JPH03219152A - Speed change gears - Google Patents
Speed change gearsInfo
- Publication number
- JPH03219152A JPH03219152A JP2013557A JP1355790A JPH03219152A JP H03219152 A JPH03219152 A JP H03219152A JP 2013557 A JP2013557 A JP 2013557A JP 1355790 A JP1355790 A JP 1355790A JP H03219152 A JPH03219152 A JP H03219152A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- gears
- shaft
- clutch
- output 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 description 13
- 238000010586 diagram Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 3
- BQCADISMDOOEFD-UHFFFAOYSA-N Silver Chemical compound [Ag] BQCADISMDOOEFD-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 229910052709 silver Inorganic materials 0.000 description 2
- 239000004332 silver Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 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
- F16H3/02—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)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、フォ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。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a power transmission device that is applied to a transmission device of an industrial vehicle such as a forklift or a construction machine such as a tire roller.
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。Figures 3 and 4 show skeleton diagrams of a conventional three-speed forward and three-speed reverse 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、本装置はクラッチ機構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、トランスファ部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 Patent Publication No. 47-21649, and the total length of this device is determined by three clutch mechanisms, and it is elongated in the front-rear direction. Furthermore, in order to make the input and output axes coaxial, it must be done in the transfer section a, which increases the number of gears and shafts used.
＠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ッチ機構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ァ部分ａが必要である
。Figure @4 is described in Japanese Patent Publication No. 58-42384, and although the entire length of this device can be accommodated within the width of two clutch mechanisms, the input/output A transfer part a is necessary to make the shafts coaxial.
（１１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、人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（、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（なり、搭載スば一ス及び重量の増
大等の問題点を生ずる。(11 In construction machinery such as tire rollers, the human power shaft and output shaft of the gear transmission are on the same axis due to the vehicle layout,
In addition, the overall length of the transmission is required to be short, but parallel shaft type gear transmissions generally have different input and output shaft positions (but if they are arranged on the same axis, the This results in 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
ァケースａ、第４図トランスミッションケース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) In many cases, a common transmission is used for different vehicles and only the output shaft position is changed, but even in this case, according to the prior art, the basic cases (transfer case a, It is necessary to change up to the transmission case b) in Figure 4, which poses problems such as a reduction in the rate of commonality.
本発明は、上記ｆｉｌ 、 （２１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。An object of the present invention is to provide a compact transmission gear device in which the input and output shafts are coaxial, which simultaneously solves the problems of fil and (21) above.
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にギヤ、クラッチ装置５゜７ 、９
、１１及び６ 、８ 、１０ 、１２を設け、これ等の
ギヤ、クラッ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６出力軸１９を中心
軸とするギヤ、クラッチ装置１５゜１６ 、１７ 、１
８を設け、ギヤ７とギヤ１５、ギヤ１１とギヤ１７を噛
合わせる。中間軸乙にギヤ加、２１を設け、ギヤ１２と
ギヤ加、ギヤ１８とギヤ２１を噛合わせる。As shown in FIG. 1, the intermediate shaft 13.14 of the gear 3.4 meshing with the input shaft gear 2 has gears and clutch devices 5.7, 9.
, 11, 6, 8, 10, and 12, and the output shaft 19 is arranged on the same axis of the input shaft 1 to avoid interference with these gears and clutch devices.6 The output shaft 19 is the central axis. gear, clutch device 15゜16, 17, 1
8 is provided, and gear 7 and gear 15 and gear 11 and gear 17 are meshed with each other. A gear addition 21 is provided on the intermediate shaft B, and the gear 12 and the gear addition, and the gear 18 and the gear 21 are meshed.
入力軸１と出力軸１９とは同軸線上に配置され、且つ前
後方同長が短縮される。出力軸１９には、ギヤ１５とク
ラッチ１６、ギヤ１１ 、１７、及びギヤ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 on the same axis, and the same length in the front and rear directions is shortened. The output shaft 19 includes a gear 15, a clutch 16, gears 11 and 17, and gears 21 and 18.
The multi-speed geared rotational force is transmitted through the gearbox.
中間軸ｎ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 n, the distance between the input and output shafts can be changed without adding any special equipment, and the system can be easily applied to multiple types of vehicles.
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 an embodiment of a three-speed forward/reverse gear, and FIG. 2 is a skeleton diagram of an embodiment of a four-speed forward/reverse gear.
第１図に１６いて、図示せざる原動機からの動力は、ト
ルクコンバータがを経て入力軸ｌ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及びクラッチ装置５と
９．６と１０が固着されている。At 16 in FIG. 1, power from a prime mover (not shown) is transmitted to the input shaft l via a torque converter. A gear 2 is fixed on the input shaft 1, and an intermediate shaft 13,
It meshes with gears 3 and 4 on top of 14. intermediate shaft 13,
Gears 7, 8 and clutch devices 5, 9, 6, and 10 are fixed to the central portion of 14.
クラッチ装置は、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ッチを
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１
９上には、同様なりラッチ装置と、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ｎには、歯車加及
び２１が固着されており、歯車加は、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。The clutch device consists of a plurality of friction plates, mating plates, and pistons, and the pistons are actuated by hydraulic pressure to press the multi-disc clutch, and gears 3, 4, 11, and 12 are rotatably held on respective intermediate shafts. It is of a known type that is connected through a spline portion at one end. Output shaft 1
9 has a similar latch device, a gear 15 having a spline at one end and rotatably held on the shaft, and a gear 17.
, 18 are fixed. A gear wheel 21 is fixed to the intermediate shaft n, the gear wheel meshes with the gear 12 on the intermediate shaft 14, and the gear 21 meshes with the gear 18 on the output shaft 19.
meshes with
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１
３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 is the gear 8 on the intermediate shaft 14.
and meshes with the gear 15 on the output shaft 19, and the intermediate shaft 1
The gear 11 on 3 meshes with the gear 17 on the output shaft 19.
次に本装置の作用を説明する。Next, the operation of this device will be explained.
前記のクラッチ装置５．６のいずれか一方、及びクラッ
チ装置９ 、１０ 、１６の内−つ、合計２つのクラッ
チ装置を保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、クラッチ装置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 bringing a total of two clutch devices, one of the clutch devices 5 and 6 and one of the clutch devices 9, 10, and 16, into the engaged state, the gear ratios of the three forward speeds and the three reverse speeds can be changed. Examples of combinations of each member are shown in Table 1. Note that the clutch devices 5 and 6 are used for selecting forward and backward movement, but they can be reversed if necessary.
（注：数字は部材符号）
第 １ 表
（前進１速） クラッチ装ｆｔ５及び１０を作用させる
と、入力軸１の動力は、歯車２−歯車３−クラッチ装置
５−歯車７−歯車８−クラッチ装置１〇−歯車１２−歯
車ｍ−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。(Note: Numbers are component codes) Table 1 (1st forward speed) When clutch devices ft5 and 10 are activated, the power of input shaft 1 is generated from gear 2 - gear 3 - clutch device 5 - gear 7 - gear 8 - clutch It is transmitted to the output shaft 19 via the device 10-gear 12-gear m-gear 21-gear 18, and rotates in the same direction as the input shaft 1.
（前進２速） クラッチ装置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−クラッチ装置５−
クラッチ装置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。(Forward 2nd speed) When clutch devices 5 and 9 are activated,
The power of the input shaft 1 is transmitted through the gear 2 - gear 3 - clutch device 5 -
It is transmitted to the output shaft 19 via the clutch device 9, gear 11, and gear 17, and rotates in the same direction as the input shaft 1.
（前進３速） クラッチ装置５及び１６を作用させると
、入力軸ｌの動力は、歯車２−歯車３−歯］Ｌ７−歯車
１５−クラッチ装置１６を介して、出力軸１９へ伝達さ
才ｌ、入力軸１と同方向に回転する。(3rd forward speed) When the clutch devices 5 and 16 are activated, the power of the input shaft 1 is transmitted to the output shaft 19 via gear 2 - gear 3 - teeth L7 - gear 15 - clutch device 16. , rotates in the same direction as the input shaft 1.
（後進１速） クラッチ装置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−クラッチ装置６
−クラッチ装置１〇−歯車１２−歯車ｍ−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。(Reverse 1st speed) When the clutch devices 6 and 10 are activated, the power of the input shaft 1 is transferred from the gear 2 to the gear 4 to the clutch device 6.
- Clutch device 10 - Gear 12 - Gear m - Gear 21 - Transmitted to the output shaft 19 via the gear 18, and rotates in the opposite direction to the input shaft 1.
（後進２速） クラッチ装置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−クラッチ装＆６−
歯車８−歯車７−クラッチ装［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。(Reverse 2nd speed) When clutch devices 6 and 9 are activated,
The power of input shaft 1 is transmitted through gear 2 - gear 4 - clutch equipment & 6 -
Gear 8-Gear 7-Clutch equipment [9-Gear 11-Gear 17
is transmitted to the output shaft 19 via the input shaft 1, and rotates in the opposite direction to the input shaft 1.
（後進３速） クラッチ装置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−クラッチ装置６
−歯車８−歯車７−歯車１５−クラッチ装置１６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。(3rd reverse speed) When the clutch devices 6 and 16 are activated, the power of the input shaft 1 is transferred from the gear 2 to the gear 4 to the clutch device 6.
- Gear 8 - Gear 7 - Gear 15 - It is transmitted to the output shaft 19 via the 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/reverse four-speed transmission shown in FIG. 2 will be explained.
第２図の如く、中間軸ｎ上にクラッチ買置乙及び歯車屑
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, a transmission with four forward speeds and four reverse speeds can be easily constructed by adding a clutch and gear scraps to the intermediate shaft n.
第２表て各部材の組合せの例を示す。Table 2 shows examples of combinations of each member.
第 ２ 表
本例では、中間軸ｎ−出力軸１９は、歯車２１と歯車１
８によって接続されているが歯車銀を歯車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。Table 2 In this example, the intermediate shaft n-output shaft 19 has gear 21 and gear 1.
8, the silver gear may be meshed with the gear 17 or the gear 18, or the same effect can be obtained by meshing the gear 21 with the gear 17.
さらにクラッチ装置９ 、１０ 、１６ 、 Ｚ３の内
任意の数を減することで変速段数を少なくすることが可
能であるａ％に前進２段、後進２段の場合、第２図のク
ラッチ装置１０ 、２３を除くことで歯車１２ 、１８
゜２１ 、２２ 、２４、中間軸ｎをな（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。Furthermore, it is possible to reduce the number of gears by reducing any number of clutch devices 9, 10, 16, and Z3.In the case of two forward speeds and two reverse speeds in a%, the clutch device 10 in FIG. , 23, gears 12, 18
゜21, 22, 24, the intermediate shaft n can be formed, and the number of parts can be significantly reduced, leading to weight reduction and manufacturing cost reduction.
第１図、第２図とも出力軸は、軸１９であるが、これを
中間軸ｎから出力しても、同じ変速段数、等段間比のト
ランスミッションとなる。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。The output shaft in both FIGS. 1 and 2 is the shaft 19, but even if it is output from the intermediate shaft n, the transmission will have the same number of gears and the same gear ratio. Therefore, in advance, the axis 19,
By aligning the positions of 22 with the respective output shaft positions, it can be mounted on a plurality of vehicles with 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１
８と、第７の歯車１２と噛合う第１１の歯車銀と、第１
１の歯車加と共通の中間軸ｎ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クラッチ
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のクラッチ装置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のクラッチ装置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
クラッチ装置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のクラッチ装置１６とからなり
、第４の歯車７と＠６の歯車８及び第５の歯車１１と第
９の歯車１７がそれぞれ噛合うようにしたことにより、
次の効果を有する。The speed change 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 is rotatably held coaxially with the fourth gear 7 fixed to the same axis, and coaxial with the sixth gear 8 fixed to the intermediate shaft 14 common to the third gear 4. A seventh gear 12 rotatably held above, an eighth gear 15 meshing with the fourth gear 7, and an output shaft 19 common to the eighth gear 15.
The ninth gear 17 and the tenth gear 1 are fixed to
8, an eleventh gear silver meshing with the seventh gear 12, and a first gear
1 fixed on the intermediate shaft n common with the 10th gear
a twelfth gear 21 meshing with a gear 18; a first clutch device 5 capable of connecting a second gear 3 and a fourth gear 7; a second clutch device 9 that can connect the third gear 4 and the sixth gear 8; a third clutch device 6 that can connect the third gear 4 and the sixth gear 8; and a sixth gear 8 and the seventh gear 12. a fourth clutch device 10 capable of connecting the eighth gear 15 and the ninth gear 17;
The fourth gear 7 and the gear 8 of @6 are made to mesh with each other, and the fifth gear 11 and the ninth gear 17 are made to mesh with each other.
It has the following effects.
（１）主要な部品（ケース、ギア、シャフト、クラッチ
装置等）を変えることなく、入出力軸間距離の異なる２
機種以上の歯車変速装置を構成することが出来るため、
部品及び型治具が共通化出来て、低コスト化が可能であ
る。(1) Two different distances between input and output shafts without changing the main parts (case, gear, shaft, clutch device, etc.)
Because it is possible to configure gear transmissions of more than one model,
Parts and mold jigs can be shared, making it possible to reduce costs.
（２）入出力軸間距離を非常に短く（同軸線も可）して
も、全長はクラッチ装置２個によって決まる長さであり
、コンパクト化、軽量化が図れる。(2) Even if the distance between the input and output shafts is very short (coaxial lines are also possible), the overall length is determined by the two clutch devices, making it compact and lightweight.
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FIG. 1 is a skeleton diagram of a 3-speed forward/reverse gearing device according to the present invention, FIG. 2 is a skeleton diagram of a 4-speed forward/reverse gearing device according to the present invention, and FIG. 3 is a skeleton diagram showing a conventional parallel shaft type gearing device. FIG. 4 is a skeleton diagram showing another conventional parallel shaft type gear device. 1...Input shaft
Claims (1)
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クラッチ装置（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のクラッチ装置（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のクラッチ
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のクラッチ装置（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のクラッチ装置（１６）とからなり、第４の歯
車（７）と第６の歯車（８）及び第５の歯車（１１）と
第９の歯車（１７）がそれぞれ噛合うことを特徴とする
変速歯車装置。Input gear (2) driven by input shaft (1), second gear (3) and third gear (4) that mesh with input gear (2), and common to second gear (3) intermediate shaft (13)
A fifth gear (11) is rotatably held coaxially with the fourth gear (7) fixed to the third gear (4).
A sixth gear (
The seventh gear (12) is rotatably held coaxially with the seventh gear (12).
), an eighth gear (15) meshing with the fourth gear (7), a ninth gear (17) fixed to a common output shaft (19) with the eighth gear (15), and 10th gear (18
) and an eleventh gear (20) that meshes with the seventh gear (12).
), a twelfth gear (21) fixed on a common intermediate shaft (22) with the eleventh gear (20) and meshing with the tenth gear (18), and a second gear ( 3) and a fourth gear (7), and a second clutch that enables a connection between the fourth gear (7) and the fifth gear (11). Device (9) and third gear (4)
and a sixth gear (8), a third clutch device (6) that can connect the sixth gear (8), and the sixth gear (8) and the seventh gear (12).
and a fifth clutch device (16) that enables connection between the eighth gear (15) and the ninth gear (17). A speed change gear device characterized in that a fourth gear (7) and a sixth gear (8) mesh with each other, and a fifth gear (11) and a ninth gear (17) mesh with each other.
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 true JPH03219152A (en) | 1991-09-26 |
| JP2680708B2 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 (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0534343U (en) * | 1991-10-15 | 1993-05-07 | 新潟コンバーター株式会社 | Transmission for Diesel vehicle |
| US7537539B2 (en) * | 2003-11-18 | 2009-05-26 | Antonov Automotive Technologies B.V. | Multiple gear ratio transmission device |
| WO2013027446A1 (en) * | 2011-08-23 | 2013-02-28 | 株式会社小松製作所 | Transmission for working vehicle |
| EP4325085A1 (en) * | 2022-08-18 | 2024-02-21 | Volvo Truck Corporation | A transmission for a vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5276272B2 (en) * | 2007-03-20 | 2013-08-28 | 株式会社小松製作所 | Industrial vehicle transmission |
| JP5091514B2 (en) * | 2007-03-20 | 2012-12-05 | 株式会社小松製作所 | Industrial vehicle transmission |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4912267A (en) * | 1972-03-17 | 1974-02-02 | ||
| 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
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4912267A (en) * | 1972-03-17 | 1974-02-02 | ||
| JPS61189346A (en) * | 1985-02-18 | 1986-08-23 | Hino Motors Ltd | Speed changing gears |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0534343U (en) * | 1991-10-15 | 1993-05-07 | 新潟コンバーター株式会社 | Transmission for Diesel vehicle |
| US7537539B2 (en) * | 2003-11-18 | 2009-05-26 | Antonov Automotive Technologies B.V. | Multiple gear ratio transmission device |
| WO2013027446A1 (en) * | 2011-08-23 | 2013-02-28 | 株式会社小松製作所 | Transmission for working vehicle |
| JP2013044368A (en) * | 2011-08-23 | 2013-03-04 | Komatsu Ltd | Transmission for working vehicle |
| US8499657B2 (en) | 2011-08-23 | 2013-08-06 | Komatsu Ltd. | Transmission for work vehicle |
| GB2497000B (en) * | 2011-08-23 | 2014-05-28 | Komatsu Mfg Co Ltd | Transmission for working vehicle |
| EP4325085A1 (en) * | 2022-08-18 | 2024-02-21 | Volvo Truck Corporation | A transmission for a vehicle |
| US12234896B2 (en) | 2022-08-18 | 2025-02-25 | Volvo Truck Corporation | Transmission for a vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2680708B2 (en) | 1997-11-19 |
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