JPH0220453A - Hydraulic circuit for running construction machine - Google Patents
Hydraulic circuit for running construction machineInfo
- Publication number
- JPH0220453A JPH0220453A JP17163088A JP17163088A JPH0220453A JP H0220453 A JPH0220453 A JP H0220453A JP 17163088 A JP17163088 A JP 17163088A JP 17163088 A JP17163088 A JP 17163088A JP H0220453 A JPH0220453 A JP H0220453A
- Authority
- JP
- Japan
- Prior art keywords
- running
- pressure
- speed
- speed range
- motor
- 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.)
- Pending
Links
- 238000010276 construction Methods 0.000 title claims description 8
- 230000005540 biological transmission Effects 0.000 claims description 19
- 238000010586 diagram Methods 0.000 description 13
- 230000007423 decrease Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000005611 electricity Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/421—Motor capacity control by electro-hydraulic control means, e.g. using solenoid valves
Landscapes
- Operation Control Of Excavators (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
この発明は油圧駆動のホイール式建設機械の走行油圧回
路に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a travel hydraulic circuit for a hydraulically driven wheeled construction machine.
従来の技術
自走式の建設機械は作業現場内での近距離移動と、作業
現場間の長距離移動が複雑に混在して要求され、特にホ
イール式の機械にあっては、作業現場内の急坂路走行、
悪路脱出のため強力な走行駆動力を求められる一方、作
業現場間の移動は、できる限り高速で走行し作業能率を
向上させることが必要である。Conventional technology Self-propelled construction machinery requires a complex mix of short-distance movement within a work site and long-distance movement between work sites, and wheel-type machines in particular require driving on steep slopes,
While strong driving force is required to escape from rough roads, it is also necessary to travel as fast as possible to improve work efficiency when moving between work sites.
このようなニーズに対しては、走行輪の駆動系に設ける
変速装置の速度段の範囲を大きくしなければならないの
で、通常の変速機または油圧駆動式では可変容積形走行
モータを採用するほか、低速度域運転と高速度域運転と
に切換えることのできる副変速機を設け、運転席近くに
設けた速度域切換手段を任意に操作して対応している。To meet these needs, it is necessary to widen the speed range of the transmission installed in the drive system of the running wheels, so in addition to using a variable displacement drive motor instead of a normal transmission or hydraulic drive type, An auxiliary transmission is provided that can switch between low speed range operation and high speed range operation, and the speed range switching means provided near the driver's seat can be operated at will.
例えば、ホイール式油圧駆動の油圧シラペルを例にとり
、その走行油圧回路の１例を示すと第４図のようになっ
ている。For example, taking a wheel-type hydraulically driven hydraulic sillpel as an example, an example of its travel hydraulic circuit is shown in FIG. 4.
図において、１はメインポンプ２，３、パイロットポン
プ４を駆動するエンジンで、メインポンプ２，３の吐出
圧油はそれぞれリリーフ弁１７゜１８の設定値の範囲内
で油圧切換弁グループＡ。In the figure, 1 is an engine that drives main pumps 2 and 3 and a pilot pump 4, and the pressure oil discharged from the main pumps 2 and 3 is controlled within the range of the set values of relief valves 17 and 18, respectively, of hydraulic switching valve group A.
Ｂに流入し、各グループに属する゛作業装置用の油圧切
換弁の操作により図示は省略したが、それぞれの作業装
置を作動させるのは勿論であるが、該油圧切換弁グルー
プＡ、 Ｂに属する走行用油圧切換弁５，６が操作さ
れると、圧油は該弁を通り合流し、旋回接手７を経て可
変容積形の走行モータ８を正逆に回転させる。また、走
行モータ８の出力軸はトランスフッケース９の入力軸に
接続され、該トランスファケース９の出力軸は前後２個
所にあり、それぞれ、その回転力はプロペラシャフト、
差動機、最終減速機などを介して前後の走行輪１０を正
逆に駆動することにより機体を前後進させる。なお、ト
ランスファケース９は走行モータ８の回転力を、前後２
個所の出力軸に分配するのみならず、内部の歯車比を低
速度域と高速度域とに切換えられる副変速機の機能をも
有し、外部からの信号を受し」る受信部ａに信号が作用
すると上記歯車比を低速度域から高速度域に切換ねるよ
うになっている。Although not shown in the figure, the hydraulic switching valves belonging to groups A and B flow into the hydraulic switching valves B and operate the hydraulic switching valves for the working devices belonging to each group. When the traveling oil pressure switching valves 5 and 6 are operated, the pressure oil passes through the valves, joins together, passes through the swing joint 7, and rotates the variable displacement traveling motor 8 in forward and reverse directions. Further, the output shaft of the travel motor 8 is connected to the input shaft of the transfer case 9, and the output shafts of the transfer case 9 are located at two locations, front and rear, and the rotational force is transmitted to the propeller shaft,
By driving the front and rear running wheels 10 in forward and reverse directions via a differential, a final reduction gear, etc., the body is moved forward and backward. Note that the transfer case 9 transfers the rotational force of the travel motor 8 to the front and rear
In addition to distributing signals to various output shafts, it also has the function of an auxiliary transmission that can switch the internal gear ratio between low speed range and high speed range, and receives signals from the outside. When a signal is applied, the gear ratio is switched from a low speed range to a high speed range.
１１は切換弁で、スイッチ１３を閉路する、−とにより
励磁されるとＣ位置からＤ位置に切換ねり、調圧された
パイロットポンプ４の吐出圧油を、該弁のＤ位置通路、
旋回接ｆ７を経由してトランスフア々−ス９の受信部ａ
に導くようにしてあり、スイッチ１３は運転席近くにあ
って自由に開閉できるようになっている。Reference numeral 11 denotes a switching valve, which switches from the C position to the D position when excited by closing the switch 13 or -, and transfers the pressure-regulated discharge pressure oil of the pilot pump 4 to the D position passage of the valve.
Receiving section a of transfer station 9 via rotating contact f7
The switch 13 is located near the driver's seat and can be opened and closed freely.
上述の如き走行油圧回路においては、可変容積形の走行
モータ８の１回転当りの容積を大小２段階に、更に、ト
ランスファケース９内の歯車比を低速度域、高速度域の
２段階に、それぞれ組合わせることにより、低速から高
速迄、合計４段階の速度段を得ることが可能であるから
、運転者は、機械の移動に際して、走行路面の状況、作
業条件等に遺した走行速度並びに走行駆動力を選択して
機械の運転をすることができる。In the traveling hydraulic circuit as described above, the volume per revolution of the variable displacement traveling motor 8 is set to two levels, large and small, and the gear ratio in the transfer case 9 is set to two levels, a low speed range and a high speed range. By combining each, it is possible to obtain a total of four speed stages from low speed to high speed, so when moving the machine, the operator can adjust the speed and speed depending on the road surface condition, work conditions, etc. You can operate the machine by selecting the driving force.
発明が解決しようとする課題
前述の如き従来の全油圧、ホイール式建設機械において
は、一般に、作業装丁作動時よりも走行時の方が大きい
動力を必要とするものであり、とりわけ、高速走行時に
最も大きい動力を投入しなければならない。Problems to be Solved by the Invention In the conventional all-hydraulic, wheel-type construction machinery as described above, generally more power is required when traveling than when operating the work equipment, and especially when traveling at high speed. The greatest power must be applied.
一方、走行についても、最低速度段を選択して低速で機
体を移動させるときは、走行輪が不必要にスリップしな
い範囲での最大の駆動力を発揮できるような走行モータ
の出力と、その出力トルクに見合う強度で、しかも、過
大とならない経済的な走行動力伝達系、すなわち、変速
機、ｌ・ランスファケース、プロペラシャ７１・、差動
機、最終減速機などを採用し、同時に、最高速度段での
走行に対しては、走行モータが走行輪を駆動する迄の減
速比を小さくして、同一の走行モータ回転に対し、走行
輪が早く回転し、しかも、その時の走行輪の駆動力が、
−船内な走行路面上での機体の走行抵抗に十分に打勝ぢ
、高速走行が維持できる能力を発揮するような組合わせ
とならねばならない。On the other hand, regarding running, when selecting the lowest speed stage and moving the aircraft at low speed, the output of the running motor that can exert the maximum driving force within the range where the running wheels do not slip unnecessarily, and its output. We have adopted an economical driving power transmission system that has strength commensurate with the torque and is not excessive, that is, a transmission, l transfer case, propeller shaft 71, differential, final reduction gear, etc., and at the same time, the maximum speed For multi-stage running, the reduction ratio until the running motor drives the running wheels is reduced, so that the running wheels rotate faster for the same running motor rotation, and the driving force of the running wheels at that time is reduced. but,
-The combination must be such that it can sufficiently overcome the running resistance of the aircraft on the running surface inside the ship and exhibit the ability to maintain high-speed running.
（７かしながら、この組合わせのちとに、高速走行をよ
り速くする目的で高速速度段における減速比を余り小さ
くすると、走行輪の駆動力が低下し、この低下をカバー
しようとして走行モータへ流入する圧油の作動圧力をリ
リーフ弁の設定により高圧にすると、低速の速度段を選
択したとき、同一の走行モータを使用するので、走行輪
の駆動力は必要以−トに増大してタイヤを損傷するよう
な異常スリップが起り易くなるのみならず、走行動力伝
達系を構成する部材を一段と強化しなければならないこ
ととなり、不経済である。(7) However, if after this combination, the reduction ratio in the high speed gear is made too small in order to make the high speed run faster, the driving force of the running wheels will decrease, and in order to compensate for this decrease, the drive motor will If the operating pressure of the inflowing pressure oil is set to a high pressure by setting the relief valve, the same traveling motor will be used when a low speed gear is selected, so the driving force of the traveling wheels will increase more than necessary and the tires will be damaged. Not only is it likely that abnormal slips that can damage the vehicle will occur, but the members that make up the traveling power transmission system will have to be further strengthened, which is uneconomical.
この発明は、上記に鑑み、走行モータへの圧油の作動圧
力を、高速走行時と低速走行時とにおいて自動的に変更
することにより、経済的な走行動力伝達系を有し、しか
も、走行性能のすぐれた建設機械の設計に寄与すること
をＲ題とするものである。In view of the above, the present invention has an economical running power transmission system by automatically changing the working pressure of pressure oil to the running motor between high-speed running and low-speed running. The purpose of this research is to contribute to the design of construction machinery with excellent performance.
課題を解決するための手段
」＝記課題を解決するため、この発明は次の如き手段を
講じた。すなわち、
イ、油圧ポンプの吐出圧油を走行用の油圧モータに供給
し、その出力で走行輪を多段階の回転域で回転させるよ
うにした走行動力伝達系および油圧回路において、
ロ、走行速度段を低速度域と、高速度域とに切換える信
号を発する機能を有する速度切換手段と、ハ、油圧ポン
プの吐出側管路に、外部からの信号で設定圧力が高低に
切換る可変リリーフ弁とを設け、
二、該可変リリーフ弁の受信部に上記速度切換手段から
の信号を導く。Means for Solving the Problem In order to solve the problem, the present invention has taken the following measures. In other words, (a) In a travel power transmission system and hydraulic circuit that supply pressure oil discharged from a hydraulic pump to a hydraulic motor for travel, and use its output to rotate the travel wheels in a multi-stage rotation range, (b) Travel speed. A speed switching means that has a function of emitting a signal to switch the stage between a low speed range and a high speed range, and (3) a variable relief valve in the discharge side line of the hydraulic pump that switches the set pressure to high or low based on an external signal. and (2) guiding the signal from the speed switching means to the receiving section of the variable relief valve.
作用
速度切換手段を高速度域に切換えると、走行動力伝達系
の速度段が切換わるとともに、該速度切換手段からの信
号は可変リリーフ弁の受（８部に作用する。このとき、
可変リリーフ弁の設定圧力が通常の値よりも高圧になる
ようにしておくと、走行用の油圧モータに作用する油圧
ポンプの吐出圧力は上昇し、該モータの出力トルクは増
大するので、走行動力伝達系が高速度域に切換ねり、減
速比が小さくても、走行輪に、高速走行に必要な駆動力
を付与する。When the operating speed switching means is switched to a high speed range, the speed stage of the traveling power transmission system is switched, and the signal from the speed switching means is applied to the receiver (8) of the variable relief valve.At this time,
If the set pressure of the variable relief valve is set higher than the normal value, the discharge pressure of the hydraulic pump acting on the hydraulic motor for traveling will increase, and the output torque of the motor will increase, so the traveling power will be reduced. The transmission system switches to a high-speed range, providing the driving force necessary for high-speed travel to the running wheels even if the reduction ratio is small.
速度切換手段を低速度域に撮作すると、可変リリーフ弁
の設定圧力は通常の圧力となるので、走行用の油圧モー
タの出力トルクは減少し、該モータから走行輪に至る走
行動力伝達系の減速比が大きいときでも、構成部材であ
るブロベラシャフ１、差動機、最終減速機などを損傷し
たり、タイヤの寿命を低下させたりすることはない。When the speed switching means is set to a low speed range, the set pressure of the variable relief valve becomes the normal pressure, so the output torque of the hydraulic motor for traveling decreases, and the power transmission system from the motor to the traveling wheels decreases. Even when the reduction ratio is large, the structural members such as the blower shaft 1, the differential, the final reduction gear, etc. will not be damaged, and the life of the tires will not be shortened.
実施例
この発明の実施例を第１図に示すホイール式油圧シッペ
ルにおける要部の電気・油圧系統図によっζ説明する。Embodiment An embodiment of the present invention will be explained with reference to an electric/hydraulic system diagram of the main parts of a wheel-type hydraulic shipper shown in FIG.
なお、第１図において第４図と同一部分には同一符号を
付して示し、詳細説明は省略するや
１４．１５はメインポンプ２，３の吐出圧油管路に設け
た可変リリーフ弁で、それぞれ、列部信号を受ける受信
部す、 ｂを有し、通常は低速度段に選択された走行
動力伝達系、。すなわち、走行モータ８から走行輪１０
までの減速比が大きい＄Ｊ！域において、走行モータ８
が走行輪１０を支障なく駆動することのできる出力トル
クに見合う設定圧力となっているが、パイロット管路１
９を経由して受信部す、ｂにパイロット圧が作用すると
、その設定圧力が上昇し、走行用油圧切換弁５，６、旋
回接手７を経由して、より高圧のメインポンプ２．３の
吐出圧油が走行モータ８に流入するようになっている。In FIG. 1, the same parts as in FIG. 4 are denoted by the same reference numerals, and detailed explanation will be omitted. Reference numeral 14.15 is a variable relief valve provided in the discharge pressure oil pipes of the main pumps 2 and 3. A traveling power transmission system, each having a receiving section (a) and (b) for receiving a train signal, and which is normally selected for a low speed stage. That is, from the running motor 8 to the running wheel 10
$J with a large reduction ratio up to! In the area, the travel motor 8
is a set pressure commensurate with the output torque that can drive the running wheels 10 without any trouble, but the pilot pipe 1
When the pilot pressure acts on the receiving portions S and B via 9, the set pressure increases, and the higher pressure main pump 2.3 is applied via the travel hydraulic switching valves 5, 6 and the swing joint 7. The discharge pressure oil flows into the travel motor 8.
１２は切換弁で、通常はＡ位置にあって、パイロット管
路１９をタンク１６に通じさせているが、スイッチ１３
、すなわち、速度域切換手段が高速度段に切換えられる
と、切換弁１１ととも（ＺＡＡｌ１らＢ位置に切換り、
パイロットポンプ４の吐出側の管路２０をパイロット管
路１９に接続させ、一方、切換弁１１は受信部ａに通じ
るパイロット管路２１と管路２０とを連通させる。Reference numeral 12 denotes a switching valve, which is normally located at the A position and allows the pilot line 19 to communicate with the tank 16, but the switch 13
That is, when the speed range switching means is switched to the high speed stage, the switching valve 11 and (ZAAl1 to B position) are switched,
A conduit 20 on the discharge side of the pilot pump 4 is connected to the pilot conduit 19, while a switching valve 11 connects the conduit 20 with a pilot conduit 21 leading to the receiving section a.
以上の構成からなるこの発明の回路の作動について説明
する。The operation of the circuit of the present invention having the above configuration will be explained.
作業中または作業現場内の小移仙においては、機体の移
動速度よりも、強力、確実な駆動力が必要であるから、
速度域切換手段は低速度段に選定しておく。この状態で
は第１図におけるスイッチ１３は開路し、切換弁１１．
１２は何れも入位置を保持し、パイロット管路１９．２
１はともにタンク１６に通じている。従って、トランス
ファケース９は低速域の歯車比を構成し、可変リリーフ
弁１４．１５は通常の設定圧力となっているので、走行
モータ８へは、メインポンプ２，３の通常の圧力の範囲
内での吐出圧油が供給され、走行輪１０は低速度段に要
求される駆動力に対し、十分で過不足のない能力を発揮
する。During work or for small transfers within a work site, strong and reliable driving force is more important than the moving speed of the machine.
The speed range switching means is selected to be a low speed stage. In this state, the switch 13 in FIG. 1 is opened, and the switching valve 11.
12 are all held in the engaged position, and the pilot pipe 19.2
1 both communicate with tank 16. Therefore, the transfer case 9 constitutes a gear ratio in the low speed range, and the variable relief valve 14.15 has a normal set pressure, so that the pressure to the travel motor 8 is within the normal pressure range of the main pumps 2 and 3. Pressure oil is supplied to the running wheels 10, and the running wheels 10 exhibit sufficient ability to meet the driving force required for the low speed gear.
次に、作業現場間の移動、回送などのため高速で自走す
るとぎ、速度域切換手段を、当然、高速度段に切換え、
従って、スイッチ１３を閉路することとなる。このとき
は、切換弁１１はＡ位置からＢ位置に切換わり、パイロ
ットポンプ４の吐出圧油は管路２０、切換弁１１の８位
１通路、バイロン（・管路２１を通り、トランスファケ
ース９の受信部ａに作用して該ケース内部の歯車比を高
速側に切換える。この結果、走行モータ８から走行輪１
０に至る動力伝達系の減速比は小さく、高速走行に必要
な走行輪１０の駆動力に見合う走行モータ８の必要出力
トルクは増大するのであるが、スイッチ１３が閉路され
ると同時に、切換弁１２も同時にＡ位置からＢ位置に切
換り、管路２０の圧油がパイロット圧として、該切換弁
１２のＢ位置通路、バイロフト管路１９を経て可変リリ
ーフ弁１４．１５の受信部すに作用し、メインポンプ２
．３の吐出圧力が、より高圧になる迄リリーフしなくな
る。従って、走行モータ８には、今までよりも高い圧油
が作用し得ることとなり、高速度域において必要な走行
モータ８のトルクが得られることとなり、機体は高速で
走行することができる。Next, when self-propelled at high speed for movement between work sites, forwarding, etc., the speed range switching means is naturally switched to the high speed stage,
Therefore, the switch 13 is closed. At this time, the switching valve 11 is switched from the A position to the B position, and the discharge pressure oil of the pilot pump 4 passes through the pipe 20, the 8th position 1 passage of the switching valve 11, the Byron pipe 21, and the transfer case 9. The gear ratio inside the case is switched to the high speed side.As a result, the transmission from the traveling motor 8 to the traveling wheel 1
The reduction ratio of the power transmission system that reaches 0 is small, and the required output torque of the travel motor 8 increases to match the driving force of the travel wheels 10 required for high-speed travel, but at the same time as the switch 13 is closed, the switching valve 12 is also simultaneously switched from the A position to the B position, and the pressure oil in the pipe line 20 acts as pilot pressure on the receiving part of the variable relief valve 14.15 via the B position passage of the switching valve 12 and the biloft pipe 19. Main pump 2
．． No relief occurs until the discharge pressure of No. 3 becomes higher. Therefore, higher pressure oil can act on the travel motor 8 than before, and the necessary torque of the travel motor 8 can be obtained in the high speed range, allowing the aircraft to travel at high speed.
以上の走行速度域切換操作による走行特性を、従来技術
のものと比較しながら第２図、第３図の線図により詳述
すると、第３図は従来の、第２図はこの発明の回路を有
する機械の走行特性線図で、４図中、線図１．ＩＩは低
速走行域の第１速、第２速の特性を示し、線図■。、■
。及び■、■はそれぞれ、従来および本発明における高
速走行域の第３速、第４速の特性で、走行速度■と走行
輪１０の外周の駆動力Ｆとを示す走行特性である。The running characteristics resulting from the above running speed range switching operation will be explained in detail with reference to the diagrams in FIGS. 2 and 3 while comparing them with those of the prior art. FIG. 3 shows the conventional circuit, and FIG. 2 shows the circuit of the present invention. This is a running characteristic diagram of a machine with II shows the characteristics of 1st speed and 2nd speed in the low speed driving range, and the diagram ■. ,■
. and ■, ■ are the characteristics of the third speed and fourth speed in the high speed driving range in the conventional and the present invention, respectively, and are the driving characteristics indicating the driving speed ■ and the driving force F of the outer periphery of the running wheels 10.
第２図、第３図における第１速、第２速、ずなわち、低
速走行域における走行特性は全く同一であるが、高速走
行域では相異しているやすなわち、第３図の従来機の第
３連の走行特性線図ｍ、における最大走行速度ｖツ゛、
最大駆動力Ｆ１、第４連の走行特性線図■。における最
大走行速度Ｖ４’、最大駆動力Ｆ４とすると、第２図で
は、トランスファケース９内の高速走行域での歯車比を
変更して、同一の走行モータ８の回転数に対して第３連
、第４速の最大速度Ｖｚ’、Ｖ−°をそれぞれＶ、、Ｖ
。The driving characteristics in the first speed and second speed in FIG. 2 and FIG. The maximum running speed v in the third running characteristic diagram m of the machine,
Maximum driving force F1, 4th series running characteristic diagram ■. Assuming maximum running speed V4' and maximum driving force F4 in FIG. , 4th speed maximum speed Vz', V-° are respectively V, ,V
.
になるように設計したものである。このようにすること
により、最大速度のみを線図上で見る限り、■、°は■
、に、■３°はＶ４に迄上昇するが、走行モータ８の出
力トルクが同一のときは、それらの走行特性線図は第２
図の点線■”、■゛ で示す如く、それぞれの最大駆動
力ＦはＦ、よりも小さいＦ３゛、Ｆ４よりも小さいＦ、
ｌとなり、走行中の緩い傾斜、悪路など、走行抵抗が僅
かに増大しても走行ｗＩ！続不能、走行速度の低下など
のため、より低速の速度段を選択しなければならなくな
るが、この発明では、速度域切換手段を操作して高速走
行段である第３速、第４速を選択、すなわち、スイッチ
１３を閉路すると、可変リリーフ弁１４゜１５の設定圧
力が上昇し、走行モータ８ば、更に大きい出力軸−・の
負荷トルクにも耐えられる大出力トルクを発生し、その
結果、走行特性線図は第２図の実線で示す線図ｍ、ｒｖ
となり、最大駆動力はＦ、、Ｆ、が保証される。It was designed to be. By doing this, as long as you look at only the maximum speed on the diagram, ■ and ° are ■
, ■ 3° increases to V4, but when the output torque of the traveling motor 8 is the same, those traveling characteristic diagrams are as follows.
As shown by the dotted lines ■'' and ■゛ in the figure, the respective maximum driving forces F are smaller than F3, F3 is smaller than F4, and F is smaller than F4.
l, and even if the running resistance increases slightly, such as when driving on a gentle slope or on a rough road, it will run wI! However, in this invention, the speed range switching means can be operated to select the high-speed 3rd and 4th gears. When selected, that is, when the switch 13 is closed, the set pressure of the variable relief valves 14 and 15 increases, and the travel motor 8 generates a large output torque that can withstand the even larger load torque of the output shaft. , the driving characteristic diagram is the diagram m, rv shown by the solid line in Fig. 2.
Therefore, the maximum driving force is guaranteed to be F,,F.
以上の実施例においては、トランスファケース９の走行
動力系歯車比を選択的に変更する受信部ａおよび可変リ
リーフ弁１４．１５の受信部す。In the embodiments described above, the receiver a selectively changes the driving power system gear ratio of the transfer case 9 and the receivers of the variable relief valves 14 and 15.
ｂに作用する信号媒体として、パイロットポンプ４から
得られる圧油をバイロフト圧として使用したが、この発
明における信号媒体は必ずしもパイロット圧油である必
要はなく、使用する切換弁などの機器のｍｉに適合した
空気圧、電気であってもよく、また、速度域切換手段の
作動によりスイッチ１３が開閉して電気信号を切換弁１
ｉ、１２に供給するようにしたが、このときの信号媒体
も上記同様、電気以外の媒体に置き換え得ることは勿論
で、要は、速度域切換手段の操作に連動して、走行動力
伝達系の歯車比が変化するとたちに、メインポンプの圧
油吐出管路に設けた可変リリーフ弁の設定圧力が自動的
に変動して、走行モータの負荷に対応すれば良いのであ
る。The pressure oil obtained from the pilot pump 4 was used as the viroft pressure as the signal medium acting on the pressure b, but the signal medium in this invention does not necessarily have to be the pilot pressure oil, and may be used depending on the mi of the equipment such as the switching valve used. The appropriate pneumatic pressure or electricity may be used, and the switch 13 opens and closes by operating the speed range switching means to send an electrical signal to the switching valve 1.
Although the signal medium at this time can of course be replaced with a medium other than electricity as described above, the point is that the signal medium in this case can be replaced with a medium other than electricity. As soon as the gear ratio of the main pump changes, the set pressure of the variable relief valve provided in the pressure oil discharge line of the main pump automatically changes to correspond to the load of the travel motor.
発明の効果
油圧駆動方式のホイール式建設機樒の走行動力伝達系の
計画に当り、この発明の走行油圧回路を採用することを
前提として設計することにより、通常の小移動のための
低速走行と、回送などのための高速走行の速度域の範囲
を広く設定することができる。このとき、走行モータと
走行輪との間の動力伝達系の減速比が大きい低速走行域
においても、走行モータの出力Ｉ・ルクが過大とならな
いよう、可変リリーフ弁のリリーフ圧設定が可能である
から、プロペラシャフト、差動機、最終減速機などの強
度は必要最小限度でよく、経済的であり、しかも、この
動力伝達系を減速比の小ざい高速走行域で使用するとき
のみ、自動的に、可変リリーフ弁のリリーフ設定圧が上
昇し、走行モータの出力トルクが、低速走行域のときよ
りも増大するので、このときの駆動力は極端に減するこ
となく円滑な高速走行が得られ、機械の作業効率向上に
寄与することができる。Effects of the Invention When planning the traveling power transmission system for a hydraulically driven wheel-type construction machine, by designing it on the assumption that the traveling hydraulic circuit of the present invention would be adopted, it was possible to achieve low-speed traveling for normal small movements and It is possible to set a wide range of speed ranges for high-speed travel for transportation, etc. At this time, it is possible to set the relief pressure of the variable relief valve so that the output I and torque of the travel motor do not become excessive even in low-speed driving ranges where the reduction ratio of the power transmission system between the travel motor and the travel wheels is large. Therefore, the strength of the propeller shaft, differential, final reducer, etc. can be kept to the minimum necessary, making it economical. Moreover, when this power transmission system is used in high-speed driving ranges with small reduction ratios, automatic , the relief setting pressure of the variable relief valve increases and the output torque of the travel motor increases more than in the low-speed travel range, so smooth high-speed travel is obtained without an extreme reduction in the driving force at this time. It can contribute to improving machine work efficiency.
第１図はこの発明の実施例を示すホイール式油圧シッペ
ルの走行油圧回路の要部の電気・油圧系統図、第２図は
この発明にかかる機械の走行特性線図、第３図は従来技
術の機械の走行特性線図の１例、第４回は従来技術の機
械の走行油圧回路の要部を示す電気・油圧系統図である
。
２．３・・・・・・・メインポンプ
５．６・・・・・・・走行用油圧切換弁８・・・・・・
・・・・走行モータ
９・・・・・・・・・・トランスファケース１１．１２
・・・・・切換弁
１３・・・・・・・・・スイッチFig. 1 is an electric/hydraulic system diagram of the main parts of the running hydraulic circuit of a wheel-type hydraulic sippel showing an embodiment of the present invention, Fig. 2 is a running characteristic diagram of the machine according to the present invention, and Fig. 3 is a conventional technology. The fourth example is an electric/hydraulic system diagram showing the main parts of the running hydraulic circuit of a machine according to the prior art. 2.3... Main pump 5.6... Travel hydraulic switching valve 8...
...Travel motor 9...Transfer case 11.12
......Switch valve 13...Switch
Claims (1)
ンプからの吐出圧油により回転する油圧モータによって
多段階の走行速度域に切換可能の変速装置を介して走行
輪を駆動する如くしたホィール式建設機械の走行油圧回
路において、速度段階を低速域と高速域に切換える信号
を発する機能を有する速度域切換手段と、油圧ポンプの
吐出管路にあって、上記速度域切換手段の信号により、
リリーフ圧力を所定値に設定する機能を有する可変リリ
ーフ弁とを設けた建設機械の走行油圧回路。A wheel-type construction machine in which a hydraulic pump driven by an engine and a hydraulic motor rotated by the pressure oil discharged from the hydraulic pump drive the running wheels through a transmission that can be switched to a multi-step running speed range. In the traveling hydraulic circuit, there is a speed range switching means having a function of emitting a signal for switching the speed stage between a low speed range and a high speed range, and a discharge pipe of the hydraulic pump, in response to a signal from the speed range switching means,
A travel hydraulic circuit for construction machinery equipped with a variable relief valve having a function of setting relief pressure to a predetermined value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17163088A JPH0220453A (en) | 1988-07-08 | 1988-07-08 | Hydraulic circuit for running construction machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17163088A JPH0220453A (en) | 1988-07-08 | 1988-07-08 | Hydraulic circuit for running construction machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0220453A true JPH0220453A (en) | 1990-01-24 |
Family
ID=15926749
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17163088A Pending JPH0220453A (en) | 1988-07-08 | 1988-07-08 | Hydraulic circuit for running construction machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0220453A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994012363A1 (en) * | 1992-11-24 | 1994-06-09 | Kabushiki Kaisha Komatsu Seisakusho | Four-wheel drive device for a large dump truck |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57205637A (en) * | 1981-06-10 | 1982-12-16 | Hitachi Constr Mach Co Ltd | Oil-pressure circuit for travelling of construction machine |
-
1988
- 1988-07-08 JP JP17163088A patent/JPH0220453A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57205637A (en) * | 1981-06-10 | 1982-12-16 | Hitachi Constr Mach Co Ltd | Oil-pressure circuit for travelling of construction machine |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994012363A1 (en) * | 1992-11-24 | 1994-06-09 | Kabushiki Kaisha Komatsu Seisakusho | Four-wheel drive device for a large dump truck |
| GB2287922A (en) * | 1992-11-24 | 1995-10-04 | Komatsu Mfg Co Ltd | Four-wheel drive device for a large dump truck |
| US5564519A (en) * | 1992-11-24 | 1996-10-15 | Kabushiki Kaisha Komatsu Seisakusho | Four-wheel traveling system for tipper |
| GB2287922B (en) * | 1992-11-24 | 1997-06-18 | Komatsu Mfg Co Ltd | Four-wheel traveling system for tipper |
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