JPS5961633A - Oil-pressure circuit for oil-pressure working machine - Google Patents
Oil-pressure circuit for oil-pressure working machineInfo
- Publication number
- JPS5961633A JPS5961633A JP57168592A JP16859282A JPS5961633A JP S5961633 A JPS5961633 A JP S5961633A JP 57168592 A JP57168592 A JP 57168592A JP 16859282 A JP16859282 A JP 16859282A JP S5961633 A JPS5961633 A JP S5961633A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- switching valve
- valve
- hydraulic pump
- oil
- 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
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2253—Controlling the travelling speed of vehicles, e.g. adjusting travelling speed according to implement loads, control of hydrostatic transmission
Landscapes
- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は複数のアクチュエータを備えた油圧ショベルな
どの油圧作業機の油圧回路に係シ、特に走行モータ以外
のアクチュエータの増速のために３つ以上の油圧ポンプ
を備えた油圧作業機にあって、走行複合操作における操
作性の向上を図シうる油圧回路に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic circuit of a hydraulic working machine such as a hydraulic excavator that is equipped with a plurality of actuators, and in particular is equipped with three or more hydraulic pumps to increase the speed of actuators other than a travel motor. The present invention relates to a hydraulic circuit that can improve operability in combined traveling operations in a hydraulic working machine.
一般に油圧作業機例えば油圧ショベルは、旋回体と走行
体とともに、ブーム、アーム、パケットなど７５）ら成
るアタッチメントを備えており、これらはそれぞれ旋回
モータ、左右走行モータ、ブームシリンダ、アームシリ
ンダ、パケットシリンダなどのアクチュエータによって
駆動きれる。そして、これらのアクチュエータは方向切
換弁によシそれぞれ制御される。第１図は油圧ショベル
の全体構成を示す側面図、第２図は第１図の平面図であ
る。これらの図において、１は旋回体で、走行体２の上
部に配設され、旋回モータ３を駆動することにより旋回
する。４は左トラツクで、左走行モータ５によって駆動
する。６は右トラツクで、右走行モータ７によって駆動
する。８はブーム、９はアーム、１０はパケットで、こ
れらによって作業機が構成されている。々お、１１はブ
ーム８を作動させるブームシリンダ、１２はアーム９を
作動させるアームシリンダ、１３はパケット１０を作動
させるパケットシリンダである。In general, a hydraulic working machine, such as a hydraulic excavator, is equipped with a revolving body, a running body, and attachments such as a boom, an arm, and a packet75). It can be driven by actuators such as These actuators are each controlled by a directional control valve. FIG. 1 is a side view showing the overall configuration of a hydraulic excavator, and FIG. 2 is a plan view of FIG. 1. In these figures, reference numeral 1 denotes a revolving body, which is disposed above a traveling body 2 and rotates by driving a revolving motor 3 . 4 is a left truck, which is driven by a left traveling motor 5. 6 is a right truck, which is driven by a right travel motor 7. 8 is a boom, 9 is an arm, and 10 is a packet, which constitute a working machine. 11 is a boom cylinder that operates the boom 8; 12 is an arm cylinder that operates the arm 9; and 13 is a packet cylinder that operates the packet 10.
第３図は上記した油圧ショベルに具備される従来の油圧
回路の一例を示す回路図である。これらの図において、
２０は第１の油圧ポンプ、２１はパケット用方向切換弁
で、これは第１の油圧ポンプ２０とパケットシリンダ１
３との間に介設しである。２２はブーム用方向切換弁で
、パケット用方向切換弁２１とブームシリンダ１１との
間に介設しである。２３は右走行用方向切換弁で、ブー
ム用方向切換弁２２と右走行モータ７との間に介設しで
ある。なお、パケット用方向切換弁２１、ブーム用方向
切換弁２２、および右走行用方向切換弁２３は第１の油
圧ポンプ２０に対してパラレル接続にしである。上記し
た第１の油圧ポンプ２０゜方向切換弁２１，２２，２３
、及びパケットシリンダ１３、ブームシリンダ１１、右
走行モータ７によって１つの独立した油圧回路を構成し
である。FIG. 3 is a circuit diagram showing an example of a conventional hydraulic circuit included in the above-mentioned hydraulic excavator. In these figures,
20 is a first hydraulic pump, 21 is a packet directional control valve, which connects the first hydraulic pump 20 and the packet cylinder 1.
It is interposed between 3 and 3. Reference numeral 22 denotes a boom directional switching valve, which is interposed between the packet directional switching valve 21 and the boom cylinder 11. Reference numeral 23 denotes a right travel direction switching valve, which is interposed between the boom direction change valve 22 and the right travel motor 7. Note that the packet directional switching valve 21, the boom directional switching valve 22, and the right travel directional switching valve 23 are connected in parallel to the first hydraulic pump 20. The above-described first hydraulic pump 20° directional control valves 21, 22, 23
, the packet cylinder 13, the boom cylinder 11, and the right travel motor 7 constitute one independent hydraulic circuit.
才た、２４は第２の油圧ポンプ、２６は旋回用方向切換
弁で、これは第２の油圧ポンプ２４と旋回モータ３との
間に介設しである。２７は左走行用方向切換弁で、旋回
用方向切換弁２６と左走行モータ５との間に介設しであ
る。旋回用方向切換弁２６と左走行用方向切換弁２７は
パラレルに接続しである。２５はアーム用方向切換弁で
、左走行用方向切換弁２７とアームシリンダ１２との間
に介設してあシ、タンデムに接続しである。油圧ショベ
ルでは一般にアーム速度が重視されるが、この回路では
左走行用方向切換弁２７とアーム用方向切換弁２５とを
連絡する管路３１に、第３の油圧ポンプ２８からの圧油
を合流させるようにしである。なお、３０は第２の油圧
ポンプ２４の吐出油供給回路とアーム用方向切換弁２５
０入力ボートとを連絡する管路である。上記した第２０
油圧ポンプ２４、第３の油圧ポンプ２８、方向切換弁２
５．２６，２７、及びアームシリンダ１２、旋回モータ
ー４＃３、左走行モータ５によって別の独立した油圧回
路を構成しである。24 is a second hydraulic pump, and 26 is a swing direction switching valve, which is interposed between the second hydraulic pump 24 and the swing motor 3. Reference numeral 27 denotes a left travel direction switching valve, which is interposed between the turning direction change valve 26 and the left travel motor 5. The turning direction switching valve 26 and the left travel direction switching valve 27 are connected in parallel. Reference numeral 25 denotes an arm directional switching valve, which is interposed between the left running directional switching valve 27 and the arm cylinder 12 and connected in tandem with the arm. In hydraulic excavators, arm speed is generally important, but in this circuit, pressure oil from the third hydraulic pump 28 is merged into a pipe 31 that connects the left travel directional control valve 27 and the arm directional control valve 25. It's like letting them do it. Note that 30 is a discharge oil supply circuit of the second hydraulic pump 24 and an arm directional control valve 25.
This is a conduit that connects with the 0 input boat. 20th above
Hydraulic pump 24, third hydraulic pump 28, directional switching valve 2
5.26, 27, the arm cylinder 12, the swing motor 4#3, and the left travel motor 5 constitute another independent hydraulic circuit.
ところでこのように構成しである従来の油圧回路にあっ
ては、次に列挙する不具合がある。すなわち、
（１）走行中にアーム９を操作する場合、アーム用方向
切換弁２５と左走行用方向切換弁２７とは管路３０で連
絡しであることから、左走行用方向切換弁２７側に比較
して負荷の軽いアーム用方向切換弁２５の方に圧油が流
れる傾向となシ、その結果左トラツク４の作動が右トラ
ツク６の作動に比べて遅くなシやすく、車体の直進走行
が不能とがる０
（２）走行中に旋回操作を行なう場合、旋回用方向切換
弁２６と左走行用方向切換弁２７とはパラレルに接続し
であることから、左走行用方向切換弁２７側に比べて旋
回用方向切換弁２６の方に圧油が流れる傾向となり、そ
の結果、左トラツク４の作動が右トラツク６の作動に比
べて遅くなりやすく、車体の直進走行が不能となる。ま
た走行負荷が軽い場合には、旋回に要する圧力が不足し
、旋回動作をおこわせにくい。However, the conventional hydraulic circuit configured as described above has the following problems. That is, (1) When operating the arm 9 while traveling, since the arm directional switching valve 25 and the left running directional switching valve 27 are connected through the conduit 30, the left running directional switching valve 27 side Pressure oil tends to flow toward the arm directional control valve 25, which has a lighter load compared to the directional control valve 25, and as a result, the operation of the left truck 4 tends to be slower than the operation of the right truck 6, which prevents the vehicle from traveling straight. (2) When performing a turning operation while driving, since the turning direction switching valve 26 and the left running direction switching valve 27 are connected in parallel, the left running direction switching valve 27 As a result, the operation of the left truck 4 tends to be slower than the operation of the right truck 6, making it impossible for the vehicle to travel straight. Furthermore, when the running load is light, the pressure required for turning is insufficient, making it difficult to perform a turning operation.
（３） 走行中にパケット１０を操作する場合、パケ
ット用方向切換弁２１と右走行用方向切換弁２３とはパ
ラレル接続にしであることから、右走行用方向切換弁２
３側に比較して負荷の軽いパケット用方向切換弁２１の
方に圧油が流れる傾向になり、その結果、右トラツク６
の作動が左トラツク４に比べて遅くなシ、車体の直進走
行が不能になる。(3) When operating the packet 10 while driving, since the packet directional switching valve 21 and the right running directional switching valve 23 are connected in parallel, the right running directional switching valve 2
Pressure oil tends to flow toward the packet directional control valve 21, which has a lighter load than the right truck 6.
The operation of the left track 4 is slower than that of the left track 4, making it impossible for the vehicle to drive straight.
（４）走行中にプーム８を操作する場合、プーム用方向
切換弁２２と右走行用方向切換弁２３とはパラレルに接
続しであることから、ブーム用方向切換弁２２にはプー
ム８を上げるのに十分な圧油が供給されず、それ故、プ
ーム８が上がらなくなる事態を生じる。(4) When operating the poom 8 while traveling, the poom 8 is raised to the boom directional control valve 22 because the boom directional control valve 22 and the right travel directional control valve 23 are connected in parallel. Sufficient pressure oil is not supplied for this purpose, resulting in a situation where the pool 8 cannot be raised.
本発明はこのようが従来技術における実情に鑑みてなさ
れたもので、その目的は、走行中に各種のアクチュエー
タを作動させる場合に、走行体を構成する左右トラック
に均一が走行力を得ることができる油圧作業機の油圧回
路を提供することにある。The present invention has been made in view of the actual situation in the prior art, and its purpose is to obtain uniform running force on the left and right tracks that make up the running body when operating various actuators during running. Our goal is to provide hydraulic circuits for hydraulic working machines that can.
この目的全達成するために本発明は、アクチュエータに
圧油を供給する複数の油圧ポンプのうちの第１の油圧ポ
ンプに、左右のうちの定められた一方の走行用方向切換
弁が優先するように配設された方向切換弁群を接続する
とともに、第２の油圧ポンプに旋回用方向切換弁、ブー
ム用方向切換弁のうちの少なくとも１つを接続し、その
下流に他方の走行用方向切換弁をタンデム接続し、この
他方の走行用方向切換弁の入力ボートと上流に位置する
第２の油圧ポンプの吐出油供給回路とを圧力調整手段を
介して連絡し、かつ上記一方の走行用方向切換弁の入力
ボートと上記他方の走行用方向切換弁の入力ボートとを
接続管によって連絡し、上記他方の走行用方向切換弁の
下流にアーム用方向切換弁をタンデム接続し、これらの
他方の走行用方向切換弁とアーム用方向切換弁とを連絡
する管路に、上記第１の油圧ポンプ及び第２の油圧ポン
プとは異なる別の第３の油圧ポンプからの圧油を合流さ
せた構成にしである。In order to achieve all of these objects, the present invention provides a system in which a predetermined one of the left and right travel direction switching valves is given priority to the first hydraulic pump of a plurality of hydraulic pumps that supply pressure oil to the actuator. At the same time, the second hydraulic pump is connected to at least one of the directional switching valve for swinging and the directional switching valve for boom, and the other directional switching valve for traveling is connected to the second hydraulic pump. The valves are connected in tandem, and the input port of the other travel direction switching valve is connected to the discharge oil supply circuit of the second hydraulic pump located upstream through a pressure regulating means, and The input boat of the switching valve and the input boat of the other traveling directional switching valve are connected by a connecting pipe, and the arm directional switching valve is connected in tandem downstream of the other traveling directional switching valve, and A configuration in which pressure oil from a third hydraulic pump different from the first hydraulic pump and the second hydraulic pump is merged into a pipe line that connects the traveling direction switching valve and the arm direction switching valve. It's Nishide.
以下、本発明の油圧作業機の油圧回路を図に基づいて説
明する。第４図は本発明の第１の実施例の構成を示す回
路図、第５図は本発明の第２の実施例の構成を示す回路
図、第６図は本発明の第３の実施例の構成を示す回路図
である。なおこれらの図において、前述した第１図がい
し第３図に示す部材と同じ部材は同一符号で示しである
。Hereinafter, the hydraulic circuit of the hydraulic working machine of the present invention will be explained based on the drawings. FIG. 4 is a circuit diagram showing the configuration of the first embodiment of the invention, FIG. 5 is a circuit diagram showing the configuration of the second embodiment of the invention, and FIG. 6 is the circuit diagram of the third embodiment of the invention. FIG. In these figures, the same members as those shown in the insulators in FIG. 1 and FIG.
第４図に示す第１の実施例におっては、右走行モータ７
を作動させる右走行用方向切換弁２３を、第１の油圧ポ
ンプ２０に対し最上流にタンデム接続し、その下流にプ
ームシリンダ１１を作動させるブーム用方向切換弁２２
とパケットシリンダ１３せる旋回用方向切換弁２６と、
ブームシリンダ１１を作動させる別のブーム用方向切換
弁４４とを第２の油圧ポンプ２４に対してパラレルに接
続するとともに、左走行モータ５を作動させる左走行用
方向切換弁２７をブーム用方向切換弁４４の下流にタン
デムに接続しである。そして、左走行用方向切換弁２７
の入力ボートと上流に位置する第２の油圧ポンプ２４の
吐出油供給回路とを、途中に逆止弁４１ｃ及び圧力調整
手段例えば絞シ４２を介設しである管路４０によって接
続しである。また、第１の油圧ポンプ２０の吐出油供給
回路と左走行用方向切換弁２７の入力ホートラ、逆止弁
４１ａを介して接続管４３で連絡しである。なお、４１
ｂは左走行用方向切換弁２７の入力ボート付近に配置し
た逆止弁である。また、左走行用方向切換弁２７の下流
に、アームシリンダ１２を作動させるアーム用方向切換
弁２５をタンデム接続してあシ、これらの方向切換弁２
７．２５の中間の管路３１に第３の油圧ポンプ２８の圧
油を合流させ、アームを増速するように構成しである。In the first embodiment shown in FIG.
A right travel directional switching valve 23 that operates the right running directional switching valve 23 is connected in tandem at the most upstream side of the first hydraulic pump 20, and a boom directional switching valve 22 that operates the boom cylinder 11 is connected downstream thereof.
and a directional switching valve 26 for turning the packet cylinder 13,
Another boom directional switching valve 44 that operates the boom cylinder 11 is connected in parallel to the second hydraulic pump 24, and the left running directional switching valve 27 that operates the left running motor 5 is connected to the boom directional switching valve 44 that operates the boom cylinder 11. They are connected in tandem downstream of the valve 44. And the left travel direction switching valve 27
The input boat and the discharge oil supply circuit of the second hydraulic pump 24 located upstream are connected by a conduit 40 with a check valve 41c and a pressure regulating means, such as a restrictor 42, interposed in the middle. . Further, the discharge oil supply circuit of the first hydraulic pump 20 is connected to the input hole of the left travel direction switching valve 27 by a connecting pipe 43 via a check valve 41a. In addition, 41
b is a check valve disposed near the input boat of the left travel direction switching valve 27. In addition, an arm directional switching valve 25 for operating the arm cylinder 12 is connected in tandem downstream of the left travel directional switching valve 27, and these directional switching valves 2
7.25, the pressure oil of the third hydraulic pump 28 is merged into the intermediate pipe line 31 to increase the speed of the arm.
なお、上述した逆止弁４１ａ＋ ４１ｂ＋ ４１ｃは吐
出油の逆流防止用に設けたものである。Note that the above-mentioned check valves 41a+ 41b+ 41c are provided to prevent backflow of discharged oil.
このように構成しである油圧回路における作用は次のと
おシである。The operation of the hydraulic circuit constructed in this way is as follows.
走行用方向切換弁２３．２７を単独操作する場合には、
通常の作動と同じである。すなわち、第１の油圧ポンプ
２０の吐出油は優先的に右走行用方向切換弁２３に供給
され、第２の油圧ポンプ２４の吐出油はセンタバイパス
回路から逆止弁４１ｂを通って左走行用方向切換弁２７
に供給される。When operating the traveling direction switching valve 23, 27 independently,
Same as normal operation. That is, the oil discharged from the first hydraulic pump 20 is preferentially supplied to the right-hand direction switching valve 23, and the oil discharged from the second hydraulic pump 24 is supplied from the center bypass circuit to the left-hand direction changeover valve 41b through the check valve 41b. Directional switching valve 27
supplied to
ｔｉ、走行用方向切換弁２３．２７を操作しての走行中
に、旋回用方向切換弁２６を操作する場合には、管路４
０に絞り４２があるので、第２の油圧ポンプ２４の吐出
油は、旋回用方向切換弁２６を介して旋回に優先して使
用され、一部の圧油のみが左走行用方向切換弁２７に供
給される。それ散在走行モータ５への油量が不足するが
、接続管４３によシ第１の油圧ポンプ２０の吐出油が左
走行モータ５及び右走行モータ７に同じように供給され
る。ここで左走行モータ５と右走行モータ７への油供給
回路は、接続管４３によってパラレルに接続されておシ
、油量が必ずしも等分に流れず直進しないように思われ
るが、走行体であるクローラ自身の持つ本質的な直進性
によって直進走行が保たれるものである。ti, when operating the turning direction switching valve 26 while driving by operating the running direction switching valve 23, 27, the pipe line 4
Since there is a throttle 42 at the left side, the oil discharged from the second hydraulic pump 24 is used preferentially for turning via the turning directional switching valve 26, and only a part of the pressure oil is passed through the left running directional switching valve 27. supplied to Although the amount of oil to the scattered traveling motors 5 is insufficient, the oil discharged from the first hydraulic pump 20 is supplied to the left traveling motor 5 and the right traveling motor 7 in the same way through the connecting pipe 43. Here, the oil supply circuits to the left travel motor 5 and the right travel motor 7 are connected in parallel by a connecting pipe 43, and it seems that the oil amount does not necessarily flow evenly and does not travel straight, but in the case of a traveling object. A crawler's inherent ability to travel in a straight line keeps it running straight.
また、走行用方向切換弁２３．２７を操作しての走行中
に、ブーム用方向切換弁２２．４４’ｔ−操作する場合
、第１の油圧ポンプ２０の圧油は、一方のブーム用方向
切換弁２２がタンデム接続であるためこのブーム用方向
切換弁２２には流れないが、第２の油圧ポンプ２４の圧
油は絞シ４２があるために優先的に他方のブーム用方向
切換弁４４に供給され、それ故、走行圧が低くなっても
圧油がブームシリンダ１１に供給され、確実にブームが
上昇する。逆にブームを下げる場合、少なくとも第１の
油圧ポンプ２０の圧油は走行用に確保されるので、従来
の様に極端に走行速度が減少することがかい。またブー
ムシリンダ１１の作動によって第２の油圧ポンプ２４か
ら左走行用方向切換弁２７に供給される圧油は減少する
が、接続管４３によって第１の油圧ポンプ２０の圧油の
一部が左走行用方向切換弁２７に供給されるので、先に
述べた理由で、ブーム作動時にあっても走行の直進性を
維持できる。In addition, when operating the boom direction changeover valve 22.44't while traveling by operating the travel direction changeover valve 23.27, the pressure oil of the first hydraulic pump 20 is Since the switching valves 22 are connected in tandem, the flow does not flow to this boom directional switching valve 22, but the pressure oil of the second hydraulic pump 24 is preferentially transferred to the other boom directional switching valve 44 because of the throttle valve 42. Therefore, even if the running pressure becomes low, pressure oil is supplied to the boom cylinder 11 and the boom is reliably raised. On the other hand, when lowering the boom, the pressure oil of at least the first hydraulic pump 20 is reserved for traveling, so there is no need for the traveling speed to be drastically reduced as in the conventional case. In addition, the pressure oil supplied from the second hydraulic pump 24 to the left travel direction switching valve 27 decreases due to the operation of the boom cylinder 11, but a part of the pressure oil from the first hydraulic pump 20 is transferred to the left by the connecting pipe 43. Since the fuel is supplied to the travel direction switching valve 27, the straightness of travel can be maintained even when the boom is activated for the reason stated above.
マタ、走行用方向切換弁２３．２７’に操作しての走行
中にアーム用方向切換弁２５を操作する場合、左走行用
方向切換弁２７とアーム用方向切換弁２５とはタンデム
接続にしであるため、走行時にアーム作動をおこなって
も、第１の油圧ポンプ２０及び第２の油圧ポンプ２４の
圧油がそれぞれの走行用方向切換弁２３．２７に供給さ
れ、直進性を維持できる。When operating the arm directional switching valve 25 while driving with the running directional switching valve 23 or 27', the left running directional switching valve 27 and the arm directional switching valve 25 must be connected in tandem. Therefore, even if the arm is operated during traveling, the pressure oil of the first hydraulic pump 20 and the second hydraulic pump 24 is supplied to the respective traveling direction switching valves 23, 27, and straight-line traveling can be maintained.
ところでこの第１の実施例にあっては、方向切換弁２６
．４４．２７のうちの少なくとも１つを切換えると、第
２の油圧ポンプ２４からの圧油はアーム用方向切換弁２
５に供給されなくなるので、第３の油圧ポンプ２８の容
量が小さい場合には、アーム速度が急変し、旋回とのマ
ツチングが悪くなるという問題がある。By the way, in this first embodiment, the directional control valve 26
．． 44. When at least one of 27 is switched, the pressure oil from the second hydraulic pump 24 is transferred to the arm directional control valve 2.
Therefore, if the capacity of the third hydraulic pump 28 is small, there is a problem that the arm speed changes suddenly and the matching with the turning becomes poor.
第５図に示す第２の実施例は上述した問題点をも解決す
るものである。この第２の実施例は第４図に示す第１の
実施例と基本的には相違はがいが、異なる点は第２の油
圧ポンプ２４の吐出油供給回路と、アーム用方向切換弁
２５の入力ボートとを逆止弁４１ｄを介して管路５０で
連絡した構成にしである。このように構成したことによ
シ、アーム用方向切換弁２５の切換え中に上流側の方向
切換弁２６．４４．２７を切換え作動させた場合でも、
管路５０を介してアーム用方向切換弁２５に第２の油圧
ポンプ２４の圧油が供給されるので、アーム速度の極端
な変化を生じることがない。The second embodiment shown in FIG. 5 also solves the above-mentioned problems. This second embodiment is fundamentally different from the first embodiment shown in FIG. The configuration is such that it is connected to the input boat through a conduit 50 via a check valve 41d. With this configuration, even if the upstream directional switching valve 26, 44, 27 is switched and operated while the arm directional switching valve 25 is being switched,
Since the pressure oil of the second hydraulic pump 24 is supplied to the arm directional switching valve 25 via the pipe line 50, extreme changes in arm speed will not occur.
また、走行用方向切換弁２３．２７を操作しての走行中
に、アーム用方向切換弁２５を操作する場合には、第１
の油圧ポンプ２０の圧油は右走行用方向切換弁２３を経
て右走行モータ７に送られ、これを駆動する。一方、第
２の油圧ポンプ２４からの圧油は、左走行用方向切換弁
２７に供給されると同時に、管路５０を通ってアーム用
方向切換弁２５にも供給される。このとき、第２の油圧
ポンプ２４の圧油は上記したように一部がアームシリン
ダ１２に流れ、その残シが左走行用方向切換弁２７に流
れるので、この左走行用方向切換弁２７への油量は不足
するが、接続管４３によって第１の油圧ポンプ２０の圧
油が左走行用方向切換弁２７にも供給されるので、左走
行モータ５は右走行モータ７と同じように駆動される。In addition, when operating the arm directional switching valve 25 while driving by operating the running directional switching valve 23, 27, the first
Pressure oil from the hydraulic pump 20 is sent to the right travel motor 7 via the right travel direction switching valve 23 to drive it. On the other hand, the pressure oil from the second hydraulic pump 24 is supplied to the left travel direction switching valve 27 and at the same time is also supplied to the arm direction switching valve 25 through the conduit 50. At this time, a part of the pressure oil of the second hydraulic pump 24 flows to the arm cylinder 12 as described above, and the remaining part flows to the left travel direction switching valve 27. Although the amount of oil is insufficient, the pressure oil of the first hydraulic pump 20 is also supplied to the left travel direction switching valve 27 through the connecting pipe 43, so the left travel motor 5 is driven in the same way as the right travel motor 7. be done.
このため前述した理由によって直進性を維持することが
できる。For this reason, straightness can be maintained for the reasons mentioned above.
また、第３の油圧ポンプ２８の圧油によって、アーム−
走行複合操作による湿地脱出をおこなう場合でもアーム
力を確保することができる。また、走行と旋回、走行と
ブームの複合操作性は第１の実施例とまったく同等であ
る。Also, the arm is moved by pressure oil from the third hydraulic pump 28.
Arm strength can be secured even when escaping from a wetland through combined running maneuvers. Further, the combined operability of traveling and turning, and traveling and boom is exactly the same as in the first embodiment.
なお、上述した第１の実施例及び第２の実施例では、走
行用方向切換弁２３．２’７ｅ操作しての走行中にパケ
ット用方向切換弁２１を操作しても、このパケット用方
向切換弁２１はタンデムに接続しであることからパケッ
トが作動しないという問題点がある。In addition, in the first embodiment and the second embodiment described above, even if the packet direction changeover valve 21 is operated while the travel direction changeover valve 23.2'7e is operated, the packet direction changeover valve 23.2'7e is operated. Since the switching valves 21 are connected in tandem, there is a problem that the packet does not operate.
第６図に示す第３の実施例は上記の問題点をも解決する
ものである。第３の実施例は第４図に示す第１の実施例
と基本的に相違はないが、異なる点は、第１の油圧ポン
プ２０の吐出油供給回路と左走行用方向切換弁２７の入
力ボートと全連絡する接続管４３中に設けた逆止弁４１
ａの下流側と、パケット用方向切換弁２１０入力ボート
を連絡する管路５１を設け、その管路５１の途中に圧力
調整手段例えば絞シ５２を介設した構成にしである。The third embodiment shown in FIG. 6 also solves the above problems. The third embodiment is basically the same as the first embodiment shown in FIG. A check valve 41 installed in a connecting pipe 43 that fully communicates with the boat.
A conduit 51 is provided that connects the downstream side of the directional control valve 210 with the input port of the packet directional switching valve 210, and a pressure regulating means, for example, a restrictor 52 is interposed in the middle of the conduit 51.
この第３の実施例では、走行用方向切換弁２３゜２７を
操作しての走行中に、パケット用方向切換弁２１を操作
した場合、第１の油圧ポンプ２０と第２の油圧ポンプ２
４のいずれか、！ｉたけ双方の圧油の一部が、接続管４
３及び管路５１を経てパケット用方向切換弁２１に供給
され、パケットシリンダ１３を作動させる。なお、管路
５１には絞シ５２を介設しであるが、一般にパケット作
動圧は走行圧よシもかなシ低いために、パケット１０は
確実に作動する。またこのとき、接続管４３があるため
走行用方向切換弁２３．２７には同じように圧油が供給
されるので、前述したような理由によシこのときの走行
の直進性は維持される。In this third embodiment, when the packet direction changeover valve 21 is operated while the travel direction changeover valves 23 and 27 are operated, the first hydraulic pump 20 and the second hydraulic pump 2
Any of 4! A portion of the pressure oil on both sides is connected to the connecting pipe 4.
3 and pipe 51 to the packet directional switching valve 21, which operates the packet cylinder 13. Although a constrictor 52 is interposed in the conduit 51, the packet 10 operates reliably because the packet operating pressure is generally lower than the running pressure. Also, at this time, since the connecting pipe 43 is present, pressurized oil is similarly supplied to the travel direction switching valves 23 and 27, so that the straightness of travel is maintained for the reasons mentioned above. .
また絞シ５２は、アーム高負荷時にパケット用方向切換
弁２１を操作した場合に、接続Ｗ４３及び管路５１を経
て第２の油圧ポンプ２４の圧油が全量、パケット用方向
切換弁２１に供給され、極端にパケット作動が速くなる
のを防ぐために必要である。この第３の実施例における
旋回・走行、アーム・走行、ブーム・走行の複合操作性
は、前述した第１の実施例及び第２の実施例とまったく
同等である。In addition, the throttle valve 52 supplies the entire amount of pressure oil from the second hydraulic pump 24 to the packet directional control valve 21 via the connection W43 and the conduit 51 when the packet directional control valve 21 is operated when the arm is under high load. This is necessary to prevent packet processing from becoming extremely fast. The combined operability of turning/traveling, arm/traveling, and boom/traveling in this third embodiment is exactly the same as in the first and second embodiments described above.
一部た上記した第１、第２、第３の実施例では、管路４
０に介設する圧力調整手段として絞り４２を挙げたが、
この絞シ４２の代シにリリーフ弁を設ける構成にしても
よい。In the first, second and third embodiments described above, the pipe line 4
Although the throttle 42 was mentioned as a pressure adjustment means interposed at 0,
A relief valve may be provided in place of the restrictor 42.
！ｉた、接続管４３の途中に開閉弁を介設し、任意に接
続管４３の断接が可能になるようにしてもよい。! Alternatively, an on-off valve may be provided in the middle of the connecting pipe 43 so that the connecting pipe 43 can be connected or disconnected as desired.
以上述べたように本発明の油圧作業機の油圧回路は、走
行モータ以外のアクチュエータの増進のために３つ以上
の油圧ポンプを備えた油圧作業機にあって、走行中に各
種のアクチュエータを作動させる場合に、接続管を介し
て第１の油圧ポンプおるいは第２の油圧ポンプからの圧
油金左走行モータ及び右走行モータに均等に供給するこ
とができ、走行体を構成する左右トラックに均一な走行
力を得ることができ、それ故、各種のアクチュエータを
適正に作動させることができるとともに、直進走行が可
能となる効果がある。As described above, the hydraulic circuit of the hydraulic working machine of the present invention is a hydraulic working machine equipped with three or more hydraulic pumps for increasing actuators other than the travel motor, and operates various actuators while traveling. In this case, the pressure oil can be evenly supplied from the first hydraulic pump or the second hydraulic pump to the left traveling motor and the right traveling motor through the connecting pipe, and the left and right trucks forming the traveling body can be Uniform running force can be obtained, and therefore, various actuators can be operated properly, and straight-line running is possible.
第１図は本発明の対象とする油圧作業機の一例として挙
げた油圧ショベルの全体構成金示す側面図、第２図は第
１図の平面図、第３図は従来の油圧作業機の油圧回路の
一例を示す回路図、第４図は本発明の油圧作業機の油圧
回路の第１の実施例を示す回路図、第５図は本発明の第
２の実施例を示す回路図、第６図は本発明の第３の実施
例を示す回路図である。
１・・・・・・旋回体、２・・・・・・走行体、３・・
・・・・旋回モータ、４・・・・・・左トラツク、５・
・・・・・左走行モータ、６・・・・・・右トラツク、
７・・・・・・右走行モータ、８・・・・・・ブーム、
９・・・・・・アーム、１０・・・・・・パケット、１
１・・・・・・ブームシリンダ、１２・・・・・・アー
ムシリンダ、１３・・・・・・パケットシリンダ、２０
・・・・・・第１の油圧ポンプ、２１・・・・・・パケ
ット用方向切換弁、２２．４４・・・・・・ブーム用方
向切換弁、２３・・・・・・右走行用方向切換弁、２４
・・・・・・第２の油圧ポンプ、２５・・・・・・アー
ム用方向切換弁、２６・・・・・・旋回用方向切換弁、
２７・・・・・・左走行用方向切換弁、２８・・・・・
・第３の油圧ポンプ、３］、４０．５０．５１・・・・
・・管路、４１ａ、４１ｂ、４１ｃ、４１ｄ−逆止弁、
４２゜５２・・・・・・絞シ（圧力調整手段）、４３・
・・・・・接続管。
第１図
２
０
第２図
−１（Fig. 1 is a side view showing the overall configuration of a hydraulic excavator as an example of a hydraulic working machine to which the present invention is applied, Fig. 2 is a plan view of Fig. 1, and Fig. 3 is a hydraulic pressure of a conventional hydraulic working machine. 4 is a circuit diagram showing an example of the circuit; FIG. 4 is a circuit diagram showing a first embodiment of a hydraulic circuit for a hydraulic working machine of the present invention; FIG. 5 is a circuit diagram showing a second embodiment of the present invention; FIG. 6 is a circuit diagram showing a third embodiment of the present invention. 1... Rotating body, 2... Traveling body, 3...
...Swivel motor, 4...Left truck, 5.
...Left travel motor, 6...Right truck,
7...Right travel motor, 8...Boom,
9...Arm, 10...Packet, 1
1...Boom cylinder, 12...Arm cylinder, 13...Packet cylinder, 20
......First hydraulic pump, 21...Packet directional switching valve, 22.44...Boom directional switching valve, 23...Right travel Directional switching valve, 24
...Second hydraulic pump, 25...Arm directional switching valve, 26...Swivel directional switching valve,
27... Directional switching valve for left travel, 28...
・Third hydraulic pump, 3], 40.50.51...
... Pipe line, 41a, 41b, 41c, 41d-check valve,
42゜52... Throttle (pressure adjustment means), 43.
...Connecting pipe. Fig. 1 2 0 Fig. 2-1 (
Claims (1)
駆動される複数のアクチュエータと、上記油圧ポンプか
ら上記アクチュエータに供給される圧油の方向及び流量
を制御する複数の方向切換弁とを備えた油圧作業機の油
圧回路において、上記油圧ポンプのうちの第１の油圧ポ
ンプに、左右のうちの定められた一方の走行用方向切換
弁が優先するように配設された方向切換弁群を接続する
とともに、第２の油圧ポンプに旋回用方向切換弁及びブ
ーム用方向切換弁のうちの少なくとも１つを接続し、そ
の下流に他方の走行用方向切換弁をタンデム接続し、こ
の他方の走行用方向切換弁の入力ポートと上記第２の油
圧ポンプの吐出油供給回路とを圧力調整手段を介して連
絡し、かつ上記第１の油圧ポンプの吐出油供給回路と上
記他方の走行用方向切換弁の入力ポートとを途中に逆止
弁を介設した接続管で連絡し、上記他方の走行用方向切
換弁の下流にアーム用方向切換弁をタンデム接続し、こ
れらの他方の走行用方向切換弁とアーム用方向切換弁と
を連絡する管路に、上記第１の油圧ポンプ及び第２の油
圧ポンプとは異なる別の油圧ポンプからの圧油を合流さ
せることを特徴とする油圧作業機の油圧回路。 ２、圧力調整手段が絞りであることを特徴とする特許請
求の範囲第１項記載の油圧作業機の油圧回路０ ３、圧力調整手段がリリーフ弁であることを特徴とする
特許請求の範囲第１項記載の油圧作業機の油圧回路。 ４、第２の油圧ポンプの吐出油供給回路とアーム用方向
切換弁とを逆止弁を介して連絡することを特徴とする特
許請求の範囲第２項または第３項記載の油圧作業機の油
圧回路。 ５、接続管中に介設した逆止弁の下流と、第１の油圧ポ
ンプに接続した方向切換弁のうちの少なくとも１つの方
向切換弁の入力ポートとを、圧力調整手段を介して連絡
したことを特徴とする特許請求の範囲第２項ないし第４
項のいずれかに記載の油圧作業機の油圧回路。[Claims] 1. A plurality of hydraulic pumps, a plurality of actuators driven by these hydraulic pumps, and a plurality of directional switches that control the direction and flow rate of pressure oil supplied from the hydraulic pumps to the actuators. In the hydraulic circuit of a hydraulic working machine equipped with a valve, a direction in which a first hydraulic pump of the hydraulic pumps is arranged so that a predetermined one of the left and right travel direction switching valves has priority. Connecting the switching valve group, connecting at least one of the swing directional switching valve and the boom directional switching valve to the second hydraulic pump, and connecting the other travel directional switching valve in tandem downstream thereof, The input port of the other travel directional control valve and the discharge oil supply circuit of the second hydraulic pump are connected via a pressure regulating means, and the discharge oil supply circuit of the first hydraulic pump and the other Connect the input port of the travel directional control valve with a connecting pipe with a check valve interposed in the middle, and connect the arm directional control valve in tandem downstream of the other travel directional control valve. It is characterized in that pressure oil from another hydraulic pump different from the first hydraulic pump and the second hydraulic pump is merged into the conduit connecting the traveling direction switching valve and the arm direction switching valve. Hydraulic circuit of hydraulic working machine. 2. The hydraulic circuit for a hydraulic working machine according to claim 1, in which the pressure adjustment means is a throttle. 3. The claim, in which the pressure adjustment means is a relief valve. A hydraulic circuit of the hydraulic working machine according to item 1. 4. A hydraulic working machine according to claim 2 or 3, characterized in that the discharge oil supply circuit of the second hydraulic pump and the arm directional switching valve are connected through a check valve. Hydraulic circuit. 5. The downstream side of the check valve interposed in the connecting pipe and the input port of at least one directional control valve of the directional control valves connected to the first hydraulic pump are connected via a pressure regulating means. Claims 2 to 4 are characterized in that:
A hydraulic circuit for a hydraulic working machine according to any of the paragraphs.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57168592A JPS5961633A (en) | 1982-09-29 | 1982-09-29 | Oil-pressure circuit for oil-pressure working machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57168592A JPS5961633A (en) | 1982-09-29 | 1982-09-29 | Oil-pressure circuit for oil-pressure working machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5961633A true JPS5961633A (en) | 1984-04-07 |
Family
ID=15870907
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57168592A Pending JPS5961633A (en) | 1982-09-29 | 1982-09-29 | Oil-pressure circuit for oil-pressure working machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5961633A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990014472A1 (en) * | 1989-05-17 | 1990-11-29 | M & H Blanch Pty Limited | Independent drive controls for skid steer loader |
| KR100961433B1 (en) | 2008-10-13 | 2010-06-09 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | hydraulic system of construction equipment |
| KR100985031B1 (en) | 2008-08-21 | 2010-10-04 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | hydraulic system of construction equipment |
-
1982
- 1982-09-29 JP JP57168592A patent/JPS5961633A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990014472A1 (en) * | 1989-05-17 | 1990-11-29 | M & H Blanch Pty Limited | Independent drive controls for skid steer loader |
| KR100985031B1 (en) | 2008-08-21 | 2010-10-04 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | hydraulic system of construction equipment |
| KR100961433B1 (en) | 2008-10-13 | 2010-06-09 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | hydraulic system of construction equipment |
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