチ１２を第１クラッチ１０に切り替えることで実現される。すなわち、エンジン２の動力は、第１クラッチ１０から第１入力軸１１及び、第１出力軸ギヤ２２Ａを介して出力軸１４に伝達される。   FIG. 7 shows a power transmission path at the fifth speed. In the case of the fifth speed, the first output shaft gear 22A and the first input shaft 11 are connected by the first sync mechanism 23 from the fourth speed state, and the first output shaft gear 22A and the output shaft are connected by the third sync mechanism 25. 14 (the first input shaft 11 and the output shaft 14 are directly connected), and the second clutch 12 is switched to the first clutch 10. That is, the power of the engine 2 is transmitted from the first clutch 10 to the output shaft 14 via the first input shaft 11 and the first output shaft gear 22A.

図８は、６速時の動力伝達経路を示している。６速の場合は、５速の状態から第４シンクロ機構３３によって第３入力軸ギヤ３２Ａと第２入力軸１３とを連結すると共に、第２シンクロ機構２４によって第１副軸ギヤ２１Ｂと副軸１５とを連結し、第１クラッチ１０を第２クラッチ１２に切り替えることで実現される。すなわち、エンジン２の動力は、第２クラッチ１２から第２入力軸１３、第２低速ギヤ列３２、副軸１５、第１副軸ギヤ２１Ｂ及び、第１低速ギヤ列２２を介して出力軸１４に伝達される。   FIG. 8 shows a power transmission path at the sixth speed. In the case of the sixth speed, the third input shaft gear 32A and the second input shaft 13 are connected by the fourth sync mechanism 33 from the fifth speed state, and the first counter gear 21B and the counter shaft are connected by the second sync mechanism 24. 15, and the first clutch 10 is switched to the second clutch 12. That is, the power of the engine 2 is output from the second clutch 12 to the output shaft 14 via the second input shaft 13, the second low speed gear train 32, the counter shaft 15, the first counter shaft gear 21 B, and the first low speed gear train 22. Is transmitted to.

図９は、７速時の動力伝達経路を示している。７速の場合は、６速の状態から第１シンクロ機構２３によって第１入力軸ギヤ２１Ａと第１入力軸１１とを連結すると共に、第２クラッチ１２を第１クラッチ１０に切り替えることで実現される。すなわち、エンジン２の動力は、第１クラッチ１０から第１入力軸１１、第１高速ギヤ列２１及び、第１低速ギヤ列２２を介して出力軸１４に伝達される。   FIG. 9 shows a power transmission path at the seventh speed. The seventh speed is realized by connecting the first input shaft gear 21A and the first input shaft 11 by the first sync mechanism 23 from the sixth speed state and switching the second clutch 12 to the first clutch 10. The That is, the power of the engine 2 is transmitted from the first clutch 10 to the output shaft 14 via the first input shaft 11, the first high speed gear train 21, and the first low speed gear train 22.

図１０は、８速時の動力伝達経路を示している。８速の場合は、７速の状態から第４シンクロ機構３３によって第２入力軸ギヤ３１Ａと第２入力軸１３とを連結すると共に、第２シンクロ機構２４によって第１副軸ギヤ２１Ｂと副軸１５とを連結し、第１クラッチ１０を第２クラッチ１２に切り替えることで実現される。すなわち、エンジン２の動力は、第２クラッチ１２から第２入力軸１３、第２高速ギヤ列３１、副軸１５、第１副軸ギヤ２１Ｂ及び、第１低速ギヤ列２２を介して出力軸１４に伝達される。   FIG. 10 shows a power transmission path at the eighth speed. In the case of the eighth speed, the second input shaft gear 31A and the second input shaft 13 are connected by the fourth sync mechanism 33 from the seventh speed state, and the first counter gear 21B and the counter shaft are connected by the second sync mechanism 24. 15, and the first clutch 10 is switched to the second clutch 12. That is, the power of the engine 2 is output from the second clutch 12 through the second input shaft 13, the second high-speed gear train 31, the countershaft 15, the first countershaft gear 21 </ b> B, and the first low-speed gear train 22. Is transmitted to.

次に、本実施形態のデュアルクラッチ式変速機による作用効果を説明する。   Next, the effect by the dual clutch transmission of this embodiment is demonstrated.

本実施形態のデュアルクラッチ式変速機では、第１クラッチ１０を有する第１入力軸１１に第１スプリッタ変速部２０が設けられると共に、第２クラッチ１２を有する第２入力軸１３に第２スプリッタ変速部３０が設けられている。そして、低速段では、低速段用ギヤ列４０を出力軸１４に連結すると共に、第１スプリッタ変速部２０及び第２スプリッタ変速部３０の各ギヤ列２１，２２，３１，３２を交互に切り替えることで計４段の変速を実現させている。さらに、高速段では、第１スプリッタ変速部２０の第１低速ギヤ列２２を出力軸１４と連結し、第１入力軸１１と出力軸１４とを直結する５速時を含め計４段の変速を実現させている。すなわち、図１３に示す従来型のデュアルクラッチ式変速機（計６速）に対し、同数の変速用ギヤ列でシンクロ機構の追加のみによって計８速の変速が可能に構成されている。   In the dual clutch transmission of the present embodiment, the first splitter transmission 20 is provided on the first input shaft 11 having the first clutch 10, and the second splitter transmission is provided on the second input shaft 13 having the second clutch 12. A portion 30 is provided. In the low speed stage, the low speed gear train 40 is connected to the output shaft 14 and the gear trains 21, 22, 31, 32 of the first splitter transmission 20 and the second splitter transmission 30 are alternately switched. In this way, a total of four speeds are realized. Further, at the high speed stage, the first low-speed gear train 22 of the first splitter transmission unit 20 is connected to the output shaft 14, and a total of four speeds including the fifth speed in which the first input shaft 11 and the output shaft 14 are directly connected are included. Is realized. In other words, the conventional dual clutch transmission (total 6 speeds) shown in FIG. 13 is configured to be capable of shifting a total of 8 speeds only by adding a synchro mechanism with the same number of shift gear trains.

したがって、本実施形態のデュアルクラッチ式変速機によれば、変速機の大型化や重量増加、コストの上昇等を効果的に抑制しつつ、変速段数を確実に増加することができる。   Therefore, according to the dual clutch transmission of the present embodiment, it is possible to reliably increase the number of shift stages while effectively suppressing an increase in the size, weight, and cost of the transmission.

なお、本発明は、上述の実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で、適宜変形して実施することが可能である。   In addition, this invention is not limited to the above-mentioned embodiment, In the range which does not deviate from the meaning of this invention, it can change suitably and can implement.

例えば、図１１に示すように、第１スプリッタ変速部２０において、第１高速ギヤ列２１を第１入力軸１１側に配置し、第１低速ギヤ列２２を出力軸１４側に配置して構成してもよい。また、図１２に示すように、図１１のデュアルクラッチ式変速機において、第４シンクロ機構３３を副軸１５側に設けると共に、第２入力軸ギヤ３１Ａ及び第３入力軸ギヤ３２Ａを第２入力軸１３に固定し、第３副軸ギヤ３１Ｂ及び第４副軸ギヤ３２Ｂを副軸１５に相対回転自在に設けて構成してもよい。これら何れの場合も、３速時に第１低速ギヤ列２２及び低速段用ギヤ列４０を用いて減速を行い、７速時に第１入力軸１１と出力軸１４とを直結すればよい。   For example, as shown in FIG. 11, in the first splitter transmission 20, the first high speed gear train 21 is disposed on the first input shaft 11 side, and the first low speed gear train 22 is disposed on the output shaft 14 side. May be. Further, as shown in FIG. 12, in the dual clutch transmission of FIG. 11, the fourth sync mechanism 33 is provided on the side of the auxiliary shaft 15, and the second input shaft gear 31A and the third input shaft gear 32A are connected to the second input. The third countershaft gear 31B and the fourth countershaft gear 32B may be fixed to the shaft 13 and provided on the subshaft 15 so as to be relatively rotatable. In any of these cases, the first low-speed gear train 22 and the low-speed gear train 40 may be used for speed reduction at the third speed, and the first input shaft 11 and the output shaft 14 may be directly connected at the seventh speed.

また、第２副軸ギヤ２２Ｂ及び第１副軸ギヤ２１Ｂは、必ずしも一体形成される必要はなく、別体に形成されてもよい。この場合は、これら第２副軸ギヤ２２Ｂ及び第１副軸ギヤ２１Ｂを選択的に副軸１５と同期させるシンクロ機構を追加すればよい。   Further, the second countershaft gear 22B and the first countershaft gear 21B are not necessarily formed integrally, and may be formed separately. In this case, a synchro mechanism that selectively synchronizes the second countershaft gear 22B and the first countershaft gear 21B with the countershaft 15 may be added.

２ エンジン
１０ 第１クラッチ
１１ 第１入力軸
１２ 第２クラッチ
１３ 第２入力軸
１４ 出力軸
１５ 副軸
２０ 第１スプリッタ変速部
２１ 第１高速ギヤ列（第１ギヤ列）
２２ 第１低速ギヤ列（第２ギヤ列）
２３ 第１シンクロ機構
２４ 第２シンクロ機構
２５ 第３シンクロ機構
３０ 第２スプリッタ変速部
３１ 第２高速ギヤ列（第３ギヤ列）
３２ 第２低速ギヤ列（第４ギヤ列）
３３ 第４シンクロ機構
４０ 低速段用ギヤ列
６０ 第５シンクロ機構 2 Engine 10 First clutch 11 First input shaft 12 Second clutch 13 Second input shaft 14 Output shaft 15 Sub shaft 20 First splitter transmission 21 First high-speed gear train (first gear train)
22 First low-speed gear train (second gear train)
23 1st synchro mechanism 24 2nd synchro mechanism 25 3rd synchro mechanism 30 2nd splitter transmission part 31 2nd high speed gear train (3rd gear train)
32 Second low-speed gear train (fourth gear train)
33 Fourth synchronization mechanism 40 Low speed gear train 60 Fifth synchronization mechanism

Claims (3)

駆動源からの動力を断接する第１クラッチを有する第１入力軸と、
前記駆動源からの動力を断接する第２クラッチを有すると共に前記第１入力軸が回転自在に挿通された第２入力軸と、
前記第１入力軸と同軸に配置された出力軸と、
前記第１入力軸、前記第２入力軸及び、前記出力軸と平行に配置された副軸と、
前記第１入力軸と前記副軸とに回転自在に設けられた第１ギヤ列、前記出力軸と前記副軸とに回転自在に設けられた第２ギヤ列、前記第１ギヤ列と前記第２ギヤ列とを前記第１入力軸に選択的に同期させる第１同期機構、前記第１ギヤ列と前記第２ギヤ列とを前記副軸に選択的に同期させる第２同期機構及び、前記第２ギヤ列を前記出力軸に選択的に同期させる第３同期機構を有する第１スプリッタ変速部と、
前記第２入力軸又は前記副軸の一方に回転自在に設けられた第３ギヤ列、前記第１入力軸又は前記副軸の一方に回転自在に設けられた第４ギヤ列及び、前記第３ギヤ列と前記第４ギヤ列とを前記第２入力軸又は前記副軸に選択的に同期させる第４同期機構を有する第２スプリッタ変速部と、を備える
ことを特徴とするデュアルクラッチ式変速機。 A first input shaft having a first clutch for connecting and disconnecting power from a drive source;
A second input shaft having a second clutch for connecting and disconnecting power from the drive source, and wherein the first input shaft is rotatably inserted;
An output shaft disposed coaxially with the first input shaft;
The first input shaft, the second input shaft, and the auxiliary shaft arranged in parallel with the output shaft;
A first gear train rotatably provided on the first input shaft and the secondary shaft; a second gear train rotatably provided on the output shaft and the secondary shaft; the first gear train and the first gear train; A first synchronization mechanism that selectively synchronizes two gear trains with the first input shaft, a second synchronization mechanism that selectively synchronizes the first gear train and the second gear train with the auxiliary shaft, and A first splitter transmission having a third synchronization mechanism for selectively synchronizing a second gear train to the output shaft;
A third gear train rotatably provided on one of the second input shaft or the secondary shaft, a fourth gear train rotatably provided on one of the first input shaft or the secondary shaft, and the third gear train. And a second splitter transmission having a fourth synchronization mechanism that selectively synchronizes the gear train and the fourth gear train with the second input shaft or the sub-shaft. . 前記第１ギヤ列及び前記第２ギヤ列の副軸側のギヤが互いに一体形成される
請求項１に記載のデュアルクラッチ式変速機。 The dual clutch transmission according to claim 1, wherein gears on the countershaft side of the first gear train and the second gear train are integrally formed with each other. 前記出力軸に回転自在に設けられ前記副軸に固定された第５ギヤ列と、
前記第５ギヤ列を前記出力軸に選択的に同期させる第５同期機構と、をさらに備え、
所定の低速段において、前記第１同期機構で前記第２ギヤ列と前記第１入力軸とを同期させると共に、前記第５同期機構で前記第５ギヤ列と前記出力軸とを同期させて、前記第２ギヤ列及び前記第５ギヤ列のギヤ比を用いて減速を行い、
所定の高速段において、前記第１同期機構で前記第２ギヤ列と前記第１入力軸とを同期させると共に、前記第３同期機構で前記第２ギヤ列と前記出力軸とを同期させて、前記第１入力軸及び前記出力軸を直結する
請求項１又は２に記載のデュアルクラッチ式変速機。 A fifth gear train rotatably provided on the output shaft and fixed to the auxiliary shaft;
A fifth synchronization mechanism that selectively synchronizes the fifth gear train with the output shaft,
At a predetermined low speed stage, the first synchronization mechanism synchronizes the second gear train and the first input shaft, and the fifth synchronization mechanism synchronizes the fifth gear train and the output shaft, Decrease using the gear ratio of the second gear train and the fifth gear train,
At a predetermined high speed stage, the first synchronization mechanism synchronizes the second gear train and the first input shaft, and the third synchronization mechanism synchronizes the second gear train and the output shaft, The dual clutch transmission according to claim 1 or 2, wherein the first input shaft and the output shaft are directly connected.
JP2013262499A 2013-12-19 2013-12-19 Dual clutch transmission Expired - Fee Related JP6343925B2 (en)

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