JP4129761B2 - Operation controller for reciprocating viscous fluid pump - Google Patents

Operation controller for reciprocating viscous fluid pump Download PDF

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JP4129761B2
JP4129761B2 JP2002016889A JP2002016889A JP4129761B2 JP 4129761 B2 JP4129761 B2 JP 4129761B2 JP 2002016889 A JP2002016889 A JP 2002016889A JP 2002016889 A JP2002016889 A JP 2002016889A JP 4129761 B2 JP4129761 B2 JP 4129761B2
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main hydraulic
hydraulic piston
stroke end
viscous fluid
pump
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JP2003214332A (en
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建良 大木
利昭 内田
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石川島建機株式会社
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Description

【０００１】
【発明の属する技術分野】
本発明はコンクリートや汚泥脱水ケーキの如き粘性流体を吸入吐出させるようにする往復動型粘性流体ポンプの運転制御装置に関するものである。
【０００２】
【従来の技術】
往復動型としたダブルピストン式の粘性流体ポンプにおいて、２本の流体圧送用の主油圧シリンダのいずれか一方の主油圧ピストンが前進してストロークエンドに達すると、近接センサが作動して吸入吐出弁（揺動弁、滑り弁等）を切り換えるようにすると共に、主油圧シリンダの主油圧ピストンを逆方向に切り換えるようにすることは公知である。
【０００３】
一例として吸入吐出弁を揺動弁型式としたコンクリートポンプについて示すと、図４に示す如く、ホッパ１の前側壁１ａの下部に２つの吸入吐出口２ａ，２ｂを左右に並べて設け、ホッパ１の前側には、上記２つの吸入吐出口２ａ，２ｂに各々連通する左右２本のコンクリートシリンダ３ａと３ｂを平行に設置し、該各コンクリートシリンダ３ａ，３ｂ内に収納したコンクリートピストン４ａ，４ｂを、上記コンクリートシリンダ３ａ，３ｂに洗浄室５を介して接続した左右２本の主油圧シリンダ６ａ，６ｂ内の主油圧ピストン７ａ，７ｂに各１本のロッド８ａ，８ｂを介して一体的に連結し、主油圧シリンダ６ａ，６ｂの主油圧ピストン７ａ，７ｂを交互に前進後退させることによってコンクリートピストン４ａ，４ｂを交互に前進後退させるようにしてある。
【０００４】
又、上記ホッパ１内には、Ｓ字状に屈曲させた揺動管９を収納位置させ、該揺動管９の前端にはバルブリング１０を取り付けて、バルブリング１０がホッパ１の前側壁１ａの内面に取り付けられたバルブプレート１１に沿い摺動して上記２つの吸入吐出口２ａ，２ｂに交互に一致できるようにすると共に、上記揺動管９の後端部をホッパ１の後側壁１ｂに連設した吐出フランジ１２を介してコンクリート輸送管１３に接続させ、且つ上記揺動管９の後端部の揺動軸心に合わせて該揺動管９の途中に固定した揺動軸１４をホッパ１の外部に設置した図示しない左右２本の揺動シリンダに操作レバーを介して連結し、操作レバーを左右に傾動させることにより揺動管９を揺動軸１４を中心に左右方向に揺動できるようにしてある。
【０００５】
更に、上記主油圧シリンダ６ａ，６ｂは、ロッド側圧力室同士を密封ライン１５で接続すると共に、ヘッド側圧力室に、アクチュエータ１６の作動で傾転角を変更できるようにした片傾転油ポンプ１７、タンク１８に接続された圧油給排ライン１９を接続し、該圧油給排ライン１９の途中に、電磁四方弁２０の作動によって切り換えられるようにした主切換弁２１を設け、主油圧シリンダ６ａ，６ｂの各前進側ストロークエンドに設けた近接センサＬＳ．１又はＬＳ．２からの信号で電磁四方弁２０のソレノイドＳＯＬ．１又はＳＯＬ．２を励磁して該電磁四方弁２０をポートａ側又はｂ側に切り換えることにより、主切換弁２１をポートａ側又はｂ側に切り換えて主油圧ピストン７ａ，７ｂを交互に前進後退させるようにしてあり、又、この動作と所要のタイミングで吸入吐出弁としての上記揺動管９が切り換えられるようにしてある。２２は安全弁を示す。
【０００６】
上記従来の揺動弁型式としたコンクリートポンプの吸入吐出弁を作動させてホッパ１内のコンクリートを吸入吐出させるときは、ホッパ１内で揺動管９を揺動させて行い、揺動管９の前端がいずれか一方の吸入吐出口２ａ又は２ｂに連通させられると、該揺動管９が連通させられた吸入吐出口２ａ又は２ｂ側のコンクリートシリンダ３ａ又は３ｂのコンクリートピストン４ａ又は４ｂを前進させて、これまでコンクリートシリンダ３ａ又は３ｂ内に吸入したコンクリートを揺動管９内を通して吐出させると同時に、別のコンクリートシリンダ３ｂ又は３ａではコンクリートピストン４ｂ又は４ａを後退させてホッパ１内のコンクリートを他方の吸入吐出口２ｂ又は２ａを通して吸入させるようにし、次に、揺動管９をこれまで吸入側であった吸入吐出口２ｂ又は２ａに切り換えて当該吸入吐出口２ｂ又は２ａ側のコンクリートシリンダ３ｂ又は３ａのピストン４ｂ又は４ａを前進させると同時にこれまで吐出側であった吸入吐出口２ａ又は２ｂ側のコンクリートシリンダ３ａ又は３ｂにコンクリートを吸入させるようにし、かかる動作を繰り返してコンクリートの吸入吐出の切り換えを行うようにしてある。
【０００７】
【発明が解決しようとする課題】
ところが、上記コンクリートポンプの場合、定常運転時は、片傾転油ポンプ１７の圧油吐出量に基づく一定速度で主油圧シリンダ６ａ，６ｂの主油圧ピストン７ａ，７ｂが動作し、主切換弁２１の作動により主油圧ピストン７ａ，７ｂの前進、後退が瞬時に切り換えられるようにしてあるため、この切り換え時に、大気開放されたコンクリートの吐出圧力が再度急激に昇圧されることに伴い、大きな圧力変動を起すことから、脈動が発生することになる。この脈動は、配管振動やブーム振動の原因となり、大きな問題となっている。
【０００８】
因に、油ポンプとして両傾転油ポンプを用いた方式の場合、傾転を逆方向に切り換えるときに油量変化が起ることから、主油圧ピストンの前進、後退の切り換え時にブレーキが掛かり、この作用が脈動を低減させる効果があるとされているが、回路構成が複雑となり、コスト高となってしまう。
【０００９】
そこで、本発明は、ポンプ運転時に発生する大きな圧力変動を緩和して脈動を効果的に低減させることができるようにしようとするものである。
【００１０】
【課題を解決するための手段】
本発明は、上記課題を解決するために、粘性流体圧送用の２本の主油圧シリンダに片傾転油ポンプから吐出された圧油を交互に供給して、いずれか一方の主油圧シリンダの主油圧ピストンが前進側ストロークエンドに達すると、吸入吐出弁を切り換えるようにすると共に主油圧ピストンの前進後退を逆方向に切り換えるようにしてある往復動型粘性流体ポンプの運転制御装置において、主油圧シリンダの前進側ストロークエンド位置よりも所要量手前の位置に近接センサを設置し、且つ主油圧ピストンが前進したときに作動する上記近接センサの作動信号に基づいて当該主油圧ピストンが近接センサの位置から前進側ストロークエンドに達するまでの間運転速度としての主油圧ピストンの１ストローク分の動作時間に基づいて設定された補正時間だけ片傾転油ポンプの傾転角を小さくして主油圧ピストンの前進速度を減速させるように補正する指令と主油圧ピストンを前進側ストロークエンドから所要量後退させるまでの間片傾転油ポンプの傾転角を大きくして元に戻すようにする指令とを発するようにした制御器を有する構成としたことを特徴とする往復動型粘性流体ポンプの運転制御装置とする。
【００１１】
主油圧シリンダの主油圧ピストンが前進側ストロークエンドに達して切り換えられる前後に、主油圧ピストンが減速、増速されるため、圧力変動が緩和され、圧送される粘性流体に対する衝撃を減少することができて脈動を低減することができる。
【００１２】
又、複雑な回路構成とすることなく、脈動を低減できて、配管振動等を抑えることができる。
【００１３】
この際、片傾転油ポンプの傾転角を小さくして主油圧ピストンの前進速度を減速させるための補正時間を、運転速度としての主油圧ピストンの１ストローク分の動作時間に応じて選定するようにした構成としてあるので、そのときのポンプの運転速度に適した制御を行うことができる。
【００１４】
【発明の実施の形態】
以下、本発明の実施の形態を図面を参照して説明する。
【００１５】
図１は本発明の実施の一形態を示すもので、図４に示したコンクリートポンプと同様な構成において、主油圧シリンダ６ａ，６ｂ前進側ストロークエンド位置ｘよりも所要量手前の位置ｙに近接センサＬＳ．３，ＬＳ．４を設置し、且つ該近接センサＬＳ．３，ＬＳ．４の作動信号に基づき吸入吐出弁や主油圧シリンダ６ａ，６ｂの切換指令及び片傾転油ポンプ１７の制御指令を出力するようにした制御器２３を備える。
【００１６】
上記制御器２３について詳述すると、該制御器２３には、近接センサＬＳ．３又はＬＳ．４が作動信号を発すると、運転速度としての主油圧ピストン７ａ又は７ｂの１ストローク分の動作時間Ｔに基づいて設定された補正時間ｔだけ片傾転油ポンプ１７の傾転角を徐々に小さくして主油圧ピストン７ａ又は７ｂの前進速度を減速させるようにすると共に、上記補正時間ｔ経過後に主油圧ピストン７ａ又は７ｂを前進側ストロークエンド位置ｘから所要量後退させる間だけ片傾転油ポンプ１７の傾転角を徐々に大きくして主油圧ピストン７ａ又は７ｂの後退速度を増速し元の運転速度に戻すような制御指令Ｓを片傾転油ポンプ１７のアクチュエータ１６に与える機能を具備させてある。又、吸入吐出弁としての揺動管９への切換指令Ｓ１と、主油圧ピストン７ａ，７ｂを逆方へ切り換えるための切換指令Ｓ２（電磁四方弁２０のソレノイドＳＯＬ．１又はＳＯＬ．２を励磁する信号）は、上記補正時間ｔが経過した後に所要のタイミングで出力されるようにしてある。
【００１７】
上記構成としてあるコンクリートポンプの運転は、図２に示すフローチャート並びに図３に示すタイムチャートに基づいて行われる。コンクリートポンプは、通常、その現場の状況に応じた運転速度、すなわち、左右の主油圧シリンダ６ａ，６ｂの主油圧ピストン７ａ，７ｂの１ストローク分の動作時間Ｔが設定される。
【００１８】
今、左側の主油圧シリンダ６ａの主油圧ピストン７ａが後退し、右側の主油圧シリンダ６ｂの主油圧ピストン７ｂが前進している場合において、図１に示す如く、右側の主油圧ピストン７ｂが前進側ストロークエンド位置ｘよりも手前に設定された位置ｙに到着すると、右側の近接センサＬＳ．４が作動させられることによりその信号が制御器２３に送られる。制御器２３では、この近接センサＬＳ．４の作動信号に基づいて、先ず、左側の主油圧ピストン７ａの前進による左側の近接センサＬＳ．３が前回作動したときから、今回右側の近接センサＬＳ．４が作動したときまでの主油圧ピストン７ｂの動作時間Ｔを算出し、この算出した時間Ｔに応じた補正時間ｔの間だけ、片傾転油ポンプ１７の傾転角を小さくするようにアクチュエータ１６に制御指令Ｓを出力する。これにより、片傾転油ポンプ１７の圧油吐出量が徐々に減少させられることで、主油圧ピストン７ｂの前進速度が減少させられる。
【００１９】
次に、上記補正時間ｔが経過すると、吸入吐出としての揺動管９の切換指令Ｓ１と左右の主油圧ピストン７ａ，７ｂを逆方向へ切り換えるための切換指令Ｓ２とを所要のタイミングで出力する。しかる後、片傾転油ポンプ１７の傾転角を大きくするようにアクチュエータ１６に制御指令Ｓを出力する。これにより、片傾転油ポンプ１７の圧油吐出量が徐々に増大させられることで、右側の主油圧ピストン７ｂの後退速度、すなわち、左側の主油圧ピストン７ａの前進速度が設定速度まで増速させられる。このようにして、左右の主油圧シリンダ６ａ，６ｂの主油圧ピストン７ａ，７ｂの前進後退が切り換えられた後も、図３のタイムチャートに示す如く、同様に制御される。
【００２０】
上記において、補正時間ｔの間だけ片傾転油ポンプ１７の圧油吐出量を減少させる領域では、図３に示す如く、設定吐出量から最小吐出量まで漸減させる領域Ａ１と最小吐出量を維持する領域Ａ２を作るようにしておく。したがって、領域Ａ１の間は主油圧ピストン７ａ，７ｂの前進速度が徐々に減速されて最低速度となり、領域Ａ２の間は主油圧ピストン７ａ，７ｂの前進速度が最低速度で維持することになる。なお、この圧油吐出量を漸減させる領域Ａ１と、補正時間ｔ経過後に圧油吐出量を漸増させる領域Ａ３の傾き角、つまり、主油圧ピストンの増速度、減速度はアンプにより任意に設定することができる。又、上記近接センサＬＳ．３，ＬＳ．４の作動信号を基に算出する主油圧ピストン７ａ，７ｂの動作時間Ｔと、算出された動作時間Ｔに応じて選定される補正時間ｔとの関係は、たとえば、表１に示す如くであり、種々の運転速度に応じて求めておいた最適値である。
【００２１】
【表１】

Figure 0004129761
【００２２】
このように、本発明においては、主油圧シリンダ６ａ，６ｂのストロークエンド位置ｘよりも手前の位置ｙに設けておいた近接センサＬＳ．３，ＬＳ．４の作動信号を基に、片傾転油ポンプ１７の圧油吐出量を減少、増大させて、主油圧シリンダ６ａ，６ｂの主油圧ピストン７ａ，７ｂの切り換え前後における作動速度を減速、増速させるように制御するので、主油圧ピストン７ａと７ｂの前進後退の切り換え時に発生する大きな圧力変動を緩和することができる。又、上述したように、片傾転油ポンプ１７の圧油吐出量の制御は、設定された運転速度に適した時間で行われるようにしてあるので、あらゆる運転状況においても、主油圧ピストン７ａ，７ｂの切り換え時の大きな圧力変動を緩和することができる。したがって、圧送されるコンクリートに対する衝撃を減少することができて、脈動を効果的に低減することができ、配管振動やブーム振動を減少させることができると共に、各付帯構造物に加わる負荷をも低減することができる。
【００２３】
なお、上記実施の形態では、吸入吐出弁の切換指令Ｓ１と主油圧シリンダ６ａ，６ｂの切換指令Ｓ２を、位置ｙの近接センサＬＳ．３，ＬＳ．４の作動信号を基準に、補正時間ｔ経過後に発するようにした場合を示したが、ストロークエンド位置ｘに別途近接センサを設けておいて、この近接センサの作動信号を基に発するようにしてもよいこと、又、コンクリートポンプについて説明したが、コンクリート以外の粘性流体等の圧送に用いられるようにしたものにも適用できること、その他本発明の要旨を逸脱しない範囲内において種々変更を加え得ることは勿論である。
【００２４】
【発明の効果】
以上述べた如く、本発明によれば、粘性流体圧送用の２本の主油圧シリンダに片傾転油ポンプから吐出された圧油を交互に供給して、いずれか一方の主油圧シリンダの主油圧ピストンが前進側ストロークエンドに達すると、吸入吐出弁を切り換えるようにすると共に主油圧ピストンの前進後退を逆方向に切り換えるようにしてある往復動型粘性流体ポンプの運転制御装置において、主油圧シリンダの前進側ストロークエンド位置よりも所要量手前の位置に近接センサを設置し、且つ主油圧ピストンが前進したときに作動する上記近接センサの作動信号に基づいて当該主油圧ピストンが近接センサの位置から前進側ストロークエンドに達するまでの間運転速度としての主油圧ピストンの１ストローク分の動作時間に基づいて設定された補正時間だけ片傾転油ポンプの傾転角を小さくして主油圧ピストンの前進速度を減速させるように補正する指令と主油圧ピストンを前進側ストロークエンドから所要量後退させるまでの間片傾転油ポンプの傾転角を大きくして元に戻すようにする指令とを発するようにした制御器を有する構成としたことを特徴とする往復動型粘性流体ポンプの運転制御装置としてあるので、次の如き優れた効果を発揮する。
【００２５】
(1) 主油圧ピストンが前進側ストロークエンドに達して切り換えられる前後に主油圧ピストンが減速、増速されることで圧力変動を緩和することができ、圧力変動に伴い発生する脈動を効果的に低減することができ、これにより、配管振動やブーム振動を減少させることができる。
【００２６】
(2) 両傾転油ポンプを用いる場合の如き複雑な回路構成とすることなく、脈動を効果的に低減することができる。
【００２７】
(3) 片傾転油ポンプの傾転角を小さくして主油圧ピストンの前進速度を減速させるための補正時間を、運転速度としての主油圧ピストンの１ストローク分の動作時間に応じて選定するようにした構成としてあるので、あらゆる運転速度においても、主油圧ピストンの切り換え時における速度を最適に制御することができる。
【図面の簡単な説明】
【図１】本発明の往復動型粘性流体ポンプの運転制御装置の実施の一形態を示すもので、コンクリートポンプへの採用例を示す概略図である。
【図２】本発明で採用するポンプ運転フローチャートである。
【図３】本発明で採用するポンプ運転タイムチャートである。
【図４】往復動型粘性流体ポンプの一例を示すコンクリートポンプの概略図である。
【符号の説明】
６ａ，６ｂ 主油圧シリンダ
７ａ，７ｂ 主油圧ピストン
９ 揺動管（吸入吐出弁）
１７ 片傾転油ポンプ
２３ 制御器
ＬＳ．３，ＬＳ．４ 近接センサ
ｘ 前進側ストロークエンド位置
ｙ 手前の位置[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a driving system GoSo location reciprocating fluid pump so as to suction and discharge a such viscous fluid concrete or sludge dehydrated cake.
[0002]
[Prior art]
In a reciprocating double piston type viscous fluid pump, when one of the two main hydraulic cylinders for fluid pressure feeding moves forward and reaches the stroke end, the proximity sensor is activated and sucks and discharges It is known to switch valves (oscillating valves, slip valves, etc.) and to switch the main hydraulic piston of the main hydraulic cylinder in the reverse direction.
[0003]
As an example, a concrete pump having an oscillating valve as a suction / discharge valve is shown. As shown in FIG. 4, two suction / discharge ports 2 a, 2 b are provided side by side at the lower part of the front side wall 1 a of the hopper 1. On the front side, two left and right concrete cylinders 3a and 3b communicating with the two suction and discharge ports 2a and 2b are installed in parallel, and concrete pistons 4a and 4b accommodated in the concrete cylinders 3a and 3b are respectively provided. The concrete cylinders 3a and 3b are integrally connected to the main hydraulic pistons 7a and 7b in the left and right main hydraulic cylinders 6a and 6b connected to the concrete cylinders 3a and 3b via the cleaning chamber 5 through one rod 8a and 8b. The concrete pistons 4a and 4b are alternately advanced and retracted by alternately advancing and retreating the main hydraulic pistons 7a and 7b of the main hydraulic cylinders 6a and 6b. It is to so that.
[0004]
In addition, a swing pipe 9 bent in an S shape is placed in the hopper 1, a valve ring 10 is attached to the front end of the swing pipe 9, and the valve ring 10 is connected to the front side wall of the hopper 1. It slides along the valve plate 11 attached to the inner surface of 1a so as to be able to coincide with the two suction / discharge ports 2a, 2b alternately, and the rear end of the swing pipe 9 is connected to the rear side wall of the hopper 1 An oscillating shaft connected to the concrete transport pipe 13 through a discharge flange 12 connected to 1b and fixed in the middle of the oscillating pipe 9 in accordance with the oscillating axis of the rear end portion of the oscillating pipe 9. 14 is connected to two left and right oscillating cylinders (not shown) installed outside the hopper 1 via an operating lever, and the oscillating tube 9 is tilted left and right to move the oscillating tube 9 about the oscillating shaft 14 in the left-right direction. Can be swung.
[0005]
Further, the main hydraulic cylinders 6a and 6b connect the rod-side pressure chambers to each other by a sealing line 15 and can change the tilt angle to the head-side pressure chamber by the operation of the actuator 16. 17, a pressure oil supply / discharge line 19 connected to the tank 18 is connected, and a main switching valve 21 is provided in the middle of the pressure oil supply / discharge line 19 so as to be switched by the operation of the electromagnetic four-way valve 20. Proximity sensor LS. Provided at each forward stroke end of cylinder 6a, 6b. 1 or LS. 2, the solenoid SOL. 1 or SOL. 2 and the electromagnetic four-way valve 20 is switched to the port a side or b side to switch the main switching valve 21 to the port a side or b side so that the main hydraulic pistons 7a and 7b are alternately advanced and retracted. In addition, the swinging tube 9 as the suction / discharge valve is switched at this operation and the required timing. Reference numeral 22 denotes a safety valve.
[0006]
When the suction / discharge valve of the above-described conventional swing valve type concrete pump is operated to suck and discharge the concrete in the hopper 1, the swing pipe 9 is swung in the hopper 1. When the front end of the cylinder is connected to one of the suction / discharge ports 2a or 2b, the concrete piston 4a or 4b of the concrete cylinder 3a or 3b on the side of the suction / discharge port 2a or 2b connected to the swing pipe 9 is advanced. The concrete that has been sucked into the concrete cylinder 3a or 3b until now is discharged through the rocking pipe 9, and at the same time, the concrete piston 4b or 4a is moved backward in the other concrete cylinder 3b or 3a so that the concrete in the hopper 1 is removed. The other suction / discharge port 2b or 2a is used for suction, and then the swing tube 9 has been on the suction side until now. The concrete cylinder 3b or 2a side of the suction discharge port 2b or 2a side is switched to the inlet / outlet port 2b or 2a and the piston 4b or 4a of the suction cylinder 2a or 3a is moved forward, and at the same time the concrete cylinder of the suction discharge port 2a or 2b side which has been the discharge side so far Concrete is sucked into 3a or 3b, and this operation is repeated to switch the suction and discharge of concrete.
[0007]
[Problems to be solved by the invention]
However, in the case of the concrete pump, during steady operation, the main hydraulic pistons 7a and 7b of the main hydraulic cylinders 6a and 6b operate at a constant speed based on the pressure oil discharge amount of the unidirectionally inclined oil pump 17, and the main switching valve 21 is operated. As the main hydraulic pistons 7a and 7b are switched forward and backward instantaneously by the operation of, a large pressure fluctuation occurs when the discharge pressure of the concrete released to the atmosphere is suddenly increased again at this switching. This causes pulsation. This pulsation causes piping vibration and boom vibration, which is a big problem.
[0008]
In the case of the system using both tilting oil pumps as the oil pump, the oil amount changes when switching the tilting in the reverse direction, so the brake is applied when switching the main hydraulic piston forward and backward, Although this action is said to have an effect of reducing pulsation, the circuit configuration becomes complicated and the cost increases.
[0009]
Therefore, the present invention is intended to relieve large pressure fluctuations that occur during pump operation and effectively reduce pulsation.
[0010]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the present invention alternately supplies the pressure oil discharged from the uni-tilt oil pump to the two main hydraulic cylinders for viscous fluid pumping, and When the main hydraulic piston reaches the forward stroke end, the suction and discharge valve is switched and the forward and backward movement of the main hydraulic piston is switched in the reverse direction. A proximity sensor is installed at a position before the stroke end position on the forward side of the cylinder by a required amount, and the main hydraulic piston is moved to the position of the proximity sensor based on the operation signal of the proximity sensor that operates when the main hydraulic piston moves forward. operation time of one stroke of the main hydraulic piston set correction based as between operation speed to reach the forward side stroke end from During piece tilting oil commands and main hydraulic piston to correct so as to only slow the forward speed of the smaller to the main hydraulic piston tilting angle piece tilting oil pump between the forward side stroke end until it is required amount retracting An operation control device for a reciprocating viscous fluid pump, characterized by having a controller that issues a command to increase the tilt angle of the pump and return it to its original state.
[0011]
Before and after the main hydraulic piston of the main hydraulic cylinder reaches the forward stroke end and is switched, the main hydraulic piston is decelerated and accelerated, so the pressure fluctuation is relaxed and the impact on the viscous fluid being pumped can be reduced. And pulsation can be reduced.
[0012]
Moreover, without the complex circuit configuration, can be reduced pulsation can be suppressed piping vibration.
[0013]
At this time , the correction time for reducing the forward angle of the main hydraulic piston by reducing the tilt angle of the uni-tilt oil pump is selected according to the operation time for one stroke of the main hydraulic piston as the operating speed. because are as in the configuration above, it is possible to perform control suitable for the operating speed of the pump at that time.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0015]
FIG. 1 shows an embodiment of the present invention. In a configuration similar to that of the concrete pump shown in FIG. 4, the main hydraulic cylinders 6a and 6b are closer to a position y before the required amount than the forward stroke end position x. Sensor LS. 3, LS. 4 and the proximity sensor LS. 3, LS. 4 is provided with a controller 23 that outputs a switching command for the intake and discharge valves and the main hydraulic cylinders 6a and 6b and a control command for the uni-tilt oil pump 17 based on the operation signal 4.
[0016]
The controller 23 will be described in detail. The controller 23 includes a proximity sensor LS. 3 or LS. When 4 generates an operation signal, the tilt angle of the uni-tilt oil pump 17 is gradually reduced by the correction time t set based on the operation time T for one stroke of the main hydraulic piston 7a or 7b as the operation speed. Thus, the forward speed of the main hydraulic piston 7a or 7b is decelerated, and after the correction time t has elapsed, the main hydraulic piston 7a or 7b is unilaterally inclined oil pump only while the required amount is retracted from the forward stroke end position x. A function of giving a control command S to the actuator 16 of the uni-tilt oil pump 17 to gradually increase the tilt angle of 17 and increase the reverse speed of the main hydraulic piston 7a or 7b to return to the original operation speed. I'm allowed. Further, a switching command S 1 to swing pipe 9 as suction and discharge valves, the main hydraulic piston 7a, solenoid SOL.1 the switching command S 2 (electromagnetic four-way valve 20 for switching 7b to reverse towards or SOL.2 Is output at a required timing after the correction time t has elapsed.
[0017]
The operation of the concrete pump configured as described above is performed based on the flowchart shown in FIG. 2 and the time chart shown in FIG. The concrete pump is usually set with an operation speed corresponding to the situation at the site, that is, an operation time T for one stroke of the main hydraulic pistons 7a and 7b of the left and right main hydraulic cylinders 6a and 6b.
[0018]
Now, when the main hydraulic piston 7a of the left main hydraulic cylinder 6a moves backward and the main hydraulic piston 7b of the right main hydraulic cylinder 6b moves forward, the right main hydraulic piston 7b moves forward as shown in FIG. When a position y set before the side stroke end position x is reached, the right proximity sensor LS. When 4 is activated, the signal is sent to the controller 23. In the controller 23, the proximity sensor LS. 4, first, the left proximity sensor LS. 3 from the previous operation, the right side proximity sensor LS. The operation time T of the main hydraulic piston 7b until the time when 4 is actuated is calculated, and the actuator is set so that the tilt angle of the uni-tilt oil pump 17 is reduced only during the correction time t corresponding to the calculated time T. The control command S is output to 16. Thereby, the forward hydraulic speed of the main hydraulic piston 7b is reduced by gradually decreasing the pressure oil discharge amount of the unidirectionally inclined oil pump 17.
[0019]
Next, when the correction time t has elapsed, the main hydraulic piston 7a and the left and right switching command S 1 of the oscillating tube 9 as suction and discharge, and a switching instruction S 2 for switching the 7b in the opposite direction at a predetermined timing Output. Thereafter, a control command S is output to the actuator 16 so as to increase the tilt angle of the uni-tilt oil pump 17. Thereby, the pressure oil discharge amount of the unidirectionally inclined oil pump 17 is gradually increased, so that the reverse speed of the right main hydraulic piston 7b, that is, the forward speed of the left main hydraulic piston 7a is increased to the set speed. Be made. Thus, even after the forward and backward movement of the main hydraulic pistons 7a and 7b of the left and right main hydraulic cylinders 6a and 6b is switched, the same control is performed as shown in the time chart of FIG.
[0020]
In the above, in the area to reduce the pressure oil discharge amount only single tilt oil pump 17 during the correction time t, as shown in FIG. 3, the minimum discharge amount area A 1 and the minimum discharge amount is gradually decreased until the set ejection amount keep to make an area a 2 to maintain. Therefore, the main hydraulic piston 7a is between the areas A 1, the forward speed of 7b is gradually decelerated to become a minimum speed, between regions A 2 is the main hydraulic piston 7a, in the forward speed of 7b is maintained at a minimum speed Become. Note that the area A 1 gradually decreasing the pressure oil discharge amount, the inclination angle of the area A 3 gradually increasing the pressure oil discharge amount after correction time t has elapsed, that is, increasing the rate of the main hydraulic piston, deceleration optionally by the amplifier Can be set. The proximity sensor LS. 3, LS. The relationship between the operation time T of the main hydraulic pistons 7a and 7b calculated based on the operation signal 4 and the correction time t selected according to the calculated operation time T is as shown in Table 1, for example. The optimum value obtained according to various operation speeds.
[0021]
[Table 1]
Figure 0004129761
[0022]
Thus, in the present invention, the proximity sensor LS.1 provided at the position y before the stroke end position x of the main hydraulic cylinders 6a, 6b. 3, LS. 4, the hydraulic oil discharge amount of the unidirectionally pumping oil pump 17 is decreased and increased, and the operating speed before and after the switching of the main hydraulic pistons 7a and 7b of the main hydraulic cylinders 6a and 6b is decelerated and increased. Therefore, it is possible to relieve large pressure fluctuations that occur when the main hydraulic pistons 7a and 7b are switched between forward and backward movements. Further, as described above, the control of the pressure oil discharge amount of the unidirectionally inclined oil pump 17 is performed in a time suitable for the set operation speed, so that the main hydraulic piston 7a can be used in any operation situation. , 7b can be relieved of large pressure fluctuations. Therefore, it is possible to reduce the impact on the concrete fed by pressure, effectively reduce pulsation, reduce pipe vibration and boom vibration, and reduce the load applied to each auxiliary structure. can do.
[0023]
In the above embodiment, switching command S 1 and the main hydraulic cylinder 6a of the suction and discharge valves, 6b of the switch command S 2, the proximity sensor LS position y. 3, LS. Although the case where it was made to emit after the lapse of the correction time t on the basis of the operation signal of No. 4 was shown, a separate proximity sensor is provided at the stroke end position x, and it is generated based on the operation signal of this proximity sensor. In addition, the concrete pump has been described, but it can also be applied to a pump that is used for pumping viscous fluids other than concrete, and other various modifications can be made without departing from the scope of the present invention. Of course.
[0024]
【The invention's effect】
As described above, according to the present invention, the pressure oil discharged from the one-side tilt oil pump is alternately supplied to the two main hydraulic cylinders for viscous fluid pumping, and the main hydraulic cylinder of either one of the main hydraulic cylinders is supplied. When the hydraulic piston reaches the forward stroke end, the main hydraulic cylinder is operated in a reciprocating viscous fluid pump operation control device which switches the suction / discharge valve and switches the forward / backward movement of the main hydraulic piston in the reverse direction. A proximity sensor is installed at a position before the required stroke end position of the forward side of the cylinder, and the main hydraulic piston is moved from the position of the proximity sensor based on the operation signal of the proximity sensor that operates when the main hydraulic piston moves forward. Correction time set based on the operation time for one stroke of the main hydraulic piston as the operating speed until reaching the forward stroke end A single tilting oil pump between a command to correct the main hydraulic piston to decelerate the forward speed of the main hydraulic piston by reducing the tilt angle of the piece tilting oil pump and the main hydraulic piston to retreat the required amount from the forward stroke end The operation control device of the reciprocating viscous fluid pump is characterized by having a controller that issues a command to increase the tilt angle of the cylinder and return it to its original state. Exhibits excellent effects.
[0025]
(1) before or after the main hydraulic piston is switched reaches the forward side stroke end to the main hydraulic piston deceleration, it is possible to relieve the pressure fluctuations by being accelerated, effectively the pulsation generated due to the pressure fluctuation Therefore, piping vibration and boom vibration can be reduced.
[0026]
(2) Pulsation can be effectively reduced without using a complicated circuit configuration as in the case of using a bi- tilting oil pump.
[0027]
(3) Select the correction time to reduce the forward angle of the main hydraulic piston by reducing the tilt angle of the uni-tilt oil pump according to the operating time for one stroke of the main hydraulic piston as the operating speed because are as in the configuration described above, even in all operating speeds, it is possible to optimally control the speed during the switching of the main hydraulic piston.
[Brief description of the drawings]
FIG. 1 is a schematic view showing an embodiment of an operation control device for a reciprocating viscous fluid pump according to the present invention, which is adopted in a concrete pump.
FIG. 2 is a flowchart of a pump operation employed in the present invention.
FIG. 3 is a pump operation time chart employed in the present invention.
FIG. 4 is a schematic view of a concrete pump showing an example of a reciprocating viscous fluid pump.
[Explanation of symbols]
6a, 6b Main hydraulic cylinders 7a, 7b Main hydraulic piston 9 Oscillating pipe (suction / discharge valve)
17 Single tilt oil pump 23 Controller LS. 3, LS. 4 Proximity sensor x Forward stroke end position y Front position

Claims (1)

粘性流体圧送用の２本の主油圧シリンダに片傾転油ポンプから吐出された圧油を交互に供給して、いずれか一方の主油圧シリンダの主油圧ピストンが前進側ストロークエンドに達すると、吸入吐出弁を切り換えるようにすると共に主油圧ピストンの前進後退を逆方向に切り換えるようにしてある往復動型粘性流体ポンプの運転制御装置において、主油圧シリンダの前進側ストロークエンド位置よりも所要量手前の位置に近接センサを設置し、且つ主油圧ピストンが前進したときに作動する上記近接センサの作動信号に基づいて当該主油圧ピストンが近接センサの位置から前進側ストロークエンドに達するまでの間運転速度としての主油圧ピストンの１ストローク分の動作時間に基づいて設定された補正時間だけ片傾転油ポンプの傾転角を小さくして主油圧ピストンの前進速度を減速させるように補正する指令と主油圧ピストンを前進側ストロークエンドから所要量後退させるまでの間片傾転油ポンプの傾転角を大きくして元に戻すようにする指令とを発するようにした制御器を有する構成としたことを特徴とする往復動型粘性流体ポンプの運転制御装置。When the pressure oil discharged from the unidirectionally pumped oil pump is alternately supplied to the two main hydraulic cylinders for viscous fluid pumping, and the main hydraulic piston of one of the main hydraulic cylinders reaches the forward stroke end, In a reciprocating viscous fluid pump operation control device in which the suction / discharge valve is switched and the forward / backward movement of the main hydraulic piston is switched in the reverse direction, the required amount is before the forward stroke end position of the main hydraulic cylinder. The operation speed until the main hydraulic piston reaches the forward stroke end from the position of the proximity sensor based on the operation signal of the proximity sensor that operates when the proximity hydraulic sensor is installed at the position and the main hydraulic piston moves forward the main hydraulic piston correction time set based on the operating time of one stroke only small a tilt angle piece tilting oil pump as The command to correct the main hydraulic piston to reduce the forward speed and the main hydraulic piston to return to the original value by increasing the tilt angle of the single tilt oil pump until the main hydraulic piston is retracted by the required amount from the forward stroke end. An operation control device for a reciprocating viscous fluid pump, characterized in that a controller is provided that issues a command to perform the operation.
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CN102213201A (en) * 2011-05-27 2011-10-12 秦月明 High-efficiency concrete or coal slurry conveying system, control method thereof, and two-position three-way hydraulically-controlled directional control valve applied to high-efficiency concrete or coal slurry conveying system
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CN102213201A (en) * 2011-05-27 2011-10-12 秦月明 High-efficiency concrete or coal slurry conveying system, control method thereof, and two-position three-way hydraulically-controlled directional control valve applied to high-efficiency concrete or coal slurry conveying system
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