JPH03234952A - Transmission gear equipped with ultra low speed switching mechanism - Google Patents
Transmission gear equipped with ultra low speed switching mechanismInfo
- Publication number
- JPH03234952A JPH03234952A JP2031146A JP3114690A JPH03234952A JP H03234952 A JPH03234952 A JP H03234952A JP 2031146 A JP2031146 A JP 2031146A JP 3114690 A JP3114690 A JP 3114690A JP H03234952 A JPH03234952 A JP H03234952A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- low speed
- switching mechanism
- power
- gear
- 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
- 230000007246 mechanism Effects 0.000 title claims abstract description 53
- 230000005540 biological transmission Effects 0.000 title claims description 88
- 230000002708 enhancing effect Effects 0.000 abstract 1
- 238000011144 upstream manufacturing Methods 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
Landscapes
- 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、農用トラクタ等の超低速切換え機構を備えた
トランスミッション装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a transmission device for agricultural tractors and the like that is equipped with a very low speed switching mechanism.
［従来技術及び発明が解決しようとする課題］一般に、
この種作業用走行機体においては、作業種類の多様化に
対応して超低速走行と前後進切換えがそれぞれレバー操
作等の操作具切換えによってできるようにしたものがあ
る。しかるに従来、これらのものは超低速走行状態で後
進切換えを行うと、そのまま超低速走行状態で後進する
構成になっており、この結果、後進速度が遅すぎて作業
性が劣るという欠点が有り、そこで作業者は、後進走行
に切換えると共に超低速走行を通常走行状態に切換えな
ければならず、そして再び超低速走行作業を再開するた
めには、再び超低速走行状態に切換える作業が強いられ
ることになって面倒かつ煩雑な切換え操作が必要で操作
性に劣るという問題が有る。[Prior art and problems to be solved by the invention] Generally,
In response to the diversification of types of work, some of these types of work traveling machines are designed to allow ultra-low speed travel and forward/backward switching by switching operating tools such as lever operations. However, conventionally, these devices have been configured so that if the reverse switch is performed while the vehicle is running at an extremely low speed, the vehicle will continue to go backwards while the vehicle is traveling at an extremely low speed.As a result, the reverse speed is too slow, resulting in poor workability. Therefore, the worker must switch to reverse driving and switch from ultra-low-speed driving to normal driving, and in order to resume ultra-low-speed driving, the worker is forced to switch back to ultra-low-speed driving. Therefore, there is a problem that a troublesome and complicated switching operation is required, resulting in poor operability.
［課題を解決する手段］
本発明は、上記の如き実情に鑑み、これらの欠点を一掃
することができる超低速切換え機構を備えた１〜ランス
ミツシヨン装置を提供することを目的として創案された
ものであって、エンジン側に連動連結される主変速軸に
入力した動力を、走行駆動輪用ピニオン軸側に連動連結
される副変速軸に伝達する動力伝動経路中に、前後進切
換え機構と超低速切換え機構とを備えるに、前後進切換
え機構は、主変速軸、該主変速軸と同心状に設けた中間
軸、および上記副変速軸との間に設けられ、前進切換え
状態では主変速軸から中間軸側に動力伝動し、後進切換
え状態では主変速軸から副変速軸側に動力伝動するよう
ギア噛合の選択をする変速ギア機構で構成する一方、超
低速切換え機構は、前記中間軸と副変速軸との間に設け
られ、超低速状態と非超低速状態とに切換えられるよう
ギア噛合の選択をする変速ギア機構で構成して、前後進
切換え機構を、前進切換え状態としたときには主変速軸
から中間軸、超低速切換え機構を経由して副変速軸側に
動力伝動をするが、後進切換え状態としたときには中間
軸、超低速切換え機構を経由することなく主変速軸から
副変速軸側に直接的に動力伝動する構成にしたことを特
徴とするものである。[Means for Solving the Problems] In view of the above-mentioned circumstances, the present invention was devised for the purpose of providing a 1-run transmission device equipped with an ultra-low speed switching mechanism capable of eliminating these drawbacks. A forward/reverse switching mechanism is included in the power transmission path that transmits the power input to the main transmission shaft, which is interlocked to the engine side, to the auxiliary transmission shaft, which is interlocked to the pinion shaft for the driving wheels. The forward/reverse switching mechanism is provided between a main shift shaft, an intermediate shaft provided concentrically with the main shift shaft, and the sub-shift shaft, and in the forward shift state, the forward/reverse shift mechanism is The transmission gear mechanism transmits power from the shaft to the intermediate shaft, and selects gear engagement so that power is transmitted from the main transmission shaft to the auxiliary transmission shaft in the reverse switching state. and an auxiliary transmission shaft, and is configured with a transmission gear mechanism that selects gear engagement so as to switch between an ultra-low speed state and a non-ultra-low speed state, and when the forward/reverse switching mechanism is in the forward switching state. Power is transmitted from the main transmission shaft to the auxiliary transmission shaft via the intermediate shaft and the ultra-low speed switching mechanism, but when the reverse gear is switched, the power is transmitted from the main transmission shaft to the auxiliary transmission shaft without passing through the intermediate shaft or the ultra-low speed switching mechanism. It is characterized by a structure in which power is transmitted directly to the shaft side.
そして本発明は、この構成によって、超低速走行状態で
後進走行に切換えると通常速度での後進走行がなされる
ようにしたものである。According to the present invention, with this configuration, when switching to reverse travel in a very low speed traveling state, reverse travel is performed at normal speed.
［実施例］
次に、本発明の一実施例を図面に基づいて説明する。図
面において、１は農用トラクタの走行機体であって、該
走行機体１にはトランスミッションケース２が装備され
るが、１ヘランスミツシヨンケース２内には次ぎのよう
なトランスミッション３
装置が内装されている。[Example] Next, an example of the present invention will be described based on the drawings. In the drawings, reference numeral 1 denotes a traveling body of an agricultural tractor, and the traveling body 1 is equipped with a transmission case 2. Inside the transmission case 2, the following transmission 3 device is installed. There is.
つまりトランスミッションケース２の一側（前側）には
、エンジンからの動力が入力する入力軸３、主駆動軸４
、油圧ポンプ駆動軸５、および前＠駆動軸６等の各軸が
回動自在に軸支されている。In other words, on one side (front side) of the transmission case 2 are an input shaft 3 to which power from the engine is input, and a main drive shaft 4.
, a hydraulic pump drive shaft 5, a front @ drive shaft 6, and other shafts are rotatably supported.
前記生恥動軸４には、トランスミッションケース２の前
部を覆蓋すへく一体的に取付けられるクラッチカバー２
ａに内装されるようにして主クラッチ７が装着されてい
るが、該主クラッチ７の主駆動軸４に自由回動自在に軸
支されたクラッチ入力ギア７ａは入力軸３に一体形成し
たギア３ａに常時噛合している。そして入力軸３からの
動力は、主クラッチ７を経由して主駆動軸に断続自在に
伝達されるように構成されているが、前記クラッチ入力
ギア７ａはさらに油圧ポンプ駆動軸５に一体的に設けた
中間ギア５ａに常時噛合していて、油圧ポンプ駆動軸Ｒ
にも動力伝達される構成になっている。さらに−駆動軸
４には、複数（実施例では四個）の変速ギア４ａが一体
的に設けられている。A clutch cover 2 is integrally attached to the shaft 4 to cover the front part of the transmission case 2.
A main clutch 7 is installed inside the main clutch 7, and a clutch input gear 7a rotatably supported on the main drive shaft 4 of the main clutch 7 is a gear integrally formed on the input shaft 3. It is always engaged with 3a. The power from the input shaft 3 is configured to be transmitted intermittently to the main drive shaft via the main clutch 7, but the clutch input gear 7a is further integrally connected to the hydraulic pump drive shaft 5. It is always meshed with the provided intermediate gear 5a, and the hydraulic pump drive shaft R
The configuration is such that power is transmitted to the Further, the drive shaft 4 is integrally provided with a plurality of (four in the embodiment) transmission gears 4a.
＝４
８は動力取出し軸（ＰＴＯ軸）、９は主変速軸であって
、これらは何れも主駆動軸４に平行となるようトランス
ミッションケース２に支持されるものであるが、主変速
軸９には、前記変速ギア４ａにそれぞれ常時噛合する変
速ギア９ａが自由回動自在に設けられている。そして主
変速軸９に一体回動するようスプライン嵌合するシフタ
ギア９ｂを選択的に変速ギア９ａに噛合せしめることに
よって主駆動軸４から主変速軸９に対して主変速切換え
がなされた動力伝動がなされる構成になっており、この
様にして主変速機構Ａが形成されている。=4 8 is a power take-off shaft (PTO shaft), 9 is a main shift shaft, both of which are supported by the transmission case 2 so as to be parallel to the main drive shaft 4; is provided with freely rotatable transmission gears 9a which are always in mesh with the transmission gears 4a. By selectively engaging the shift gear 9a with the shifter gear 9b, which is spline-fitted to rotate integrally with the main shift shaft 9, the power is transmitted from the main drive shaft 4 to the main shift shaft 9 during the main shift change. In this way, the main transmission mechanism A is formed.
さらに主変速軸９には、自由回動自在に後進切換え用変
速ギア９ｃが、また一体回動するよう前後進切換え用シ
フタギア９ｄがそれぞれ設けられている。１０は主変速
軸９に対して同心状に配された中間軸であって、先端部
（後端部）はデファレンシャルギア部１３を越えて後方
に延びてトランスミッションケース２に回動自在に支持
されているが、該中間軸１０の主変速軸９に対向する部
位に前進切換え用変速ギア１０ａが一体回動するよう設
けられている。さらに１１は中間軸］Ｏに平行に配設さ
れた副変速軸であって、該副変速軸１１に一体回動する
よう設けた後進用受動ギア１１ ａと前記主変速軸９側
の後進切換え用変速ギア９ｃとの間は、トランスミッシ
ョンケース２に装着したピン軸］、２ａに自由回動自在
に軸支された中間ギア］２を介して連動連結されている
。そして前後進切換え用シフタギア９ｄを、後進切換え
用変速ギア９ｃに選択噛合させた場合には、主変速軸９
からの動力は、前後進切換え用シフタギア９ｄから後進
切換え用変速ギア９ｃ、中間ギア１２、後進用受動ギア
ｌｌａを経て副変速軸］、１に動力伝動され、また前進
切換え用変速ギア］、Ｏａに選択噛合させた場合には、
主変速軸９からの動力は、前後進切換え用シフタギア９
ｄから前進切換え用変速ギア１０ａを経て中間軸１０に
動力伝動される構成になっており、この様にして前後進
切換え機構Ｂが形成されている。Further, the main speed change shaft 9 is provided with a freely rotatable reverse gear change gear 9c and a forward/reverse change shift gear 9d that rotates integrally with the main shift shaft 9. Reference numeral 10 denotes an intermediate shaft disposed concentrically with respect to the main transmission shaft 9, whose tip (rear end) extends rearward beyond the differential gear section 13 and is rotatably supported by the transmission case 2. However, a forward switching transmission gear 10a is provided at a portion of the intermediate shaft 10 facing the main transmission shaft 9 so as to rotate integrally with the intermediate shaft 10. Further, reference numeral 11 denotes an auxiliary transmission shaft arranged parallel to the intermediate shaft]O, which is connected to a reverse passive gear 11a provided to rotate integrally with the auxiliary transmission shaft 11, and a reverse gear changeover on the main transmission shaft 9 side. The transmission gear 9c is interlocked with the transmission gear 9c via a pin shaft attached to the transmission case 2 and an intermediate gear rotatably supported by the transmission case 2a. When the forward/reverse switching shifter gear 9d is selectively engaged with the reverse switching gear 9c, the main shift shaft 9
Power is transmitted from the forward/reverse switching shifter gear 9d to the reverse switching gear 9c, the intermediate gear 12, and the reverse passive gear lla to the auxiliary transmission shaft], 1, and also to the forward switching gear], Oa. When selectively meshed with
The power from the main transmission shaft 9 is transferred to a shifter gear 9 for switching forward/backward.
d, power is transmitted to the intermediate shaft 10 via the forward switching gear 10a, thus forming the forward/reverse switching mechanism B.
さらに前記中間軸１０のデファレンシャルギア部１３を
越えた後端部には、一体回動する超低速用変速ギア１０
ｂと自由回動する変速ギア１０ｃとが設けられており、
一方、副変速軸１１には、前記超低速用変速ギア１０ｂ
に大きな減速比を呈する関係で常時噛合する自由回動自
在な超低速用受動ギア１１ｂと、スプライン嵌合された
超低速切換え用シフタギアｌｌｃとが設けられている。Further, at the rear end of the intermediate shaft 10 beyond the differential gear section 13, there is provided an ultra-low speed transmission gear 10 that rotates integrally with the intermediate shaft 10.
b and a freely rotating speed change gear 10c,
On the other hand, the sub-transmission shaft 11 has the ultra-low speed transmission gear 10b.
A freely rotatable ultra-low speed passive gear 11b that is always in mesh with each other so as to exhibit a large reduction ratio, and a spline-fitted ultra-low speed switching shifter gear llc are provided.
そして超低速切換え用シフタギア１１Ｃを変速ギア１０
ｃに噛合させた場合には、前記中間軸１０からの動力は
、変速ギア１０ｃから超低速切換え用シフタギア１１ｃ
を経て副変速軸１１に伝達されるが、超低速用受動ギア
ｌｌｂに噛合させた場合には、前記中間軸１０からの動
力は、超低速用変速ギア１０ｂから超低速用受動ギアｌ
ｌｂ、超低速切換え用シフタギアｌｌｃを経て副変速軸
１１に対して大きな減速比を呈する状態で伝達される構
成になっており、この様にして超低速切換え機構Ｃが形
成されている。Then shift the super low speed switching shifter gear 11C to the transmission gear 10.
c, the power from the intermediate shaft 10 is transferred from the transmission gear 10c to the ultra-low speed switching shifter gear 11c.
However, when the intermediate shaft 10 is engaged with the very low speed passive gear llb, the power from the intermediate shaft 10 is transmitted from the very low speed transmission gear 10b to the very low speed passive gear llb.
lb and ultra-low speed switching shifter gear llc to be transmitted to the sub-transmission shaft 11 in a state exhibiting a large reduction ratio, thus forming an ultra-low speed switching mechanism C.
さらに副変速軸１１−の前端部には副変速ギア１１ｄが
一体回動するよう設けられており、一方、一
前記デファレンシャルギア部１３に噛合するピニオン軸
１４に副変速用シフタギア１４ａがスプライン嵌合され
ている。そして副変速用シフタギア１４ａを副変速ギア
１１ ｄに選択噛合させることによって、副変速軸１１
からの動力が副変速された状態でピニオン軸１４に伝達
され、後輪駆動をする構成になっており、この様にして
副変速機構りが形成されている。Further, a sub-transmission gear 11d is provided at the front end of the sub-transmission shaft 11- to rotate integrally therewith, and a sub-transmission shifter gear 14a is spline-fitted to a pinion shaft 14 that meshes with the differential gear section 13. has been done. By selectively meshing the sub-transmission shifter gear 14a with the sub-transmission gear 11d, the sub-transmission shaft 11
The power is transmitted to the pinion shaft 14 in a sub-shifted state to drive the rear wheels, thus forming a sub-transmission mechanism.
一方、前記動力取出し軸８の基端部には、スプライン嵌
合されたＰＴ○変速用のシフタギア８ａ、変速ギア４ａ
に常時噛合した自由回動自在な変速ギア８１）が設けら
れ、さらにトランスミッションケース２に設けられたピ
ン軸１５ａには中間ギア１５が自由回動自在に支持され
ているが、該中間ギア１５は実施例では最も前方側の変
速ギア４ａに常時噛合している。そして前側のシフタギ
ア８ａを中間ギア１５に噛合させた場合には、動力取出
し軸８は逆転回動することになるが、前後のシフタギア
８ａを変速ギア４ａに選択噛合させ、また後側シフタギ
ア８ａを変速ギア８ｂに選択噛合８−
させることによって、動力取出し軸８は変速された状態
での正転回動をするようになっており、この様にして動
力取出し軸周変速機構Ｅが形成されている。On the other hand, at the base end of the power take-off shaft 8, there is a shifter gear 8a for PT○ transmission fitted with a spline, and a transmission gear 4a.
A freely rotatable transmission gear 81) is provided which is always in mesh with the transmission case 2, and an intermediate gear 15 is freely rotatably supported on a pin shaft 15a provided in the transmission case 2. In the embodiment, it is always engaged with the forwardmost transmission gear 4a. When the front shifter gear 8a is engaged with the intermediate gear 15, the power take-off shaft 8 rotates in the reverse direction, but the front and rear shifter gears 8a are selectively engaged with the transmission gear 4a, and the rear shifter gear 8a is By selectively meshing the speed change gear 8b, the power take-off shaft 8 rotates in the forward direction in a gear-changed state, and in this way, a power take-off shaft circumferential speed change mechanism E is formed. .
さらに動力取出し軸８の中間部には前輪駆動軸６を変速
するための変速ギア機構Ｆが設けられている。Furthermore, a speed change gear mechanism F for changing the speed of the front wheel drive shaft 6 is provided at the intermediate portion of the power take-off shaft 8.
一方、１７は油圧ポンプであって、該油圧ポンプ１７は
トランスミッションケース２の一側（実施例では右側）
面に対向するよう並列して配され、そして油圧ポンプ１
７は、クラッチカバー２８のトランスミッションケース
２から側方に突出する部位に一体的に止着されており、
前記油圧ポンプ暉動軸の中間ギア５ａに油圧ポンプ入力
軸１７ａが一体的に嵌合連結することで連動連結されて
いる。On the other hand, 17 is a hydraulic pump, and the hydraulic pump 17 is on one side of the transmission case 2 (on the right side in the embodiment).
A hydraulic pump 1 is arranged in parallel to face the surface, and a hydraulic pump 1
7 is integrally fixed to a portion of the clutch cover 28 that protrudes laterally from the transmission case 2;
A hydraulic pump input shaft 17a is integrally fitted and connected to the intermediate gear 5a of the hydraulic pump displacement shaft.
叙述のごとく構成された本発明の実施例において、機体
の走行速度は、通常、主変速機構Ａ、副変速機構りによ
って必要な変速切換えがなされ、さらに前後進切換えは
前後進切換え機構Ｂによつて、また溝掘り作業等の牽引
負荷の大きい作業を行う場合には超低速切換え機構Ｃを
超低速側に切換え操作して超低速走行状態に切換えれば
良い。In the embodiment of the present invention configured as described above, the traveling speed of the aircraft is normally changed as necessary by the main transmission mechanism A and the auxiliary transmission mechanism, and the forward/reverse changeover is performed by the forward/reverse switching mechanism B. Furthermore, when performing work with a large traction load such as trench digging work, it is sufficient to switch the ultra-low speed switching mechanism C to the ultra-low speed side to switch to an ultra-low speed running state.
この様に超低速切換えを含めた走行変速ができるもので
あるが、超低速前進走行状態から後進走行状態に切換え
たとき、機体は超低速で後進走行することはない。つま
りこのものは、主変速軸９から副変速軸１１に至る動力
伝動経路において、該経路上手側に前後進切換え機構を
配し、そして後進切換え状態としたときは、主変速軸９
から中間軸１０を経由することなく、中間ギア１２を介
してそのまま副変速軸１１側に動力伝動をし、−方、前
進走行状態に切換えたときには中間軸１０から超低速切
換え機構Ｃを経由して副変速軸１１に動力伝動する構成
になっている。従って後進切換え状態にした場合、従来
のように超低速切換え機構Ｃを経由することなく、主変
速軸９から副変速軸１１への直接的な動力伝動がなされ
、もって超低速状態で後進走行することがない。この結
果、超低速走行状態で後進変速した場合に、従来のよう
にいちいち超低速切換えを解除して通常走行状態にする
必要がなく、作業性の改善が計れることになる。In this way, it is possible to change the traveling speed, including switching to very low speeds, but when switching from the very low speed forward traveling state to the reverse traveling state, the aircraft does not travel backward at very low speed. In other words, in the power transmission path from the main transmission shaft 9 to the auxiliary transmission shaft 11, a forward/reverse switching mechanism is disposed on the upper side of the path, and when the reverse switching state is established, the main transmission shaft 9
The power is transmitted directly to the auxiliary transmission shaft 11 side via the intermediate gear 12 without passing through the intermediate shaft 10, and when switching to the forward running state, the power is transmitted from the intermediate shaft 10 via the ultra-low speed switching mechanism C. The configuration is such that power is transmitted to the sub-transmission shaft 11 through the transmission. Therefore, when switching to reverse, power is transmitted directly from the main transmission shaft 9 to the auxiliary transmission shaft 11 without passing through the ultra-low speed switching mechanism C as in the conventional case, and the vehicle travels in reverse at an ultra-low speed. Never. As a result, when the reverse gear is changed while the vehicle is running at a very low speed, there is no need to cancel the super low speed switch each time to return to the normal running state, as is the case in the past, and workability can be improved.
しかもこのものでは、超低速切換え機構がデファレンシ
ャルギア部１３の後方に配設されているため、トランス
ミッションケース２内後部のデッドスペースの有効利用
ができる。そして超低速切換え機構は、大きな減速比を
必要とするため、大きなギア径の超低速用ギアｌｌｂを
用いなければならない。従って超低速切換え機構を、各
種変速機構が複雑に配設されるデファレンシャルギア部
１３の前方に配した場合、超低速切換え用の大径ギアが
あることを配慮して隣接する各軸との軸間距離を大きく
する必要がなく、中間軸１ｏと副変速軸１１との両軸間
の間隔のみを互いに噛合するギアに合わせれば良く、も
って各軸間の間隔を、超低速切換え用大径ギアのギア径
を殆ど考慮することなく設定できて、トランスミッショ
ンをコンパクト化できることになる。Moreover, in this case, since the ultra-low speed switching mechanism is disposed behind the differential gear section 13, the dead space at the rear inside the transmission case 2 can be effectively utilized. Since the ultra-low speed switching mechanism requires a large reduction ratio, it is necessary to use an ultra-low speed gear llb with a large gear diameter. Therefore, when the ultra-low speed switching mechanism is placed in front of the differential gear section 13 where various speed change mechanisms are arranged in a complicated manner, it is necessary to take into account the presence of large-diameter gears for ultra-low speed switching. There is no need to increase the distance between the two shafts, and it is only necessary to match the distance between the intermediate shaft 1o and the sub-transmission shaft 11 to the gears that mesh with each other. The gear diameter can be set without much consideration, and the transmission can be made more compact.
［作用効果］
１１
以上要するに、本発明は叙述の如く構成されたものであ
るから、超低速状態での作業走行ができるものであるが
、超低速前進状態から後進走行状態に切換えた場合に、
主変速軸から、超低速切換え機構が形成される中間軸側
を経由することなく、直接的に副変速軸側に後進状態で
の動力伝動がなされることとなり、従って後進切換えを
した場合に、超低速機構は超低切換え速状態のままで、
通常変速状態での後進走行ができることとなって、従来
のようにいちいち超低速切換え機構を非超低速状態に切
換える必要がなく、作業性、操作性の向上が計れること
になる。[Operations and Effects] 11 In short, since the present invention is configured as described above, it is possible to perform work at an extremely low speed, but when switching from an extremely low speed forward state to a reverse traveling state,
Power is transmitted directly from the main transmission shaft to the auxiliary transmission shaft in the reverse state without passing through the intermediate shaft where the ultra-low speed switching mechanism is formed. Therefore, when switching to reverse, The ultra-low speed mechanism remains in the ultra-low switching speed state,
Since it is possible to travel backwards in the normal gear change state, there is no need to switch the ultra-low speed switching mechanism to a non-ultra-low speed state each time as in the past, and workability and operability can be improved.
図面は、本発明に係る超低速切換え機構を備えたトラン
スミッション装置の実施例を示したものであって、第１
図は農用トラクタの全体側面図、第２図は動力伝動系を
示す伝動回路図、第３図はトランスミッション機構の展
開断面図、第４図はトランスミッションケースの正面図
、第５図は同上平面断面図である。
１２−
図中、１は走行機体、２はトランスミッションケース、
９は主変速軸、１０は中間軸、１１は副変速軸、Ｂは前
後進切換え機構、Ｃは超低速切換え機構である。The drawings show an embodiment of a transmission device equipped with an ultra-low speed switching mechanism according to the present invention.
The figure is an overall side view of the agricultural tractor, Figure 2 is a power transmission circuit diagram showing the power transmission system, Figure 3 is an exploded sectional view of the transmission mechanism, Figure 4 is a front view of the transmission case, and Figure 5 is a cross-sectional plan view of the same. It is a diagram. 12- In the figure, 1 is the traveling aircraft, 2 is the transmission case,
9 is a main transmission shaft, 10 is an intermediate shaft, 11 is an auxiliary transmission shaft, B is a forward/reverse switching mechanism, and C is a very low speed switching mechanism.
Claims (1)
、走行駆動輪用ピニオン軸側に連動連結される副変速軸
に伝達する動力伝動経路中に、前後進切換え機構と超低
速切換え機構とを備えるに、前後進切換え機構は、主変
速軸、該主変速軸と同心状に設けた中間軸、および上記
副変速軸との間に設けられ、前進切換え状態では主変速
軸から中間軸側に動力伝動し、後進切換え状態では主変
速軸から副変速軸側に動力伝動するようギア噛合の選択
をする変速ギア機構で構成する一方、超低速切換え機構
は、前記中間軸と副変速軸との間に設けられ、超低速状
態と非超低速状態とに切換えられるようギア噛合の選択
をする変速ギア機構で構成して、前後進切換え機構を、
前進切換え状態としたときには主変速軸から中間軸、超
低速切換え機構を経由して副変速軸側に動力伝動をする
が、後進切換え状態としたときには中間軸、超低速切換
え機構を経由することなく主変速軸から副変速軸側に直
接的に動力伝動する構成にしたことを特徴とする超低速
切換え機構を備えたトランスミッション装置。A forward/reverse switching mechanism and an ultra-low speed switching mechanism are included in the power transmission path that transmits the power input to the main transmission shaft, which is interlocked to the engine side, to the auxiliary transmission shaft, which is interlocked to the driving wheel pinion shaft side. The forward/reverse switching mechanism is provided between a main transmission shaft, an intermediate shaft provided concentrically with the main transmission shaft, and the sub-transmission shaft, and in the forward switching state, the forward/reverse switching mechanism is located between the main transmission shaft and the intermediate shaft. The ultra-low speed switching mechanism is configured with a transmission gear mechanism that selects gear engagement so that power is transmitted from the main transmission shaft to the auxiliary transmission shaft in the reverse switching state. The forward/reverse switching mechanism is configured with a speed change gear mechanism that is provided between
When in the forward switching state, power is transmitted from the main transmission shaft to the auxiliary transmission shaft via the intermediate shaft and ultra-low speed switching mechanism, but when in the reverse switching state, power is transmitted without passing through the intermediate shaft and the ultra-low speed switching mechanism. A transmission device equipped with an ultra-low speed switching mechanism characterized by a configuration in which power is directly transmitted from a main transmission shaft to an auxiliary transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2031146A JPH0826923B2 (en) | 1990-02-09 | 1990-02-09 | Transmission device with ultra-low speed switching mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2031146A JPH0826923B2 (en) | 1990-02-09 | 1990-02-09 | Transmission device with ultra-low speed switching mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03234952A true JPH03234952A (en) | 1991-10-18 |
| JPH0826923B2 JPH0826923B2 (en) | 1996-03-21 |
Family
ID=12323300
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2031146A Expired - Lifetime JPH0826923B2 (en) | 1990-02-09 | 1990-02-09 | Transmission device with ultra-low speed switching mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0826923B2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5989228A (en) * | 1982-11-12 | 1984-05-23 | Iseki & Co Ltd | Travel speed change gear for tractor |
-
1990
- 1990-02-09 JP JP2031146A patent/JPH0826923B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5989228A (en) * | 1982-11-12 | 1984-05-23 | Iseki & Co Ltd | Travel speed change gear for tractor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0826923B2 (en) | 1996-03-21 |
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