JPS6224055A - Speed change gear for tractor - Google Patents

Speed change gear for tractor

Info

Publication number
JPS6224055A
JPS6224055A JP60164278A JP16427885A JPS6224055A JP S6224055 A JPS6224055 A JP S6224055A JP 60164278 A JP60164278 A JP 60164278A JP 16427885 A JP16427885 A JP 16427885A JP S6224055 A JPS6224055 A JP S6224055A
Authority
JP
Japan
Prior art keywords
gear
shaft
clutch
gears
clutches
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
JP60164278A
Other languages
Japanese (ja)
Other versions
JPH0545813B2 (en
Inventor
Hirokazu Enomoto
博計 榎本
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.)
Fuji Tool and Die Co Ltd
Original Assignee
Fuji Tool and Die Co 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 Fuji Tool and Die Co Ltd filed Critical Fuji Tool and Die Co Ltd
Priority to JP60164278A priority Critical patent/JPS6224055A/en
Publication of JPS6224055A publication Critical patent/JPS6224055A/en
Publication of JPH0545813B2 publication Critical patent/JPH0545813B2/ja
Granted 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0936—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only two idle gears and one gear fixed to the countershaft

Abstract

PURPOSE:To reduce the number of parts and to decrease the gear in size and weight by holding down the number of clutches, shafts and gear trains to be used to the minimum required. CONSTITUTION:The first to third clutches 11-13 are connected to the first shaft 1. A gear (h) is engaged with a gear (d) integral with a gear (g), and the gears (g), (h) are connected to the second shaft 2 through the fifth clutch 15. Further, gears (k), (l) are engaged with the gear (h). A gear (q) is mounted on the fifth shaft 5 in such a manner as to engage with a gear (m) and freely rotate relatively therewith, and the gear (q) is connected to the fifth shaft 5 through the eighth clutch 18. A gear (r) is mounted on the fifth shaft 5 in such a manner as to engage with a gear (p) and freely rotate relatively therewith, and the gear (r) is connected to the fifth shaft 5 through a clutch 19. This arrangement can reduce the number of parts and decrease the gear in size and weight.

Description

【発明の詳細な説明】 （産業上の利用分野） 本発明は、液圧クラッチの選択切換で前進１６段、後進
４段の変速切換を行なうトラクタ用変速装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a tractor transmission device that performs gear shifting of 16 forward gears and 4 reverse gears by selectively switching a hydraulic clutch.

（従来技術） 従来、液圧クラッチによるギア比の選択で前進１６段、
後進４段の切換機能をもつトラクタ用変速装置としては
、例えば第４図のものが知られている。(Prior art) Conventionally, 16 forward gears were selected by selecting the gear ratio using a hydraulic clutch.
As a tractor transmission device having a switching function of four reverse gears, for example, the one shown in FIG. 4 is known.

第４図において、（Ａ）はエンジンであり、エンジン（
Ａ）からの動力回転をまず２段の切換機能をもった変速
は（Ｂ）に伝え、更に８段の切換機能をもった変速機（
ｃ）に伝え、最終的にチェーン（Ｄ）によって車輪側の
ドライブシャツ１へ（Ｅ）に動力を伝達するようにして
いる。In Fig. 4, (A) is an engine, and the engine (
The power rotation from A) is first transmitted to the transmission with a two-speed switching function (B), and then the transmission with an eight-speed switching function (
c), and finally the power is transmitted to the drive shirt 1 on the wheel side (E) by the chain (D).

即ち、２段の切換機能をもった変速機（Ｂ）と８段の切
換機能をもった変速機（ｃ）との組合わせで前進１６段
、後進４段の変速機能を実現するようにしている。That is, by combining a transmission (B) with a two-speed switching function and a transmission (c) with an eight-speed switching function, a transmission function of 16 forward speeds and 4 reverse speeds is realized. There is.

（発明が解決しようとする問題点） しかしながら、このような従来の変速装置にあっては、
２段切換の変速機と８段切換の変速機を組合わせている
ことから装置が大型化し、また全体として使用する液圧
クラッチの数か多くなり、更に変速機が直列的に配首さ
れることからチェーンにより車輪側のドライブシャフト
への動力伝達を行なわなければならないという問題があ
った。(Problems to be solved by the invention) However, in such a conventional transmission device,
Because it combines a two-speed transmission and an eight-speed transmission, the device becomes larger, the number of hydraulic clutches used increases overall, and the transmissions are arranged in series. Therefore, there was a problem in that power had to be transmitted to the drive shaft on the wheel side using a chain.

（問題点を解決するための手段） 本発明は、このような従来の問題点に°鑑みてなされた
もので、最小のクラッチ数および軸数をもち、且つギア
トレイン自体もコンパクトな前進１６段、後進４段の変
速機能をもつトラクタ用変速装置を提供することを目的
とする。(Means for Solving the Problems) The present invention has been made in view of these conventional problems, and has a minimum number of clutches and shafts, and a compact gear train itself with 16 forward speeds. , an object of the present invention is to provide a tractor transmission having a four-speed reverse gear shifting function.

この目的を達成するため本発明にあっては、第１図に示
すように、５軸、９クラッチでなるギアトレインを備え
た装置を実現したものでおる。In order to achieve this object, the present invention realizes a device equipped with a gear train consisting of five axes and nine clutches, as shown in FIG.

（実施例） 第１図は本発明の実施例をシンボリックに示した説明図
で必る。(Embodiment) FIG. 1 is an explanatory diagram symbolically showing an embodiment of the present invention.

まず構成を説明すると、駆動軸はエンジンからの動力回
転が入力する第１クラッチパツク（１０）の第１軸（１
）と、第２クラッチパツク（２０）の第２軸（２）と、
カウンタ部（３０）の第３軸（３）と、第３クラッチパ
ツク（４０）の第４軸（４）と、動力回転を外部に取り
出す第４クラッチパツク（５０）の第５軸（５）とで成
る５本の軸を使用している。First, to explain the configuration, the drive shaft is the first shaft (1
), the second shaft (2) of the second clutch pack (20),
The third shaft (3) of the counter part (30), the fourth shaft (4) of the third clutch pack (40), and the fifth shaft (5) of the fourth clutch pack (50) that extracts the power rotation to the outside. It uses five axes consisting of.

一方、ギア比を前進１６段、後進４段に切換えるための
液圧クラッチとしては、第１クラッチ（１１〉〜第９ク
ラッチ（１９）の９個の液圧クラッチを使用している。On the other hand, nine hydraulic clutches, the first clutch (11> to the ninth clutch (19)), are used to switch the gear ratio to 16 forward gears and 4 reverse gears.

次に各クラッチパック及びカウンタ部に分けてギアトレ
イン及びクラッチ機構を説明すると、次の様になる。Next, the gear train and clutch mechanism will be explained separately for each clutch pack and counter section as follows.

まずエンジンからの動力回転が入力される第１軸（１〉
を備えた第１クラツヂパツク（１０）においては、第１
軸（１）にギア（ａ　）を直結すると共に第１．第２及
び第３のクラッチ（１１）。First, the first shaft (1) receives the power rotation from the engine.
In the first clutch pack (10) equipped with
A gear (a) is directly connected to the shaft (1), and the first. Second and third clutches (11).

（１２）、（１３）で第１軸（１）に連結される３つの
ギア（ｂ　＞、　　（ｃ　＞、　　（ｄ　）を備えてい
る。It is equipped with three gears (b>, (c>, (d)) connected to the first shaft (1) at (12) and (13).

ここでクラッチ（１１）は後進用のクラッチである。Here, the clutch (11) is a clutch for reverse movement.

次に第２クラッチパツク（２０＞においては、第１クラ
ッチパツク（１０）のギア（ａ）、、（ｃ）、（ｄ）の
それぞれに噛み合ったギア（ｅ）。Next, in the second clutch pack (20>), the gear (e) meshes with each of the gears (a), (c), and (d) of the first clutch pack (10).

（ｇ）ｌｈ）を有し、更に次段へ連結するためのギア（
ｆ　）を備えている。このギアトレインのうち、ギア（
ａ　）に噛み合うギア（ｅ　）は第２軸（２）に直結さ
れており、第１軸（１）の動力回転を第２軸（２）に伝
えている。またギア（ｆ〉。(g) lh), and a gear (
f). Of this gear train, the gear (
The gear (e) that meshes with the gear a) is directly connected to the second shaft (2) and transmits the power rotation of the first shaft (1) to the second shaft (2). Also gear (f).

（ｑ）、（ｈ）のそれぞれは第２軸（２）に相対回転自
在に装置されている。ギア（ｆ　）はクラッチ（１４）
と一体に形成されており、クラッチ（１４）に作動液圧
を供給すると、第２軸（２）に連結されて動力回転を次
段に連結する。またギア（ｐ）、（ｈ）のそれぞれは、
第５クラッチ（１５）と一体に形成されており、作動液
圧の供給により第２軸（２）に連結される。この第２ク
ラッチパツク（２０）に設けた第２軸（２）の他端には
オイルポンプ（７０）が連結されており、第２軸（２）
はギア（ｅ　）と（ａ　＞の噛合いにより常時第１軸（
１）の動力回転を受けることから、オイルポンプ（７０
）の駆動軸として利用される。Each of (q) and (h) is relatively rotatably mounted on the second shaft (2). Gear (f) is clutch (14)
When hydraulic pressure is supplied to the clutch (14), it is connected to the second shaft (2) to connect the power rotation to the next stage. Also, each of the gears (p) and (h) is
It is formed integrally with the fifth clutch (15), and is connected to the second shaft (2) by supply of hydraulic pressure. An oil pump (70) is connected to the other end of the second shaft (2) provided on the second clutch pack (20), and the second shaft (2)
is always the first shaft (
1), the oil pump (70
) is used as a drive shaft.

次にカウンタ部（３０）において、第３＠ＩＩ（３）に
はギア（ｉ　＞、　　（ｊ　＞、　　（ｋ　＞、　　（
１１，）が固着されており、ギア（ｉ　）は前段のギア
（ｆ　”）と噛合うと共に破線で示す様に第１クラッチ
パツク（１０）のギア（ｂ　）とも噛合っており、第１
クラッチ（１１）の作動でギア（ｂ）、（ｉ）を介して
第３駆動軸（３）に動力回転を伝達することで後進を選
択する。またギア（ｉ　）は前段のギア（ｈ　）に噛合
い、残りのギア（ｊ＞、（ｍ＞は次段のギアに噛合う。Next, in the counter section (30), the gear (i >, (j >, (k >, (
11,) is fixed, and the gear (i) meshes with the preceding gear (f'') and also meshes with the gear (b) of the first clutch pack (10) as shown by the broken line.
Reverse travel is selected by operating the clutch (11) to transmit power rotation to the third drive shaft (3) via the gears (b) and (i). Further, the gear (i) meshes with the gear (h) at the previous stage, and the remaining gears (j>, (m>) mesh with the gears at the next stage.

更に第３クラッチパツク（４０）においては、第４軸（
４）に固着されたギア（ｍ）、（ｐ）を有すると共に相
対回転自在に装着したギア（ｎ　）と（Ｏ）を有し、ギ
ア（ｎ　）は第６クラッチ（１６）と一体に形成され、
且つ前段のギア（ｊ　＞に噛合い、第６クラッチ（１６
）の作動で第４軸（４）に連結される。またギア（Ｏ）
は第７クラツヂ（１７）と一体に形成され、且つ前段の
ギア（止）と噛合っており、第７クラッチ（１７）の作
動で第４軸（４）に連結される。更にギア（ｍ　）、（
ｐ）のそれぞれは次段に動力を伝達するために設ける。Furthermore, in the third clutch pack (40), the fourth shaft (
4) has gears (m) and (p) fixed to the clutch, and also has gears (n) and (O) attached so as to be relatively rotatable, and the gear (n) is formed integrally with the sixth clutch (16). is,
In addition, it meshes with the previous gear (j >, and the sixth clutch (16
) is connected to the fourth shaft (4). Also gear (O)
is formed integrally with the seventh clutch (17) and meshes with the preceding gear (stop), and is connected to the fourth shaft (4) by the operation of the seventh clutch (17). Furthermore, gear (m), (
Each of p) is provided to transmit power to the next stage.

最終段となる第４クラッチパツク（５０）においては、
出力軸となる第５軸（５）に相対回転自在にギア（ｑ）
ｌｒ）を装置しており、ギア（ｑ　）は第８クラッチ（
１８）と一体に形成され、且つ前段のギア（ｍ　＞に噛
合い、またギア（ｒ　）は第９クラッチ（１つ）と一体
に形成され、且つ前段のギア（ｐ　＞に噛合っている。In the fourth clutch pack (50), which is the final stage,
A gear (q) is attached to the fifth shaft (5), which is the output shaft, so that it can rotate freely.
lr), and the gear (q) is the eighth clutch (
The gear (r) is formed integrally with the ninth clutch (one) and meshes with the preceding gear (m>), and is formed integrally with the ninth clutch (one) and meshes with the preceding gear (p>). .

尚、第１図において第１クラッチ（１１）〜第９クラッ
チ（１つ）のそれぞれは公知の液圧クラッチ装置であり
、複数のクラッチを同じ軸に設けているが、同時に２以
上のクラッチが作動されることはなく、必ず単一のクラ
ッチのみが作動される様になる。In Fig. 1, each of the first clutch (11) to the ninth clutch (one) is a known hydraulic clutch device, and multiple clutches are provided on the same shaft, but two or more clutches may be connected at the same time. It is never activated, and only a single clutch is always activated.

次に第１図の実施例の作用を説明する。Next, the operation of the embodiment shown in FIG. 1 will be explained.

第２図は第１図の実施例による前進１６段、後進４段の
切換選択におけるギア比とクラッチ選択状態を一覧表で
示す。尚、クラッチ選択の状態は、クラッチに一体に形
成されたギアの符号で表わしており、例えば第１段を見
るとギア（ｃ）、（ｎ＞、（ｑ）のそれぞれにクラッチ
作動を示す丸印があることから、ギア（ｃ）を備えた第
２クラッチ（１２）　、ギア（ｎ　）を協えた第６クラ
ッチ（１６）及びギア（ｑ　）を備えた第８クラッチ（
１８）のそれぞれが作動して各ギアを軸に連結している
ことになる。FIG. 2 shows a list of gear ratios and clutch selection states in the switching selection of 16 forward speeds and 4 reverse speeds according to the embodiment shown in FIG. The state of clutch selection is indicated by the symbol of the gear integrally formed with the clutch. For example, when looking at the first stage, there is a circle indicating clutch operation for gears (c), (n>, and (q)). The marks indicate that the second clutch (12) is equipped with a gear (c), the sixth clutch (16) is equipped with a gear (n), and the eighth clutch (16) is equipped with a gear (q).
18) are operated to connect each gear to the shaft.

そこで第２図に従って具体的な変速動作を説明すると、
次の様になる。Therefore, the specific gear shifting operation will be explained according to Fig. 2.
It will look like this:

今、第２図の段数１となる変速操作を行なったとすると
、丸印で示すギア（ｃ＞、　　（ｎ　＞、　　（ｑ　’
）を一体に備えた第２クラッチ（１２）、第６クラツヂ
（１６）及び第８クラッチ（１８〉が作動し、ギア（ｃ
　）を第’１（１）に、ギア（ｒｌ）を第４軸（４）に
、更にギア（ｇ　）を第５軸（５）に連結する。このた
め、第１軸（１〉に与えられたエンジンからの動力回転
はギア（ｃ）、（ｇ＞、更にギア（ｈ）、（ｋ）を介し
てカウンタ部（３０）の第３軸（３）に伝達される。更
に、カウンタ部（３０）からギア（ｊ＞、（ｎ）を介し
て第３クラッチパツク（４０）の第４軸（４〉に伝達さ
れ、更にギア（ｍ）、（ｑ）を介して第８クラッチ（１
Ｂ）で連結されている第５１軸（５）に動力が伝達され
る。Now, if we perform a gear change operation that results in the number of gears being 1 in Fig. 2, the gears (c>, (n>, (q'
), the second clutch (12), the sixth clutch (16), and the eighth clutch (18>) operate, and the gear (c
) to the first shaft (1), the gear (rl) to the fourth shaft (4), and the gear (g) to the fifth shaft (5). Therefore, the power rotation from the engine applied to the first shaft (1>) is transmitted to the third shaft ( Furthermore, the signal is transmitted from the counter portion (30) to the fourth shaft (4>) of the third clutch pack (40) via the gears (j>, (n), and further transmitted to the gear (m), (q) to the eighth clutch (1
Power is transmitted to the 51st shaft (5) connected at B).

この様なりラッチ選択による変速は第２図の段数２〜１
６についても丸印で示すクラッチ選択で図示のギア比を
もった変速出力が得られる。In this way, the gear shift by latch selection is the number of stages 2 to 1 in Figure 2.
6 as well, by selecting the clutch indicated by the circle, a shift output having the gear ratio shown in the figure can be obtained.

一方、後退については、例えば第２図の段数Ｒ１を例に
とると、ギア（ｂ　）を一体に備えた第１クラッチ（１
１）の作動で第１軸（１）の動力回転を点線で示す様に
ギア（ｂ）、（ｉ）を介してカウンタ部（３０）の第１
ｊ（３）に伝達し、第２クラッチバツク（２０）に設け
たギアが介在しないことがらカウンタ部（３０）のギア
回転は逆方向となる。この力【ランク部（３０）におけ
る逆方向の動力回転は、第３クラッチパツク（４０）に
おける第６クラッチ（１Ｇ）の作動及び第４タラツヂバ
ツク（５０）における第８クラツヂ（′１８）の作動で
定まるギア比８もつで最終段の第５’ｔ’［ＩＩ（５）
に伝達される。この後進変速は残りの段数Ｒ２〜Ｒ４に
ついても第１クラツヂ（１１）か固定的に選択された状
態で第３及び第４クラッチパツク（４０）、（５０）の
クラッチ（１６）。On the other hand, regarding reversing, if we take the number of stages R1 in Fig. 2 as an example, the first clutch (1
1), the power rotation of the first shaft (1) is transmitted through the gears (b) and (i) to the first shaft of the counter part (30) as shown by the dotted line.
Since the gear provided in the second clutch bag (20) is not interposed, the gear rotation of the counter portion (30) is in the opposite direction. This force [power rotation in the opposite direction in the rank section (30) is caused by the operation of the sixth clutch (1G) in the third clutch pack (40) and the operation of the eighth clutch ('18) in the fourth clutch pack (50). With a fixed gear ratio of 8, the final stage 5't' [II (5)
transmitted to. This reverse gear change is performed by the clutches (16) of the third and fourth clutch packs (40) and (50), with the first clutch (11) being fixedly selected for the remaining gears R2 to R4.

（１７）、（１８）、（１９）を適宜に選択することで
、後進４段の切換えかできる。By appropriately selecting (17), (18), and (19), it is possible to switch between four reverse gears.

第３図は本発明の変速装置の設置状態を第４図の従来例
と対比して示したもので、エンジン（Ａ＞の動力回転は
単一ユニツ１〜となる本発明の変速装置（１００）に入
力され、車輪側のドライブシＶフト（Ｅ）の位置に出力
側となる第５１ＮＩ（５）の配置位置を決定することで
、チェーンによる動力伝達を不要にすることができる。FIG. 3 shows the installed state of the transmission of the present invention in comparison with the conventional example shown in FIG. 4. The transmission of the present invention (100 ), and by determining the location of the 51st NI (5) on the output side at the position of the drive shift V-shift (E) on the wheel side, it is possible to eliminate the need for power transmission by a chain.

また使用した軸数及びクラッチ数を最小としていること
から、変速機自体をコンパクトに構成することができる
。Furthermore, since the number of shafts and clutches used is minimized, the transmission itself can be configured compactly.

（発明の効果） 以上、説明してきた様に本発明によれば、前進１６段、
後進４段の合計２０段の変速機能をもつトラクタ用変速
装置として、９クラッチ、５軸及びギアトレインで成る
最小限の装置構成をもって実現できる様にしたため、従
来の２段変速機と８段変速機を組合わせた場合に比べ、
使用するクラッチ数、軸数及びギアトレインの数を必要
最小限に抑えることができ、部品点数の低減により装置
の小型軽量化及びコストの低減を図ることかでき、且つ
最小限の構成であることから動力損失の低減にも大きく
寄与する。(Effects of the Invention) As explained above, according to the present invention, there are 16 forward speeds,
A tractor transmission with a total of 20 speeds, including 4 reverse speeds, can be realized with a minimal device configuration consisting of 9 clutches, 5 axles, and a gear train. Compared to a combination of machines,
The number of clutches, shafts, and gear trains used can be kept to the minimum required, and by reducing the number of parts, the device can be made smaller and lighter, and the cost can be reduced, and the configuration is minimal. This greatly contributes to reducing power loss.

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

第１図は本発明の実施例をシンボリックに示した説明図
、第２図は第１図の実施例にお（プる前進１６段、後進
４段のギア比とクラッチ選択状態を示した一覧表の説明
図、第３図は本発明のユニツ］〜構成の説明図、第４図
は従来例の説明図である。 １：第１軸 ２：第２軸 ３：第３１Ｎ１ ４：第４ｆ’［ｔｌ ５：第５１ｉ１１ １０：第１クラッチパツク ２０：第２クラッチパツク ３０：カウンタ部 ４０：第３クラツヂパツク ５０：第４クラッチパツク ６０：パワー１〜レインアウトプツト ７０ニオイルポンプ １１〜１９：第１〜第９クラッチ ａ〜ｒ；ギアFig. 1 is an explanatory diagram symbolically showing an embodiment of the present invention, and Fig. 2 is a list showing the embodiment of Fig. 1 (16 forward gears and 4 reverse gear ratios and clutch selection states). An explanatory diagram of the table, FIG. 3 is an explanatory diagram of the structure of the unit of the present invention, and FIG. 4 is an explanatory diagram of the conventional example. 1: First axis 2: Second axis 3: 31st N1 4: 4th f '[tl 5: 51i11 10: 1st clutch pack 20: 2nd clutch pack 30: Counter section 40: 3rd clutch pack 50: 4th clutch pack 60: Power 1 to rain output 70 oil pumps 11 to 19: 1st to 9th clutches a to r; gear

Claims (1)

【特許請求の範囲】 エンジンからの動力回転が入力された第１軸（１）と、
該第１軸（１）に固着されたギア（ａ）と、該１軸（１
）に相対回転自在に装着したギア（ｂ）、（ｃ）、（ｄ
）と、該ギア（ｂ）、（ｃ）、（ｄ）の各々を前記第１
軸（１）に連結する第１、第２及び第３クラッチ（１１
）、（１２）、（１３）、とを備えた第１クラッチパッ
クと；第２軸（２）と、該第２軸（２）に固着され前記
ギア（ａ）と噛合ったギア（ｅ）と、該第２軸（２）に
相対回転自在に装着したギア（ｆ）と、該ギア（ｆ）を
第２軸（２）に連結する第４クラッチ（１４）と、前記
ギア（ｃ）と噛合あって第２軸（２）に相対回転自在に
装着したギア（ｇ）と、該ギア（ｇ）と一体に形成され
前記ギア（ｄ）に噛合ったギア（ｈ）と、前記ギア（ｇ
）、（ｈ）を前記第２軸（２）に連結する第５クラッチ
（１５）とを備えた第２クラッチパックと； 前記ギア（ｅ）に噛合うギア（ｊ）、前記ギア（ｆ）及
び（ｂ）に噛合うギア（ｉ）、前記ギア（ｈ）に噛合う
ギア（ｋ）、及びギア（ｌ）を第３軸（３）に固着した
カウンタギア部と； 第４軸（４）と、前記ギア（ｊ）に噛合って該第４軸（
４）に相対回転自在に装着されたギア（ｎ）と、該ギア
（ｎ）を第４軸（４）に連結する第６クラッチ（１６）
と、前記ギア（ｌ）に噛合って第４軸（４）に相対回転
自在に装着されたギア（Ｏ）と、該ギア（Ｏ）を第４軸
（４）に連結する第７クラッチ（１７）と、第４軸（４
）に固着されたギア（ｍ）、（ｐ）とを備えた第４クラ
ッチパックと； 動力回転を外部に取出す第５軸（５）と、前記ギア（ｍ
）に噛合って該５軸（５）に相対回転自在に装着された
ギア（ｑ）と、該ギア（ｑ）を第５軸（５）に連結する
第８クラッチ（１８）と、前記ギア（ｐ）に噛合って第
５軸（５）に相対回転自在に装着されたギア（ｒ）と、
該ギア（ｒ）を第５軸（５）に連結する第９クラッチ（
１９）とを備えた第４クラッチパックとで成ることを特
徴とするトラクタ用変速装置。[Claims] A first shaft (1) to which power rotation from an engine is input;
A gear (a) fixed to the first shaft (1) and a gear (a) fixed to the first shaft (1).
) gears (b), (c), (d
), and each of the gears (b), (c), and (d) is
First, second and third clutches (11) connected to the shaft (1)
), (12), and (13); a second shaft (2); and a gear (e) fixed to the second shaft (2) and meshing with the gear (a); ), a gear (f) relatively rotatably mounted on the second shaft (2), a fourth clutch (14) that connects the gear (f) to the second shaft (2), and a fourth clutch (14) that connects the gear (f) to the second shaft (2); ), a gear (g) meshed with the second shaft (2) and relatively rotatably mounted on the second shaft (2); a gear (h) formed integrally with the gear (g) and meshed with the gear (d); Gear (g
), (h) and a fifth clutch (15) that connects the gears (h) to the second shaft (2); a gear (j) meshing with the gear (e), and a gear (f); and (b) a gear (i) that meshes with the gear (h), a gear (k) that meshes with the gear (h), and a counter gear portion in which the gear (l) is fixed to the third shaft (3); ) and the fourth shaft (
4) and a sixth clutch (16) that connects the gear (n) to the fourth shaft (4).
a gear (O) that meshes with the gear (l) and is relatively rotatably mounted on the fourth shaft (4); and a seventh clutch (O) that connects the gear (O) to the fourth shaft (4). 17) and the fourth axis (4
); a fourth clutch pack comprising gears (m) and (p) fixed to the gear; a fifth shaft (5) for extracting power rotation to the outside;
), the gear (q) meshes with the fifth shaft (5) and is relatively rotatably mounted on the fifth shaft (5), an eighth clutch (18) connects the gear (q) to the fifth shaft (5), and the gear (p) and a gear (r) that is relatively rotatably mounted on the fifth shaft (5);
a ninth clutch () connecting the gear (r) to the fifth shaft (5);
19) A fourth clutch pack comprising:
JP60164278A 1985-07-25 1985-07-25 Speed change gear for tractor Granted JPS6224055A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP60164278A JPS6224055A (en) 1985-07-25 1985-07-25 Speed change gear for tractor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60164278A JPS6224055A (en) 1985-07-25 1985-07-25 Speed change gear for tractor

Publications (2)

Publication Number Publication Date
JPS6224055A true JPS6224055A (en) 1987-02-02
JPH0545813B2 JPH0545813B2 (en) 1993-07-12

Family

ID=15790049

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60164278A Granted JPS6224055A (en) 1985-07-25 1985-07-25 Speed change gear for tractor

Country Status (1)

Country Link
JP (1) JPS6224055A (en)

Also Published As

Publication number Publication date
JPH0545813B2 (en) 1993-07-12

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