JP2000027239A - Hydraulic system branch circuit to working attachment for construction machine - Google Patents
Hydraulic system branch circuit to working attachment for construction machineInfo
- Publication number
- JP2000027239A JP2000027239A JP10198403A JP19840398A JP2000027239A JP 2000027239 A JP2000027239 A JP 2000027239A JP 10198403 A JP10198403 A JP 10198403A JP 19840398 A JP19840398 A JP 19840398A JP 2000027239 A JP2000027239 A JP 2000027239A
- Authority
- JP
- Japan
- Prior art keywords
- branch
- hydraulic
- feed pipe
- oil
- return pipe
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000010276 construction Methods 0.000 title claims abstract description 14
- 210000000078 claw Anatomy 0.000 claims description 29
- 238000010586 diagram Methods 0.000 description 8
- 230000007935 neutral effect Effects 0.000 description 5
- 230000008602 contraction Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Operation Control Of Excavators (AREA)
- Shovels (AREA)
- Working Measures On Existing Buildindgs (AREA)
- Crushing And Grinding (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、建設機械の作業ア
タッチメントへの油圧系統を爪の開閉及び本体の旋回に
共用するための油圧分岐回路に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic branch circuit for sharing a hydraulic system to a work attachment of a construction machine for opening and closing a claw and turning a main body.
【０００２】[0002]
【従来の技術】建造物の解体に使用する建設機械には、
図６に見られるように、アーム30先端に作業アタッチメ
ント(全旋回ペンチ、全旋回つかみや全旋回破砕機等)31
を取り付ける。この作業アタッチメント31は、爪１を油
圧により開閉し、通常本体18を旋回可能にしている。本
体18の旋回は、爪１の開閉同様油圧を用いるものと、い
わゆる「当て回し」と呼ぶ方法を用いるものとがある。油
圧を用いる場合、図７に見られるように、爪１(図６参
照)を開閉させる油圧シリンダ10及び本体18を旋回させ
る油圧モータ３に対してそれぞれ独立した油圧系統を有
する。それぞれの油圧系統には、油の送り配管11,11と
戻し配管12,12とが必要だから、計４本の油圧配管をブ
ーム32及びアーム30に付設することになる(実際には、
更にブーム32の屈曲やアーム30の伸縮等で通常10本程度
の油圧配管がある)。当然、爪１の開閉と本体18の旋回
とは、互いに無関係で独立した操作である。2. Description of the Related Art Construction machines used for dismantling buildings include:
As shown in FIG. 6, a work attachment (full swing pliers, full swing grip, full swing crusher, etc.) 31 at the tip of the arm 30
Attach. The work attachment 31 opens and closes the claw 1 by hydraulic pressure, and normally allows the main body 18 to pivot. The turning of the main body 18 may be performed by using a hydraulic pressure in the same manner as the opening and closing of the claw 1, or may be performed by using a so-called "rotating" method. When hydraulic pressure is used, as shown in FIG. 7, the hydraulic cylinder 10 for opening and closing the pawl 1 (see FIG. 6) and the hydraulic motor 3 for turning the main body 18 have independent hydraulic systems. Since each hydraulic system requires oil feed pipes 11, 11 and return pipes 12, 12, a total of four hydraulic pipes are attached to the boom 32 and the arm 30 (actually,
Further, there are usually about 10 hydraulic pipes due to the bending of the boom 32 and the expansion and contraction of the arm 30). Naturally, the opening and closing of the claw 1 and the turning of the main body 18 are independent operations independent of each other.
【０００３】「当て回し」を用いる場合、本体旋回用の油
圧系統は存在しない。本体は旋回自由であり、アームと
の接続部位である旋回面にラッチ機構を設けて特定角度
毎に旋回角度を保持できるようにしている。作業者は、
ブーム又はアームを操作して作業アタッチメントを壁等
にぶつけ、その衝撃によって一時的にラッチによる旋回
角度保持を解除し、かつ衝撃によって本体を旋回させる
のである。本体の旋回が直観的でわかりやすく、好まれ
て使用されている。[0003] In the case of using the "rotation", there is no hydraulic system for turning the main body. The main body is freely swingable, and a latch mechanism is provided on a swing surface which is a connection portion with the arm so that the swing angle can be maintained at a specific angle. The worker
By operating the boom or the arm, the work attachment is hit against a wall or the like, and the impact temporarily releases the holding of the turning angle by the latch, and the main body is turned by the impact. Intuitive and easy to understand the rotation of the main body, it is used favorably.
【０００４】[0004]
【発明が解決しようとする課題】爪開閉用と本体旋回用
との２つの油圧系統を有する建設機械では、両者の油タ
ンクを共用するとしても、油圧ポンプ以降の油圧配管は
個別に必要となり、それだけブーム及びアームに数多く
の油圧配管を配さなければならず、構造上好ましくな
い。また、図７からも明らかなように、爪開閉と本体旋
回とが互いに無関係で独立した操作であることは、それ
だけ余分な操作を作業者に課すことになり、必ずしも好
ましいことではなかった。In a construction machine having two hydraulic systems for opening and closing the pawl and for turning the main body, even if both oil tanks are used in common, hydraulic piping after the hydraulic pump is required individually. As a result, a large number of hydraulic piping must be arranged on the boom and the arm, which is not preferable in terms of structure. Further, as is apparent from FIG. 7, the fact that the claw opening and closing and the main body turning are independent operations independent of each other imposes an extra operation on the worker, which is not always preferable.
【０００５】また、「当て回し」による本体旋回は、本体
旋回用油圧系統が不要になることから、上述した油圧配
管の数に関わる問題が緩和されるが、作業アタッチメン
トと壁等との衝突角度や衝撃の程度によって回転角度が
左右されるため、作業者の希望通りにアタッチメントを
旋回させることが難しく、熟練を要する作業となってい
た。何よりも問題となるのが、周囲に作業アタッチメン
トをぶつける壁等が存在しない場合、本体の旋回ができ
なくなってしまうことにある。そこで、わかりやすい操
作性を実現しながら自律的な本体の旋回を可能とし、か
つ油圧配管の数の低減を目指し、作業アタッチメントに
必要な油圧系統について検討した。[0005] In addition, since the turning of the main body by "applying" eliminates the need for a hydraulic system for turning the main body, the above-mentioned problem relating to the number of hydraulic pipes is alleviated, but the collision angle between the work attachment and a wall or the like is reduced. Since the rotation angle depends on the degree of impact and the degree of impact, it is difficult to rotate the attachment as desired by the operator, and this requires skill. Most importantly, if there is no wall or the like around which the work attachment is hit, the main body cannot be turned. Therefore, in order to realize easy-to-understand operability and enable autonomous turning of the main body and to reduce the number of hydraulic pipes, the hydraulic system necessary for the work attachment was studied.
【０００６】[0006]
【課題を解決するための手段】検討の結果開発したもの
が、油圧シリンダにより爪を開閉し、油圧モータにより
この本体を旋回させる作業アタッチメントをアーム先端
に取り付けた建設機械において、油圧シリンダまで延設
した油の送り配管及び戻し配管からそれぞれ分岐した分
岐送り配管及び分岐戻し配管を油圧モータに接続してな
り、旋回開始油圧以上が加わった場合に開通するシーケ
ンスバルブを分岐送り配管に設けた建設機械の作業アタ
ッチメントへの油圧系統分岐回路である。SUMMARY OF THE INVENTION What has been developed as a result of the study is that a work attachment that opens and closes a pawl with a hydraulic cylinder and turns the main body with a hydraulic motor is attached to the tip of the arm, and is extended to the hydraulic cylinder. Construction machine that connects a branch feed pipe and a branch return pipe branched from the oil feed pipe and the return pipe, respectively, to a hydraulic motor, and has a sequence valve in the branch feed pipe that opens when a turning start hydraulic pressure or more is applied. 5 is a hydraulic system branch circuit to the work attachment.
【０００７】上記油圧系統分岐回路では、爪の全開又は
全閉直後から生ずる油圧の上昇を利用して、前記上昇分
の油圧により作業アタッチメント旋回用の油圧モータを
旋回させる。通常、爪を開いた状態でアームを動かして
作業対象へ導くことから、送り配管を爪開時に油を油圧
シリンダへ送り込む油圧配管とすることが好ましい。こ
の場合、送り配管に油を流して爪を開いている間は、油
圧シリンダが縮退し続けているので油圧はほとんど上昇
しない。ところが、爪が全開して油圧シリンダの縮退が
なくなると、送り配管内の油圧が上昇し始める。この油
圧が旋回開始油圧以上になると、シーケンスバルブが連
通して油が油圧モータへと流れはじめ、油圧モータが旋
回し始めるのである。In the above hydraulic system branch circuit, the hydraulic motor for turning the work attachment is rotated by the increased hydraulic pressure by utilizing the increase in the hydraulic pressure that occurs immediately after the claw is fully opened or fully closed. Usually, since the arm is moved to guide the work object with the pawl open, the feed pipe is preferably a hydraulic pipe that feeds oil to the hydraulic cylinder when the pawl is opened. In this case, while the claw is opened by flowing the oil through the feed pipe, the hydraulic pressure hardly increases because the hydraulic cylinder continues to contract. However, when the claw is fully opened and the hydraulic cylinder is no longer retracted, the hydraulic pressure in the feed pipe starts to rise. When this oil pressure becomes equal to or higher than the turning start oil pressure, the sequence valve communicates and oil starts flowing to the hydraulic motor, and the hydraulic motor starts turning.
【０００８】上記油圧系統分岐回路において、分岐戻し
配管に油を戻す方向にのみ流すチェック弁を設けると、
爪全閉直後から上昇する戻し配管の油圧がチェック弁に
より遮られるので、油圧モータへ不要な圧力上昇が伝達
しなくなる。一般に、油圧シリンダが伸長又は縮退しつ
くした後に生ずる油圧の上昇分は、油圧モータの許容油
圧を上回るので、油圧モータの保護を図る意味で、分岐
戻し配管におけるチェック弁を設けることが安全性の観
点から好ましい。[0008] In the above-mentioned hydraulic system branch circuit, if a check valve is provided for flowing oil only in a direction of returning oil to the branch return pipe,
Unnecessary pressure rise is not transmitted to the hydraulic motor because the hydraulic pressure of the return pipe, which rises immediately after the claw is fully closed, is blocked by the check valve. In general, the increase in hydraulic pressure that occurs after the hydraulic cylinder has fully extended or retracted exceeds the allowable hydraulic pressure of the hydraulic motor, so providing a check valve in the branch return pipe is a safety measure to protect the hydraulic motor. Preferred from a viewpoint.
【０００９】また、上記油圧系統分岐回路では、分岐送
り配管に油が流れない間は自律的に油圧モータが回転し
ないだけであって、外部から爪又は本体に衝撃が加わる
ことによって、分岐戻し配管を通じて油が流出し、本体
が勝手に旋回してしまう虞がある。そこで、分岐送り配
管に旋回開始油圧以上が加わった場合にこの分岐送り配
管に油を送り方向にのみ流すチェック弁を割り当て分岐
戻し配管を連通する正流路と、分岐送り配管に旋回開始
油圧より少ない圧力が加わった場合に分岐送り配管及び
分岐戻し配管に対向するチェック弁をそれぞれ割り当て
る閉鎖流路とからなるカウンターバランスバルブを分岐
送り配管及び分岐戻し配管と油圧モータとの間に介在さ
せるとよい。これにより、分岐送り配管に油が流れない
間は自律的に油圧モータが回転しないだけではなく、閉
鎖流路が油圧モータ前後の油の流れを抑制するため、仮
に外部から爪又は本体に衝撃が加わっても本体が旋回す
る心配がなくなる。一般に、油圧モータには、正逆方向
の旋回を実現するため、先の正流路、閉鎖流路に加えて
逆流路(分岐戻し配管に所定油圧以上が加わった場合に
油を送り方向にのみ流すチェック弁を割り当て分岐送り
配管を連通する)を有するカウンターバランスバルブを
設けている。本発明では、この従来のカウンターバラン
スバルブの正流路及び閉鎖流路のみを利用できる。Further, in the above hydraulic system branch circuit, the hydraulic motor does not rotate only autonomously while oil does not flow through the branch feed pipe. Oil may flow out through the main body, and the main body may turn without permission. Therefore, when a turning start hydraulic pressure or more is applied to the branch feed pipe, a check valve that allows oil to flow only in the feed direction is assigned to the branch feed pipe, and a positive flow path that communicates with the branch return pipe, and a turning start hydraulic pressure is applied to the branch feed pipe. When a small pressure is applied, a counterbalance valve composed of a closed flow path that allocates a check valve facing the branch feed pipe and the branch return pipe, respectively, may be interposed between the branch feed pipe and the branch return pipe and the hydraulic motor. . As a result, not only does the hydraulic motor not autonomously rotate while oil does not flow through the branch feed pipe, but also because the closed flow path suppresses the flow of oil before and after the hydraulic motor, shocks may be applied to the claws or body from outside. There is no need to worry about the body turning even if it is added. In general, in order to realize forward and reverse turning in a hydraulic motor, in addition to the forward flow path and the closed flow path, a reverse flow path (when a predetermined oil pressure or more is applied to the branch return pipe, oil is supplied only in the feed direction) A counterbalance valve having a flow check valve and communicating with a branch feed pipe) is provided. In the present invention, only the normal flow path and the closed flow path of the conventional counterbalance valve can be used.
【００１０】[0010]
【発明の実施の形態】以下、本発明の実施形態につい
て、図を参照しながら説明する。図１は爪１を全閉にし
た状態における油圧系統回路図、図２は同油圧系統を割
り当てた全旋回ペンチ２の側面図、図３は爪１を開き始
めた状態における同油圧系統回路図、図４は爪１を全開
にした状態における同油圧系統回路図であり、図５は爪
１を閉じ始めた状態における同油圧系統回路図である。
本例に示す油圧系統分岐回路は、分岐戻し配管14にチェ
ック弁17を設け、油圧モータ３に対して正流路４、閉鎖
流路５及び逆流路６を備えたカウンターバランスバルブ
７を配したもので、最も理想的な構成である。本例では
更に油圧モータ３と並列に正逆両方向のブレーキ弁８,
８を設けているが、このブレーキ弁８は本願発明に必須
ではなく、適宜選択的に付加又は除去できる。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a hydraulic circuit diagram in a state in which the pawl 1 is fully closed, FIG. 2 is a side view of a full swing pliers 2 to which the hydraulic system is assigned, and FIG. FIG. 4 is a circuit diagram of the hydraulic system when the claw 1 is fully opened, and FIG. 5 is a circuit diagram of the hydraulic system when the claw 1 is started to be closed.
In the hydraulic system branch circuit shown in this example, a check valve 17 is provided in a branch return pipe 14, and a counterbalance valve 7 having a forward flow path 4, a closed flow path 5, and a reverse flow path 6 is provided for the hydraulic motor 3. And the most ideal configuration. In this example, furthermore, the brake valves 8 in both forward and reverse directions are provided in parallel with the hydraulic motor 3.
Although the brake valve 8 is provided, the brake valve 8 is not essential to the present invention, and can be selectively added or removed as appropriate.
【００１１】図１により、油圧系統分岐回路について説
明する。油圧系統分岐回路９は、図１中破線枠内に相当
する部位である。まず、爪１(図２参照)を開閉させる油
圧シリンダ10への油の送り配管11及び戻し配管12をそれ
ぞれ分岐して分岐送り配管13及び分岐戻し配管14を延設
し、カウンターバランスバルブ７を介して油圧モータ３
に接続している。分岐送り配管13には、分岐点から順に
絞り弁15、シーケンスバルブ16を設け、分岐戻し配管14
には油を戻し方向にのみ流すチェック弁17を設けてい
る。チェック弁17は、爪全閉時に上昇する戻し配管12の
圧力から油圧モータ３を保護するため、分岐戻し配管14
への油の流れ込みを防止し、戻し配管12から油圧モータ
３への圧力伝達を阻止する働きを有する。爪１又は本体
18への外部からの衝撃に対する油圧モータ３の旋回防止
には、後述するカウンターバランスバルブ７が必要であ
る。絞り弁15は、油の流量を加減することで油圧モータ
３の旋回速度を調節する。シーケンスバルブ16は、旋回
開始油圧Ｐthを決定する。The hydraulic system branch circuit will be described with reference to FIG. The hydraulic system branch circuit 9 is a part corresponding to the area within the broken line frame in FIG. First, the oil feed pipe 11 and the return pipe 12 to the hydraulic cylinder 10 for opening and closing the claw 1 (see FIG. 2) are branched, and the branch feed pipe 13 and the branch return pipe 14 are extended. Via hydraulic motor 3
Connected to. The branch feed pipe 13 is provided with a throttle valve 15 and a sequence valve 16 in order from the branch point, and a branch return pipe 14 is provided.
Is provided with a check valve 17 that allows oil to flow only in the return direction. The check valve 17 protects the hydraulic motor 3 from the pressure of the return pipe 12 which rises when the claw is fully closed.
It has a function of preventing oil from flowing into the hydraulic motor 3 and preventing transmission of pressure from the return pipe 12 to the hydraulic motor 3. Nail 1 or body
In order to prevent the hydraulic motor 3 from turning in response to an external shock applied to 18, a counterbalance valve 7 described later is required. The throttle valve 15 adjusts the turning speed of the hydraulic motor 3 by adjusting the flow rate of the oil. The sequence valve 16 determines the turning start oil pressure Pth.
【００１２】本例のカウンターバランスバルブ７は、一
般的な油圧モータに取り付けられているものを流用して
いる。すなわち、正流路４、閉鎖流路５及び逆流路６を
有するカウンターバランスバルブ７のうち、正流路４及
び閉鎖流路５のみを用い、常態では閉鎖流路５を分岐送
り配管13及び分岐戻し配管14と油圧モータ３との間に介
在させ、分岐送り配管13に旋回開始油圧Ｐth以上が加わ
った場合に正流路４を用いて油を油圧モータ３へ流し込
む。図１中、本発明では使用しない逆流路６は破線表示
している。このカウンターバランスバルブ７は、自律的
な油圧モータ３の旋回を保証するもので、例えば油圧モ
ータ３停止時に爪１又は本体18(頭２参照)に外部から衝
撃が加わったとしても、対向するチェック弁を有する閉
鎖流路５が油圧モータ３前後の油の流れを遮断すること
で、不要な旋回を防止する働きを有している。あくまで
外部からの衝撃に対して油圧モータ３の旋回を防止する
もので、本例で言えば、爪１閉時における油圧上昇から
油圧モータ３を保護するには、上述のチェック弁17が必
要である。As the counterbalance valve 7 of this embodiment, a valve mounted on a general hydraulic motor is used. That is, of the counterbalance valve 7 having the positive flow path 4, the closed flow path 5, and the reverse flow path 6, only the positive flow path 4 and the closed flow path 5 are used, and the closed flow path 5 is normally branched into the feed pipe 13 and the branch pipe. It is interposed between the return pipe 14 and the hydraulic motor 3, and when the turning start oil pressure Pth or more is applied to the branch feed pipe 13, the oil flows into the hydraulic motor 3 using the positive flow path 4. In FIG. 1, the reverse flow path 6 not used in the present invention is indicated by a broken line. This counterbalance valve 7 guarantees the autonomous turning of the hydraulic motor 3. For example, even if an external impact is applied to the claw 1 or the main body 18 (see the head 2) when the hydraulic motor 3 is stopped, the counterbalance valve 7 is checked. The closed flow path 5 having a valve has a function of blocking an oil flow before and after the hydraulic motor 3 to prevent unnecessary turning. The check valve 17 is necessary to protect the hydraulic motor 3 from a rise in hydraulic pressure when the claw 1 is closed, in this example, in order to prevent the hydraulic motor 3 from turning in response to an external impact. is there.
【００１３】油圧系統分岐回路９及び油圧モータ３を除
けば、従来通りの油圧シリンダ10用の油圧系統となる。
図１に見られるように、本例では油圧シリンダ10の伸縮
を速めるために、差動回路19を介して油圧シリンダ10と
送り配管11及び戻し配管12とを繋いでいる。差動回路19
は本願発明に必須ではなく、適宜選択的に付加又は除去
できる。油圧ポンプ20によって油タンク21から汲み上げ
られた油は、コントロールバルブ22を経て送り配管11又
は戻し配管12のいずれかに流れ込み、油圧シリンダ10か
ら戻される油はコントローブバルブ22を通って油タンク
21へ還る。送り配管11に並設したメインリリーフ弁23
は、油圧シリンダ10への過剰な油供給を防止するため、
油圧ポンプ20からの油を直接油タンク21へ戻すものであ
る。コントロールバルブ22は、平行流路24、中立流路25
及び交差流路26の切換により、爪１を開閉し、爪１を全
開したのに続けて本体18を旋回させる操作を担う。Except for the hydraulic system branch circuit 9 and the hydraulic motor 3, a conventional hydraulic system for the hydraulic cylinder 10 is provided.
As shown in FIG. 1, in this example, the hydraulic cylinder 10 is connected to the feed pipe 11 and the return pipe 12 via a differential circuit 19 in order to accelerate the expansion and contraction of the hydraulic cylinder 10. Differential circuit 19
Is not essential to the present invention, and can be selectively added or removed as appropriate. The oil pumped from the oil tank 21 by the hydraulic pump 20 flows through the control valve 22 into either the feed pipe 11 or the return pipe 12, and the oil returned from the hydraulic cylinder 10 passes through the control valve 22 through the oil tank.
Return to 21. Main relief valve 23 juxtaposed with feed pipe 11
Is to prevent excessive oil supply to the hydraulic cylinder 10,
The oil from the hydraulic pump 20 is directly returned to the oil tank 21. The control valve 22 includes a parallel flow path 24 and a neutral flow path 25.
In addition, by switching the cross flow path 26, the claw 1 is opened and closed, and the operation of rotating the main body 18 after the claw 1 is fully opened is performed.
【００１４】次に、本体18の旋回について説明する。ま
ず、爪１を開くために、図３に見られるように、コント
ロールバルブ22を中立流路25から交差流路26に切り換
え、同時に油圧ポンプ20を作動させて油圧シリンダ前部
27へ油を送り込む(図１中太矢印)。油を送り込まれた油
圧シリンダ前部27が拡大するにつれ、油圧シリンダ後部
28からは油が排出され、戻し配管12を通って油タンク21
へ還る。この状態にあっては、油圧シリンダ10が縮退を
続けているため、前部油圧Ｐfは非常に低く、シーケン
スバルブ16に設定した旋回開始油圧ＰthとはＰth>>Ｐf
の関係にある。このため、分岐送り配管13へ油が流れ込
むことはなく、本体18は旋回することなく爪１を開き続
ける。Next, the turning of the main body 18 will be described. First, in order to open the pawl 1, the control valve 22 is switched from the neutral flow path 25 to the cross flow path 26, as shown in FIG.
Oil is fed into 27 (thick arrow in FIG. 1). As the front part 27 of the hydraulic cylinder into which the oil is supplied expands, the rear part of the hydraulic cylinder
The oil is discharged from 28 and passes through the return pipe 12 to the oil tank 21
Return to In this state, since the hydraulic cylinder 10 continues to contract, the front hydraulic pressure Pf is very low, and the turning start hydraulic pressure Pth set for the sequence valve 16 is Pth >> Pf
In a relationship. Therefore, no oil flows into the branch feed pipe 13, and the main body 18 continues to open the claw 1 without turning.
【００１５】爪１が全開すると、図４に見られるよう
に、油圧シリンダ10の縮退が停止するに伴って前部油圧
Ｐfが上昇し始める。この前部油圧Ｐfの上昇は、分岐送
り配管13にも伝わる。本例に示した差動回路19には油圧
シリンダ10と並列にシーケンス弁29を設けてあるため、
旋回開始油圧Ｐthは前記シーケンス弁29が作動し始める
油圧より低い圧力に定めておく必要がある。こうするこ
とで、やがてＰth≦Ｐfになるとシーケンスバルブ16が
開いて油を油圧モータ３へと流し始める。本例では、更
にカウンターバランスバルブ７を閉鎖流路５から正流路
４へと移行させることによって初めて油が油圧モータ３
へ至り、本体18を旋回させることになる。本体18はＰth
≦Ｐfである間は旋回するが、(1)Ｐth>>Ｐfになる、(2)
コントロールバルブ22を中立流路25にする、(3)油圧ポ
ンプ20を止めることで停止する。また、本体18の旋回停
止後、再び図４の状態で油を送り始めると、爪１は全開
したままで本体18の旋回を再開することができる。When the pawl 1 is fully opened, as shown in FIG. 4, the front hydraulic pressure Pf starts to increase as the retraction of the hydraulic cylinder 10 stops. This increase in the front hydraulic pressure Pf is transmitted to the branch feed pipe 13 as well. Since the differential circuit 19 shown in this example is provided with the sequence valve 29 in parallel with the hydraulic cylinder 10,
The turning start oil pressure Pth needs to be set to a pressure lower than the oil pressure at which the sequence valve 29 starts operating. Thus, when Pth ≦ Pf, the sequence valve 16 is opened and oil starts flowing to the hydraulic motor 3. In the present example, the oil is first transferred to the hydraulic motor 3 by moving the counterbalance valve 7 from the closed flow path 5 to the positive flow path 4.
And the main body 18 is turned. Body 18 is Pth
It turns while ≤Pf, but (1) Pth >> Pf, (2)
The control valve 22 is set to the neutral flow path 25. (3) The operation is stopped by stopping the hydraulic pump 20. Further, after the rotation of the main body 18 is stopped, if oil is started to be fed again in the state of FIG. 4, the rotation of the main body 18 can be resumed with the claw 1 fully opened.
【００１６】目的とする旋回角度にまで本体18の旋回を
終えた後、コントロールバルブ22を平行流路24に切り換
えて油圧ポンプ20を作動させると、図５に見られるよう
に、戻し配管12を通じて油圧シリンダ後部28へ油が送り
込まれ、今度は油圧シリンダ10が伸長し、送り配管11は
油圧シリンダ前部27の油を油タンク21へと戻す(図５中
太矢印)。爪１が全閉すると、上述同様に後部油圧Ｐrは
上昇し、この油圧の上昇分は分岐戻し配管14にも伝わる
が、分岐戻し配管14にはチェック弁17を設けているため
に前記油圧は油圧モータ３へ至らず、また油も流れない
ので、本体18が旋回することはない。After turning the main body 18 to the desired turning angle, the control valve 22 is switched to the parallel flow path 24 to operate the hydraulic pump 20, and as shown in FIG. The oil is fed into the rear part 28 of the hydraulic cylinder, the hydraulic cylinder 10 is extended this time, and the feed pipe 11 returns the oil in the front part 27 of the hydraulic cylinder to the oil tank 21 (thick arrow in FIG. 5). When the claw 1 is fully closed, the rear hydraulic pressure Pr rises as described above, and the increase in the hydraulic pressure is transmitted to the branch return pipe 14, but since the branch return pipe 14 is provided with the check valve 17, the hydraulic pressure becomes lower. Since the oil does not reach the hydraulic motor 3 and no oil flows, the main body 18 does not turn.
【００１７】以上をまとめると、次のようになる。作業
者は、通常、コントロールバルブ22を平行流路24及び交
差流路26を切り換えて爪１を開閉し、建造物を解体す
る。本体18を旋回するためには、作業者はコントロール
バルブ22を交差流路26に切り換え、まず爪１を全開する
(図３)。そのまま、コントロールバルブ22を交差流路26
にしたまま油圧ポンプ20を作動させ続けると、Ｐth≦Ｐ
fとなった段階で油圧モータ３が作動し始め、本体18の
旋回が始まる(図４)。この本体18の旋回は一方向であ
り、作業者は本体18が目的の旋回角度に至ったところ
で、コントロールバルブ22を中立流路25又は平行流路24
に移行して本体18の旋回を停止させる。以後、コントロ
ールバルブ22の切り換えによって爪１を開閉して解体作
業を続けるのである。コントロールバルブ22の切り換え
だけで、爪１を開閉し、本体18を旋回させることができ
るので、操作が作業者にとってわかりやすい。また、操
作レバー等の新たな操作系及び駆動系が不要であるの
で、既存の建設機械に対して適用しやすい利点がある。The above is summarized as follows. An operator normally switches the control valve 22 between the parallel flow path 24 and the cross flow path 26 to open and close the claw 1 and dismantle the building. In order to rotate the main body 18, the operator switches the control valve 22 to the cross flow path 26, and first fully opens the claw 1.
(FIG. 3). As it is, the control valve 22
If the hydraulic pump 20 continues to operate with the pressure
At the stage of f, the hydraulic motor 3 starts operating, and the turning of the main body 18 starts (FIG. 4). The turning of the main body 18 is unidirectional, and when the main body 18 reaches the target turning angle, the operator switches the control valve 22 to the neutral flow path 25 or the parallel flow path 24.
Then, the turning of the main body 18 is stopped. Thereafter, the pawl 1 is opened and closed by switching the control valve 22, and the dismantling operation is continued. The claw 1 can be opened and closed and the main body 18 can be turned only by switching the control valve 22, so that the operation is easy for the operator to understand. Further, since a new operation system such as an operation lever and a drive system are not required, there is an advantage that it can be easily applied to existing construction machines.
【００１８】[0018]
【発明の効果】本発明により、作業アタッチメントにお
ける爪の開閉及び本体の旋回を連続的に実現することが
でき、極めて簡単かつ良好な操作性を作業者に提供でき
るようになる。しかも、本体の旋回に油圧駆動という自
律性を持たせながら、必要な油圧配管は作業アタッチメ
ント毎に２本だけとなるから、油圧配管の数の低減とい
う目的も実現しうる。そして、以上を実現する油圧系統
分岐回路は、新たな操作系及び駆動系を要せず、既存の
油圧モータを利用できるので、従来の建設機械にも適用
できる利点があるのである。According to the present invention, the opening and closing of the pawl and the turning of the main body of the work attachment can be continuously realized, and extremely simple and good operability can be provided to the operator. In addition, since only two hydraulic pipes are required for each work attachment while giving the autonomy of hydraulic drive to the turning of the main body, the object of reducing the number of hydraulic pipes can be realized. The hydraulic system branch circuit that realizes the above does not require a new operation system and drive system, and can use an existing hydraulic motor. Therefore, there is an advantage that it can be applied to a conventional construction machine.
【図１】爪を全閉にした状態における油圧系統回路図で
ある。FIG. 1 is a hydraulic circuit diagram in a state where a claw is fully closed.
【図２】同油圧系統を割り当てた全旋回ペンチの側面図
である。FIG. 2 is a side view of the all-turn pliers to which the hydraulic system is assigned.
【図３】爪を開き始めた状態における同油圧系統回路図
である。FIG. 3 is a circuit diagram of the hydraulic system in a state where the pawl has begun to open.
【図４】爪を全開にした状態における同油圧系統回路図
である。FIG. 4 is a circuit diagram of the hydraulic system in a state where a claw is fully opened.
【図５】爪を閉じ始めた状態における同油圧系統回路図
である。FIG. 5 is a circuit diagram of the hydraulic system in a state where the claws have begun to close.
【図６】建設機械の全体図である。FIG. 6 is an overall view of a construction machine.
【図７】作業アタッチメントに対する従来の油圧系統回
路図である。FIG. 7 is a circuit diagram of a conventional hydraulic system for a work attachment.
１ 爪 ２ 全旋回ペンチ ３ 油圧モータ ４ 正流路 ５ 閉鎖流路 ６ 逆流路 ７ カウンターバランスバルブ ８ ブレーキ弁 ９ 油圧系統分岐回路 10 油圧シリンダ 11 送り配管 12 戻し配管 13 分岐送り配管 14 分岐戻し配管 15 絞り弁 16 シーケンスバルブ 17 チェック弁 18 本体 19 差動回路 20 油圧ポンプ 21 油タンク 22 コントロールバルブ 23 メインリリーフ弁 24 平行流路 25 中立流路 26 交差流路 27 油圧シリンダ前部 28 油圧シリンダ後部 29 シーケンス弁 30 アーム 31 作業アタッチメント 32 ブーム Ｐf シリンダ前部の油圧 Ｐr シリンダ後部の油圧 Ｐth 旋回開始油圧 1 Claw 2 Fully turning pliers 3 Hydraulic motor 4 Forward flow path 5 Closed flow path 6 Reverse flow path 7 Counterbalance valve 8 Brake valve 9 Hydraulic system branch circuit 10 Hydraulic cylinder 11 Feed pipe 12 Return pipe 13 Branch feed pipe 14 Branch return pipe 15 Throttle valve 16 Sequence valve 17 Check valve 18 Main unit 19 Differential circuit 20 Hydraulic pump 21 Oil tank 22 Control valve 23 Main relief valve 24 Parallel flow path 25 Neutral flow path 26 Cross flow path 27 Front of hydraulic cylinder 28 Rear of hydraulic cylinder 29 Sequence Valve 30 Arm 31 Work attachment 32 Boom Pf Hydraulic pressure at front of cylinder Pr Pr Hydraulic pressure at rear of cylinder Pth Hydraulic pressure at turning start
Claims (3)
ータにより本体を旋回させる作業アタッチメントをアー
ム先端に取り付けた建設機械において、油圧シリンダま
で延設した油の送り配管及び戻し配管からそれぞれ分岐
した分岐送り配管及び分岐戻し配管を油圧モータに接続
してなり、旋回開始油圧以上が加わった場合に開通する
シーケンスバルブを分岐送り配管に設けてなる建設機械
の作業アタッチメントへの油圧系統分岐回路。1. A construction machine in which a work attachment for opening and closing a claw by a hydraulic cylinder and turning a main body by a hydraulic motor is attached to an end of an arm, a branch branched from an oil feed pipe and a return pipe extending to the hydraulic cylinder. A hydraulic system branch circuit to a work attachment of a construction machine in which a feed pipe and a branch return pipe are connected to a hydraulic motor, and a sequence valve that is opened when branch pressure or more is applied is provided in the branch feed pipe.
岐戻し配管に設けてなる請求項１記載の建設機械の作業
アタッチメントへの油圧系統分岐回路。2. The hydraulic system branch circuit for a work attachment of a construction machine according to claim 1, wherein a check valve for flowing oil only in a direction in which oil is returned is provided in the branch return pipe.
った場合に該分岐送り配管に油を送り方向にのみ流すチ
ェック弁を割り当て分岐戻し配管を連通する正流路と、
分岐送り配管に旋回開始油圧より少ない圧力が加わった
場合に分岐送り配管及び分岐戻し配管に対向するチェッ
ク弁をそれぞれ割り当てる閉鎖流路とからなるカウンタ
ーバランスバルブを分岐送り配管及び分岐戻し配管と油
圧モータとの間に介在してなる請求項１記載の建設機械
の作業アタッチメントへの油圧系統分岐回路。3. A forward flow path which communicates with a branch return pipe by allocating a check valve for flowing oil only in the feed direction to the branch feed pipe when a turning start hydraulic pressure or more is applied to the branch feed pipe;
When a pressure less than the turning start hydraulic pressure is applied to the branch feed pipe, a counterbalance valve consisting of a closed flow path that allocates a check valve opposed to the branch feed pipe and the branch return pipe is provided by a branch feed pipe, a branch return pipe, and a hydraulic motor. 2. The hydraulic circuit branch circuit for a work attachment of a construction machine according to claim 1, interposed between the hydraulic system branch and the work attachment.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19840398A JP3190618B2 (en) | 1998-07-14 | 1998-07-14 | Hydraulic system branch circuit to construction machine work attachment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19840398A JP3190618B2 (en) | 1998-07-14 | 1998-07-14 | Hydraulic system branch circuit to construction machine work attachment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000027239A true JP2000027239A (en) | 2000-01-25 |
| JP3190618B2 JP3190618B2 (en) | 2001-07-23 |
Family
ID=16390559
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19840398A Expired - Fee Related JP3190618B2 (en) | 1998-07-14 | 1998-07-14 | Hydraulic system branch circuit to construction machine work attachment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3190618B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002063118A1 (en) * | 2001-02-07 | 2002-08-15 | Okada Aiyon Corporation | Pulverizer |
| JP2006075726A (en) * | 2004-09-09 | 2006-03-23 | Furukawa Co Ltd | Oil pressure crusher |
| CN1328515C (en) * | 2005-01-17 | 2007-07-25 | 江苏华宏科技股份有限公司 | Differential speed accelerating circuits |
| JP2007298085A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic cylinder device and pinching treatment device equipped with it |
| JP2011089355A (en) * | 2009-10-26 | 2011-05-06 | Takeuchi Seisakusho:Kk | Working machine |
| US8204655B2 (en) | 2006-10-19 | 2012-06-19 | Hitachi Construction Machinery Co., Ltd. | Construction machine |
| CN104405004A (en) * | 2014-11-07 | 2015-03-11 | 徐州徐工挖掘机械有限公司 | Rotating overflow energy recycling system of hydraulic excavator |
| CN106394533A (en) * | 2016-11-01 | 2017-02-15 | 广西柳工机械股份有限公司 | Vehicle hydraulic braking system |
| JP2020002647A (en) * | 2018-06-28 | 2020-01-09 | オカダアイヨン株式会社 | Attachment of work machine, and hydraulic operation valve for attachment of work machine |
| JP2021143510A (en) * | 2020-03-11 | 2021-09-24 | 株式会社日立建機ティエラ | Work machine |
-
1998
- 1998-07-14 JP JP19840398A patent/JP3190618B2/en not_active Expired - Fee Related
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1361322A1 (en) * | 2001-02-07 | 2003-11-12 | Okada Aiyon Corporation | Pulverizer |
| EP1361322A4 (en) * | 2001-02-07 | 2006-04-26 | Okada Aiyon Corp | Pulverizer |
| US7234659B2 (en) | 2001-02-07 | 2007-06-26 | Okada Aiyon | Pulverizer |
| WO2002063118A1 (en) * | 2001-02-07 | 2002-08-15 | Okada Aiyon Corporation | Pulverizer |
| JP2006075726A (en) * | 2004-09-09 | 2006-03-23 | Furukawa Co Ltd | Oil pressure crusher |
| CN1328515C (en) * | 2005-01-17 | 2007-07-25 | 江苏华宏科技股份有限公司 | Differential speed accelerating circuits |
| JP2007298085A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic cylinder device and pinching treatment device equipped with it |
| JP4531720B2 (en) * | 2006-04-28 | 2010-08-25 | 北都建機サービス株式会社 | Sandwiching device |
| US8204655B2 (en) | 2006-10-19 | 2012-06-19 | Hitachi Construction Machinery Co., Ltd. | Construction machine |
| JP2011089355A (en) * | 2009-10-26 | 2011-05-06 | Takeuchi Seisakusho:Kk | Working machine |
| CN104405004A (en) * | 2014-11-07 | 2015-03-11 | 徐州徐工挖掘机械有限公司 | Rotating overflow energy recycling system of hydraulic excavator |
| CN106394533A (en) * | 2016-11-01 | 2017-02-15 | 广西柳工机械股份有限公司 | Vehicle hydraulic braking system |
| CN106394533B (en) * | 2016-11-01 | 2019-04-05 | 广西柳工机械股份有限公司 | Hydraulic vehicle brake system |
| JP2020002647A (en) * | 2018-06-28 | 2020-01-09 | オカダアイヨン株式会社 | Attachment of work machine, and hydraulic operation valve for attachment of work machine |
| JP2021143510A (en) * | 2020-03-11 | 2021-09-24 | 株式会社日立建機ティエラ | Work machine |
| JP7165155B2 (en) | 2020-03-11 | 2022-11-02 | 株式会社日立建機ティエラ | working machine |
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