JPH0621614B2 - Transmission for traveling of work vehicle - Google Patents
Transmission for traveling of work vehicleInfo
- Publication number
- JPH0621614B2 JPH0621614B2 JP61047102A JP4710286A JPH0621614B2 JP H0621614 B2 JPH0621614 B2 JP H0621614B2 JP 61047102 A JP61047102 A JP 61047102A JP 4710286 A JP4710286 A JP 4710286A JP H0621614 B2 JPH0621614 B2 JP H0621614B2
- Authority
- JP
- Japan
- Prior art keywords
- transmission
- shaft
- output
- traveling
- transmission mechanism
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Gear-Shifting Mechanisms (AREA)
- Structure Of Transmissions (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、主変速機構及び副変速機構を設けた作業車の
走行用伝動装置に関する。Description: TECHNICAL FIELD The present invention relates to a power transmission device for traveling of a work vehicle provided with a main transmission mechanism and an auxiliary transmission mechanism.
かかる作業車の走行用伝動装置において、従来では、主
変速機構により変速された動力すべてを副変速機構を介
して走行装置に出力するようにしていた。In such a traveling transmission device for a work vehicle, conventionally, all the power changed by the main transmission mechanism is output to the traveling device via the auxiliary transmission mechanism.
ところで、一つの作業地での作業を終了して、次の作業
地へ作業車を迅速に移動させたい場合等に主変速機構を
高速側に操作して前進最高速度で作業車を走行させるこ
とになる。By the way, when you want to move the work vehicle to the next work place quickly after finishing work at one work place, operate the main speed change mechanism to the high speed side to drive the work vehicle at the maximum forward speed. become.
しかしながら、上記従来構成では、主変速機構を高速側
に操作して前進最高速度に変速操作しているにも拘ら
ず、例えば副変速機構が低速側に操作されていると、前
進最高速度に変速することができないため、その副変速
機構を高速側へ切換え操作しなければならず、前進最高
速度に変速するための操作が煩わしいものであった。However, in the above-mentioned conventional configuration, when the main transmission mechanism is operated to the high speed side to perform the shift operation to the maximum forward speed, when the auxiliary transmission mechanism is operated to the low speed side, the maximum forward speed is changed. Therefore, the sub-transmission mechanism must be switched to the high speed side, and the operation for shifting to the maximum forward speed is troublesome.
本発明の目的は、副変速機構が低速側に操作されている
場合であえっても、主変速機構を操作するだけで前進最
高速度に変速することができるようにするとともに、そ
のための構造を簡単な構成で得ることにある。An object of the present invention is to make it possible to shift to the maximum forward speed only by operating the main transmission mechanism even when the auxiliary transmission mechanism is operated to the low speed side, and to simplify the structure for that. It is to obtain with a simple configuration.
本発明の特徴構成は、主変速装置及び副変速機構を備
え、それらの変速機構での変速後のエンジン出力を後車
輪側へ導くための走行用出力軸と、前車輪側に導くため
の前輪用伝動軸とを設けた作業車の走行用伝動装置にお
いて、前記主変速機構の前進最高速度を除く速度の出力
部を前記副変速機構に連動連結し、前記主変速機構の前
進最高速度の出力部を、前記副変速機構の伝動上手側か
ら前記前輪用伝動軸を介して、副変速機構の伝動下手側
に迂回させて前記走行用出力軸に連動連結した点にあ
る。A characteristic configuration of the present invention includes a main transmission device and an auxiliary transmission mechanism, a traveling output shaft for guiding engine output after gear shifting by the transmission mechanisms to the rear wheel side, and a front wheel for guiding to the front wheel side. In a transmission for traveling of a work vehicle provided with a power transmission shaft, an output unit of speeds other than the maximum forward speed of the main speed change mechanism is interlocked with the auxiliary speed change mechanism to output the maximum forward speed of the main speed change mechanism. The part is detoured from the transmission upper side of the auxiliary transmission mechanism to the transmission lower side of the auxiliary transmission mechanism via the front wheel transmission shaft, and is linked to the traveling output shaft.
すなわち、主変速機構を前進最高速度を除く速度に変速
操作した出力は、副変速機構を介して走行装置に伝達さ
れるのである。又、主変速機構を前進最高速度に変速操
作した出力は直接走行装置に伝達されるのである。That is, the output obtained by shifting the main transmission mechanism to a speed other than the maximum forward speed is transmitted to the traveling device via the auxiliary transmission mechanism. Further, the output obtained by shifting the main transmission mechanism to the maximum forward speed is directly transmitted to the traveling device.
したがって、主変速機構を前進最高速度にするための変
速操作を行なうだけで、副変速機構の変速操作状態に拘
らず、前進最高速度に変速することができ、操作性の向
上を図ることができるようになった。Therefore, only by performing the gear shifting operation to bring the main transmission mechanism to the maximum forward speed, it is possible to shift to the maximum forward speed regardless of the gear shift operation state of the auxiliary transmission mechanism, and the operability can be improved. It became so.
また、前進最高速を走行用出力部に伝達する際に副変速
機構を迂回させるための手段として、前輪駆動のために
備えられている前輪用伝動軸が利用されるものであるた
め、迂回伝動させるための新たな伝動軸の付加などを必
要としない。したがって、構造上の複雑化や配設スペー
スを確保する必要性などの不利を招くことなく、簡単な
構成で前述の操作性のよい走行用伝動装置を得られる効
果がある。Further, since the front wheel drive shaft provided for driving the front wheels is used as a means for bypassing the auxiliary transmission mechanism when transmitting the maximum forward speed to the traveling output section, the bypass transmission is used. There is no need to add a new transmission shaft to do this. Therefore, there is an effect that the above-described traveling transmission device with a simple structure can be obtained with a simple structure without causing disadvantages such as complication of the structure and necessity of securing an installation space.
作業車の一例である農用トラクタの走行用伝動装置につ
いて説明する。A traveling transmission device of an agricultural tractor, which is an example of a work vehicle, will be described.
第1図に示すように、エンジン(図示せず)からの動力
が伝動される連結作業装置への伝動系の駆動側伝動軸
(1)と従動側伝動軸(2)との間に湿式の摩擦クラッチ(3)
を設けると共に、この従動側伝動軸(2)に伝動された動
力をギヤ減速機構(4)を介して動力取出し軸としてのP
TO軸(5)に伝動すべく構成すると共に、前記従動側伝
動軸(2)にライブ・ニュートラル・グランドPTO伝動
状態を現出する切換ギヤ(6)を設けてPTO伝動系を構
成してある。As shown in FIG. 1, a drive side transmission shaft of a transmission system to a connecting work device to which power from an engine (not shown) is transmitted.
Wet friction clutch (3) between (1) and driven shaft (2)
And the power transmitted to the driven side transmission shaft (2) is transmitted through the gear reduction mechanism (4) as a power take-off shaft.
A PTO transmission system is configured by transmitting the power to the TO shaft (5) and providing a switching gear (6) for displaying the live neutral ground PTO transmission state on the driven side transmission shaft (2). .
次に、走行伝動系について説明すれば、前記駆動側伝動
軸(1)の伝動上手側に走行用第1伝動軸(7)を駆動側伝動
軸に対して相対回転自在に外嵌し、この走行用第1伝動
軸(7)を伝動上手側伝動軸(7A)と伝動下手側伝動軸(7B)
とから構成すると共に、これら伝動軸(7A),(7B)同志間
に摩擦多板式油圧クラッチを介した遊星ギヤ式高低速切
換装置(8)(いわゆるデユアル変速機構と呼ばれるもの
で、高速に対して25%の速度減速を行なうもの)を設
けると共に、前記伝動下手側伝動軸(7B)と平行に架設さ
れた走行用第2伝動軸(9)との間に前進8段後進1段に
変速可能なシンクロメツシユ式ギヤ変速装置を備えた主
変速機構(10)を設けてある。Next, the traveling transmission system will be described. A traveling first transmission shaft (7) is fitted on the transmission side of the drive side transmission shaft (1) so as to be rotatable relative to the drive side transmission shaft. Transmission 1st transmission shaft (7) for transmission Transmission upper transmission shaft (7A) and lower transmission shaft (7B)
And a planetary gear type high / low speed switching device (8) (a so-called dual transmission mechanism, which is a so-called dual speed change mechanism) between these transmission shafts (7A) and (7B) via a friction multi-plate hydraulic clutch between them. 25% speed deceleration) is provided, and 8 forward speeds and 1 reverse speed are provided between the second lower transmission shaft (7B) and the traveling second transmission shaft (9) installed in parallel. A main transmission mechanism (10) having a possible synchronized mesh type gear transmission is provided.
前記主変速機構(10)の前進最高速度を除く速度の出力部
としての走行用第2伝動軸(9)を副変速機構12に連動連
結すると共に、この伝動軸(9)に対して相対回転自在な
走行用第3伝動軸(11)を突合せ対向配置させてある。A second drive shaft for traveling (9) as an output unit of speeds other than the maximum forward speed of the main speed change mechanism (10) is linked to the auxiliary speed change mechanism 12 and is rotated relative to the drive shaft (9). A freely traveling third transmission shaft (11) is butted and opposed.
前記副変速機構(12)について説明すれば、前記第2伝動
軸(9)に固着の出力ギヤ(13)と前記第3伝動軸(11)にク
ラツチスリーブ(14)を介して遊嵌される入力ギヤ(15)夫
々に咬合する中継ギヤ(16),(17)を、第2伝動軸(9)及
び第3伝動軸(11)に対して平行に架設された前輪用伝動
軸(18)に遊嵌して減速機構(19)を構成して、クラツチス
リーブ(14)の切換操作によって、第2伝動軸(9)を第3
伝動軸(11)に直結する高速伝動状態と第2伝動軸(9)の
出力を減速機構(19)を介して第3伝動軸(11)に伝動する
低速伝動状態とを切換可能に構成してある。Explaining the sub-transmission mechanism (12), the output gear (13) fixed to the second transmission shaft (9) and the third transmission shaft (11) are loosely fitted to each other via a clutch sleeve (14). Transmission gears (18) for the front wheels, in which relay gears (16), (17) that mesh with the input gears (15) are installed in parallel with the second transmission shaft (9) and the third transmission shaft (11) The reduction gear mechanism (19) is loosely fitted to the second transmission shaft (9) by switching the clutch sleeve (14).
It is configured to be switchable between a high-speed transmission state in which it is directly connected to the transmission shaft (11) and a low-speed transmission state in which the output of the second transmission shaft (9) is transmitted to the third transmission shaft (11) via the reduction mechanism (19). There is.
そして、前記走行用第3伝動軸(11)の後端に、走行装置
としての後輪デフ装置(20)へ動力を伝動するベベルギヤ
(21)を外嵌着した走行用出力軸(22)を配置すると共に、
前記第3伝動軸(11)と前記出力軸(22)との間に高低2段
に変速可能な超減速機構(23)を設けてある。この超減速
機構(23)を構成するに、前記第3伝動軸(11)に出力ギヤ
(24)を且つ前記出力軸(22)に入力ギヤ(25)兼用のクラツ
チスリーブ(26)を夫々設けると共に、両ギヤ(24),(25)
に咬合する中継用ギヤ(27),(28)をミツシヨンケース(2
9)側に支承された軸(30)に設けてある。A bevel gear for transmitting power to a rear wheel differential device (20) as a traveling device is provided at a rear end of the traveling third transmission shaft (11).
While arranging the traveling output shaft (22) with (21) fitted on the outside,
An ultra-reduction mechanism (23) is provided between the third transmission shaft (11) and the output shaft (22) so that the speed can be changed between high and low. This super reduction mechanism (23) comprises an output gear on the third transmission shaft (11).
(24) and the output shaft (22) is provided with a clutch sleeve (26) also serving as an input gear (25), and both gears (24), (25)
Install the relay gears (27) and (28) that mesh with the mesh case (2
It is provided on the shaft (30) supported on the 9) side.
このようにして、主変速機構(10)で変速された前進最高
速度を除く速度の出力を前記副変速機構(12)及び前記超
減速機構(23)を介して前記後輪デフ装置(20)に入力する
と共に、前記前輪用伝動軸(18)にギヤ機構(31)を介して
伝達し、その伝動軸(18)に伝達された出力を前輪用出力
軸(32)に減速機構(33)を介して伝達するようにして、後
輪と同期した出力を前輪に伝達すべく構成してある。そ
して、前記主変速機構(10)で変速された前進最高速度の
出力を前記副変速機構(12)を迂回させて前記後輪デフ装
置(20)及び前輪デフ装置(図示せず)に伝達するように
してある。記述すれば、第2図に示すように、前記主変
速機構(10)の前進最高速度の出力部としてのオーバート
ップ用ギヤ(34)を前記前輪用伝動軸(18)に遊嵌すると共
に、このギヤ(34)に伝達される出力をシンクロメツシユ
式で前記伝動軸(18)に伝達することを断続可能に構成し
て、第4図に示す如く、主変速切換レバー(35)をオーバ
ートツプ位置に操作することにより走行用第1伝動軸
(7)からの動力を前記副変速機構(12)を迂回して前輪用
伝動軸(18)から前輪用出力軸(32)及び走行用出力軸(22)
へ伝達するように構成してある。In this way, the output of speeds other than the maximum forward speed changed by the main transmission mechanism (10) is output through the auxiliary transmission mechanism (12) and the super speed reduction mechanism (23) to the rear wheel differential device (20). Input to the front wheel transmission shaft (18) and transmitted to the front wheel output shaft (18) via the gear mechanism (31), and the output transmitted to the transmission shaft (18) is output to the front wheel output shaft (32) to the reduction mechanism (33). The output synchronized with the rear wheels is transmitted to the front wheels. Then, the output of the maximum forward speed changed by the main transmission mechanism (10) is bypassed to the sub transmission mechanism (12) and transmitted to the rear wheel differential device (20) and the front wheel differential device (not shown). Is done. More specifically, as shown in FIG. 2, an overtop gear (34) as an output portion of the maximum forward speed of the main transmission mechanism (10) is loosely fitted to the front wheel transmission shaft (18), and The transmission of the output transmitted to the gear (34) to the transmission shaft (18) by the synchro mesh type is constructed so as to be intermittent so that the main gear changeover lever (35) is overdriven as shown in FIG. The first drive shaft for traveling by operating to the top position
The power from (7) bypasses the auxiliary transmission mechanism (12) and is transmitted from the front wheel transmission shaft (18) to the front wheel output shaft (32) and the traveling output shaft (22).
It is configured to transmit to.
尚、前記切換ギヤ(6)を操作する操作レバー(36)の下部
にその切換ギヤ(6)をニユートラルPTOからライプP
TOへ又はライプPTOからニユートラルPTOへ切換
え操作する場合にのみ前記摩擦クラツチ(3)を断続操作
するための電磁バルブ(37)操作用リミットスイツチ(38)
を設けてある。つまり、切換ギヤ(6)をニユートラルP
TOからライブPTOへ操作する場合に操作レバー(36)
の初期操作に伴つて操作レバー(36)の下端部に形成の突
部(36A) に接当することにより、リミツトスイツチ(38)
をON状態にして、電磁バルブ(37)を切換えて摩擦クラ
ツチ(3)を切り操作し、前記操作レバー(36)をさらに操
作してライブPTOへ切換えるに従つてリミツトスイツ
チ(38)をOFF状態にして前記バルブ(37)をスプリング
(39)の付勢力によりドレン位置に切換えて摩擦クラツチ
(3)を入り操作するようにして、ギヤ同志の咬合を咬合
部の損傷を招くことなく行なえるようにしてある。又、
前記切換ギヤ(6)をライブPTOからニユートラルPT
Oへ操作する場合には上記同様に摩擦クラッチ(3)を切
り操作してからギヤ同志の咬合を解除するようにして、
切換ギヤ(6)を操作する操作レバー(36)の操作力の軽減
化を図るようにしてある。In addition, the switching gear (6) is provided below the operation lever (36) for operating the switching gear (6) from the neutral PTO to the drive lever (36).
Electromagnetic valve (37) for operating the friction clutch (3) intermittently only when switching to the TO or from the leap PTO to the neutral PTO The limit switch (38) for operating
Is provided. In other words, switch gear (6) to neutral P
Operation lever (36) when operating from TO to live PTO
By contacting the projection (36A) formed on the lower end of the operation lever (36) with the initial operation of, the limit switch (38)
Is turned on, the electromagnetic valve (37) is switched, the friction clutch (3) is turned off, and the operating lever (36) is further operated to switch to the live PTO, and the limit switch (38) is turned off. Spring the valve (37)
The friction clutch is switched to the drain position by the urging force of (39).
By operating (3), the gears can be engaged with each other without damaging the occlusal part. or,
Change the switching gear (6) from live PTO to neutral PT
When operating to O, disengage the friction clutch (3) in the same manner as above and then release the engagement of the gears,
The operating force of the operating lever (36) for operating the switching gear (6) is reduced.
尚、第1図中(40)は、2輪(後輪)駆動と4輪駆動とを
切換えるためのクラツチである。Incidentally, reference numeral (40) in FIG. 1 denotes a clutch for switching between two-wheel (rear wheel) drive and four-wheel drive.
図面は本発明に係る作業車の走行用伝動装置の実施例を
示し、第1図はミツシヨンケース内の伝動系統図、第2
図は主変速機構の断面図、第3図は切換ギヤの切換状態
を示す概略図、第4図は変速切換表示部の平面図であ
る。 (9),(34)……出力部、(10)……主変速機構、(12)……
副変速機構、(18)……前輪用伝動軸、(22)……走行用出
力部、(20)……走行装置。The drawings show an embodiment of a transmission system for traveling of a work vehicle according to the present invention, and FIG. 1 is a transmission system diagram in a mesh case, and FIG.
FIG. 4 is a sectional view of the main transmission mechanism, FIG. 3 is a schematic view showing a switching state of a switching gear, and FIG. 4 is a plan view of a shift switching display portion. (9), (34) …… Output section, (10) …… Main transmission mechanism, (12) ……
Auxiliary speed change mechanism, (18) ... front wheel transmission shaft, (22) ... traveling output section, (20) ... traveling device.
Claims (1)
え、それらの変速機構(10,12)での変速後のエンジン出
力を後車輪側へ導くための走行用出力軸(22)と、前車輪
側に導くための前輪用伝動軸(18)とを設けた作業車の走
行用伝動装置であって、 前記主変速機構(10)の前進最高速度を除く速度の出力部
(9)を前記副変速機構(12)に連動連結し、 前記主変速機構(10)の前進最高速度の出力部(34)を、前
記副変速機構(12)の伝動上手側から前記前輪用伝動軸(1
8)を介して、副変速機構(12)の伝動下手側に迂回させて
前記走行用出力軸(22)に連動連結してある作業車の走行
用伝動装置。1. A traveling output shaft (1) comprising a main transmission device (10) and an auxiliary transmission mechanism (12), for guiding engine output after shifting by these transmission mechanisms (10, 12) to the rear wheel side. 22) and a front wheel transmission shaft (18) for guiding to the front wheel side, which is a work transmission transmission device for a working vehicle, wherein a speed output unit other than the maximum forward speed of the main transmission mechanism (10) is output.
(9) is linked to the sub-transmission mechanism (12), and the maximum forward speed output section (34) of the main transmission mechanism (10) is connected to the front wheel from the transmission side of the sub-transmission mechanism (12). Transmission shaft (1
A work transmission device for a working vehicle, which is circumvented to the transmission lower side of the auxiliary transmission mechanism (12) via 8) and is interlockingly connected to the travel output shaft (22).
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP61047102A JPH0621614B2 (en) | 1986-03-03 | 1986-03-03 | Transmission for traveling of work vehicle |
AU64391/86A AU572741B2 (en) | 1986-03-03 | 1986-10-24 | Transmission for working vehicle with an overtop drive |
NZ218090A NZ218090A (en) | 1986-03-03 | 1986-10-28 | Vehicle transmission with extra-high top gear and bypass of auxiliary reduction |
ES8602853A ES2003443A6 (en) | 1986-03-03 | 1986-10-31 | Transmission for working vehicle having overtop drive |
US06/928,561 US4750580A (en) | 1986-03-03 | 1986-11-10 | Transmission for working vehicle having overtop drive |
DE19863639097 DE3639097A1 (en) | 1986-03-03 | 1986-11-15 | TRANSMISSION ARRANGEMENT FOR A HIGH SPEED WORK VEHICLE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP61047102A JPH0621614B2 (en) | 1986-03-03 | 1986-03-03 | Transmission for traveling of work vehicle |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS62204038A JPS62204038A (en) | 1987-09-08 |
JPH0621614B2 true JPH0621614B2 (en) | 1994-03-23 |
Family
ID=12765814
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP61047102A Expired - Lifetime JPH0621614B2 (en) | 1986-03-03 | 1986-03-03 | Transmission for traveling of work vehicle |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0621614B2 (en) |
-
1986
- 1986-03-03 JP JP61047102A patent/JPH0621614B2/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JPS62204038A (en) | 1987-09-08 |
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