JPH0121233Y2 - - Google Patents
Info
- Publication number
- JPH0121233Y2 JPH0121233Y2 JP19657883U JP19657883U JPH0121233Y2 JP H0121233 Y2 JPH0121233 Y2 JP H0121233Y2 JP 19657883 U JP19657883 U JP 19657883U JP 19657883 U JP19657883 U JP 19657883U JP H0121233 Y2 JPH0121233 Y2 JP H0121233Y2
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- shaft
- fluid pressure
- operated
- intermediate shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012530 fluid Substances 0.000 claims description 18
- 230000005540 biological transmission Effects 0.000 claims description 16
- 241000239290 Araneae Species 0.000 claims description 9
- 230000007246 mechanism Effects 0.000 claims description 9
- 230000033001 locomotion Effects 0.000 claims description 3
- 230000008859 change Effects 0.000 description 4
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000009412 basement excavation Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Landscapes
- Gear-Shifting Mechanisms (AREA)
- Arrangement Of Transmissions (AREA)
- Arrangement Or Mounting Of Control Devices For Change-Speed Gearing (AREA)
Description
本考案は、入力軸、第1中間軸及び第2中間軸
を同芯状に配置し、前記第1中間軸に後進用筒軸
をかつ前記第2中間軸に出力用筒軸を夫々相対回
転自在に取付け、スパイダーの両端を前記両筒軸
に各別にかつ相対回転自在に取付け、前記入力軸
と第1中間軸の間に流体圧操作式第1クラツチ
を、前記入力軸と後進用筒軸の間に流体圧操作式
第2クラツチを、かつ、前記第2中間軸と出力用
筒軸の間に流体圧操作式第3クラツチを夫々設
け、前記第1及び第2中間軸に各別に固着した第
1及び第2外歯ギヤに各別に常時咬合する第3及
び第4外歯ギヤを前記スパイダーに相対回転自在
に取付け、前記両筒軸に各別に固着した第5及び
第6外歯ギヤに各別に咬合すると共に前記第3及
び第4外歯ギヤに各別に咬合する第7及び第8外
歯ギヤを前記スパイダーに相対回転自在に取付
け、前記後進用筒軸に対する流体圧操作式第1ブ
レーキ、前記第3外歯ギヤに常時咬合する内歯ギ
ヤに対する流体圧操作式第2ブレーキ、及び、前
記第2中間軸に対する流体圧操作式第3ブレーキ
を設け、前進状態において前記第1クラツチを入
り状態に維持させて前記第2、第3クラツチ及び
前記第1ないし第3ブレーキを選択操作し、且
つ、後進状態において前記第2クラツチを入り状
態に維持させて前記第3クラツチ及び前記第2、
第3ブレーキを選択操作する弁機構を設けた流体
圧操作式走行変速装置に関する。
かかる走行変速装置において、変速操作のため
の弁機構を構成するに、従来、単に1つの制御弁
を設けるようにしているが、この場合、一方向に
沿つて往復移動させる変速レバーにて、制御弁に
おける一方向に沿つて往復移動自在なスプールを
操作する点に起因して、変速操作が行ない難い不
利があると共に、誤操作し易い不利があり、改善
の余地があつた。
さらに詳述すれば、変速レバーにおいては、隣
り合う変速位置の間隔を大にして各変速位置を分
り易くすることが望まれるものとなるが、上記従
来構造の場合において隣り合う変速位置の間隔を
大にすると、変速レバーの操作範囲が大きくなつ
て、作業者が手を大きく伸ばしながら変速レバー
を操作しなければならない不利があり、これを回
避すべく、隣り合う変速位置の間隔を小にする
と、変速位置が分り難いものとなつて誤操作を生
じるものであつた。
本考案は、上記実状に鑑みて為されたものであ
つて、その目的は、本来構成を有効利用した簡単
な改造によつて、操作性の向上を図る点にある。
本考案による流体圧操作式走行変速装置の特徴
構成は、前記弁機構を構成するに、前記第1及び
第2クラツチに択一的に流体圧を供給する前後進
切換用第1制御弁、並びに、前記第2、第3クラ
ツチ及び前記第1ないし第3ブレーキに選択的に
流体圧を供給する速度設定用第2制御弁を設け、
前記第1、第2制御弁を、シヤトル弁を介して前
記第2クラツチに並列接続すると共に、異なる2
方向に操作自在な1つの変速レバーを、一方向の
操作で前記第1制御弁を、且つ、他方向の操作で
前記第2制御弁を操作するように前記両制御弁に
連係した点にあり、その作用効果の次の通りであ
る。
すなわち、前進状態では第1クラツチが、且
つ、後進状態では第2クラツチが入り状態に維持
される点に着目して、前後進切換用の第1制御弁
と速度設定用の第2制御弁とを各別に設けるよう
にし、そして、前後進状態のいずれにおいても入
り操作される第2クラツチに供給される流体が、
前進状態において第1制御弁を通して排油される
ことを、且つ、後進状態において第2制御弁を通
して排油されることを阻止すべく、シヤトル弁を
用いて第2クラツチを第1、第2制御弁に接続さ
せることによつて、第1、第2制御弁の操作によ
り所定の変速を行なえるようにし、しかも、1つ
の変速レバーを異なる2方向に操作しながら2つ
の制御弁を操作できるようにしてある。
従つて、1つの変速レバーにて変速する利点を
活かしながらも、異なる2方向夫々に沿う変速レ
バーの操作ストロークを極力小さくした状態で、
各方向夫々における隣り合う変速位置の間隔を充
分大きくすることができるのであり、もつて、多
段変速を行なわせながらも変速レバーを良好に操
作させることができるようになつた。
次に本考案の実施例を例示図に基いて詳述す
る。
第1図に示すように、左右一対の前車輪1を備
えた前部車体2と、左右一対の後車輪3を備えた
後部車体4とを、縦軸芯P周りで相対揺動自在に
連結し、前部車体2に昇降操作自在なフロントロ
ーダー5を装備すると共に、後部車体4に搭乗運
転部6、原動部7、及び、バツクホウ装置8を装
備し、そして、前後両車体2,4に亘つて架設し
た油圧シリンダ9によりステアリングハンドル6
aの操作量に応じた量だけ前後両車体2,4を相
対駆動揺動させて車体操向を行なうように構成す
ると共に、原動部7においてエンジン10に連動
連結した走行用ミツシヨンケース11からの変速
動力を前車輪1及び後車輪3に夫々伝達するよう
に構成し、もつて、土砂等の運搬作業並びに掘削
作業を行なう土工車を構成してある。
前記走行用ミツシヨンケース11における変速
構造を構成するに、第2図、及び、第3図に示す
ように、入力軸12、第1中間軸13、及び、第
2中間軸14を同芯状に配置し、第1中間軸13
に後進用筒軸15を、かつ、第2中間軸14に出
力用筒軸16を夫々相対回転自在に取付け、スパ
イダー17の両端側円盤状部材17a,17bを
両筒軸15,16に各別に夫々相対回転自在に取
付け、入力軸12と第1中間軸13の間に多板型
の第1伝動クラツチ18を、入力軸12と後進用
筒軸15との間に多板型の第2伝動クラツチ19
を、かつ、第2中間軸14と出力用筒軸16との
間に第3伝動クラツチ20を夫々設け、第1、第
2中間軸13,14に各別に取付けた第1、第2
ギヤG1,G2に各別に常時咬合する第3、第4ギ
ヤG3,G4をスパイダー17に相対回転自在に取
付け、両筒軸15,16に各別に取付けた第5、
第6ギヤG5,G6に各別に咬合すると共に第3、
第4ギヤG3,G4に各別に咬合する第7、第8ギ
ヤG7,G8をスパイダー17に相対回転自在に取
付け、後進用筒軸15をケース11に固定するた
めの多板型第1ブレーキ21、第3ギヤG3に常
時咬合する内歯ギヤGFをケース11に固定する
ための多板型第2ブレーキ22、及び、第2中間
軸14をケース11に固定するための多板型第3
ブレーキ23を設け、さらに、入力軸12を走行
クラツチ24及びギヤ連動機構を介してエンジン
10に連動連結し、かつ、出力用筒軸16をギヤ
連動機構を介して前後車輪1,3に対する出力軸
25に連動連結してある。そして、各伝動クラツ
チ18〜23に伝動切り状態側に常時付勢した状
態で付設するクラツチ操作用油圧シリンダ部18
a〜23aに対して油圧ポンプ26からの圧油を
選択供給する弁機構を設け、もつて、前進5段
F1〜F5、後進2段R1,R2、及び、変速中立状態
Nに切換自在に構成してある。
さらに詳述すると、前進状態においては、第1
クラツチ18を入り状態に維持させて第2、第3
クラツチ19,20及び第1ないし第3ブレーキ
21,22,23を選択操作し、且つ、後進状態
においては、第2クラツチ19を入り状態に維持
させて第3クラツチ20及び第2、第3ブレーキ
22,23を選択操作することになる。そして、
次表に各変速状態夫々における圧油供給状態を示
してある。但し、(〇)は圧油供給を、且つ、
(×)は排油を示すものである。
In the present invention, an input shaft, a first intermediate shaft, and a second intermediate shaft are arranged concentrically, and a reverse cylinder shaft is provided on the first intermediate shaft, and an output cylinder shaft is rotated relative to the second intermediate shaft. A first hydraulic clutch is mounted between the input shaft and the first intermediate shaft, and a fluid pressure operated first clutch is connected between the input shaft and the reverse cylinder shaft. A fluid pressure operated second clutch is provided between the clutches, and a fluid pressure operated third clutch is provided between the second intermediate shaft and the output cylindrical shaft, and is fixed to the first and second intermediate shafts respectively. third and fourth external gears that are always in mesh with the first and second external gears, respectively, are attached to the spider so as to be relatively rotatable, and fifth and sixth external gears are respectively fixed to the two cylindrical shafts. Seventh and eighth external gears that engage with the third and fourth external gears respectively are attached to the spider so as to be relatively rotatable, and a fluid pressure operated first a brake, a fluid-pressure-operated second brake for an internal gear that is always engaged with the third external gear, and a fluid-pressure-operated third brake for the second intermediate shaft, and the first clutch is operated in a forward movement state. The second and third clutches and the first to third brakes are selectively operated while the clutches are in the engaged state, and the second clutch is maintained in the engaged state and the third clutch and the second brake are selectively operated in the reverse state. ,
The present invention relates to a hydraulically operated travel transmission equipped with a valve mechanism for selectively operating a third brake. Conventionally, in such a traveling transmission, a valve mechanism for speed change operation is provided with just one control valve, but in this case, the control is performed by a speed change lever that reciprocates in one direction. Due to the fact that a spool that can be reciprocated in one direction in the valve is operated, there is a disadvantage that it is difficult to perform a speed change operation, and there is also a disadvantage that it is easy to operate erroneously, so there is room for improvement. To be more specific, in the case of a shift lever, it is desirable to increase the distance between adjacent shift positions so that each shift position can be easily identified, but in the case of the above conventional structure, the distance between adjacent shift positions is If it is set too high, the operating range of the gear shift lever becomes large, which has the disadvantage that the operator has to operate the gear shift lever while extending his/her hand.To avoid this, it is recommended to reduce the distance between adjacent gear shift positions. However, the shift position was difficult to determine, leading to erroneous operation. The present invention has been developed in view of the above-mentioned circumstances, and its purpose is to improve operability through simple modification that effectively utilizes the original configuration. A characteristic configuration of the fluid pressure operated travel transmission according to the present invention is that the valve mechanism includes a first control valve for switching forward and backward travel that selectively supplies fluid pressure to the first and second clutches; , a second speed setting control valve for selectively supplying fluid pressure to the second and third clutches and the first to third brakes;
The first and second control valves are connected in parallel to the second clutch via a shuttle valve, and different two control valves are connected in parallel to the second clutch via a shuttle valve.
A single gear shift lever that can be freely operated in one direction is linked to both control valves so that operation in one direction operates the first control valve and operation in the other direction operates the second control valve. , its functions and effects are as follows. That is, focusing on the fact that the first clutch is maintained in the engaged state in the forward traveling state and the second clutch is maintained in the engaged state in the reverse traveling state, the first control valve for forward/reverse switching and the second control valve for speed setting are controlled. are provided separately for each, and the fluid supplied to the second clutch, which is engaged in both forward and backward motion, is
In order to prevent oil from being drained through the first control valve in the forward drive state and to prevent oil from being drained through the second control valve in the reverse drive state, the second clutch is controlled by the first and second control valves using a shuttle valve. By connecting it to the valve, it is possible to perform a predetermined speed change by operating the first and second control valves, and furthermore, it is possible to operate two control valves while operating one shift lever in two different directions. It is set as. Therefore, while taking advantage of the advantage of shifting with a single gear lever, the operation stroke of the gear lever in each of the two different directions is minimized.
The distance between adjacent shift positions in each direction can be made sufficiently large, so that the shift lever can be operated satisfactorily while performing multi-stage shifting. Next, embodiments of the present invention will be described in detail based on illustrative drawings. As shown in FIG. 1, a front vehicle body 2 equipped with a pair of left and right front wheels 1 and a rear vehicle body 4 equipped with a pair of left and right rear wheels 3 are connected so as to be relatively swingable around a vertical axis P. The front body 2 is equipped with a front loader 5 that can be freely raised and lowered, and the rear body 4 is equipped with a boarding section 6, a driving section 7, and a backhoe device 8. The steering handle 6 is controlled by the hydraulic cylinder 9 installed over the
The structure is configured to relatively drive and sway both the front and rear vehicle bodies 2 and 4 by an amount corresponding to the amount of operation a, and perform vehicle direction. The earthmoving vehicle is configured to transmit the variable speed power to the front wheels 1 and the rear wheels 3, respectively, and thereby performs earth-moving work and excavation work. To configure the transmission structure in the traveling transmission case 11, as shown in FIGS. 2 and 3, the input shaft 12, the first intermediate shaft 13, and the second intermediate shaft 14 are arranged concentrically. and the first intermediate shaft 13
The reverse cylindrical shaft 15 is attached to the second intermediate shaft 14, and the output cylindrical shaft 16 is attached to the second intermediate shaft 14 so as to be relatively rotatable. A multi-plate first transmission clutch 18 is mounted between the input shaft 12 and the first intermediate shaft 13, and a multi-plate second transmission clutch is mounted between the input shaft 12 and the reverse cylinder shaft 15. clutch 19
and a third transmission clutch 20 is provided between the second intermediate shaft 14 and the output cylinder shaft 16, and first and second transmission clutches are respectively attached to the first and second intermediate shafts 13 and 14.
The third and fourth gears G 3 and G 4 , which are always engaged with the gears G 1 and G 2 respectively, are attached to the spider 17 so as to be relatively rotatable, and the fifth gears are attached respectively to the double cylinder shafts 15 and 16, respectively.
The 6th gear G 5 and G 6 are engaged separately, and the 3rd gear
The 7th and 8th gears G 7 and G 8 that engage with the 4th gears G 3 and G 4 separately are attached to the spider 17 so as to be relatively rotatable, and the multi-plate type is used to fix the reverse cylinder shaft 15 to the case 11. A first brake 21, a multi-plate second brake 22 for fixing to the case 11 the internal gear GF that is always engaged with the third gear G3 , and a multi-plate second brake 22 for fixing the second intermediate shaft 14 to the case 11. Plate type 3
A brake 23 is provided, and the input shaft 12 is interlocked and connected to the engine 10 via a travel clutch 24 and a gear interlocking mechanism, and the output cylinder shaft 16 is connected to the output shaft for the front and rear wheels 1 and 3 via the gear interlocking mechanism. 25 is interlocked and connected. A hydraulic cylinder section 18 for clutch operation is attached to each transmission clutch 18 to 23 in a state where it is always biased toward the transmission disengaged state.
A valve mechanism is provided to selectively supply pressure oil from the hydraulic pump 26 to a to 23a, and a five-stage forward speed is provided.
It is configured to be switchable between F 1 to F 5 , two reverse gears R 1 and R 2 , and a neutral shift state N. More specifically, in the forward state, the first
The clutch 18 is maintained in the engaged state and the second and third
The clutches 19, 20 and the first to third brakes 21, 22, 23 are selectively operated, and in the reverse driving state, the second clutch 19 is maintained in the engaged state and the third clutch 20 and the second and third brakes are operated. 22 and 23 will be selected. and,
The following table shows the pressure oil supply state in each gear shift state. However, (〇) indicates pressure oil supply and
(x) indicates drained oil.
【表】
前記弁機構を構成するに、第3図及び第4図に
示すように、第1及び第2クラツチ18,19に
択一的に流体圧を供給する前後進切換用第1制御
弁V1、並びに、第2、第3クラツチ19,20
及び第1ないし第3ブレーキ21,22,23に
選択的に流体圧を供給する速度設定用の第2制御
弁V2を設け、第1、第2制御弁V1,V2を、シヤ
トル弁27を介して第2クラツチ19に並列接続
してある。
そして、第1、第2制御弁V1,V2を操作する
に、1つの変速レバー28を、前後方向並びに左
右方向に揺動自在に球支点Zを用いて支承し、縦
軸芯(X)周りの揺動によつて第1制御弁V1を
操作するアーム29に、前後方向に沿う長孔状の
レバー挿入孔30を形成し、横軸芯(Y)周りの
揺動によつて第2制御弁V2を操作するアーム3
1に、左右方向に沿う長孔状のレバー挿入孔32
を形成し、さらに、レバー挿通溝33を備えたレ
バーガイド枠34を設け、もつて、変速レバー2
8の揺動操作により変速できるように構成してあ
る。
本考案を実施するに、変速レバー28を、前後
方向並びにレバー軸芯方向に移動自在に支承し、
そして、レバー軸芯方向の移動で第1制御弁V1
を、且つ、前後方向の移動で第2制御弁V2を操
作させるようにする等、変速レバー28の支承構
造、及び、変速レバー28と第1、第2制御弁
V1,V2との連係構造は各種変更できる。
又、本案の走行変速装置は、建設作業車の他、
農用作業車等の各種作業車に適用できる。[Table] As shown in FIGS. 3 and 4, the valve mechanism includes a first control valve for forward/reverse switching that selectively supplies fluid pressure to the first and second clutches 18, 19. V 1 and the second and third clutches 19, 20
and a second control valve V 2 for speed setting that selectively supplies fluid pressure to the first to third brakes 21, 22, 23, and the first and second control valves V 1 and V 2 are configured as shuttle valves. 27 to the second clutch 19 in parallel. In order to operate the first and second control valves V 1 and V 2 , one shift lever 28 is supported on a ball fulcrum Z so as to be swingable in the longitudinal direction and in the left and right directions. ) An elongated lever insertion hole 30 along the front-rear direction is formed in the arm 29 that operates the first control valve V 1 by swinging around the horizontal axis (Y). Arm 3 that operates the second control valve V 2
1, a long lever insertion hole 32 along the left and right direction.
Furthermore, a lever guide frame 34 having a lever insertion groove 33 is provided, and the shift lever 2
It is constructed so that the gear can be changed by the rocking operation of 8. To carry out the present invention, the gear shift lever 28 is supported so as to be movable in the longitudinal direction and in the lever axis direction,
Then, by moving the lever in the axial direction, the first control valve V 1
and a support structure for the shift lever 28, such as allowing the second control valve V2 to be operated by moving in the front-rear direction, and the shift lever 28 and the first and second control valves.
The linkage structure with V 1 and V 2 can be changed in various ways. In addition, the traveling transmission device of this proposal can be used not only for construction work vehicles, but also for
It can be applied to various work vehicles such as agricultural work vehicles.
図面は本考案に係る流体圧操作式走行変速装置
の実施例を示し、第1図は土工車の側面図、第2
図は走行変速装置の概略図、第3図は油圧回路
図、第4図は弁操作構成を示す斜視図である。
12……入力軸、13……第1中間軸、14…
…第2中間軸、15……後進用筒軸、16……出
力用筒軸、17……スパイダー、18……第1ク
ラツチ、19……第2クラツチ、21……第1ブ
レーキ、22……第2ブレーキ、23……第3ブ
レーキ、27……シヤトル弁、28……変速レバ
ー、G1ないしG8……外歯ギヤ、GF……内歯ギ
ヤ、V1……第1制御弁、V2……第2制御弁。
The drawings show an embodiment of the hydraulically operated traveling transmission device according to the present invention, and FIG. 1 is a side view of an earthmoving vehicle, and FIG.
FIG. 3 is a schematic diagram of the traveling transmission, FIG. 3 is a hydraulic circuit diagram, and FIG. 4 is a perspective view showing a valve operation configuration. 12...Input shaft, 13...First intermediate shaft, 14...
... Second intermediate shaft, 15 ... Reverse cylinder shaft, 16 ... Output cylinder shaft, 17 ... Spider, 18 ... First clutch, 19 ... Second clutch, 21 ... First brake, 22 ... ...Second brake, 23...Third brake, 27...Shuttle valve, 28...Speed lever, G1 to G8 ... External gear, GF...Internal gear, V1 ...First control valve , V 2 ... second control valve.
Claims (1)
4を同芯状に配置し、前記第1中間軸13に後進
用筒軸15をかつ前記第2中間軸14に出力用筒
軸16を夫々相対回転自在に取付け、スパイダー
17の両端を前記両筒軸15,16に各別にかつ
相対回転自在に取付け、前記入力軸12と第1中
間軸13の間に流体圧操作式第1クラツチ18
を、前記入力軸12と後進用筒軸15の間に流体
圧操作式第2クラツチ19を、かつ、前記第2中
間軸14と出力用筒軸16の間に流体圧操作式第
3クラツチ20を夫々設け、前記第1及び第2中
間軸13及び14に各別に固着した第1及び第2
外歯ギアG1及びG2に各別に常時咬合する第3及
び第4外歯ギヤG3及びG4を前記スパイダー17
に相対回転自在に取付け、前記両筒軸15,16
に各別に固着した第5及び第6外歯ギヤG5及び
G6に各別に咬合すると共に前記第3及び第4外
歯ギヤG3及びG4に各別に咬合する第7及び第8
外歯ギヤG7及びG8を前記スパイダー17に相対
回転自在に取付け、前記後進用筒軸15に対する
流体圧操作式第1ブレーキ21、前記第3外歯ギ
ヤ29に常時咬合する内歯ギヤGFに対する流体
圧操作式第2ブレーキ22、及び、前記第2中間
軸14に対する流体圧操作式第3ブレーキ23を
設け、前進状態において前記第1クラツチ18を
入り状態に維持させて前記第2、第3クラツチ1
9,20及び前記第1ないし第3ブレーキ21,
22,23を選択操作し、且つ、後進状態におい
て前記第2クラツチ19を入り状態に維持させて
前記第3クラツチ20及び前記第2、第3ブレー
キ22,23を選択操作する弁機構を設けた流体
圧操作式走行変速装置であつて、前記弁機構を構
成するに、前記第1及び第2クラツチ18,19
に択一的に流体圧を供給する前後進切換用第1制
御弁V1、並びに、前記第2、第3クラツチ19,
20及び前記第1ないし第3ブレーキ21,2
2,23に選択的に流体圧を供給する速度設定用
第2制御弁V2を設け、前記第1、第2制御弁V1,
V2を、シヤトル弁27を介して前記第2クラツ
チ19に並列接続すると共に、異なる2方向に操
作自在な1つの変速レバー28を、一方向の操作
で前記第1制御弁V1を、且つ、他方向の操作で
前記第2制御弁V2を操作するように前記両制御
弁V1,V2に連係してある流体圧操作式走行変速
装置。 Input shaft 12, first intermediate shaft 13, and second intermediate shaft 1
4 are arranged concentrically, a reverse cylinder shaft 15 is attached to the first intermediate shaft 13, and an output cylinder shaft 16 is attached to the second intermediate shaft 14 so as to be relatively rotatable, and both ends of the spider 17 are connected to the two ends of the spider 17. A fluid pressure operated first clutch 18 is mounted on the cylindrical shafts 15 and 16 separately and relatively rotatably, and between the input shaft 12 and the first intermediate shaft 13.
A fluid pressure operated second clutch 19 is provided between the input shaft 12 and the reverse cylinder shaft 15, and a fluid pressure operated third clutch 20 is provided between the second intermediate shaft 14 and the output cylinder shaft 16. are provided, respectively, and are fixed to the first and second intermediate shafts 13 and 14, respectively.
The third and fourth external gears G 3 and G 4 , which are always engaged with the external gears G 1 and G 2 separately, are attached to the spider 17.
The two cylinder shafts 15, 16 are mounted so as to be relatively rotatable.
The fifth and sixth external gears G5 and
Seventh and eighth gears that engage G 6 separately and engage the third and fourth external gears G 3 and G 4 , respectively.
External gears G 7 and G 8 are attached to the spider 17 so as to be relatively rotatable, and a fluid pressure operated first brake 21 for the reverse cylindrical shaft 15 and an internal gear GF constantly meshed with the third external gear 29. A fluid pressure operated second brake 22 is provided for the second intermediate shaft 14, and a fluid pressure operated third brake 23 is provided for the second intermediate shaft 14 to maintain the first clutch 18 in the engaged state in the forward movement state. 3 clutch 1
9, 20 and the first to third brakes 21,
A valve mechanism is provided for selectively operating the third clutch 20 and the second and third brakes 22 and 23 by selectively operating the third clutch 22 and 23, and maintaining the second clutch 19 in the engaged state in the reverse traveling state. In the hydraulically operated traveling transmission, the valve mechanism includes the first and second clutches 18 and 19.
a first control valve V 1 for forward/reverse switching that selectively supplies fluid pressure to
20 and the first to third brakes 21, 2
A second speed setting control valve V 2 is provided to selectively supply fluid pressure to the first and second control valves V 1 , 23 .
V 2 is connected in parallel to the second clutch 19 via the shuttle valve 27, and one shift lever 28 that can be operated in two different directions is operated in one direction to control the first control valve V 1 and , a hydraulically operated travel transmission connected to both control valves V 1 and V 2 so as to operate the second control valve V 2 by operation in the other direction.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19657883U JPS60103747U (en) | 1983-12-21 | 1983-12-21 | Fluid pressure operated travel transmission |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19657883U JPS60103747U (en) | 1983-12-21 | 1983-12-21 | Fluid pressure operated travel transmission |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS60103747U JPS60103747U (en) | 1985-07-15 |
JPH0121233Y2 true JPH0121233Y2 (en) | 1989-06-26 |
Family
ID=30421667
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19657883U Granted JPS60103747U (en) | 1983-12-21 | 1983-12-21 | Fluid pressure operated travel transmission |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60103747U (en) |
-
1983
- 1983-12-21 JP JP19657883U patent/JPS60103747U/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPS60103747U (en) | 1985-07-15 |
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