JPH02146336A - Twin clutch type transmission - Google Patents
Twin clutch type transmissionInfo
- Publication number
- JPH02146336A JPH02146336A JP63298305A JP29830588A JPH02146336A JP H02146336 A JPH02146336 A JP H02146336A JP 63298305 A JP63298305 A JP 63298305A JP 29830588 A JP29830588 A JP 29830588A JP H02146336 A JPH02146336 A JP H02146336A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- clutch
- subshaft
- gears
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title claims description 11
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000004323 axial length Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は、自動車等の回転動力伝達系に用いられるツイ
ンクラッチ式変速機に関するものである。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a twin clutch type transmission used in a rotary power transmission system of an automobile or the like.
〈従来の技術〉
同軸線上に２つのクラッチを備え、一方のクラッチが接
続されている間に他方のフリーなりラッチ側でシフトが
行われ、クラッチの切り換えにより瞬間的に変速して変
速操作時間の短縮化を図ったツインクラッチ式変速機は
例えば特開昭５７−１７９４５７号で公知となっている
。<Prior art> Two clutches are provided on the same axis, and while one clutch is engaged, a shift is performed on the other free latch side, and by switching the clutch, the gear is changed instantaneously, reducing the shift operation time. A twin clutch type transmission with a shortened length is known, for example, from Japanese Patent Laid-Open No. 57-179457.
〈発明が解決しようとする課題〉
上記従来の変速機は、２つのクラッチが入力軸側の同一
線上で大きく離れた位置に配置され、しかも入力軸側の
変速ギヤ群と出力軸側の変速ギヤ群は、変速段数に応じ
た直列に配置噛合している構成である。従って、例えば
６段の変速段数の場合には、同軸上に６枚のギヤを直列
配置することになり、多段変速を可能にすればするほど
変速機の軸方向長さが長くなり、これに伴い２つのクラ
ッチも大きく離間して大型化する不具合がある。<Problems to be Solved by the Invention> In the conventional transmission described above, the two clutches are arranged on the same line on the input shaft side but at widely separated positions, and the transmission gear group on the input shaft side and the transmission gear group on the output shaft side The groups are arranged and meshed in series according to the number of gears. Therefore, for example, in the case of 6 gears, 6 gears are arranged in series on the same axis, and the more gears that can be shifted, the longer the axial length of the transmission becomes. Accordingly, there is a problem that the two clutches are also separated by a large distance and become larger.
〈課題を解決するための手段〉
本発明は、上記従来の不具合を改善したツインクラッチ
式変速機を提供するもので、その特徴とする構成は、入
力軸上に逆転軸承したロードライフギヤと入力軸と一体
のハイドライブギヤとを備え、前記入力軸にトルク伝達
する第１クラッチと前記ロードライフギヤにトルク伝達
する第２クラッチとを近接して直列配置し、前記入力軸
と同一軸線で回転自在に軸承された出力軸上に歯数の異
なる複数枚のメインギヤを配列し、前記出力軸を挾んで
第１副軸と第２副軸とを全て平行な軸線で配置すると共
に、前記第１副軸には前記ロードライフギヤと噛合する
第１ドリブンギヤを、前記第２副軸には前記ハイドライ
ブギヤと噛合する第２ドリブンギヤを有し、前記第１副
軸上に前記各メインギヤと噛合する奇数速ギヤを、前記
第２副軸上に前記各メインギヤと噛合する偶数速ギヤを
遊転軸示し、前記出力軸とハイドライブギヤ間にドッグ
クラッチを設け、前記第１副軸上には隣り合う２枚の奇
数速ギヤ間に、前記第２副軸上には隣り合う２枚の偶数
速ギヤ間にドッグクラッチを設けたものである。<Means for Solving the Problems> The present invention provides a twin clutch type transmission that improves the above-mentioned conventional problems, and its characteristic configuration is that a road life gear with a reverse rotation bearing on the input shaft and an input A high drive gear integrated with the shaft, a first clutch that transmits torque to the input shaft and a second clutch that transmits torque to the road life gear are arranged in series adjacent to each other, and rotate on the same axis as the input shaft. A plurality of main gears having different numbers of teeth are arranged on a freely supported output shaft, a first sub-shaft and a second sub-shaft are arranged with parallel axes with the output shaft sandwiched between them, and the first The subshaft has a first driven gear that meshes with the road life gear, the second subshaft has a second driven gear that meshes with the high drive gear, and the first subshaft has a second driven gear that meshes with each of the main gears. Odd-number speed gears are shown on the second countershaft, and even-number speed gears that mesh with the main gears are shown as idle shafts, a dog clutch is provided between the output shaft and the high drive gear, and an adjacent A dog clutch is provided between two matching odd-number speed gears and between two adjacent even-number speed gears on the second subshaft.
〈作 用〉
本発明は上記の構成により、一方のクラッチが接続され
ている間に他方のフリーのクラッチ側の副軸上のドッグ
クラッチをシフトし、クラッチの切り換えを交互に行っ
て、奇数速ギヤと偶数速ギヤとの交互の瞬間的な変速作
用とし、少数のギヤセット枚数により多段変速が可能と
なり、軸線方向の全長を短縮したコンパクトな多段変速
機を提供するものである。<Operation> According to the above configuration, the present invention shifts the dog clutch on the subshaft on the side of the other free clutch while one clutch is connected, and alternately switches the clutches to shift the dog clutch to the odd speed. To provide a compact multi-stage transmission that has an instantaneous shifting action of alternating gears and even speed gears, enables multi-stage shifting with a small number of gear sets, and has a shortened overall length in the axial direction.
〈実施例〉
以下本発明の実施例を図面に基づいて説明する。１はエ
ンジンより回転動力が伝達される入力軸である。この入
力軸１上にはロードライフギヤ２が遊転軸示され、また
入力軸１と一体のハイドライブギヤ３が前記ロードライ
フギヤ２と直列配置されている。<Example> Hereinafter, an example of the present invention will be described based on the drawings. 1 is an input shaft to which rotational power is transmitted from the engine. A road life gear 2 is shown as an idling shaft on the input shaft 1, and a high drive gear 3, which is integrated with the input shaft 1, is arranged in series with the road life gear 2.
４ａは前記入力軸１にトルク伝達する第１クラッチであ
り、４ｂはロードライフギヤ２にトルク伝達する第２ク
ラッチであって、これらは近接して直列配置されている
。4a is a first clutch that transmits torque to the input shaft 1, and 4b is a second clutch that transmits torque to the road life gear 2, which are arranged in series in close proximity.
５は前記入力軸１と同一軸線で回転自在に軸承された出
力軸（主軸）である、この出力軸５上には歯数の異なる
複数のメインギヤが配列されている０図例の場合、直結
を含めて９段変速を可能とするもので、第１メインギヤ
６、第２メインギヤ７、第３メインギヤ８及び第４メイ
ンギヤ９の４枚のメインギヤ配列構成である。5 is an output shaft (main shaft) that is rotatably supported on the same axis as the input shaft 1. In the case of the example shown in Fig. 0, where a plurality of main gears with different numbers of teeth are arranged on this output shaft 5, it is directly connected. It is possible to change gears in 9 stages including 1st main gear 6, 2nd main gear 7, 3rd main gear 8, and 4th main gear 9, and has a main gear arrangement configuration.
１１は第１副軸であり、１２は第２副軸である。11 is a first minor axis, and 12 is a second minor axis.
この第１．２副軸１１．１２は前記出力軸５を挾んで全
て平行な軸線で配置されている。そして、第１副軸１１
には前記ロードライフギヤ２と噛合する第１ドリブンギ
ヤ２１が、また第２副軸１２には前記ハイドライブギヤ
３と噛合する第２ドリブンギヤ２２が設けられている。The first and second subshafts 11.12 are arranged with axes that are parallel to each other, sandwiching the output shaft 5. And the first sub-shaft 11
is provided with a first driven gear 21 that meshes with the road life gear 2, and a second driven gear 22 that meshes with the high drive gear 3 is provided on the second subshaft 12.
前記第１副軸１１上には複数枚の奇数速ギヤが、また第
２副軸１２上には偶数速ギヤが遊転軸示され前記各メイ
ンギヤと噛合している。すなわち、国側の場合、第１副
軸１１側には第１速ギヤ１３、第３速ギヤ１４、第５速
ギヤ１５及び第７速ギヤ１６が配列され、第２副軸１２
側には第２遍ギヤ１７、第４速ギヤ１８、第６速ギヤ１
９及び第８速ギヤ２０が配列されている。そして、第１
速ギヤ１３と第２速ギヤ１７は第１メインギヤ６に噛合
し、以下第３速ギヤ１４と第４速ギヤ１８は第２メイン
ギヤ７に、第５速ギヤ１５と第６速ギヤ１９は第３メイ
ンギヤ８に、第７速ギヤ１６と第８速ギヤ２０は第４メ
インギヤ９にそれぞれ噛合している。A plurality of odd speed gears are shown on the first subshaft 11, and even speed gears are shown as idle rotation shafts on the second subshaft 12, and mesh with each of the main gears. That is, in the case of the country side, a first speed gear 13, a third speed gear 14, a fifth speed gear 15, and a seventh speed gear 16 are arranged on the first subshaft 11 side, and the second subshaft 12
On the side are 2nd gear 17, 4th gear 18, and 6th gear 1.
9 and 8th speed gear 20 are arranged. And the first
The gear 13 and the second gear 17 mesh with the first main gear 6, the third gear 14 and the fourth gear 18 mesh with the second main gear 7, and the fifth gear 15 and the sixth gear 19 mesh with the second main gear 7. The third main gear 8 meshes with the seventh speed gear 16 and the eighth speed gear 20 mesh with the fourth main gear 9, respectively.
さらに、出力軸５とハイドライブギヤ３間に第１ドツグ
クラッチ２３が設けられ、第１副軸１１上では第１速ギ
ヤ１３と第３速ギヤ１４間に第２ドラグクラッチ２４が
、また第５遠ギヤ１５と第７速ギヤ１６間に第３ドツグ
クラッチ２５が設けられている。Further, a first dog clutch 23 is provided between the output shaft 5 and the high drive gear 3, a second drag clutch 24 is provided between the first speed gear 13 and the third speed gear 14 on the first subshaft 11, and a fifth dog clutch 24 is provided between the first speed gear 13 and the third speed gear 14. A third dog clutch 25 is provided between the far gear 15 and the seventh gear 16.
一方、第２副軸１２上にも第２速ギヤ１７と第４遠ギヤ
１８間に第４ドツグクラッチ２６が、第６速ギヤ１９と
第８速ギヤ２０間に第５ドツグクラッチ２７が設けられ
ている。On the other hand, a fourth dog clutch 26 is also provided on the second subshaft 12 between the second gear 17 and the fourth far gear 18, and a fifth dog clutch 27 is provided between the sixth gear 19 and the eighth gear 20. There is.
次に上記構成の動作について説明する。先ず第２〜５ド
ツグクラッチ２４．２５．２６．２７を中立位置とし、
第１ドツグクラッチ２３をハイドライブギヤ３側ヘシフ
トし、第１クラッチ４ａを接にすると入力軸１と出力軸
５は直結された第９変速段となる。このときは第２クラ
ッチ４ｂが接で第１クラッチ４ａがフリーの状態で第１
ドツグクラッチ２３をシフトし、その後第２クラッチ４
ｂをフリーに第１クラッチ４ａを接に切り換える。Next, the operation of the above configuration will be explained. First, set the second to fifth dog clutches 24, 25, 26, and 27 to the neutral position,
When the first dog clutch 23 is shifted to the high drive gear 3 side and the first clutch 4a is brought into contact, the input shaft 1 and the output shaft 5 are directly coupled to become the ninth gear stage. At this time, the second clutch 4b is engaged, the first clutch 4a is free, and the first clutch 4b is engaged.
Shift the dog clutch 23, and then shift the second clutch 4.
Switch b to free and first clutch 4a to close.
また、第１速段から第８遠段の変速は、奇数変速段と偶
数変速段とが交互に切り換え作動される。すなわち、第
１速段は第２クラッチ４ｂのフリー状態で第２ドツグク
ラッチ２４が第１速ギヤ１３側ヘシフトされ、その後第
１クラッチ４ａがフリーに第２クラッチ４ｂが接に切り
換えられる。Further, the gears from the first gear to the eighth far gear are operated by alternating between an odd gear and an even gear. That is, in the first gear position, the second dog clutch 24 is shifted to the first gear 13 side with the second clutch 4b in the free state, and then the first clutch 4a is switched to the free state and the second clutch 4b is switched to the engaged state.
これによりロードライフギヤ２、第１ドリブンギヤ２１
を経て第１副軸１１に入力される動力は第２ドツグクラ
ッチ２４、第１速ギヤ１３、第１メインギヤ６を経て出
力軸５に伝達されるのである。As a result, the road life gear 2, the first driven gear 21
The power input to the first subshaft 11 via the second dog clutch 24, the first speed gear 13, and the first main gear 6 is transmitted to the output shaft 5.
この状態で第１クラッチ４ａがフリーとなっている第２
副軸１２１１１の第４ドツグクラッチ２６を第２速ギヤ
１７１ＦＩヘシフトし、第２クラッチ４ｂをフリーに第
１クラッチ４ａを接に切り換えることにより瞬時に第２
速段に変速される。この第２副軸１２は第１クラ・ツチ
４ａの接によりハイドライブギヤ３及び第２ドリブンギ
ヤ２２を介して動力が伝達される。従って、第４ドツグ
クラッチ、第２速ギヤ１７、第１メインギヤ６を介して
第２速段のトルクが出力軸５に伝達されるのである。In this state, the first clutch 4a is free and the second clutch 4a is free.
By shifting the fourth dog clutch 26 of the subshaft 12111 to the second gear 171FI and switching the second clutch 4b to free and the first clutch 4a to close, the second
The gear is shifted to gear. Power is transmitted to the second subshaft 12 via the high drive gear 3 and the second driven gear 22 when the first clutch 4a comes into contact with the second subshaft 12. Therefore, the torque of the second gear is transmitted to the output shaft 5 via the fourth dog clutch, the second gear 17, and the first main gear 6.
この第２速段の状態では第２クラッチ４ｂはフリーとな
っていて第１副軸１１には動力伝達されていない、そこ
で第２ドツグクラッチ２４を第３速ギヤ１４ＩＩＩヘシ
フトし、第１クラッチ４ａをフリに第２クラッチ４ｂを
接に切り換えることによりロードライフギヤ２、第１ド
リブンギヤ２１、第２副軸１１、第２ドツグクラッチ２
４、第３速ギヤ１４、第２メインギヤ７を経て第３速段
の動力が出力軸５に瞬時に取り出される。In this second gear state, the second clutch 4b is free and power is not transmitted to the first subshaft 11. Therefore, the second dog clutch 24 is shifted to the third gear 14III, and the first clutch 4a is shifted to the third gear 14III. By freely switching the second clutch 4b to close, the road life gear 2, the first driven gear 21, the second subshaft 11, and the second dog clutch 2 are activated.
4. The power of the third speed stage is instantaneously taken out to the output shaft 5 via the third speed gear 14 and the second main gear 7.
上記の要領で第４ドツグクラ・ｙチ２６を第４速ギヤ１
８側にシフトし、第２クラッチ４ｂをフリに第１クラッ
チ４ａを接に切り換えることにより第４速段に、第３ド
ツグクラッチ２５を第５速ギヤ１５１１１１にシフトし
て第１．２クラッチ４ａ、４ｂを切り換えることにより
第５速段に、第５ドツグクラッチ２７を第６遠ギヤ１９
側にシフトして第１．２クラッチ４ａ、４ｂを切り換え
ることにより第６速段に、第３ドツグクラッチ２５を第
７速ギヤ１６側にシフトして第１．２クラッチ４ａ、４
ｂを切り換えることにより第７速段に、第５ドツグクラ
ッチ２７を第８速ギヤ２０１ＩＩ！Ｉにシフトして第１
．２クラッチ４ａ、４ｂを切り換えることにより第８速
段に変速され、前記第１ドツグクラッチ２３による直結
を含めて都合９速段の変速が、この変速段の約半分のギ
ヤセット数によって得られる。As described above, move the 4th dog clutch y-chi 26 to 4th gear 1.
8 side, and by switching the second clutch 4b freely and the first clutch 4a to engage, the third dog clutch 25 is shifted to the fifth gear 151111, and the first clutch 4a is shifted to the fourth gear. 4b to shift the fifth dog clutch 27 to the sixth far gear 19.
by shifting the third dog clutch 25 to the seventh gear 16 side and switching the first and second clutches 4a and 4b to the sixth gear.
By switching b, the fifth dog clutch 27 is shifted to the seventh gear and the fifth dog clutch 27 is shifted to the eighth gear 201II! Shift to I and move to 1st
．． By switching the two clutches 4a and 4b, the gear is shifted to the eighth gear, and a total of nine gears, including the direct connection by the first dog clutch 23, can be obtained by approximately half the number of gear sets of this gear.
尚、第１．２クラッチ４ａ、４ｂ、各ドッグクラッチ２
３．２４．２５．２６．２７の作動は油圧、空几、電磁
等のアクチュエータをコンピュータにより制御する自動
変速制御方式が用いられる。In addition, the first and second clutches 4a and 4b, each dog clutch 2
For the operation of 3.24.25.26.27, an automatic speed change control method is used in which hydraulic, pneumatic, electromagnetic, etc. actuators are controlled by a computer.
〈発明の効果〉
以上のように本発明によれば、１本の出力軸に対して２
本の副軸を配置し、その一方の副軸には奇数速ギヤを他
方の副軸には偶数速ギヤを配列して前記出力軸上のメイ
ンギヤに噛合し、前記２本の副軸に対しそれぞれ動力を
伝達する２つのクラッチを設け、各副軸上には奇数速ギ
ヤ、偶数速ギヤと係脱するドッグクラッチを配置し、こ
のドッグクラッチを奇数、偶数遠ギヤの交互に、また２
つのクラッチを交換に切り換えるようにした構成である
から、ギヤセット数が変速段の約半分となり軸方向の全
長の短い多段変速着替えられ、しかも２つのクラッチの
切り換えにより瞬間的に変速が行われる利点を有してい
る。<Effects of the Invention> As described above, according to the present invention, two
A main gear is arranged on one of the subshafts, an odd speed gear is arranged on the other subshaft, an even speed gear is arranged on the other subshaft, and the main gear is meshed with the main gear on the output shaft. Two clutches are provided to transmit power, and a dog clutch that engages and disengages the odd and even speed gears is placed on each subshaft.
Since the configuration is such that two clutches can be switched interchangeably, the number of gear sets is approximately half the number of gears, allowing multi-stage shifting with a short overall length in the axial direction.Moreover, the advantage is that shifting can be performed instantaneously by switching two clutches. have.
図面は本発明の実施例を示す断面図である。
１・・・入力軸、２・・・ロードライフギヤ、３・・・
ノ１イドライブギヤ、４ａ・・・第１クラッチ、４ｂ・
・・第２クラッチ、５・・・出力軸、６．７．８．９・
・・メインギヤ、１１・・・第１副軸、１２・・・第２
副軸、１３・・・第１速ギヤ、１４・・・第３速ギヤ、
１５・・・第５速ギヤ、１６・・・第７速ギヤ、１７・
・・第２速ギヤ、１８・・・第４速ギヤ、１９・・・第
６速ギヤ、２０・・・第８速ギヤ、２１・・・第１ドリ
ブンギヤ、２２・・・第２ドリブンギヤ、２３・・・第
１ドツグクラッチ、２４・・・第２ドツグクラッチ、２
５・・・第３ドツグクラッチ、２６・・・第４ドツグク
ラッチ、２７・・・第５ドツグクラッチ。The drawings are cross-sectional views showing embodiments of the present invention. 1...Input shaft, 2...Road life gear, 3...
1st drive gear, 4a... 1st clutch, 4b...
...Second clutch, 5...Output shaft, 6.7.8.9.
...Main gear, 11...1st subshaft, 12...2nd
Subshaft, 13...1st speed gear, 14...3rd speed gear,
15...5th gear, 16...7th gear, 17.
... 2nd speed gear, 18... 4th speed gear, 19... 6th speed gear, 20... 8th speed gear, 21... 1st driven gear, 22... 2nd driven gear, 23...First dog clutch, 24...Second dog clutch, 2
5... Third dog clutch, 26... Fourth dog clutch, 27... Fifth dog clutch.
Claims (1)
体のハイドライブギヤとを備え、前記入力軸にトルク伝
達する第１クラッチと前記ロードライフギヤにトルク伝
達する第２クラッチとを近接して直列配置し、前記入力
軸と同一軸線で回転自在に軸承された出力軸上に歯数の
異なる複数枚のメインギヤを配列し、前記出力軸を挾ん
で第１副軸と第２副軸とを全て平行な軸線で配置すると
共に、前記第１副軸には前記ロードライフギヤと噛合す
る第１ドリブンギヤを、前記第２副軸には前記ハイドラ
イブギヤと噛合する第２ドリブンギヤを有し、前記第１
副軸上に前記各メインギヤと噛合する奇数速ギヤを、前
記第２副軸上に前記各メインギヤと噛合する偶数速ギヤ
を遊転軸承し、前記出力軸とハイドライブギヤ間にドッ
グクラッチを設け、前記第１副軸上には隣り合う２枚の
奇数速ギヤ間に、前記第２副軸上には隣り合う２枚の偶
数速ギヤ間にドッグクラッチを設けたことを特徴とする
ツインクラッチ式変速機。A road life gear freely rotatably supported on an input shaft and a high drive gear integrated with the input shaft are provided, and a first clutch that transmits torque to the input shaft and a second clutch that transmits torque to the road life gear are arranged close to each other. A plurality of main gears having different numbers of teeth are arranged on an output shaft which is arranged in series and rotatably supported on the same axis as the input shaft, and a first sub-shaft and a second sub-shaft are arranged with the output shaft in between. are all arranged with parallel axes, the first sub-shaft has a first driven gear that meshes with the road life gear, and the second sub-shaft has a second driven gear that meshes with the high drive gear, Said first
An odd speed gear that meshes with each of the main gears is freely rotatably supported on the subshaft, an even speed gear that meshes with each of the main gears is supported on the second subshaft, and a dog clutch is provided between the output shaft and the high drive gear. , a twin clutch characterized in that a dog clutch is provided between two adjacent odd speed gears on the first subshaft and between two adjacent even speed gears on the second subshaft. type transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63298305A JPH02146336A (en) | 1988-11-28 | 1988-11-28 | Twin clutch type transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63298305A JPH02146336A (en) | 1988-11-28 | 1988-11-28 | Twin clutch type transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02146336A true JPH02146336A (en) | 1990-06-05 |
Family
ID=17857927
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63298305A Pending JPH02146336A (en) | 1988-11-28 | 1988-11-28 | Twin clutch type transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02146336A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6463821B1 (en) * | 2001-06-29 | 2002-10-15 | Daimlerchrysler Corporation | Method of controlling a transmission having a dual clutch system |
| US6755089B2 (en) * | 2000-02-15 | 2004-06-29 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transfer device more particularly with double clutch transmission |
| JP2006527337A (en) * | 2003-06-06 | 2006-11-30 | ダイムラークライスラー・アクチェンゲゼルシャフト | Twin clutch transmission |
| US7409886B2 (en) | 2003-08-01 | 2008-08-12 | Daimler Ag | Twin clutch transmission with coaxial drive and output |
| WO2010103984A1 (en) * | 2009-03-11 | 2010-09-16 | 株式会社日立ニコトランスミッション | Twin clutch transmission for large-sized vehicle |
| EP2149725B1 (en) * | 2008-08-02 | 2012-05-23 | Daimler AG | Gear unit |
| CN105508513A (en) * | 2015-12-16 | 2016-04-20 | 湖南机油泵股份有限公司 | Non-standard reducer for kiln |
-
1988
- 1988-11-28 JP JP63298305A patent/JPH02146336A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6755089B2 (en) * | 2000-02-15 | 2004-06-29 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transfer device more particularly with double clutch transmission |
| US6463821B1 (en) * | 2001-06-29 | 2002-10-15 | Daimlerchrysler Corporation | Method of controlling a transmission having a dual clutch system |
| JP2006527337A (en) * | 2003-06-06 | 2006-11-30 | ダイムラークライスラー・アクチェンゲゼルシャフト | Twin clutch transmission |
| JP4692771B2 (en) * | 2003-06-06 | 2011-06-01 | ダイムラー・アクチェンゲゼルシャフト | Twin clutch transmission |
| US7409886B2 (en) | 2003-08-01 | 2008-08-12 | Daimler Ag | Twin clutch transmission with coaxial drive and output |
| EP2149725B1 (en) * | 2008-08-02 | 2012-05-23 | Daimler AG | Gear unit |
| WO2010103984A1 (en) * | 2009-03-11 | 2010-09-16 | 株式会社日立ニコトランスミッション | Twin clutch transmission for large-sized vehicle |
| JP2010210027A (en) * | 2009-03-11 | 2010-09-24 | Hitachi Nico Transmission Co Ltd | Twin clutch type transmission for large vehicle |
| CN102341616A (en) * | 2009-03-11 | 2012-02-01 | 株式会社日立Nico传动设备 | Twin clutch transmission for large-sized vehicle |
| CN105508513A (en) * | 2015-12-16 | 2016-04-20 | 湖南机油泵股份有限公司 | Non-standard reducer for kiln |
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