JPS6228501Y2 - - Google Patents
Info
- Publication number
- JPS6228501Y2 JPS6228501Y2 JP1977075228U JP7522877U JPS6228501Y2 JP S6228501 Y2 JPS6228501 Y2 JP S6228501Y2 JP 1977075228 U JP1977075228 U JP 1977075228U JP 7522877 U JP7522877 U JP 7522877U JP S6228501 Y2 JPS6228501 Y2 JP S6228501Y2
- Authority
- JP
- Japan
- Prior art keywords
- transmission
- transmission shaft
- gears
- gear
- low speed
- 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
Links
- 230000005540 biological transmission Effects 0.000 claims description 207
- 230000007246 mechanism Effects 0.000 claims description 17
- 230000009467 reduction Effects 0.000 claims description 9
- 230000008859 change Effects 0.000 description 15
- 238000006073 displacement reaction Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 2
- 239000002689 soil Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000000415 inactivating effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Landscapes
- Arrangement Of Transmissions (AREA)
Description
【考案の詳細な説明】
この考案は、農用トラクター等の自走式作業車
を超低速で走行（クリープ走行）させるための機
構を組込んである歯車変速装置に関する。[Detailed Description of the Invention] This invention relates to a gear transmission incorporating a mechanism for causing a self-propelled working vehicle such as an agricultural tractor to run at an extremely low speed (creep running).
トラクター等をクリープ走行させて行なわれ
る、いわゆるクリープ作業としては圃場内での溝
切り作業（トレンチヤ作業）、深耕ロータリ作
業、ロータリ砕土作業とか路上での除雪作業とか
があるが、トレンチヤ作業及び深耕ロータリ作業
には低いクリープ車速が、またロータリ砕土作業
にはそれより高いクリープ車速が、それぞれ要求
されるといつたように作業種によつて、また除雪
作業時に積雪量の多少によりクリープ車速を変更
するといつたように作業条件によつて、クリープ
車速を変更することが要求されるが少なくとも望
ましいといつた事情がある。 The so-called creep work performed by creeping a tractor etc. includes trench cutting work in the field (trencher work), deep plow rotary work, rotary soil crushing work, and snow removal work on the road, but trencher work and deep plow rotary work As mentioned above, a low creep vehicle speed is required for work, and a higher creep vehicle speed is required for rotary soil crushing work, so the creep vehicle speed may be changed depending on the type of work or depending on the amount of snowfall during snow removal work. As mentioned above, depending on the work conditions, it is required, but at least desirable, to change the creep vehicle speed.
しかし従来はこの事情に対する特別の対策はと
られておらず、需要者の要望に従い工場サイド
で、クリープ用歯車の減速比を変更するとかクリ
ープ機構をカセツト式としておいて減速比の異な
る複数カセツトの中から適当したものを選択して
組込むといつた手段によつており、組立てミスが
起きるとか全体的なコスト及び在庫管理の点で不
経済であるとかの問題点があつた。 However, in the past, no special measures have been taken to address this situation, and factories have had to change the reduction ratio of the creep gear or make the creep mechanism a cassette type and use multiple cassettes with different reduction ratios in response to customer requests. This method involves selecting and assembling an appropriate one from among them, which has the problems of causing assembly errors and being uneconomical in terms of overall cost and inventory control.
そこでこの考案はかかる問題点を他の不具合を
伴なうことは解消する、農用トラクター等におけ
る新規な歯車変速装置を提供しようとするもので
ある。 Therefore, this invention aims to provide a new gear transmission device for agricultural tractors, etc., which solves this problem without accompanying other problems.
この考案課題を解決するために、この考案は農
用トラクター等の自走式作業車に設けられる歯車
変速装置において、添付図に例示するように、
Ａ 変速歯車２３，２４，２５を固定せる第１の
伝動軸１８と該変速歯車２３，２４，２５に選
択的に噛合されるシフト歯車２６，２７，２８
を摺動のみ可能に支持せる第２の伝動軸２２と
の他に、上記両伝動軸１８，２２に平行に配し
た中間伝動軸２９と上記第１の伝動軸１８と同
一軸線上に配した超低速用伝動軸３０とを設
け、上記の第１の伝動軸１８と中間伝動軸２９
と超低速用伝動軸３０とをこの順で減速歯車伝
動機構を介して連動連結し、上記超低速用伝動
軸３０に固定せる超低速用変速歯車３１に上記
した第２の伝動軸２２上のシフト歯車２６，２
７，２８のうちの最低速変速段用のシフト歯車
２６を噛合せて超低速を得るように構成し、
Ｂ また前記中間伝動軸２９上に摺動のみ可能に
支持された、互に径を異にする少なくとも２個
の伝動歯車３２，３３（第２−４図）または５
１，５２（第５図）を設け、該中間伝動軸２９
と前記第１の伝動軸１８または前記超低速用伝
動軸３０間を、該第１の伝動軸１８または超低
速用伝動軸３０に固定せる、互に径を異にする
少なくとも２個の他の伝動歯車２３，２４（第
２−４図）または５３，５４（第５図）の１つ
に中間伝動軸２９上の上記伝動歯車３２，３３
（第２−４図）または５１，５２（第５図）の
１つを選択的に噛合せて連動連結するように構
成する、
といつた技術的手段を講じた。 In order to solve the problem of this invention, this invention is a gear transmission device installed in a self-propelled working vehicle such as an agricultural tractor, as illustrated in the attached drawing. transmission shaft 18 and shift gears 26, 27, 28 selectively meshed with the transmission gears 23, 24, 25;
In addition to the second transmission shaft 22 that can support only sliding, an intermediate transmission shaft 29 arranged parallel to both the transmission shafts 18 and 22, and an intermediate transmission shaft 29 arranged on the same axis as the first transmission shaft 18. A very low speed transmission shaft 30 is provided, and the first transmission shaft 18 and the intermediate transmission shaft 29 are provided.
and an ultra-low speed transmission shaft 30 are interlocked in this order via a reduction gear transmission mechanism, and the ultra-low speed transmission gear 31 fixed to the ultra-low speed transmission shaft 30 is connected to the ultra-low speed transmission gear 31 on the second transmission shaft 22. Shift gear 26,2
The shift gears 26 for the lowest speed of the gears 7 and 28 are meshed with each other to obtain an extremely low speed; At least two different transmission gears 32, 33 (Figs. 2-4) or 5
1 and 52 (Fig. 5), and the intermediate transmission shaft 29
and the first power transmission shaft 18 or the very low speed power transmission shaft 30, at least two other shafts having different diameters are fixed to the first power transmission shaft 18 or the very low speed power transmission shaft 30. The transmission gear 32, 33 on the intermediate transmission shaft 29 is attached to one of the transmission gears 23, 24 (Figs. 2-4) or 53, 54 (Fig. 5).
(Fig. 2-4) or one of 51 and 52 (Fig. 5) is configured to selectively engage and interlock.
したがつてこの考案によれば、通常車速域での
変速は第２の伝動軸２２上のシフト歯車２６，２
７，２８を第１の伝動軸１８上の変速歯車２３，
２４，２５に対し選択的に噛合せて行なえ、また
クリープ車速は第２の伝動軸２２上のシフト歯車
２６を超低速用伝動軸３０上の超低速用変速歯車
３１に対し噛合せて得ることができる。 Therefore, according to this invention, the shift gears 26 and 2 on the second transmission shaft 22 are used for shifting in the normal vehicle speed range.
7, 28 are the transmission gears 23 on the first transmission shaft 18,
24 and 25, and the creep vehicle speed can be obtained by meshing the shift gear 26 on the second transmission shaft 22 with the very low speed transmission gear 31 on the very low speed transmission shaft 30. Can be done.
そして上記のクリープ車速は、中間伝動軸２９
上の摺動のみ可能な複数伝動歯車の１つを第１の
伝動軸１８または超低速用伝動軸３０上の対応す
る伝動歯車に選択的に噛合せることで、超低速用
伝動軸３０ないしその上の超低速用変速歯車３１
を複数段の超低速のうちの１速度で選択的に回転
させ得ることからして、複数段に変更できる。 The above creep vehicle speed is determined by the intermediate transmission shaft 29
By selectively meshing one of the plurality of transmission gears capable of sliding only with the corresponding transmission gear on the first transmission shaft 18 or the ultra-low-speed transmission shaft 30, the ultra-low-speed transmission shaft 30 or its Super low speed gear 31 above
Since it is possible to selectively rotate at one speed out of a plurality of ultra-low speeds, it is possible to change to a plurality of stages.
実施例について説明すると、第１図はこの考案
の一実施例を装備する農用トラクターを示してい
る。 To explain an embodiment, FIG. 1 shows an agricultural tractor equipped with an embodiment of this invention.
同トラクターは機体前部にエンジン１を塔載
し、このエンジン１により機体の一部を構成する
ミツシヨンケース２内等の伝動機構を介し、左右
の後輪３を回転駆動するようになすと共に機体後
部へ連結される作業機（図示せず）へ伝動する
PTO軸４を回転駆動するようになし、また乗用
座席５に座席せる作業者が操縦ハンドルにより左
右の前輪７を旋回操作して機体の操向を行なうよ
うに構成されている。 The tractor has an engine 1 mounted on the front of the machine, and this engine 1 rotates the left and right rear wheels 3 via a transmission mechanism inside a transmission case 2, which forms a part of the machine. Power is transmitted to a working machine (not shown) connected to the rear of the machine.
The PTO shaft 4 is rotatably driven, and a worker seated on a passenger seat 5 turns the left and right front wheels 7 using a control handle to steer the aircraft.
第２図は、前記エンジン１から後輪３に至るま
での走行動力伝動機構を示している。 FIG. 2 shows a traveling power transmission mechanism from the engine 1 to the rear wheels 3.
この走行動力伝動機構は主クラツチＣと、この
主クラツチＣを介し前記エンジン１に連動連結さ
れた走行動力変速部８であつて前記ミツシヨンケ
ース２内に配置されている走行動力変速部８と、
この走行動力変速部８より傘歯車９，１０を介し
入力される、左右後輪３用の差動装置１１と、こ
の差動装置１１の左右出力軸１１ａと左右後輪車
軸３ａ間を減速連動連結する左右の最終歯車減速
装置１２とを、備えたものに構成されている。上
記の走行動力変速部８は、油圧クラツチ式の走行
動力主変速装置１３と歯車式ないし機械式の走行
動力副変速装置１４とから、該両変速装置１３，
１４をこの順で直列に接続して構成されている。
また上記の差動装置１１には該差動装置１１を選
択的に非作動とするためのデフロツク装置１５を
配設してあると共に、上記の差動装置出力軸１１
ａ端には左右後輪３を選択的に制動するための左
右のブレーキ１６を配設してある。 This traveling power transmission mechanism includes a main clutch C, a traveling power transmission section 8 interlockingly connected to the engine 1 via the main clutch C, and located inside the transmission case 2. ,
A differential device 11 for the left and right rear wheels 3 receives input from the traveling power transmission unit 8 via bevel gears 9 and 10, and a deceleration interlock is provided between the left and right output shafts 11a of the differential device 11 and the left and right rear wheel axles 3a. It is configured to include a connecting left and right final gear reduction gear 12. The above-mentioned traveling power transmission section 8 includes a hydraulic clutch type traveling power main transmission 13 and a gear type or mechanical type traveling power auxiliary transmission 14.
14 are connected in series in this order.
Further, the differential device 11 is provided with a deflock device 15 for selectively inactivating the differential device 11.
Left and right brakes 16 for selectively braking the left and right rear wheels 3 are disposed at the a end.
上記した走行動力副変速装置１４が、この考案
に従つたものに構成されている。 The traveling power sub-transmission device 14 described above is constructed in accordance with this invention.
すなわち走行動力副変速装置１４は第２−４図
に示すように、走行動力主変速装置１３における
原動側の伝動軸１７の後方延長部１７ａに遊嵌し
て設けられた中空伝動軸１８であつて上記主変速
装置１３における被動側の伝動軸１９により、該
伝動軸１９先端に固定せる小径歯車２０と中空伝
動軸１８基端に固定せる大径歯車２１とを噛合せ
て構成された歯車減速機構を介し、回転せしめら
れる中空伝動軸１８（以下、第１の伝動軸とい
う。）と、この第１の伝動軸１８に平行させて上
記伝動軸１９の延長線上に設けられた第２の伝動
軸２２とを、備えている。そして第１の伝動軸１
８には互に径を異にする３個の変速歯車２３，２
４，２５を固定すると共に、第２の伝動軸２２に
は一体的な２個のシフト歯車２６，２７と他の１
個のシフト歯車２８とを、スプライン嵌合により
摺動のみ可能に支持させ、各シフト歯車２６，２
７，２８の選択的な摺動変位で歯車２３，２６間
の噛合い、歯車２４，２７間の噛合い、もしくは
歯車２５，２８間の噛合いを選択的に得て、３段
の変速比でもつて第１及び第２の伝動軸１８，２
２間を選択的に連動連結し得るようになされてい
る。 That is, as shown in FIG. 2-4, the traveling power sub-transmission device 14 is a hollow power transmission shaft 18 that is loosely fitted into the rear extension portion 17a of the driving side transmission shaft 17 in the traveling power main transmission device 13. The driven side transmission shaft 19 of the main transmission 13 is configured by meshing a small diameter gear 20 fixed to the tip of the transmission shaft 19 and a large diameter gear 21 fixed to the base end of the hollow transmission shaft 18. A hollow power transmission shaft 18 (hereinafter referred to as a first power transmission shaft) rotated through a mechanism, and a second power transmission shaft provided parallel to the first power transmission shaft 18 on an extension of the power transmission shaft 19. A shaft 22 is provided. and the first transmission shaft 1
8 has three speed change gears 23, 2 with mutually different diameters.
4 and 25 are fixed, and the second transmission shaft 22 has two integral shift gears 26 and 27 and another one.
The shift gears 28 are supported by spline fitting so that they can only slide, and each of the shift gears 26, 2
Through selective sliding displacement of gears 7 and 28, the meshing between the gears 23 and 26, the meshing between the gears 24 and 27, or the meshing between the gears 25 and 28 is selectively obtained, and a three-stage gear ratio is achieved. However, the first and second transmission shafts 18, 2
The two can be selectively linked together.
さらに上記第１，第２の伝動軸１８，２２の他
に、該両軸１８，２２に平行に配した中間伝動軸
２９と、上記の伝動軸延長部１７ａの先端部に遊
嵌して第１の伝動軸１８と同一軸線上に配された
中空の超低速用伝動軸３０とが、副変速装置１４
に設けられている。そして第１の伝動軸１８と上
記の中間伝動軸２９と超低速用伝動軸３０とを、
この順で減速歯車機構を介して連動連結し、超低
速用伝動軸３０に固定せる超低速用変速歯車３１
に第２の伝動軸２２上の上記シフト歯車２６を、
該シフト歯車２６の摺動変位により噛合せて、第
２の伝動軸２２に超低速を得るようになされてい
る。 Furthermore, in addition to the first and second transmission shafts 18 and 22, there is also an intermediate transmission shaft 29 disposed parallel to the two shafts 18 and 22, and an intermediate transmission shaft 29 that is loosely fitted into the tip of the transmission shaft extension 17a. A hollow ultra-low speed transmission shaft 30 disposed on the same axis as the transmission shaft 18 of the sub-transmission device 14
It is set in. Then, the first transmission shaft 18, the intermediate transmission shaft 29, and the very low speed transmission shaft 30,
The ultra-low speed transmission gear 31 is interlocked and connected in this order via a reduction gear mechanism and fixed to the ultra-low speed transmission shaft 30.
the shift gear 26 on the second transmission shaft 22,
The shifting gears 26 are brought into mesh by sliding displacement, and the second transmission shaft 22 is provided with an extremely low speed.
上記の減速歯車機構は、特に次のようなものに
構成されている。 The above-mentioned reduction gear mechanism is particularly configured as follows.
すなわち同様に第２−４図に示すように中間伝
動軸２９上には、互に径を異にする一体的な２個
のシフト歯車３２，３３であつて第１の伝動軸１
８上の前記変速歯車２３，２４にそれぞれ噛合せ
得る伝動歯車３２，３３を、スプライン嵌合によ
り摺動のみ可能に支持して設けると共に、もう１
個の伝動歯車３４を固定して設けてあり、この後
者の伝動歯車３４は、超低速用伝動軸３０に固定
して設けたより小径の伝動歯車３５と常時噛合せ
てある。したがつて第１の伝動軸１８上の最小径
の変速歯車２３に中間伝動軸２９上の大径側の伝
動歯車３２を、該伝動歯車３２の摺動変位により
噛合せると、第１の伝動軸１８の回転が変速歯車
２３、伝動歯車３２、中間伝動軸２９、伝動歯車
３４及び伝動歯車３５を介し超低速用伝動軸３０
に、したがつて該軸３０上の超低速用変速歯車３
１に、極めて減速されて伝達される。また第１の
伝動軸１８上の２番目に小径の変速歯車２４に中
間伝動軸２９上の小径側の伝動歯車３３を、該伝
動歯車３３の摺動変位により噛合せると、第１の
伝動軸１８の回転が変速歯車２４、伝動歯車３
３、中間伝動軸２９、伝動歯車３４及び伝動歯車
３５を介し超低速用伝動軸３０に、したがつて該
軸３０上の超低速用変速歯車３１に、上記の歯車
２３，３２間の噛合せの場合よりも減速度を若干
大として伝達されることとなる。 That is, as shown in FIG. 2-4, two integral shift gears 32 and 33 having different diameters are provided on the intermediate transmission shaft 29.
Transmission gears 32, 33 that can be engaged with the speed change gears 23, 24 on the 8 are supported by spline fitting so as to be capable of sliding only.
One transmission gear 34 is fixedly provided, and this latter transmission gear 34 is always meshed with a smaller diameter transmission gear 35 fixedly provided on the extra-low speed transmission shaft 30. Therefore, when the large diameter transmission gear 32 on the intermediate transmission shaft 29 is meshed with the smallest diameter speed change gear 23 on the first transmission shaft 18 by sliding displacement of the transmission gear 32, the rotation of the first transmission shaft 18 is transmitted to the extra-low speed transmission shaft 30 through the speed change gear 23, the transmission gear 32, the intermediate transmission shaft 29, the transmission gear 34 and the transmission gear 35.
Therefore, the very low speed variable speed gear 3 on the shaft 30
When the small-diameter transmission gear 33 on the intermediate transmission shaft 29 is brought into mesh with the second smallest-diameter speed change gear 24 on the first transmission shaft 18 by sliding displacement of the transmission gear 33, the rotation of the first transmission shaft 18 is transmitted through the speed change gear 24, the transmission gear 3
3. The power is transmitted through the intermediate transmission shaft 29, the transmission gear 34 and the transmission gear 35 to the very low speed transmission shaft 30, and hence to the very low speed variable speed gear 31 on said shaft 30, at a deceleration slightly greater than in the case of the meshing of the gears 23, 32 described above.
以上のようであるから、歯車２３，３２間の噛
合い或は歯車２４，３３間の噛合いを、中間伝動
軸２９上での一体的な伝動歯車３２，３３の摺動
変位で予め得ておいて、第２の伝動軸２２上のシ
フト歯車２６を超低速用伝動軸３０上の超低速用
変速歯車３１に噛合せることで、第２の伝動軸２
２に２段の超低速を選択的に得ることができる
が、中間伝動軸２９上の摺動可能な伝動歯車３
２，３３は、これを歯車２３，３２間の噛合い位
置或は歯車２４，３３間の噛合い位置に選択的に
摺動変位させた上で、摺動変位用の操作手段をロ
ツクする等で、該噛合い位置にロツクするか、或
は第１図に示す変速操作レバー３６のような操作
手段で何時でも任意に変位操作して、第１の伝動
軸１８上の変速歯車２３，２４に選択的に噛合せ
得るようにされる。 As described above, the mesh between the gears 23 and 32 or the mesh between the gears 24 and 33 can be obtained in advance by sliding displacement of the transmission gears 32 and 33 integrally on the intermediate transmission shaft 29. By meshing the shift gear 26 on the second transmission shaft 22 with the very low speed transmission gear 31 on the very low speed transmission shaft 30, the second transmission shaft 2
2, two-stage ultra-low speed can be selectively obtained, but the sliding transmission gear 3 on the intermediate transmission shaft 29
2 and 33 selectively slide and displace this to the meshing position between the gears 23 and 32 or the meshing position between the gears 24 and 33, and then lock the operating means for sliding displacement, etc. Then, the transmission gears 23 and 24 on the first transmission shaft 18 are locked in the meshing position, or can be arbitrarily displaced at any time using an operating means such as the transmission operation lever 36 shown in FIG. can be selectively engaged with.
なお図示の走行動力副変速装置１４にはさら
に、主変速装置１３における前記伝動軸１９端に
形成せる噛合片３７ａと、第２の伝動軸２２上の
シフト歯車２８に形成せる他の噛合片３７ｂとか
ら成る噛合いクラツチ３７を設け、シフト歯車２
８の摺動変位により該噛合いクラツチ３７を選択
的に係合させ伝動軸１９，２２間を直結して、最
高速の変速比を得ることができるようになされて
いる。 The illustrated running power sub-transmission 14 further includes a meshing piece 37a formed on the end of the transmission shaft 19 in the main transmission 13, and another meshing piece 37b formed on the shift gear 28 on the second transmission shaft 22. A meshing clutch 37 consisting of the shift gear 2 is provided.
The dog clutch 37 is selectively engaged by the sliding displacement of 8, and the transmission shafts 19 and 22 are directly connected to each other, thereby making it possible to obtain the highest speed gear ratio.
なお走行動力主変速装置１３は、第２図に示す
ように次のような油圧クラツチ式変速装置、つま
り原動側の伝動軸１７に嵌着して設けたF1変速
歯車３８、F2変速歯車３９、F3変速歯車４０及
びＲ変速歯車４１と、被動側の伝動軸１９に遊嵌
され上記変速歯車３８−４１のうちの相当するも
のに直接またはＲ中間歯車４１ａを介し噛合され
たF1遊転歯車４２、F2遊転歯車４３、F3遊転歯
車４４及びＲ遊転歯車４５と、一方の摩擦板を上
記遊転歯車４２−４５の各々に、他方の摩擦板を
伝動軸１９に固定せるクラツチハウジングに、そ
れぞれクラツチ軸線方向に摺動のみ自在に支持さ
せて多板式油圧クラツチに構成された油圧クラツ
チ４６−４９であつて圧油作用による上記摩擦板
間の係合によつて作動せしめられ遊転歯車４２−
４５の各々を選択的に伝動軸１９に結合するF1
油圧クラツチ４６，F2油圧クラツチ４７，F3油
圧クラツチ４８及びＲ油圧クラツチ４９とを備え
た、それ自体は公知の油圧クラツチ式変速装置に
構成されている。 As shown in FIG. 2, the traveling power main transmission 13 is a hydraulic clutch type transmission as shown below, that is, an F 1 speed change gear 38 and an F 2 speed change gear that are fitted onto the power transmission shaft 17 on the drive side. 39, the F 3 transmission gear 40 and the R transmission gear 41, and the F 1 which is loosely fitted on the driven side transmission shaft 19 and meshes with the corresponding one of the transmission gears 38-41 either directly or via the R intermediate gear 41a. Idle gear 42, F2 idle gear 43, F3 idle gear 44, and R idle gear 45, one friction plate is attached to each of the idle gears 42-45, and the other friction plate is attached to the transmission shaft 19. Hydraulic clutches 46 to 49 are configured as a multi-plate hydraulic clutch by being supported by a clutch housing fixed to the clutch housing so as to be slidable only in the direction of the clutch axis, and the hydraulic clutches 46 to 49 are configured as a multi-plate hydraulic clutch by engagement between the friction plates by pressure oil action. The idle gear 42- is activated.
45 selectively coupled to the transmission shaft 19 .
It is constructed as a known hydraulic clutch transmission with a hydraulic clutch 46, an F2 hydraulic clutch 47, an F3 hydraulic clutch 48 and an R hydraulic clutch 49.
次に第５図に図示の他の実施例について説明す
ると、この実施例では、中間伝動軸２９上に第１
の伝動軸１８上の最小径変速歯車２３と常時噛合
される伝動歯車５０を固定して、中間伝動軸２９
を第１の伝動軸１８に常時減速連動連結すると共
に、該中間伝動軸２９上に互に径を異にする一体
的な２個の伝動歯車５１，５２を、スプライン嵌
合により摺動のみ可能に支持し、この伝動歯車５
１，５２をそれぞれ選択的に噛合せ得る２個の伝
動歯車５３，５４を超低速用伝動軸３０に固定し
て設けている。伝動歯車５１，５２は前記伝動歯
車３２，３３同様に、これを歯車５１，５３噛合
い位置或は歯車５２，５４噛合い位置に選択的に
変位させて該位置にロツクし得るか、或は何時で
も任意に超低速用伝動軸３０上の伝動歯車５３，
５４に選択的に噛合せるように変位させ得るもの
に、構成されている。したがつてこの実施例の場
合にも先の実施例の場合同様に、第２の伝動軸２
２に２段の超低速を選択的に得ることができる。 Next, another embodiment shown in FIG. 5 will be explained. In this embodiment, a first
The transmission gear 50, which is always meshed with the smallest diameter transmission gear 23 on the transmission shaft 18, is fixed, and the intermediate transmission shaft 29 is fixed.
is connected to the first transmission shaft 18 in a constant deceleration manner, and two integral transmission gears 51 and 52 with different diameters are mounted on the intermediate transmission shaft 29 and can only slide by spline fitting. This transmission gear 5
Two transmission gears 53 and 54, which can be selectively engaged with gears 1 and 52, respectively, are provided fixed to the ultra-low speed transmission shaft 30. Like the transmission gears 32 and 33, the transmission gears 51 and 52 can be selectively displaced to the meshing position of the gears 51 and 53 or the meshing position of the gears 52 and 54 and locked in that position, or At any time, the transmission gear 53 on the ultra-low speed transmission shaft 30,
54 so as to be able to be displaced to selectively engage with it. Therefore, in this embodiment, as in the previous embodiment, the second power transmission shaft 2
2. Two stages of ultra-low speed can be selectively achieved.
なお以上の２実施例では、超低速を２段に速度
変更可能としたが、中間伝動軸２９上の摺動のみ
可能な異径の伝動歯車の個数を３個以上とすると
共に、対応して該伝動歯車が選択的に噛合され
る、第１の伝動軸１８または超低速用伝動軸３０
上の固定伝動歯車の個数を３個以上とし、第２の
伝動軸２２に３段以上の超低速を選択的に得るこ
とができるようにも、なし得るものである。また
この考案の歯車変速装置を、第１の実施例におけ
るように、中間伝動軸２９上の摺動のみ可能な伝
動歯車３２，３３を第１の伝動軸１８上の対応す
る歯車２３，２４と選択的に噛合せ得るように構
成する場合において、第１の伝動軸１８上の上記
歯車２３，２４を、第２の伝動軸２２上のシフト
歯車２６，２７が選択的に噛合される変速歯車２
３，２４兼用のものとする他、このような変速歯
車とは別に第１の伝動軸１８に固定せる伝動歯車
とすることも可能である。 In the above two embodiments, the ultra-low speed can be changed to two stages, but the number of transmission gears of different diameters that can only slide on the intermediate transmission shaft 29 is set to three or more, and the corresponding The first transmission shaft 18 or the very low speed transmission shaft 30 with which the transmission gear is selectively meshed.
It is also possible to increase the number of upper fixed transmission gears to three or more so that the second transmission shaft 22 can selectively achieve three or more stages of extremely low speed. Further, in the gear transmission of this invention, as in the first embodiment, the transmission gears 32 and 33 that can only slide on the intermediate transmission shaft 29 are connected to the corresponding gears 23 and 24 on the first transmission shaft 18. In the case where the gears 23 and 24 on the first transmission shaft 18 are configured to be selectively meshed, the gears 23 and 24 on the first transmission shaft 18 are changed into gears with which the shift gears 26 and 27 on the second transmission shaft 22 are selectively meshed. 2
In addition to using a transmission gear that can be used for both 3 and 24 transmission gears, it is also possible to use a transmission gear that is fixed to the first transmission shaft 18 separately from such a transmission gear.
この考案が奏する効果は、次の通りである。 The effects of this idea are as follows.
歯車変速装置自体にクリープ車速を複数段に
わたり変更可能とするクリープ機構を組込んだ
本案装置は、トラクター等の出荷時に、需要者
が希望するクリープ車速が得られるように中間
伝動軸２９上の摺動可能な歯車３２，３３また
は５１，５２位置をロツクするか、或は需要者
が自ら該歯車３２，３３または５１，５２の位
置変更によりクリープ車速を変更できることと
しておくように、利用できる。需要者の作業種
目が変わつたり増加したような場合にも簡単に
対応できることになる。つまりこの考案によれ
ばクリープ走行の速度を簡単に変更できる。 The proposed device, which incorporates a creep mechanism that can change the creep vehicle speed over multiple stages in the gear transmission itself, has a sliding mechanism on the intermediate transmission shaft 29 so that the creep vehicle speed desired by the user can be obtained when the tractor, etc. is shipped. It can be used so that the position of the movable gears 32, 33 or 51, 52 is locked, or the user himself can change the creep vehicle speed by changing the position of the gears 32, 33 or 51, 52. This makes it easy to respond to cases where the type of work performed by the customer changes or increases. In other words, according to this invention, the creep speed can be easily changed.
クリープ機構を含む歯車変速装置が単一のも
のとされることから組立てミスがないと共に在
庫管理が複雑化せず、また歯車個数が増すとい
つても組立て上及び在庫管理上の有利さとクリ
ープ車速を変更できる点とで全体的なコストの
上でも有利となる。 Since the gear transmission including the creep mechanism is a single unit, there are no assembly errors and inventory management is not complicated, and when the number of gears increases, there are advantages in assembly and inventory management, and creep vehicle speed is reduced. It is advantageous in terms of overall cost as well, as it allows for changes to be made.
超低速の車速を無理のない構造で得るため通
常車速域内での変速伝動がその間で行なわれる
第１及び第２の伝動軸１８，２２とは別に、減
速歯車機構のために利用する中間伝動軸２９を
設ける構造において、クリープ車速を変更する
ために摺動可能に支持した少なくとも２個の歯
車３２，３３または５１，５２を上記中間伝動
軸２９上に設けて、クリープ車速を得る操作自
体は通常車速域の最低速段のシフト歯車２６の
シフト操作で得ることとしているから、クリー
プ車速を簡単に変更できるものでありながら同
一の操作系で通常車速域内の変速とクリープ車
速とを得させ、操作機構を複雑としない。また
作業中に過負荷が作用したとき等に車速を順次
低めて行く操作がよく行なわれるが、その場合
に本案によれば、通常車速域の最低速変速段と
してもなお車速が過剰であるとそのまま同一レ
バーで、中間伝動軸２９を利用した無理のない
大幅減速機構によつて得られる超低速のクリー
プ車速へと車速を下げることができ、緊急事態
への対処を速やかに行なえる。 In order to obtain ultra-low vehicle speeds with a reasonable structure, there is an intermediate transmission shaft used for the reduction gear mechanism, in addition to the first and second transmission shafts 18 and 22 between which gear transmission within the normal vehicle speed range is performed. 29, at least two slidably supported gears 32, 33 or 51, 52 are provided on the intermediate transmission shaft 29 in order to change the creep vehicle speed, and the operation itself to obtain the creep vehicle speed is normally performed. Since the creep speed is obtained by shifting the shift gear 26 at the lowest gear in the vehicle speed range, the creep vehicle speed can be easily changed, but the same operating system can be used to obtain the creep vehicle speed and the shift within the normal vehicle speed range. The mechanism is not complicated. In addition, when an overload occurs during work, it is common to gradually reduce the vehicle speed, but in this case, according to the present proposal, the vehicle speed is still excessive even when the lowest gear in the normal vehicle speed range is used. With the same lever, the vehicle speed can be lowered to the ultra-low creep vehicle speed obtained by the reasonable large speed reduction mechanism using the intermediate transmission shaft 29, and emergency situations can be quickly dealt with.
第１図はこの考案の一実施例を装備した農用ト
ラクターの概略側面図、第２図は同農用トラクタ
ーにおける走行動力の伝導系統図、第３図は同実
施例の縦断側面図、第４図は同実施例要部の横断
平面図、第５図は他の実施例の伝動機構図であ
る。
８……走行動力変速部、１４……走行動力副変
速装置、１８……第１の伝動軸、２２……第２の
伝動軸、２３，２４，２５……変速歯車、２６，
２７，２８……シフト歯車、２９……中間伝動
軸、３０……超低速用伝動軸、３１……超低速用
変速歯車、３２，３３……伝動歯車、３４……伝
動歯車、３５……伝動歯車、５０……伝動歯車、
５１，５２……伝動歯車、５３，５４……伝動歯
車。
Fig. 1 is a schematic side view of an agricultural tractor equipped with an embodiment of this invention, Fig. 2 is a transmission system diagram of running power in the agricultural tractor, Fig. 3 is a vertical side view of the embodiment, and Fig. 4 5 is a cross-sectional plan view of the main part of the same embodiment, and FIG. 5 is a diagram of the transmission mechanism of another embodiment. 8... Travel power transmission unit, 14... Travel power sub-transmission device, 18... First transmission shaft, 22... Second transmission shaft, 23, 24, 25... Speed change gear, 26,
27, 28...Shift gear, 29...Intermediate transmission shaft, 30...Very low speed transmission shaft, 31...Very low speed transmission gear, 32, 33...Transmission gear, 34...Transmission gear, 35... Transmission gear, 50... Transmission gear,
51, 52... Transmission gear, 53, 54... Transmission gear.
Claims (1)
動軸１８と該変速歯車２３，２４，２５に選択的
に噛合されるシフト歯車２６，２７，２８を摺動
のみ可能に支持せる第２の伝動軸２２との他に、
上記両伝動軸１８，２２に平行に配した中間伝動
軸２９と上記第１の伝動軸１８と同一軸線上に配
した超低速用伝動軸３０とを設け、上記の第１の
伝動軸１８と中間伝動軸２９と超低速用伝動軸３
０とをこの順で減速歯車伝動機構を介して連動連
結し、上記超低速用伝動軸３０に固定せる超低速
用変速歯車３１に上記した第２の伝動軸２２上の
シフト歯車２６，２７，２８のうちの最低速変速
段用のシフト歯車２６を噛合せて超低速を得るよ
うに構成し、 前記中間伝動軸２９上に摺動のみ可能に支持さ
れた、互に径を異にする少なくとも２個の伝動歯
車３２，３３，５１，５２を設け、該中間伝動軸
２９と前記第１の伝動軸１８間または前記超低速
用伝動軸３０間を、該第１の伝動軸１８または超
低速用伝動軸３０に固定せる、互に径を異にする
少なくとも２個の他の伝動歯車２３，２４，５
３，５４の１つに中間伝動軸２９上の上記伝動歯
車３２，３３，５１，５２の１つを選択的に噛合
せて連動連結するように構成したことを特徴とす
る、農用トラクター等における歯車変速装置。[Claims for Utility Model Registration] First transmission shaft 18 to which transmission gears 23, 24, 25 are fixed and shift gears 26, 27, 28 selectively meshed with the transmission gears 23, 24, 25 are slid. In addition to the second transmission shaft 22, which can only be supported by
An intermediate transmission shaft 29 arranged parallel to both the transmission shafts 18 and 22 and an extremely low-speed transmission shaft 30 arranged on the same axis as the first transmission shaft 18 are provided. Intermediate transmission shaft 29 and ultra-low speed transmission shaft 3
0 are interlocked and connected in this order via a reduction gear transmission mechanism, and the shift gears 26, 27, The shift gear 26 for the lowest speed of the 28 gears is configured to mesh with each other to obtain an extremely low speed, and at least two gears having mutually different diameters are slidably supported on the intermediate transmission shaft 29. Two transmission gears 32, 33, 51, 52 are provided, and a connection between the intermediate transmission shaft 29 and the first transmission shaft 18 or between the very low speed transmission shaft 30 is provided, and At least two other transmission gears 23, 24, 5 with mutually different diameters are fixed to the transmission shaft 30.
In an agricultural tractor or the like, characterized in that one of the transmission gears 32, 33, 51, 52 on the intermediate transmission shaft 29 is selectively meshed and interlocked with one of the transmission gears 3, 54. Gear transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977075228U JPS6228501Y2 (en) | 1977-06-08 | 1977-06-08 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977075228U JPS6228501Y2 (en) | 1977-06-08 | 1977-06-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS541830U JPS541830U (en) | 1979-01-08 |
| JPS6228501Y2 true JPS6228501Y2 (en) | 1987-07-22 |
Family
ID=28989470
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1977075228U Expired JPS6228501Y2 (en) | 1977-06-08 | 1977-06-08 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6228501Y2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS509922B2 (en) * | 1972-03-03 | 1975-04-17 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5621619Y2 (en) * | 1973-05-24 | 1981-05-21 |
-
1977
- 1977-06-08 JP JP1977075228U patent/JPS6228501Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS509922B2 (en) * | 1972-03-03 | 1975-04-17 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS541830U (en) | 1979-01-08 |
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