JPH02146337A - Twin clutch type transmission - Google Patents

Twin clutch type transmission

Info

Publication number
JPH02146337A
JPH02146337A JP63298306A JP29830688A JPH02146337A JP H02146337 A JPH02146337 A JP H02146337A JP 63298306 A JP63298306 A JP 63298306A JP 29830688 A JP29830688 A JP 29830688A JP H02146337 A JPH02146337 A JP H02146337A
Authority
JP
Japan
Prior art keywords
gear
speed
clutch
counter
dog clutch
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.)
Granted
Application number
JP63298306A
Other languages
Japanese (ja)
Other versions
JPH0674825B2 (en
Inventor
Masaaki Kamiya
神谷　正明
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hino Motors Ltd
Original Assignee
Hino Motors Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hino Motors Ltd filed Critical Hino Motors Ltd
Priority to JP63298306A priority Critical patent/JPH0674825B2/en
Publication of JPH02146337A publication Critical patent/JPH02146337A/en
Publication of JPH0674825B2 publication Critical patent/JPH0674825B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 parallel flow paths, e.g. dual clutch transmissions
    • 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
    • F16H2003/0807—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 with gear ratios in which the power is transferred by axially coupling idle gears to each other

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

PURPOSE:To perform a multi-shift speed change by selecting an input to high and low drive gears by the first and second clutches and providing the first to third gears in an output shaft and the first to third counter gears in a countershaft. CONSTITUTION:An input is obtained of a low drive gear 2, integral with an input shaft 1, from the first clutch 4a and an idly rotating high drive gear 3 from the second clutch 4b. An output shaft 5 provides the first to third gears 6 to 8, and a countershaft 12 provides the first and second driven gears 13, 14, respectively meshed with the high drive gear 3 and the low drive gear 2, and the first to third speed counter gears 15 to 17. By combination of dog clutches 9 to 11, 18 to 20 connecting and disconnecting each gear and the first and second clutches, selection is performed of the first to sixth speed shifts. Since the first speed gear of high load is placed approaching a bearing, bending moment is reduced, while a number of speed change shifts is obtained two times or more the number of sheets of gears, and even the total length is shortened.

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。<Conventional technology> Two clutches are provided on the same axis, and while one clutch is engaged, the other clutch is free and shifts are performed on the latch side, resulting in an instantaneous shift by switching the clutch, reducing shift operation time. A twin-clutch type transmission designed to achieve this is known, for example, from Japanese Patent Laid-Open No. 57-179457.

く発Ｊ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 that Kuhatsu J is trying to solve> 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 gear 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.

く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
力軸上に遊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−Ｅに前記入
力軸側から第３速ギヤ、第２速ギヤ及び第１速ギヤが遊
転軸承され、前記ロードライフギヤ及び第３速ギヤと出
力軸とを断、接する第３速ドッグクラッチと、第２速ギ
ヤと出力軸とを断、接する第２速ドッグクラッチと、第
１速ギヤと出力軸とを断、接する第１速ドッグクラッチ
とを配設し、前記出力軸と平行な軸線で配置されたカウ
ンタシャフトに前記ハイドライブギヤと噛合した第１ド
リブンギヤと前記第１速ギヤと噛合した第１速カウンタ
ギヤとを一体に設け、カウンタシャフト上には前記ロー
ドライフギヤと噛合する第２ドリブンギヤと、前記第３
速ギヤと噛合する第３速カウンタギヤと、前記第２速ギ
ヤと噛合する第２速カウンタギヤとが遊転軸承され、前
記第２ドリブンギヤと第３速カウンタギヤとを断、接す
る第１カウンタシャフトドッグクラッチと、前記第３速
カウンタギヤと第２速カウンタギヤとを断、接する第２
カウンタシャフトドッグクラッチと、カウンタシャフト
と第２速カウンタギヤとを断、接する第３カウンタシャ
フトドッグクラッチとを備えたものである。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 of a road life gear that is freely rotatably supported on the input shaft. A high drive gear integrated with an input 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 in close proximity, and are coaxial with the input shaft. A third speed gear, a second speed gear, and a first speed gear are freely rotatably supported on the rotatably supported output shaft -E from the input shaft side, and the road life gear and third speed gear are connected to the output shaft. A third speed dog clutch that disconnects and connects the second speed gear and the output shaft, a second speed dog clutch that disconnects and connects the first speed gear and the output shaft, and a first speed dog clutch that disconnects and connects the first speed gear and the output shaft are provided. A first driven gear that meshes with the high drive gear and a first speed counter gear that meshes with the first speed gear are integrally provided on a countershaft arranged on an axis parallel to the output shaft, and a first driven gear that meshes with the high drive gear and a first speed counter gear that meshes with the first speed gear are integrally provided, a second driven gear that meshes with the road life gear; and a third driven gear that meshes with the road life gear.
A third speed counter gear that meshes with the second speed gear and a second speed counter gear that meshes with the second speed gear are rotatably supported, and a first counter that disconnects and contacts the second driven gear and the third speed counter gear. a shaft dog clutch, and a second gear which disconnects and connects the third gear counter gear and the second gear counter gear.
It includes a countershaft dog clutch and a third countershaft dog clutch that connects and disconnects the countershaft and the second speed counter gear.

く作　用〉 本発明は上記の構成により、第１〜３速ドッグクラッチ
と第１〜３カウンタシャフトドッグクラッチの計６つの
ドッグクラッチのシフトの組合せと、２つのクラッチの
交互の接、断切り換えによりロー、ハイドライブギヤよ
り交互に入力されるトルク伝達系路によってそれぞれ３
枚の変速ギヤとカウンタギヤとの少数ギヤ構成で第１速
から第７迷の多段変速を可能とし、全長を短縮した多段
変速機を提供するものである。Function> The present invention has the above-described configuration, and is capable of combining a total of six dog clutches, the first to third speed dog clutches and the first to third countershaft dog clutches, and alternately engaging and disengaging the two clutches. 3 by the torque transmission path alternately input from the low and high drive gears.
To provide a multi-stage transmission that enables multi-stage shifting from the first speed to the seventh gear with a small number of gears consisting of two speed change gears and a counter gear, and has a shortened overall length.

〈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ｌ上にはハイドライブギヤ３が遊転軸承され、また
入力軸１と一体のロードライフギヤ２が前記ハイドライ
ブギヤ３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 high drive gear 3 is rotatably supported on the input shaft l, and a road life gear 2, which is integrated with the input shaft 1, is arranged in series with the high drive gear 3.

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はハイドライブギヤ３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 high drive gear 3, 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
力軸である。この出力軸５上には前記入力軸１側から第
３速ギヤ８、第２速ギヤ７及び第１速ギヤ６が遊転軸承
されている。Reference numeral 5 denotes an output shaft rotatably supported on the same axis as the input shaft 1. A third speed gear 8, a second speed gear 7, and a first speed gear 6 are rotatably supported on the output shaft 5 from the input shaft 1 side.

前記ロードライフギヤ２と第３遠ギヤ８との間には、出
力軸５とロードライフギヤ２、第３速ギヤ８との相互の
断、接する第３遠ドッグクラッチ１１が設けられ、第２
速ギヤ７と出力軸５とを断、接する第２速ドッグクラッ
チ１０と、第１′Ｍギヤ６と出力軸５とを断、接する第
１速ドッグクラッチ９とが配設されている。A third far dog clutch 11 is provided between the road life gear 2 and the third far gear 8, and the third far dog clutch 11 connects and disconnects the output shaft 5, the road life gear 2, and the third gear 8.
A second speed dog clutch 10 that connects and disconnects the speed gear 7 and the output shaft 5, and a first speed dog clutch 9 that connects and disconnects the 1'M gear 6 and the output shaft 5 are provided.

１２は前記出力軸５と平行な軸線で配置されているカウ
ンタシャフトである。このカウンタシャフト１２には前
記ハイドライブギヤ３と噛合した第１ドリブンギヤ１３
と前記第１速ギヤ６と噛合した第１速カウンタギヤ１５
とが一体に設けられ、カウンタシャフト１２上には前記
ロードライフギヤ２と噛合する第２ドリブンギヤ１４と
、前記第３速ギヤ８と噛合する第３速カウンタギヤ１７
と前記第２速ギヤ７と噛合する第２速カウンタギヤ１６
とが遊転軸承されている。そして、第２ドリブンギヤ１
４と第３速カウンタギヤ１７とを断、接する第１カウン
タシャフトドッグクラッチ２０と、第３速カウンタギヤ
１７と第２速カウンタギヤ１６とを断、接する第２カウ
ンタシャフトドッグクラッチ１８と、第２速カウンタギ
ヤ１６とカウンタシャフト１２間を断、接する第３カウ
ンタシャフトドッグクラッチ１９とを設けた構成である
。Reference numeral 12 denotes a countershaft arranged along an axis parallel to the output shaft 5. A first driven gear 13 that meshes with the high drive gear 3 is connected to the counter shaft 12.
and a first speed counter gear 15 that meshes with the first speed gear 6.
A second driven gear 14 that meshes with the road life gear 2 and a third speed counter gear 17 that meshes with the third speed gear 8 are provided on the counter shaft 12.
and a second speed counter gear 16 that meshes with the second speed gear 7.
and are freely rotatable bearings. And second driven gear 1
A first countershaft dog clutch 20 that disconnects and contacts the third speed counter gear 17 and the third speed counter gear 17; a second countershaft dog clutch 18 that disconnects and connects the third speed counter gear 17 and the second speed counter gear 16; This configuration includes a third countershaft dog clutch 19 that connects and disconnects between the second speed counter gear 16 and the countershaft 12.

次に上記構成の動作について説明する。先ず第１速ドッ
グクラッチ９を第１速ギヤ６側ヘシフトし、第１カウン
タシャフトドッグクラッチ２Ｇを第３速カウンタギヤ１
７側ヘシフトして第２ドリブンギヤ１４と第３速カウン
タギヤ１７とを接続し、第２カウンタシャフトドッグク
ラッチ１８を第３速カウンタギヤ１７（１１！！へ、ま
た第３カウンタシャフトドッグクラッチ１９を第２遠カ
ウンタギヤ１６側へシフトする。この状態で第１クラッ
チ４ａを接続すると１運ロー（実質的には第１速段）と
なる、すなわち、第１クラッチ４ａから入力軸１に入力
されるトルクはロードライフギヤ２、第２ドリブンギヤ
１４、第３速カウンタギヤ１７、第２カウンタギヤ１６
、カウンタシャフト１２、第１速カウンタギヤ１５、第
１速ギヤ６を経由して出力軸５に伝達する。そして、第
２クラッチ４ｂを接に、第１クラッチ４ａを断に切り換
えると第１速ハイ（実質的には第２速段）となる、すな
わち、第２クラッチ４ｂからハイドライブギヤ３に入力
されるトルクは第１ドリブンギヤ１３、カウンタシャフ
ト１２、第１速カウンタギヤ１５、第１速ギヤ６を経由
して出力軸５に伝達する。Next, the operation of the above configuration will be explained. First, the first gear dog clutch 9 is shifted to the first gear 6 side, and the first countershaft dog clutch 2G is shifted to the third gear counter gear 1.
7 side to connect the second driven gear 14 and the third speed counter gear 17, and shift the second countershaft dog clutch 18 to the third speed counter gear 17 (11!!), and also connect the third countershaft dog clutch 19 to the third speed counter gear 17 (11!!). Shift to the second far counter gear 16 side.If the first clutch 4a is connected in this state, it will be in 1st gear low (substantially the 1st gear), that is, the input from the first clutch 4a to the input shaft 1 will be The torque is generated by the road life gear 2, the second driven gear 14, the third speed counter gear 17, and the second counter gear 16.
, the counter shaft 12 , the first speed counter gear 15 , and the first speed gear 6 . Then, when the second clutch 4b is turned on and the first clutch 4a is turned off, the first speed is high (substantially the second speed), that is, the input from the second clutch 4b to the high drive gear 3 is set. The torque is transmitted to the output shaft 5 via the first driven gear 13, the counter shaft 12, the first speed counter gear 15, and the first speed gear 6.

前記第１クラッチ４ａの断の時に第２速ドッグクラッチ
１０を第２速ギヤ７１１１１！Ｉへ、第３カウンタシャ
フトドッグクラッチ１９を第２カウンタギヤ１６より切
り離される側（図において右方）へそれぞれシフトする
。そして、第１クラッチ４ａを接に、第２クラッチ４ｂ
を断に切り換えることにより第２速ロー（実質的には第
３速段）に変速される。すなわち、トルクの入出力系路
は、第１クラッチ４ａ、ロードライフギヤ２、第２ドリ
ブンギヤ１４、第３速カウンタギヤ１１、第２速カウン
タギヤ１６、第２速ギヤ７、第２速ドッグクラッチ１０
を経て出力軸５に取り出される。When the first clutch 4a is disengaged, the second speed dog clutch 10 is shifted to the second speed gear 71111! I, the third countershaft dog clutch 19 is shifted to the side where it is disconnected from the second counter gear 16 (to the right in the figure). Then, the first clutch 4a is connected, and the second clutch 4b is connected.
By switching to OFF, the gear is shifted to second speed low (substantially third speed). That is, the torque input/output path includes the first clutch 4a, the road life gear 2, the second driven gear 14, the third speed counter gear 11, the second speed counter gear 16, the second speed gear 7, and the second speed dog clutch. 10
It is then taken out to the output shaft 5.

この第２速ローの状態、すなわち、第２クラッチ４ｂが
断のときに第３カウンタシャフトドッグクラッチ１９を
第２速カウンタギヤ１６側ヘシフトし、第２クラッチ４
ｂを接、第１クラッチ４ａを断に切り換えると第２速ハ
イ（実質的には第４速段）に変速される。このときのト
ルクの入出力系路は第２クラッチ４ｂ、ハイドライブギ
ヤ３、第１ドリブンギヤ１３、カウンタシャフト１２、
第３カウンタシャフトドッグクラッチ１９、第２３！１
カウンタギヤ１６、第２速ギヤ７、第２速ドッグクラッ
チ１０を経て出力軸に取り出される。In this second speed low state, that is, when the second clutch 4b is disengaged, the third countershaft dog clutch 19 is shifted to the second speed counter gear 16 side, and the second clutch 4b is shifted to the second speed counter gear 16 side.
When the clutch 4a is turned on and the first clutch 4a is turned off, the gear is shifted to the second high speed (substantially the fourth speed). The torque input/output path at this time is the second clutch 4b, high drive gear 3, first driven gear 13, countershaft 12,
3rd countershaft dog clutch 19, 23rd!1
It is taken out to the output shaft via the counter gear 16, second speed gear 7, and second speed dog clutch 10.

次に第３遠ロー（実質的には第５速段）の変速は、第２
クラッチ４ｂを断にして第３カウンタシャフトドッグク
ラッチ１９を第２速カウンタギヤ１６より切り離される
側ノーシフトし、第３速ドッグクラッチ１１を第３速ギ
ヤ８１１！！ｌヘシフトして第１クラッチ４ａを接、第
２クラッチ４ｂを断に切り換えることにより得られる。Next, when shifting to the 3rd far-low (actually the 5th gear), the 2nd
Disconnect the clutch 4b, shift the third countershaft dog clutch 19 to the side that is disconnected from the second speed counter gear 16, and shift the third speed dog clutch 11 to the third speed gear 811! ! This can be achieved by shifting to 1, engaging the first clutch 4a, and disengaging the second clutch 4b.

このときの入出力系路は、第１クラッチ４ａ、ロードラ
イフギヤ２、第２ドリブンギヤ１４、第３速カウンタギ
ヤ１７、第３速ギヤ８、第３速ドッグクラッチ１１を経
て出力軸５に取り出される。At this time, the input/output path is taken out to the output shaft 5 via the first clutch 4a, the road life gear 2, the second driven gear 14, the third speed counter gear 17, the third speed gear 8, and the third speed dog clutch 11. It will be done.

第３速ハイ（実質的には第６速段）の変速は、第１クラ
ッチ４ａを断にして第１カウンタシャフトドッグクラッ
チ２０を第２ドリブンギヤ１４側ヘシフトし、第３カウ
ンタシャフトドッグクラッチ１９を第２速カウンタギヤ
１６側へ、第２カウンタシャフトドッグクラッチ１８を
第３速カウンタギヤ１７側ヘシフトして第２クラッチ４
ｂを接に切り換えることによって得られる。このときの
トルクの入出力系路は、第２クラッチ４ｂ、ハイドライ
ブギヤ３、第１ドリブンギヤ１３、カウンタシャフト１
２、第３カウンタシャフトドッグクラッチ１９、第２速
カウンタギヤ１６、第２カウンタシャフトドッグクラッ
チ１８、第３速カウンタギヤ１７、第３速ギヤ８、第３
速ドッグクラッチ１１を経で出力軸５に取り出される。To shift to 3rd gear high (substantially 6th gear), the first clutch 4a is disengaged, the first countershaft dog clutch 20 is shifted to the second driven gear 14 side, and the third countershaft dog clutch 19 is shifted to the second driven gear 14 side. The second countershaft dog clutch 18 is shifted to the second speed counter gear 16 side, and the second countershaft dog clutch 18 is shifted to the third speed counter gear 17 side.
It is obtained by switching b to a tangent. At this time, the torque input/output path includes the second clutch 4b, the high drive gear 3, the first driven gear 13, and the countershaft 1.
2, third countershaft dog clutch 19, second speed counter gear 16, second countershaft dog clutch 18, third speed counter gear 17, third speed gear 8, third speed counter gear
It is taken out to the output shaft 5 via the fast dog clutch 11.

尚第３速口及びハイのときには第２速ドッグクラッチ１
０は第２速ギヤ７より切り離されている。In addition, when 3rd speed is on and high, 2nd speed dog clutch 1
0 is disconnected from the second speed gear 7.

さらに、第２クラッチ４ｂを断にして第３速ドッグクラ
ッチ１１をロードライフギヤ２側ヘシフトし、第１クラ
ッチ４ａを接に切り換えることにより入力軸１と出力軸
５とは直結され、第７速段に変速される。Furthermore, the input shaft 1 and the output shaft 5 are directly connected by disengaging the second clutch 4b, shifting the third speed dog clutch 11 to the road life gear 2 side, and switching the first clutch 4a to the connected position. The gears are shifted into gears.

また、上記のギヤ配列は、出力軸５上では入力軸１側よ
り第３遠ギヤ６、第２速ギヤ７及び第３速ギヤ８と順次
ギヤ径が大径となっているので、最も高負荷が作用する
第１速ギヤは出力軸５の軸受に近接され、出力軸５に対
する曲げモーメントを軽減する。In addition, in the above gear arrangement, the diameter of the gears on the output shaft 5 becomes larger sequentially from the input shaft 1 side to the third far gear 6, second gear 7, and third gear 8, so the gear diameter is the highest. The first speed gear on which the load is applied is located close to the bearing of the output shaft 5 to reduce the bending moment with respect to the output shaft 5.

尚、第１．２クラッチ４ａ、４ｂの切り換え、各ド・ｙ
グツラッチ９．１０．１１．１８．１９．２０のシフト
は油圧、空圧、ＹＳ　ｆｉｌｌ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, switching of the 1st and 2nd clutches 4a and 4b, each de-y
For shifting of Gutsuratch 9, 10, 11, 18, 19, and 20, an automatic shift control system is used in which actuators such as hydraulic pressure, pneumatic pressure, and YS fill are controlled by a computer.

〈発明の効果〉 以上のように本発明によれば、２つのクラッチの切り換
えによってロードリブンギヤ及びバイドリブンギヤによ
る入力系路とし、かつ変速ギヤ側のドッグクラッチ並び
にカウンタギヤ側のドッグクラッチのシフトによって変
速する機構であるから、変速ギヤ及びカウンタギヤの枚
数の２倍以上の変速段数が得られ、少数のギヤ配列構成
によるコンパクトなツインクラッチ式の多段変速機が得
られる。<Effects of the Invention> As described above, according to the present invention, an input system is established by a load-driven gear and a bid-driven gear by switching two clutches, and a shift is performed by shifting a dog clutch on the transmission gear side and a dog clutch on the counter gear side. Since this is a mechanism that allows the number of speed change stages to be twice or more the number of speed change gears and counter gears, it is possible to obtain a compact twin-clutch type multi-stage transmission with a small number of gear arrangement configurations.

また、各遠ギヤ配列は出力軸に対する曲げモーメントを
軽減する構成となっているため、出力軸の回転軸心が確
保され、ギヤの噛合を円滑にする利点がある。Further, since each of the far gear arrays is configured to reduce the bending moment relative to the output shaft, the rotational axis of the output shaft is ensured, which has the advantage of smooth gear meshing.

【図面の簡単な説明】[Brief explanation of the drawing]

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・・・
ハイドライブギヤ、４ａ・・・第１クラッチ、４ｂ・・
・第２クラッチ、５・・・出力軸、６・・・第１速ギヤ
、７・・・第２速ギヤ、８・・・第３速ギヤ、９・・・
第１速ドッグクラッチ、１０・・・第２速ドッグクラッ
チ、１１・・・第３速ドッグクラッチ、１２・・・カウ
ンタシャフト、１３・・・第１ドリブンギヤ、１４・・
・第２ドリブンギヤ、１５・・・第１速カウンタギヤ、
１６・・・第２速カウンタギヤ、１７・・・第３速カウ
ンタギヤ、１８・・・第２カウンタシャフトドッグクラ
ッチ、１９・・・第３カウンタシャフトドッグクラッチ
、２０・・・第１カウンタシャフトドッグクラッチ。 図面 特許出願人　　日野自動車工業株式会社１１′ソThe drawings are cross-sectional views showing embodiments of the present invention. 1...Input shaft, 2...Road life gear, 3...
High drive gear, 4a...1st clutch, 4b...
・Second clutch, 5... Output shaft, 6... First gear, 7... Second gear, 8... Third gear, 9...
1st speed dog clutch, 10... 2nd speed dog clutch, 11... 3rd speed dog clutch, 12... Counter shaft, 13... 1st driven gear, 14...
・Second driven gear, 15...first speed counter gear,
16... 2nd speed counter gear, 17... 3rd speed counter gear, 18... 2nd countershaft dog clutch, 19... 3rd countershaft dog clutch, 20... 1st countershaft dog clutch. Drawing patent applicant: Hino Motors Co., Ltd.

Claims (1)

【特許請求の範囲】[Claims] 入力軸上に遊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前記入
力軸側から第３速ギヤ、第２速ギヤ及び第１速ギヤが遊
転軸承され、前記ロードライフギヤ及び第３速ギヤと出
力軸とを断、接する第３速ドッグクラッチと、第２速ギ
ヤと出力軸とを断、接する第２速ドッグクラッチと、第
１速ギヤと出力軸とを断、接する第１速ドッグクラッチ
とを配設し、前記出力軸と平行な軸線で配置されたカウ
ンタシャフトに前記ハイドライブギヤと噛合した第１ド
リブンギヤと前記第１速ギヤと噛合した第１速カウンタ
ギヤとを一体に設け、カウンタシャフト上には前記ロー
ドライフギヤと噛合する第２ドリブンギヤと、前記第３
速ギヤと噛合する第３速カウンタギヤと、前記第２速ギ
ヤと噛合する第２速カウンタギヤとが遊転軸承され、前
記第２ドリブンギヤと第３速カウンタギヤとを断、接す
る第１カウンタシャフトドッグクラッチと、前記第３速
カウンタギヤと第２速カウンタギヤとを断、接する第２
カウンタシャフトドッグクラッチと、カウンタシャフト
と第２速カウンタギヤとを断、接する第３カウンタシャ
フトドッグクラッチとを備え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 third speed gear, a second speed gear, and a first speed gear are freely rotatably supported from the input shaft side on the output shaft, which is arranged in series and rotatably supported on the same axis as the input shaft. Disconnect the gear and the third speed gear from the output shaft, disconnect the third speed dog clutch that is in contact with the output shaft, disconnect the second speed dog clutch that is in contact with the output shaft, and disconnect the second speed dog clutch that is in contact with the first speed gear and the output shaft. , a first speed dog clutch in contact with the first speed dog clutch, a first driven gear meshed with the high drive gear on a counter shaft disposed along an axis parallel to the output shaft, and a first speed counter meshed with the first speed gear. A second driven gear that meshes with the road life gear and a third driven gear are provided on the countershaft.
A third speed counter gear that meshes with the second speed gear and a second speed counter gear that meshes with the second speed gear are rotatably supported, and a first counter that disconnects and contacts the second driven gear and the third speed counter gear. a shaft dog clutch, and a second gear which disconnects and connects the third gear counter gear and the second gear counter gear.
A twin clutch type transmission characterized by comprising a countershaft dog clutch and a third countershaft dog clutch that connects and disconnects the countershaft and the second speed counter gear.
JP63298306A 1988-11-28 1988-11-28 Twin clutch transmission Expired - Lifetime JPH0674825B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP63298306A JPH0674825B2 (en) 1988-11-28 1988-11-28 Twin clutch transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP63298306A JPH0674825B2 (en) 1988-11-28 1988-11-28 Twin clutch transmission

Publications (2)

Publication Number Publication Date
JPH02146337A true JPH02146337A (en) 1990-06-05
JPH0674825B2 JPH0674825B2 (en) 1994-09-21

Family

ID=17857937

Family Applications (1)

Application Number Title Priority Date Filing Date
JP63298306A Expired - Lifetime JPH0674825B2 (en) 1988-11-28 1988-11-28 Twin clutch transmission

Country Status (1)

Country Link
JP (1) JPH0674825B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2772451A1 (en) * 1997-12-16 1999-06-18 Renault GEARBOX COMPRISING A HOUSING WITH THREE BEARINGS PER SHAFT
WO1999031410A1 (en) * 1997-12-16 1999-06-24 Renault Motor vehicle gearbox

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2772451A1 (en) * 1997-12-16 1999-06-18 Renault GEARBOX COMPRISING A HOUSING WITH THREE BEARINGS PER SHAFT
WO1999031410A1 (en) * 1997-12-16 1999-06-24 Renault Motor vehicle gearbox

Also Published As

Publication number Publication date
JPH0674825B2 (en) 1994-09-21

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