JP2680708B2 - Transmission gearing - Google Patents
Transmission gearingInfo
- Publication number
- JP2680708B2 JP2680708B2 JP2013557A JP1355790A JP2680708B2 JP 2680708 B2 JP2680708 B2 JP 2680708B2 JP 2013557 A JP2013557 A JP 2013557A JP 1355790 A JP1355790 A JP 1355790A JP 2680708 B2 JP2680708 B2 JP 2680708B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- clutch device
- shaft
- clutch
- gears
- 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.)
- Expired - Lifetime
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
- F16H3/02—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
-
- 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
-
- 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
- F16H2003/0826—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 wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、フオークリフト等産業車両、およびタイヤ
ローラ等建設機械の変速装置に適用される動力伝達装置
に関する。Description: TECHNICAL FIELD The present invention relates to a power transmission device applied to a transmission such as an industrial vehicle such as a forklift and a construction machine such as a tire roller.
〔従来の技術〕 従来の前進３段後進３段平行軸方式歯車変速装置のス
ケルトン図を第3,4図に示す。[Prior Art] FIGS. 3 and 4 are skeleton diagrams of a conventional three-stage forward three-stage reverse three-stage parallel shaft type gear transmission.
第３図は特公昭47−21649号公報に記載されているも
のであり、本装置はクラツチ機構３個分で全長が決ま
り、前後方向に長くなる。また入出力軸を同一軸線にす
るためには、トランスフア部ａで行わなければならず、
使用する歯車や軸の数が多くなる。FIG. 3 is described in Japanese Examined Patent Publication No. 47-21649, and the total length of this device is determined by three clutch mechanisms, and it becomes long in the front-rear direction. Also, in order to make the input and output axes the same axis, it must be done in the transfer part a,
The number of gears and shafts used increases.
第４図は特公昭58−42384号公報に記載されているも
のであり、本装置は全長をクラツチ機構２個分の巾に納
めることができるが、第３図の装置と同様に、入出力軸
の同一軸線化にはトランスフア部分ａが必要である。FIG. 4 is described in Japanese Examined Patent Publication No. 58-42384, and the entire length of this device can be accommodated within the width of two clutch mechanisms, but like the device of FIG. The transfer part a is required for making the shafts the same axis.
（１） タイヤローラ等の建設機械では、車両配置上か
ら歯車変速装置は、入力軸と出力軸が同一軸線上にあ
り、かつ変速装置全長も短かいことが要求されるが、平
行軸形式の歯車変速装置は、一般に入出力軸位置が異な
ることが多く、同一軸線上に配置しようとすると、第３
図のように前後方向に長くなり、搭載スペース及び重量
の増大等の問題点を生ずる。(1) In construction machines such as tire rollers, the gear transmission is required to have an input shaft and an output shaft on the same axis line and a short overall transmission length because of the vehicle arrangement. Generally, gear transmissions often have different input / output shaft positions, and if they are arranged on the same axis, they will be
As shown in the figure, it becomes long in the front-rear direction, causing problems such as an increase in mounting space and weight.
（２） 異なった車両に対し、共通の変速機を使用し、
出力軸位置のみ変更することが多いが、この場合でも従
来技術によると、基本となるケース類（第３図トランス
フアケースａ、第４図トランスミツシヨンケースｂ）ま
で変更しなければならず、共通化の割合が低くなる等の
問題点がある。(2) Use a common transmission for different vehicles,
Often, only the output shaft position is changed, but even in this case, according to the prior art, even the basic cases (the transfer case a in FIG. 3 and the transmission case b in FIG. 4) must be changed. There are problems such as a low ratio of common use.
本発明は、上記（１），（２）の問題点を同時に解決
した入出力軸が同一軸線上にあるコンパクトな変速歯車
装置を提供することを目的とするものである。SUMMARY OF THE INVENTION It is an object of the present invention to provide a compact transmission gear device in which the input and output shafts are on the same axis and which solves the problems (1) and (2) at the same time.
第１図に示す如く、入力軸歯車２と噛合う歯車３、４
の中間軸13、14に、クラツチ装置５及び６を設け、これ
等のクラツチ装置との干渉を避けて、且つ入力軸１の同
軸線上に、出力軸19を配置する。As shown in FIG. 1, gears 3 and 4 meshing with the input shaft gear 2.
The intermediate shafts 13 and 14 are provided with the clutch devices 5 and 6, and the output shaft 19 is disposed on the coaxial line of the input shaft 1 while avoiding interference with these clutch devices.
出力軸19を中心軸とするクラツチ装置15、16を設け、
歯車７と歯車15、歯車11と歯車17を噛合わせる。中間軸
22に歯車20、21を設け、歯車12と歯車20、歯車18と歯車
21を噛合わせる。The clutch devices 15 and 16 having the output shaft 19 as the central axis are provided,
The gear 7 and the gear 15, and the gear 11 and the gear 17 are meshed with each other. Intermediate shaft
22 is provided with gears 20 and 21, gear 12 and gear 20, gear 18 and gear
21 bite.
入力軸１と出力軸19とは同軸線上に配置され、且つ前
後方向長が短縮される。出力軸19には歯車15とクラツチ
16、歯車11、17、及び歯車21、18を介して、多段変速さ
れた回転力が伝達される。The input shaft 1 and the output shaft 19 are arranged coaxially, and the length in the front-rear direction is shortened. The output shaft 19 has a gear 15 and a clutch.
Through the 16, the gears 11 and 17, and the gears 21 and 18, the rotational force subjected to the multi-speed shifting is transmitted.
中間軸22から出力を取り出すことにより、特別な装置
を付加することなく、入出力軸間距離を変えることがで
き、複数の型式の車両えの適用が容易になる。By taking out the output from the intermediate shaft 22, the distance between the input and output shafts can be changed without adding a special device, and the application of a plurality of vehicle models becomes easy.
第１図は、前後進３段の一実施例のスケルトン図であ
り、第２図は前後進４段のスケルトン図である。FIG. 1 is a skeleton diagram of one embodiment of three stages of forward and backward movement, and FIG. 2 is a skeleton diagram of four stages of forward and backward movement.
第１図において、図示せざる原動機から動力は、トル
クコンバータ26を経て入力軸１へと伝達される。入力軸
１上には、歯車２が固着されており、中間軸13,14上の
歯車3,4と噛み合っている。中間軸13,14には、中央部分
に歯車7,8及びクラツチ装置５と９、６と10が固着され
ている。クラツチ装置は、複数の摩擦板、相手板及びピ
ストンからなり、油圧によりピストンが作動して多板ク
ラツチを押圧し、それぞれの中間軸上に回転自由に保持
された歯車3,4,11,12の一端のスプライン部を介して結
合状態となる公知の形式のものである。出力軸19上に
は、同様なクラツチ装置と、一端にスプラインを有し軸
上に回転自由に保持された歯車15と、歯車17,18とが固
着されている。中間軸22には、歯車20及び21が固着され
ており、歯車20は、中間軸14上の歯車12と噛合い、歯車
21は、出力軸19上の歯車18と噛合う。In FIG. 1, power from an unillustrated prime mover is transmitted to the input shaft 1 via the torque converter 26. The gear 2 is fixed on the input shaft 1 and meshes with the gears 3, 4 on the intermediate shafts 13, 14. Gears 7, 8 and clutch devices 5, 9 and 6 and 10 are fixed to the central portions of the intermediate shafts 13 and 14, respectively. The clutch device is composed of a plurality of friction plates, mating plates and pistons, and the pistons are actuated by hydraulic pressure to press the multi-plate clutches, and the gears 3, 4, 11, 12 are rotatably held on their respective intermediate shafts. It is of a known type in which it is brought into a coupled state through a spline portion at one end of the. On the output shaft 19, a similar clutch device, a gear 15 having a spline at one end and rotatably held on the shaft, and gears 17, 18 are fixed. Gears 20 and 21 are fixed to the intermediate shaft 22, and the gear 20 meshes with the gear 12 on the intermediate shaft 14,
21 meshes with gear 18 on output shaft 19.
また、中間軸13上の歯車７は、中間軸14上の歯車８及
び出力軸19上の歯車15と噛合っており、中間軸13上の歯
車11は、出力軸19の歯車17と噛合っている。Further, the gear 7 on the intermediate shaft 13 meshes with the gear 8 on the intermediate shaft 14 and the gear 15 on the output shaft 19, and the gear 11 on the intermediate shaft 13 meshes with the gear 17 on the output shaft 19. ing.
次に本装置の作用を説明する。 Next, the operation of the present apparatus will be described.
前記のクラツチ装置5,6のいずれか一方、及びクラツ
チ装置9,10,16の内一つ、合計２つのクラツチ装置を係
合状態にすることで、前進３段、後進３段の変速比を得
るもので第１表に各部材の組合せの例を示す。尚、クラ
ツチ装置5,6は、前後進選択用であるが必要に応じて逆
にすることも可能である。By engaging one of the clutch devices 5 and 6 and one of the clutch devices 9, 10 and 16, a total of two clutch devices, a gear ratio of three forward gears and three reverse gears can be obtained. Table 1 shows examples of combinations of each member. The clutch devices 5 and 6 are for selecting forward and backward movement, but they can be reversed if necessary.
（前進１速） クラツチ装置５及び10を作用させると、
入力軸１の動力は、歯車２−歯車３−クラツチ装置５−
歯車７−歯車８−クラツチ装置10−歯車12−歯車20−歯
車21−歯車18を介して、出力軸19へ伝達され、入力軸１
と同方向に回転する。 (1st forward speed) When the clutch devices 5 and 10 are operated,
The power of the input shaft 1 is gear 2 -gear 3 -clutch device 5-
It is transmitted to the output shaft 19 via the gear 7-gear 8-the clutch device 10-gear 12-gear 20-gear 21-gear 18, and the input shaft 1
And rotate in the same direction.
（前進２速） クラツチ装置５及び９を作用させると、
入力軸１の動力は、歯車２−歯車３−クラツチ装置５−
クラツチ装置９−歯車11−歯車17を介して、出力軸19へ
伝達され、入力軸１と同方向に回転する。(2nd forward speed) When the clutch devices 5 and 9 are operated,
The power of the input shaft 1 is gear 2 -gear 3 -clutch device 5-
It is transmitted to the output shaft 19 via the clutch device 9-gear 11-gear 17, and rotates in the same direction as the input shaft 1.
（前進３速） クラツチ装置５及び16を作用させると、
入力軸１の動力は、歯車２−歯車３−歯車７−歯車15−
クラツチ装置16を介して、出力軸19へ伝達され、入力軸
１と同方向に回転する。(3rd forward speed) When the clutch devices 5 and 16 are operated,
The power of the input shaft 1 is gear 2-gear 3-gear 7-gear 15-
It is transmitted to the output shaft 19 through the clutch device 16 and rotates in the same direction as the input shaft 1.
（後進１速） クラツチ装置６及び10を作用させると、
入力軸１の動力は、歯車２−歯車４−クラツチ装置６−
クラツチ装置10−歯車12−歯車20−歯車21−歯車18を介
して、出力軸19へ伝達され、入力軸１と逆方向に回転す
る。(First reverse speed) When the clutch devices 6 and 10 are operated,
The power of the input shaft 1 is gear 2-gear 4-clutch device 6-
It is transmitted to the output shaft 19 through the clutch device 10-gear 12-gear 20-gear 21-gear 18 and rotates in the opposite direction to the input shaft 1.
（後進２速） クラツチ装置６及び９を作用させると、
入力軸１の動力は、歯車２−歯車４−クラツチ装置６−
歯車８−歯車７−クラツチ装置９−歯車11−歯車17を介
して、出力軸19へ伝達され、入力軸１と逆方向に回転す
る。(2nd reverse speed) When the clutch devices 6 and 9 are operated,
The power of the input shaft 1 is gear 2-gear 4-clutch device 6-
It is transmitted to the output shaft 19 via the gear 8-the gear 7-the clutch device 9-the gear 11-the gear 17 and rotates in the opposite direction to the input shaft 1.
（後進３速） クラツチ装置６及び16を作用させると、
入力軸１の動力は、歯車２−歯車４−クラツチ装置６−
歯車８−歯車７−歯車15−クラツチ装置16介して、出力
軸19へ伝達され、入力軸１と逆方向に回転する。(3rd reverse speed) When the clutch devices 6 and 16 are operated,
The power of the input shaft 1 is gear 2-gear 4-clutch device 6-
It is transmitted to the output shaft 19 via the gear 8-gear 7-gear 15-clutch device 16 and rotates in the opposite direction to the input shaft 1.
次に第２図に示した前後進４段変速装置について説明
する。Next, the forward / backward four-speed transmission shown in FIG. 2 will be described.
第２図の如く、中間軸22上にクラツチ装置23及び歯車
24を追加することで容易に前進４段後進４段の変速機が
構成出来る。As shown in FIG. 2, the clutch device 23 and the gears are mounted on the intermediate shaft 22.
By adding 24, a transmission with four forward gears and four reverse gears can be easily configured.
第２表に各部材の組合せの例を示す。 Table 2 shows examples of combinations of the respective members.
本例では、中間軸22−出力軸19は、歯車21と歯車18に
よって接続されているが歯車20を歯車17又は歯車18と噛
合せてもよく、また歯車21を歯車17と噛合せても同様の
効果が得られる。 In this example, the intermediate shaft 22 and the output shaft 19 are connected by the gear 21 and the gear 18, but the gear 20 may be meshed with the gear 17 or the gear 18, or the gear 21 may be meshed with the gear 17. The same effect can be obtained.
さらにクラツチ装置9,10,16,23の内任意の数を減ずる
ことで変速段数を少なくすることが可能である。特に前
進２段、後進２段の場合、第２図のクラツチ装置10,23
を除くことで歯車12,18,21,22,24、中間軸22をなくすこ
とが出来、大幅に部品点数が減らせるため、重量軽減、
製造コストの減少につながる。Further, it is possible to reduce the number of gear stages by reducing any number of the clutch devices 9, 10, 16, 23. Especially in the case of two forward gears and two reverse gears, the clutch devices 10, 23 of FIG.
By removing the gears 12, 18, 21, 22, 24, and the intermediate shaft 22, the number of parts can be greatly reduced, reducing the weight.
This leads to a reduction in manufacturing costs.
第１図、第２図とも出力軸は、軸19であるが、これを
中間軸22から出力しても、同じ変速段数、等段間比のト
ランスミツシヨンとなる。従ってあらかじめ軸19,22の
位置をそれぞれ出力軸位置にあわせることで、出力軸位
置の異なる複数の車両に搭載することができる。Although the output shaft is the shaft 19 in both FIGS. 1 and 2, even if it is output from the intermediate shaft 22, the transmission has the same number of gears and the same gear ratio. Therefore, by adjusting the positions of the shafts 19 and 22 to the output shaft positions in advance, they can be mounted on a plurality of vehicles having different output shaft positions.
本発明による変速歯車装置は、入力軸１により駆動さ
れる入力歯車２と、入力歯車２に噛合う第２の歯車３お
よび第３の歯車４と、第２の歯車３と共通の中間軸13に
固着されている第４の歯車７と同軸上に回転可能に保持
された第５の歯車11と、第３の歯車４と共通の中間軸14
に固着されている第６の歯車８と同軸上に回転可能に保
持された第７の歯車12と、第４の歯車７に噛合う第８の
歯車15と、第８の歯車15と共通の出力軸19に固着されて
いる第９の歯車17および第10の歯車18と、第７の歯車12
と噛合う第11の歯車20と、第11の歯車20と共通の中間軸
22上に固定され、かつ第10の歯車18と噛合っている第12
の歯車21と、第２の歯車３と第４の歯車７とを接続可能
とする第１クラツチ装置５と、第４の歯車７と第５の歯
車11とを接続可能とする第２のクラツチ装置９と、第３
の歯車４と第６の歯車８とを接続可能とする第３のクラ
ツチ装置６と、第６の歯車８と第７の歯車12とを接続可
能とする第４のクラツチ装置10と、第８の歯車15と第９
の歯車17とを接続可能とする第５のクラツチ装置16とか
らなり、第１のクラツチ装置５及び第２のクラツチ装置
９に直接結合された第４の歯車７と、第３のクラツチ装
置６及び第４のクラツチ装置10に直接結合された第６の
歯車８が、ともに第５のクラツチ装置16に直接結合され
た第８の歯車15に噛合うようにしたものであるからそれ
により２個のクラツチ装置に結合された歯車が他のクラ
ツチ装置に結合された歯車とは直接噛合って歯車と軸の
数を減らし、かつ変速歯車装置全体のスペースをコンパ
クトにする効果を有する。The transmission gear device according to the present invention includes an input gear 2 driven by an input shaft 1, a second gear 3 and a third gear 4 meshing with the input gear 2, and an intermediate shaft 13 common to the second gear 3. A fifth gear 11 rotatably held coaxially with a fourth gear 7 fixed to the third gear 4, and an intermediate shaft 14 common to the third gear 4.
The seventh gear 12 rotatably held coaxially with the sixth gear 8 fixed to the, the eighth gear 15 meshing with the fourth gear 7, and the eighth gear 15 The ninth gear 17 and the tenth gear 18, which are fixed to the output shaft 19, and the seventh gear 12
An eleventh gear 20 that meshes with the eleventh gear and an intermediate shaft common to the eleventh gear 20
12th fixed on 22 and meshed with 10th gear 18
Gear 21, a first clutch device 5 for connecting the second gear 3 and the fourth gear 7, and a second clutch for connecting the fourth gear 7 and the fifth gear 11. Device 9 and third
The third clutch device 6 capable of connecting the fourth gear 6 and the sixth gear 8, the fourth clutch device 10 capable of connecting the sixth gear 8 and the seventh gear 12, and the eighth clutch device 8. Gears 15 and 9
A fifth clutch device 16 which can be connected to the gear 17 of the third gear device 6, and a fourth gear device 7 directly connected to the first clutch device 5 and the second clutch device 9 and a third clutch device 6 And the sixth gear 8 directly coupled to the fourth clutch device 10 is adapted to mesh with the eighth gear 15 directly coupled to the fifth clutch device 16 so that two gears are thereby provided. The gears connected to the clutch device directly mesh with the gears connected to the other clutch devices to reduce the number of gears and shafts and to make the space of the transmission gear device compact.
第１図は本発明による前後進３速変速歯車装置のスケル
トン図、第２図は本発明による前後進４速変速歯車装置
のスケルトン図、第３図は従来の平行軸方式歯車装置を
示すスケルトン図、第４図は他の従来の平行軸方式歯車
装置を示すスケルトン図である。 １……入力軸 2,3,4,7,8,11,12,15,17,18,20,21……歯車 5,6,9,10,16……クラツチ 13,14……中間軸、19……中心軸兼出力軸FIG. 1 is a skeleton diagram of a forward / reverse 3 speed transmission gear device according to the present invention, FIG. 2 is a skeleton diagram of a forward / reverse 4 speed transmission gear device according to the present invention, and FIG. 3 is a skeleton showing a conventional parallel shaft type gear device. FIG. 4 and FIG. 4 are skeleton diagrams showing another conventional parallel shaft type gear device. 1 …… Input shaft 2,3,4,7,8,11,12,15,17,18,20,21 …… Gear 5,6,9,10,16 …… Crutch 13,14 …… Intermediate shaft , 19 ... Center axis and output axis
Claims (1)
入力歯車２に噛合う第２の歯車３及び第３の歯車４と、
第２の歯車３と共通の中間軸13に固着されている第４の
歯車７と同軸上に回転可能に保持された第５の歯車11
と、第３の歯車４と共通の中間軸14に固着されている第
６の歯車８と同軸上に回転可能に保持された第７の歯車
12と、第４の歯車７に噛合う第８の歯車15と、第８の歯
車15と共通の出力軸19に固着されている第９の歯車17お
よび第10の歯車18と、第７の歯車12と噛合う第11の歯車
20と、第11の歯車20と共通の中間軸22上に固定され、且
つ第10の歯車18と噛合っている第12の歯車21と、第２の
歯車３と第４の歯車７とを接続可能とする第１のクラツ
チ装置５と、第４の歯車７と第５の歯車11とを接続可能
とする第２のクラツチ装置９と、第３の歯車４と第６の
歯車８とを接続可能とする第３のクラツチ装置６と、第
６の歯車８と第７の歯車12とを接続可能とする第４のク
ラツチ装置10と、第８の歯車15と第９の歯車17とを接続
可能とする第５のクラツチ装置16とからなり、第１のク
ラツチ装置５及び第２のクラツチ装置９に直接結合され
た第４の歯車７と、第３のクラツチ装置６及び第４のク
ラツチ装置10に直接結合された第６の歯車８とが、とも
に第５のクラツチ装置16に直接結合された第８の歯車15
に噛合うようにしたことを特徴とする変速歯車装置。1. An input gear 2 driven by an input shaft 1,
A second gear 3 and a third gear 4 that mesh with the input gear 2;
A fifth gear 11 rotatably held coaxially with a fourth gear 7 fixed to an intermediate shaft 13 common to the second gear 3.
And a seventh gear which is rotatably held coaxially with a sixth gear 8 fixed to an intermediate shaft 14 common to the third gear 4.
12, an eighth gear 15 that meshes with the fourth gear 7, a ninth gear 17 and a tenth gear 18 that are fixed to an output shaft 19 common to the eighth gear 15, and a seventh gear 15. Eleventh gear meshing with gear 12
20, a twelfth gear 21 fixed on an intermediate shaft 22 common to the eleventh gear 20 and meshing with the tenth gear 18, a second gear 3 and a fourth gear 7. The first clutch device 5 that can be connected, the second clutch device 9 that can connect the fourth gear 7 and the fifth gear 11, and the third gear 4 and the sixth gear 8 The third clutch device 6 which can be connected, the fourth clutch device 10 which can connect the sixth gear 8 and the seventh gear 12, the eighth gear 15 and the ninth gear 17 A fourth gear 7, which comprises a fifth clutch device 16 which can be connected and is directly connected to the first clutch device 5 and the second clutch device 9, and a third clutch device 6 and a fourth clutch device 7. A sixth gear 8 directly connected to the device 10 and an eighth gear 15 both directly connected to the fifth clutch device 16
A speed change gear device characterized in that it meshes with a gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013557A JP2680708B2 (en) | 1990-01-25 | 1990-01-25 | Transmission gearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013557A JP2680708B2 (en) | 1990-01-25 | 1990-01-25 | Transmission gearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03219152A JPH03219152A (en) | 1991-09-26 |
| JP2680708B2 true JP2680708B2 (en) | 1997-11-19 |
Family
ID=11836482
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2013557A Expired - Lifetime JP2680708B2 (en) | 1990-01-25 | 1990-01-25 | Transmission gearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2680708B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008114547A1 (en) * | 2007-03-20 | 2008-09-25 | Komatsu Ltd. | Transmission for industrial vehicle |
| CN101627224B (en) * | 2007-03-20 | 2012-05-30 | 株式会社小松制作所 | Transmission for industrial vehicle |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2565596Y2 (en) * | 1991-10-15 | 1998-03-18 | 新潟コンバーター株式会社 | Transmission for diesel vehicles |
| FR2862363B1 (en) * | 2003-11-18 | 2007-01-26 | Antonov Automotive Europ | MULTI-REPORTING TRANSMISSION DEVICE, IN PARTICULAR FOR THE AUTOMOBILE |
| JP5095849B1 (en) * | 2011-08-23 | 2012-12-12 | 株式会社小松製作所 | Work vehicle transmission |
| EP4325085A1 (en) * | 2022-08-18 | 2024-02-21 | Volvo Truck Corporation | A transmission for a vehicle |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1426718A (en) * | 1972-03-17 | 1976-03-03 | Turner Mfg C Oltd | Gear boxes |
| JPS61189346A (en) * | 1985-02-18 | 1986-08-23 | Hino Motors Ltd | Speed changing gears |
-
1990
- 1990-01-25 JP JP2013557A patent/JP2680708B2/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008114547A1 (en) * | 2007-03-20 | 2008-09-25 | Komatsu Ltd. | Transmission for industrial vehicle |
| JP2008232246A (en) * | 2007-03-20 | 2008-10-02 | Komatsu Ltd | Transmission for industrial vehicle |
| CN101622472B (en) * | 2007-03-20 | 2012-05-09 | 株式会社小松制作所 | Transmission for industrial vehicle |
| CN101627224B (en) * | 2007-03-20 | 2012-05-30 | 株式会社小松制作所 | Transmission for industrial vehicle |
| US8356528B2 (en) | 2007-03-20 | 2013-01-22 | Komatsu Ltd. | Transmission for industrial vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03219152A (en) | 1991-09-26 |
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