JPH0517961B2 - - Google Patents
Info
- Publication number
- JPH0517961B2 JPH0517961B2 JP60272883A JP27288385A JPH0517961B2 JP H0517961 B2 JPH0517961 B2 JP H0517961B2 JP 60272883 A JP60272883 A JP 60272883A JP 27288385 A JP27288385 A JP 27288385A JP H0517961 B2 JPH0517961 B2 JP H0517961B2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic motor
- displacement volume
- load
- pressure
- hydraulic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 238000006073 displacement reaction Methods 0.000 claims description 80
- 230000007423 decrease Effects 0.000 claims description 6
- 230000010349 pulsation Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/423—Motor capacity control by fluid pressure control means
Landscapes
- Fluid-Pressure Circuits (AREA)
Description
【発明の詳細な説明】
Ａ 産業上の利用分野
本発明は可変容積油圧モータを用いた油圧駆動
装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION A. Field of Industrial Application The present invention relates to a hydraulic drive device using a variable displacement hydraulic motor.
Ｂ 従来の技術
従来から、可変容積形油圧モータを用いた油圧
ウインチや走行装置等が知られている。この種の
油圧ウインチ、例えば移動式クレーンの巻上用ウ
インチでは、油圧モータの押除け容積を大、小２
段階に設定する押除け容積設定手段備え、運転席
内の操作指示手段として機能する高低速切換レバ
ーによりオペレータが所望に応じていずれかの押
除け容積を選択指示すると、それにより押除け容
積設定手段が油圧モータの押除け容積をいずれか
に設定するように構成されている。B. Prior Art Hydraulic winches, traveling devices, and the like that use variable displacement hydraulic motors have been known. In this type of hydraulic winch, for example, a hoisting winch for a mobile crane, the displacement volume of the hydraulic motor is set to 2 large and 2 small.
The displacement volume setting means is provided to set the displacement volume in stages, and when the operator selects and instructs one of the displacement volumes as desired using a high/low speed switching lever that functions as an operation instruction means in the driver's seat, the displacement volume setting means is configured to set the displacement volume of the hydraulic motor to either one.
Ｃ 発明が解決しようとする問題点
ここで、高速巻上を指示すると押除け容積が小
さくなり、油圧ポンプからの吐出量を一定とすれ
ば巻上速度は速くなるが、その一方、巻上圧力を
一定とすれば油圧モータの出力トルクは小さくな
る。従つて、同一負荷を巻上げるために必要な巻
上圧力は、高速時、すなわち押除け容積が小さい
ほど高くなり、低速から高速への切換えにより、
巻上回路に予め設定されたリリーフ圧力よりも高
い圧力が生じると、負荷、例えば吊り荷が巻上げ
られなかつたり、巻上中に切換わると吊り荷が保
持できない場合がある。このような場合、オペレ
ータは、高低速切換レバーにより油圧モータの押
除け容積を大きくして吊り荷が巻上げられるよう
にする必要があり、操作性、安全性に問題がる。C Problems to be solved by the invention Here, if high-speed hoisting is instructed, the displacement volume becomes smaller, and if the discharge amount from the hydraulic pump is kept constant, the hoisting speed becomes faster, but on the other hand, the hoisting pressure If is constant, the output torque of the hydraulic motor will be small. Therefore, the hoisting pressure required to hoist the same load increases at higher speeds, that is, when the displacement volume is smaller, and by switching from low speed to high speed,
If a pressure higher than a preset relief pressure is generated in the hoisting circuit, the load, for example, a suspended load, may not be hoisted, or the hoisted load may not be held if the hoisting circuit is switched during hoisting. In such a case, the operator must use the high/low speed switching lever to increase the displacement volume of the hydraulic motor so that the suspended load can be hoisted, which poses problems in operability and safety.
また、この従来のものでは、高速切換時に巻上
圧力がリリーフ圧力を僅かに越えるような負荷の
場合でも、低速側に切換えなければ巻上げができ
ず、従つて、そのとき設定された低速側の押除け
容積により定まる油圧モータの出力トルクは、負
荷の巻上に必要なトルクよりもかなり大きくなり
エネルギ損失も大きい。 In addition, with this conventional system, even if the hoisting pressure slightly exceeds the relief pressure during high-speed switching, hoisting cannot be performed unless the hoisting pressure is switched to the low-speed side. The output torque of the hydraulic motor determined by the displacement volume is considerably larger than the torque required to hoist the load, resulting in large energy loss.
本発明の目的は、このような問題点を解消し、
高速側で可変容量形油圧モータを運転する際には
負荷の大きさに応じてその押除け容積を設定する
ようにした油圧駆動装置を提供することにある。 The purpose of the present invention is to solve these problems,
An object of the present invention is to provide a hydraulic drive device in which the displacement of a variable displacement hydraulic motor is set according to the size of the load when operating the variable displacement hydraulic motor at high speed.
Ｄ 問題点を解決するための手段
本発明は、操作指示手段で指示された押除け容
積で油圧モータが回転駆動されるように押除け容
積設定手段を制御する押除け容積制御を有し、そ
の押除け容積制御手段は、操作指示手段が低速指
示位置にあるときに、押除け容積が最大となるよ
うに押除け容積設定手段を制御するとともに、操
作指示手段が高速指示位置にあるときに、油圧モ
ータの負荷が所定値より大きいときに押除け容積
を最大値とし、負荷が所定値以下では負荷が小さ
くなるにつれて押除け容積が小さくなるように押
除け容積設定手段を制御する。D. Means for Solving the Problems The present invention has a displacement volume control that controls a displacement volume setting means so that a hydraulic motor is rotationally driven with a displacement volume instructed by an operation instruction means. The displacement volume control means controls the displacement volume setting means so that the displacement volume is maximized when the operation instruction means is at the low speed instruction position, and when the operation instruction means is at the high speed instruction position, The displacement volume setting means is controlled such that the displacement volume is set to a maximum value when the load of the hydraulic motor is larger than a predetermined value, and the displacement volume becomes smaller as the load becomes smaller when the load is less than the predetermined value.
押除け容積制御手段は、操作指示手段が高速指
示位置でかつ油圧モータの負荷が所定値以下のと
き油圧モータの負荷圧力の変化に基づいて絞り量
が変化する絞り切換弁を備え、高速指示位置かつ
油圧モータの負荷が所定値以下のときに当該絞り
切換弁から出力される油圧モータの負荷圧力に基
づいて押除け容積設定手段を制御する。 The displacement volume control means includes a throttle switching valve that changes the amount of throttling based on a change in the load pressure of the hydraulic motor when the operation instruction means is at the high speed instruction position and the load on the hydraulic motor is below a predetermined value. Further, the displacement volume setting means is controlled based on the load pressure of the hydraulic motor outputted from the throttle switching valve when the load of the hydraulic motor is less than a predetermined value.
押除け容積設定手段としては、油圧モータの負
荷圧力が絞り切換弁を介して一方の油室へ導か
れ、油圧モータの負荷圧力が絞り切換弁を迂回し
て他方の油室へ導かれる油シリンダを用いること
ができる。 The displacement volume setting means is an oil cylinder in which the load pressure of the hydraulic motor is guided to one oil chamber via a throttle switching valve, and the load pressure of the hydraulic motor is guided to the other oil chamber bypassing the throttle switching valve. can be used.
Ｅ 作用
操作指示手段が低速指示位置にある場合、押除
け容積設定手段の制御の下にモータの押除け容積
は最大値に設定されて低速駆動可能となり、高速
指示位置にある場合には、油圧モータの負荷が所
定値より大きければ油圧モータの押除け容積は最
大値に設定されて低速駆動可能となり、負荷が所
定値以下ならば負荷が小さくなるにつれて押除け
容積が小さく設定されて高速駆動可能となる。E Effect When the operation instruction means is at the low speed instruction position, the displacement volume of the motor is set to the maximum value under the control of the displacement volume setting means, making it possible to drive at low speed, and when the operation instruction means is at the high speed instruction position, the hydraulic pressure is If the load on the motor is greater than a predetermined value, the displacement volume of the hydraulic motor is set to the maximum value and low-speed drive is possible; if the load is less than a predetermined value, the displacement volume is set to be smaller as the load decreases, allowing high-speed drive. becomes.
高速指示位置でかつ油圧モータの負荷が所定値
以下の領域では、絞り切換弁から出力される油圧
モータの負荷圧力の増減に応じて油圧モータの押
除け容積が変化する。絞り切換弁は、油圧ポンプ
の吐出圧の脈動や油圧モータの負荷変動に伴う油
圧モータ負荷圧力の細かな変動を緩和して出力
し、油圧モータの押除け容積の過剰な変化を防止
する。 At the high-speed instruction position and in a region where the load on the hydraulic motor is less than a predetermined value, the displacement volume of the hydraulic motor changes in accordance with an increase or decrease in the load pressure on the hydraulic motor output from the throttle switching valve. The throttle switching valve reduces and outputs fine fluctuations in the hydraulic motor load pressure due to pulsations in the discharge pressure of the hydraulic pump and fluctuations in the load on the hydraulic motor, and prevents excessive changes in the displacement volume of the hydraulic motor.
押除け容積設定手段を油圧シリンダとし、その
一方の油室に絞り切換弁から出力される油圧モー
タの負荷出力を導き、他方の油室に絞り切換弁を
迂回した油圧モータの負荷圧力を導くと、絞り切
換弁が最大開度に達して絞り作用がなくなつても
油圧モータの負荷圧力の微小な変動による押除け
容積の過剰な変化が防がれる。 When the displacement volume setting means is a hydraulic cylinder, the load output of the hydraulic motor output from the throttle switching valve is guided to one oil chamber, and the load pressure of the hydraulic motor bypassing the throttle switching valve is guided to the other oil chamber. Even if the throttle switching valve reaches its maximum opening and the throttle action is no longer present, excessive changes in the displacement volume due to minute fluctuations in the load pressure of the hydraulic motor are prevented.
Ｆ 実施例
第１図は本発明を巻上用油圧装置に適用した場
合の一実施例を示し、可変容量形油圧ポンプ１は
油圧切換式のコントロールバルブ２を介して巻上
用の可変容量形油圧モータ３と接続されていて、
コントロールバルブ２は操作指示手段４からのパ
イロツト圧力により切換え制御される。すなわ
ち、操作指示手段４は、中立、低速および高速位
置でデテント可能な操作レバー４１とその操作量
に応じた圧力を発生する減圧弁４２，４３とを有
し、コントロールバルブ２の各パイロツトポート
は各減圧弁４２，４３と接続されている。ここ
で、操作レバー４１の低速位置における減圧弁４
２，４３の吐出圧力をPPL、高速位置における減
圧弁４２，４３の吐出圧力をPPH（＞PPL）とする
と、コントロールバルブ２のクランキング圧力は
PPLより小さく設定される。可変容量形油圧モー
タ３は、油圧シリンダ５１とそのピストンに固着
され油圧モータ３の傾転量、すなわち押除け容積
を制御するロツド５２とを有する押除け容積設定
手段５によりその押除け容積が設定される。F Embodiment FIG. 1 shows an embodiment in which the present invention is applied to a hoisting hydraulic system, in which a variable displacement hydraulic pump 1 is connected to a variable displacement hydraulic pump for hoisting via a hydraulic switching type control valve 2. It is connected to the hydraulic motor 3,
The control valve 2 is switched and controlled by pilot pressure from the operation instruction means 4. That is, the operation instruction means 4 includes an operation lever 41 that can be detented at neutral, low speed, and high speed positions, and pressure reducing valves 42 and 43 that generate pressure according to the amount of operation of the operation lever 41, and each pilot port of the control valve 2 It is connected to each pressure reducing valve 42, 43. Here, the pressure reducing valve 4 at the low speed position of the operating lever 41
If the discharge pressure of the pressure reducing valves 42 and 43 at the high speed position is P PH (>P PL ), then the cranking pressure of the control valve 2 is
P Set smaller than PL . The displacement volume of the variable displacement hydraulic motor 3 is set by a displacement volume setting means 5 having a hydraulic cylinder 51 and a rod 52 fixed to its piston for controlling the amount of tilting of the hydraulic motor 3, that is, the displacement volume. be done.
押除け容積の設定は、押除け容積設定手段５を
構成する油圧シリンダ５１に供給される圧油を押
除け容積制御手段６により制御して行われる。こ
の押除け容積制御手段６は、固定容量形油圧ポン
プ６１と、減圧弁４２，４３の吐出圧力によつて
「イ」←→「ロ」へ切換制御される方向切換弁６
２と、油圧ポンプ６１の吐出圧力および油圧モー
タ３の入口圧力が第１および第２の制御ポートに
それぞれ作用してその位置が「イ」←→「ロ」ま
たはその中間位置に切換え制御される方向切換弁
６３とを有する。そして、方向切換弁６２は減圧
弁４２，４３の二次圧力がPPLを越えると「イ」
→「ロ」へ切換わる。方向切換弁６３の第２の制
御ポートには油圧モータ３の入口圧力が常時作用
するとともに、第１の制御ポートには方向切換弁
６２が「イ」の位置のときに油圧ポンプ６１の吐
出圧力PHが作用し、方向切換弁６３は、第１ま
たは第２の制御ポートに圧力PHより高い圧力が
作用すると「イ」から「ロ」へ完全に切換わるよ
うにそのばね６４が設定されている。また、方向
切換弁６２が「ロ」の位置にあるときには油圧モ
ータ３の入口圧力だけが方向切換弁６３の第２の
制御ポートに作用し、その圧力がＯ〜PHの範囲
ではその圧力に応じた位置、すなわち「イ」と
「ロ」の間の中間位置で保持されるように構成さ
れている。また、油圧シリンダ５１の小径室５１
１には、方向切換弁６２の入口圧力PHと油圧モ
ータ３の入口圧力（負荷により変動）とが常時作
用するようにされ、油圧シリンダ５１の大径室５
１２には、方向切換弁６３の切換位置に応じてタ
ンク圧力または油圧モータ３の圧力と方向切換弁
６２の入口圧力とが作用するようにされている。
すなわち、方向切換弁６３が「イ」の位置では大
径室５１２はタンク１５と連通され、「ロ」の位
置では、大径室５１２が油圧モータ３の入口側お
よび方向切換弁６２の入口側と連通される。 The displacement volume is set by controlling the pressure oil supplied to the hydraulic cylinder 51 constituting the displacement volume setting means 5 by the displacement volume control means 6. This displacement volume control means 6 includes a fixed displacement hydraulic pump 61 and a directional switching valve 6 which is controlled to switch from "A" to "B" by the discharge pressure of the pressure reducing valves 42 and 43.
2, the discharge pressure of the hydraulic pump 61 and the inlet pressure of the hydraulic motor 3 act on the first and second control ports, respectively, and the positions thereof are controlled to be switched from "A" to "B" or an intermediate position thereof. It has a directional switching valve 63. Then, when the secondary pressure of the pressure reducing valves 42 and 43 exceeds P PL , the directional control valve 62 switches to "I".
→ Switch to “Ro”. The inlet pressure of the hydraulic motor 3 always acts on the second control port of the directional switching valve 63, and the discharge pressure of the hydraulic pump 61 acts on the first control port when the directional switching valve 62 is in the "A" position. The spring 64 of the directional control valve 63 is set so that when a pressure higher than the pressure P H acts on the first or second control port, the directional control valve 63 completely switches from "A" to "B". ing. Further, when the directional control valve 62 is in the "B" position, only the inlet pressure of the hydraulic motor 3 acts on the second control port of the directional control valve 63, and when the pressure is in the range of O to P H , It is configured to be held at a corresponding position, that is, an intermediate position between "A" and "B". In addition, the small diameter chamber 51 of the hydraulic cylinder 51
1, the inlet pressure P H of the directional control valve 62 and the inlet pressure of the hydraulic motor 3 (which varies depending on the load) are always applied to the large diameter chamber 5 of the hydraulic cylinder 51.
Tank pressure or the pressure of the hydraulic motor 3 and the inlet pressure of the directional switching valve 62 act on the directional switching valve 62 depending on the switching position of the directional switching valve 63.
That is, when the directional switching valve 63 is in the "A" position, the large diameter chamber 512 is communicated with the tank 15, and when the directional switching valve 63 is in the "B" position, the large diameter chamber 512 is connected to the inlet side of the hydraulic motor 3 and the inlet side of the directional switching valve 62. will be communicated with.
方向制御弁６３が「イ」と「ロ」の中間位置に
あるときは、大径室５１２が、タンク１５側に通
じる管路と、油圧モータ３の入口側および方向制
御弁６２の入口側に通じる管路の双方と、方向制
御弁６３の切換え位置に応じた開度で連通する。
そして、方向制御弁６３が「イ」位置から「ロ」
位置へ向かうほど油圧モータ３および方向制御弁
６２側から大径室５１２へ向う流路の開度が増加
する。 When the direction control valve 63 is in the intermediate position between "A" and "B", the large diameter chamber 512 is connected to the pipe leading to the tank 15 side, the inlet side of the hydraulic motor 3, and the inlet side of the direction control valve 62. It communicates with both of the communicating pipes with an opening degree corresponding to the switching position of the directional control valve 63.
Then, the direction control valve 63 changes from the “A” position to the “B” position.
The opening degree of the flow path from the hydraulic motor 3 and directional control valve 62 side toward the large diameter chamber 512 increases as the position increases.
なお、第１図において、７は減速機８を介して
油圧モータ３と接続された巻上用ドラム、９は減
圧弁４２，４３の油圧源としての固定容量形油圧
ポンプ、１０は巻上用油圧ポンプ１の吐出圧力を
制限するリリーフ弁、１１は高低速切換用油圧ポ
ンプ６１の吐出圧力を制限するリリーフ弁、１２
は操作用油圧ポンプ９の吐出圧力を制限するリリ
ーフ弁、１３はカウンタバランス弁、１４は巻下
時の圧力を制限するシヨツクリリーフ弁、１６は
シヤトル弁、６５〜６７はチエツク弁である。 In FIG. 1, 7 is a hoisting drum connected to the hydraulic motor 3 via a speed reducer 8, 9 is a fixed displacement hydraulic pump as a hydraulic power source for the pressure reducing valves 42 and 43, and 10 is a hoisting drum. A relief valve 11 limits the discharge pressure of the hydraulic pump 1; 11 a relief valve 12 limits the discharge pressure of the high-low speed switching hydraulic pump 61;
13 is a counter balance valve, 14 is a shot relief valve that limits the pressure during lowering, 16 is a shuttle valve, and 65 to 67 are check valves.
このように構成された本実施例の作用について
説明する。 The operation of this embodiment configured in this way will be explained.
(1) 操作レバー４１が低速指示位置の場合
操作レバー４１が中立位置から低速位置までの
間で操作される場合であり、この範囲では減圧弁
４２，４３の二次圧力はＯ〜PPLに可変であり、
コントロールバルブ２はそのクラツキング圧以上
のパイロツト圧により巻上または巻下げ方向に切
換えられるが、方向切換弁６２は図示「イ」の位
置のままである。この場合、油圧ポンプ６１の吐
出圧PHが切換弁６３の第１の制御ポートに作用
し、方向切換弁６３は「ロ」の位置へ切換えられ
る。その結果、油圧シリンダ５１の小径室５１１
および大径室５１２には、ともに油圧モータ３の
入口圧力および油圧ポンプ６１の吐出圧力が作用
するので、２つの室の受圧面積差によりロツド５
２は上方へ移動し、これにより油圧モータ３の押
除け容積は最大値に設定され油圧モータ３は低速
側で駆動される。(1) When the operating lever 41 is in the low speed instruction position This is a case where the operating lever 41 is operated between the neutral position and the low speed position, and in this range, the secondary pressure of the pressure reducing valves 42 and 43 is from O to P PL. variable;
The control valve 2 is switched to the hoisting or hoisting direction by the pilot pressure which is higher than the cracking pressure, but the directional control valve 62 remains in the position "A" shown in the figure. In this case, the discharge pressure P H of the hydraulic pump 61 acts on the first control port of the switching valve 63, and the directional switching valve 63 is switched to the "ro" position. As a result, the small diameter chamber 511 of the hydraulic cylinder 51
Since the inlet pressure of the hydraulic motor 3 and the discharge pressure of the hydraulic pump 61 act on both the large-diameter chamber 512, the rod 5
2 moves upward, and as a result, the displacement volume of the hydraulic motor 3 is set to the maximum value, and the hydraulic motor 3 is driven at a low speed.
(2) 操作レバー４１が高速指示位置の場合
操作レバー４１が低速位置を越えて高速位置へ
操作されるまでの場合であり、この範囲では減圧
弁４２，４３の二次圧力はPPL〜PPHの範囲で可変
であり、方向切換弁６２は「ロ」の位置に切換え
られる。これにより、油圧ポンプ６１の吐出油は
遮断され、方向切換弁６３の第１の制御ポートは
タンク１５と連通されるので、方向切換弁６３は
その第２の制御ポートへ作用する巻上モータ３の
入口圧力に応じた位置に制御される。油圧モータ
３の入口圧力がPHより高ければ低速時の「ロ」
の位置のままであり、低速位置と同様にして油圧
モータ３の押除け容積は最大値を維持し、高速運
転はできないが低速運転される。従つて、高速へ
の切換えに伴い吊り荷が巻上がらない、あるいは
保持していた吊り荷が落下するということがな
い。(2) When the operating lever 41 is in the high-speed command position This is a case where the operating lever 41 exceeds the low-speed position and is operated to the high-speed position. In this range, the secondary pressure of the pressure reducing valves 42 and 43 is P PL ~ P It is variable within the PH range, and the directional switching valve 62 is switched to the "ro" position. As a result, the discharge oil of the hydraulic pump 61 is cut off, and the first control port of the directional control valve 63 is communicated with the tank 15, so that the directional control valve 63 acts on the second control port of the hoisting motor 3. The position is controlled according to the inlet pressure. If the inlet pressure of the hydraulic motor 3 is higher than P H , "B" at low speed.
As in the low speed position, the displacement of the hydraulic motor 3 maintains the maximum value, and high speed operation is not possible, but low speed operation is performed. Therefore, there is no possibility that the suspended load will not be hoisted up or that the suspended load that was being held will fall due to the change to high speed.
一方、油圧モータ３の入口圧力がPH以下の場
合には、その入口圧力に応じて「イ」と「ロ」位
置の中間位置に方向切換弁６３は保持され、これ
により大径室５１２と小径室５１１に作用する圧
力に従つてロツド５２も入口圧力に応じた位置を
とる。油圧モータ３の入口圧力が非常に小さくば
ね６４のばね力により方向切換弁６３が図示
「イ」の位置にあれば、小径室５１１にのみ圧力
が作用するのでロツド５２が最つとも下の位置に
移動し、その結果、油圧モータ３の押除け容積は
最小値となり油圧モータ３に与えられた最高速で
巻上が行なわれる。そして、負荷が大きくなりモ
ータ３の入口圧力がPHに近づくにつれて方向切
換弁６３は「ロ」の位置へ動き、それにつれて大
径室５１２に作用する圧力がタンク圧から上昇し
てロツド５２が図中上方へ移動し、入口圧力に応
じた位置に保持される。すなわち、油圧モータ３
の入口圧力が大きくなると、まず方向制御弁６３
が「イ」位置から「ロ」位置へ向けて移動し、こ
れに伴つて大径室５１２の圧力が上昇して油圧モ
ータ３の押除け容積が増加する。押除け容積が増
加すると、油圧モータ３の負荷が一定であれば油
圧モータ３の入口圧力が低下し、方向制御弁６３
は「イ」側へ戻り始める。方向制御弁６３が戻り
始めると再び油圧モータ３の入口圧力が上昇し、
これにより方向制御弁６３が再度「ロ」側へ移動
する。これらの動作が繰り返されつつ次第に収束
して油圧モータ３の押除け容積が負荷に応じた適
正値となる。その結果、油圧モータ３の押除け容
積は最小値と最大値の中間値となり、その押除け
容積に応じた高速運転が可能となる。 On the other hand, when the inlet pressure of the hydraulic motor 3 is lower than P H , the directional control valve 63 is held at the intermediate position between the "A" and "B" positions according to the inlet pressure, and thereby the large diameter chamber 512 and According to the pressure acting on the small diameter chamber 511, the rod 52 also assumes a position according to the inlet pressure. If the inlet pressure of the hydraulic motor 3 is very small and the spring force of the spring 64 causes the directional control valve 63 to be in position ``A'' in the figure, the pressure acts only on the small diameter chamber 511, so that the rod 52 is at the lowest position. As a result, the displacement volume of the hydraulic motor 3 becomes the minimum value, and hoisting is performed at the maximum speed given to the hydraulic motor 3. Then, as the load increases and the inlet pressure of the motor 3 approaches P H , the directional control valve 63 moves to the "B" position, and the pressure acting on the large diameter chamber 512 rises from the tank pressure, causing the rod 52 to move. It moves upward in the figure and is held at a position according to the inlet pressure. That is, the hydraulic motor 3
When the inlet pressure of the directional control valve 63 increases, first the directional control valve 63
moves from the "A" position to the "B" position, and along with this, the pressure in the large diameter chamber 512 increases and the displacement volume of the hydraulic motor 3 increases. When the displacement volume increases, if the load on the hydraulic motor 3 is constant, the inlet pressure of the hydraulic motor 3 decreases, and the directional control valve 63
begins to return to the "I" side. When the direction control valve 63 begins to return, the inlet pressure of the hydraulic motor 3 rises again.
This causes the direction control valve 63 to move to the "ro" side again. These operations are repeated and gradually converge, and the displacement volume of the hydraulic motor 3 becomes an appropriate value according to the load. As a result, the displacement volume of the hydraulic motor 3 becomes an intermediate value between the minimum value and the maximum value, and high-speed operation according to the displacement volume becomes possible.
ここで、油圧モータ３の入口圧力は、油圧ポン
プ１の圧力の脈動やウインチドラムのロープ巻取
り層数の変化などにより常時細かく変動する。こ
のため、油圧モータ３の入口圧力をそのまま油圧
シリンダ５１へ導くと、油圧シリンダ５１が過剰
に反応して油圧モータ３の押除け容積が頻繁に変
化し、油圧モータ３の回転が安定しなくなる。と
ころが、本実施例では方向制御弁６３の絞り作用
により油圧モータ３の入口圧力の細かな変動が緩
和されて大径室５１２へ導かれるので、油圧モー
タ３の押除け容積の過剰な変化が防止され、油圧
モータ３の回転が安定する。 Here, the inlet pressure of the hydraulic motor 3 constantly fluctuates minutely due to pulsations in the pressure of the hydraulic pump 1, changes in the number of rope winding layers on the winch drum, and the like. Therefore, if the inlet pressure of the hydraulic motor 3 is directly led to the hydraulic cylinder 51, the hydraulic cylinder 51 will react excessively, the displacement volume of the hydraulic motor 3 will change frequently, and the rotation of the hydraulic motor 3 will become unstable. However, in this embodiment, small fluctuations in the inlet pressure of the hydraulic motor 3 are alleviated by the throttling action of the directional control valve 63 and guided to the large diameter chamber 512, thereby preventing excessive changes in the displacement volume of the hydraulic motor 3. The rotation of the hydraulic motor 3 becomes stable.
しかも、油圧シリンダ５１の小径室５１１およ
び大径室５１２の双方に油圧モータ３の入口圧力
を導いているので、方向制御弁６３が最大開度
（「ロ」位置）に達して絞り作用がなくなつても、
小径室５１１と大径室５１２の圧力が同じように
変化して油圧モータ３の入口圧力の脈動が打ち消
され、この結果、油圧モータ３の押除け容積が安
定する。 Moreover, since the inlet pressure of the hydraulic motor 3 is guided to both the small-diameter chamber 511 and the large-diameter chamber 512 of the hydraulic cylinder 51, the directional control valve 63 reaches its maximum opening (the "B" position) and there is no throttling action. Even when I get old,
The pressures in the small diameter chamber 511 and the large diameter chamber 512 change in the same way, canceling out the pulsations in the inlet pressure of the hydraulic motor 3, and as a result, the displacement volume of the hydraulic motor 3 becomes stable.
なお、押除け容積制御手段６を構成する油圧ポ
ンプ６１を省略して、操作回路用の油圧ポンプ９
からの吐出圧油により方向切換弁６３を切換制御
してもよい。また、この種の油圧ウインチを複数
組、例えば、巻上用の第１および第２ウインチを
用いてそれぞれに上述した装置を組み込むことが
できる。この場合、油圧ポンプ６１と９とを共有
化できる。 Note that the hydraulic pump 61 constituting the displacement volume control means 6 is omitted, and the hydraulic pump 9 for the operation circuit is used.
The directional control valve 63 may be controlled by the pressure oil discharged from the directional control valve 63. Furthermore, it is possible to incorporate the above-mentioned device into each of a plurality of sets of this type of hydraulic winch, for example, a first winch and a second winch for hoisting. In this case, the hydraulic pumps 61 and 9 can be shared.
以上説明した実施例において、油圧ポンプ１を
いわゆる全馬力制御で運転し、吐出圧力が高くな
るにつれて押除け容積が小さくなるように制御す
れば、原動機の出力馬力をより一層効率よく利用
できる。また、従来の巻上モータの高速運転は、
いわゆる２ポンプ合流方式により行なわれていた
が、本実施例のように１ポンプ−１モータ方式で
高速運転を行うことにより、配管系統の簡素化お
よび回路中の圧損が低減できるという効果もあ
る。 In the embodiment described above, the output horsepower of the prime mover can be used more efficiently by operating the hydraulic pump 1 under so-called full horsepower control and controlling the displacement volume to become smaller as the discharge pressure increases. In addition, the high-speed operation of conventional hoisting motors is
The so-called two-pump merging system has been used, but by performing high-speed operation using the one-pump-one-motor system as in this embodiment, it is possible to simplify the piping system and reduce pressure loss in the circuit.
更に、以上では巻上ウインチについて説明した
が、本発明は巻上以外、走行等にも適用できる。 Furthermore, although the hoisting winch has been described above, the present invention can also be applied to traveling, etc. other than hoisting.
Ｇ 発明の効果
本発明によれば、オペレータが高速運転を指示
したときに、油圧モータの負荷が所定値よりも大
きければ油圧モータの押除け容積を最大値に維持
し、油圧モータの負荷が所定値以下の場合にはそ
の負荷が小さくなるにつれて押除け容積を小さく
したので、高速運転指示に伴つて油圧モータの入
口圧力が回路最高圧力以上にならず、従つて、油
圧モータの負荷が所定値より大きいときに高速運
転を指示しても作業が中断したり改めて低速運転
を指示し直すことがなく操作性が向上するのに加
えて、例えば吊り荷を保持している場合に高速運
転指示しても吊り荷が落下することもなく安全性
も向上する。G Effect of the Invention According to the present invention, when the operator instructs high-speed operation, if the load on the hydraulic motor is larger than a predetermined value, the displacement volume of the hydraulic motor is maintained at the maximum value, and the load on the hydraulic motor is reduced to the predetermined value. If it is below the specified value, the displacement volume is reduced as the load decreases, so the inlet pressure of the hydraulic motor does not exceed the circuit maximum pressure when high-speed operation is instructed, and therefore the load of the hydraulic motor decreases to the specified value. In addition to improving operability by not interrupting work or instructing low-speed operation again even if high-speed operation is instructed when the load is larger, for example, when a suspended load is being held, high-speed operation may be instructed. Safety is also improved because the suspended load does not fall.
また、高速運転を指示しておくことにより、連
続的に負荷が変わる場合に、油圧モータの押除け
容積が負荷に応じて変わり作業能率が向上する。 Further, by instructing high-speed operation, when the load changes continuously, the displacement volume of the hydraulic motor changes according to the load, improving work efficiency.
操作指示手段が高速指示位置でかつ油圧モータ
の負荷が所定値以下のときは、絞り切換弁によ
り、油圧ポンプの吐出圧力の脈動や油圧モータの
負荷変動に伴う油圧モータ負荷圧力の変動が緩和
され、油圧モータの押除け容積の過剰な変化が防
止されるので、油圧モータの回転数が安定する。 When the operation instruction means is in the high-speed instruction position and the load on the hydraulic motor is below a predetermined value, the throttle switching valve alleviates fluctuations in the hydraulic motor load pressure due to pulsations in the discharge pressure of the hydraulic pump and fluctuations in the load on the hydraulic motor. Since excessive changes in the displacement volume of the hydraulic motor are prevented, the rotation speed of the hydraulic motor is stabilized.
押除け容積設定手段を油圧シリンダとし、その
一方の油室に絞り切換弁から出力される油圧モー
タの負荷圧力を導き、他方の油室に絞り切換弁を
迂回した油圧モータの負荷圧力を導いたときは、
絞り切換弁が最大開度に達して絞り作用がなくな
つても油圧モータの負荷圧力の変動による押除け
容積の過剰な変化が防がれる。 The displacement volume setting means is a hydraulic cylinder, the load pressure of the hydraulic motor output from the throttle switching valve is guided into one oil chamber, and the load pressure of the hydraulic motor bypassing the throttle switching valve is guided into the other oil chamber. when,
Even when the throttle switching valve reaches its maximum opening and the throttle action is no longer present, excessive changes in the displacement volume due to fluctuations in the load pressure of the hydraulic motor are prevented.
第１図は本発明の一実施例を示す油圧回路図で
ある。
１……可変容量形油圧ポンプ、２……コントロ
ールバルブ、３……可変容量形油圧モータ、４…
…操作指示手段、５……押除け容積設定手段、６
……押除け容積制御手段、７……巻上ドラム、５
１……油圧シリンダ、５２……ロツド、６２，６
３……方向切換弁。
FIG. 1 is a hydraulic circuit diagram showing one embodiment of the present invention. 1... Variable displacement hydraulic pump, 2... Control valve, 3... Variable displacement hydraulic motor, 4...
...Operation instruction means, 5... Displacement volume setting means, 6
...Displacement volume control means, 7...Hoisting drum, 5
1... Hydraulic cylinder, 52... Rod, 62,6
3... Directional switching valve.
Claims (1)
より回転駆動される可変容量形油圧モータと、そ
の油圧モータの押除け容積を設定する押除け容積
設定手段と、その設定手段により設定すべき押除
け容積を指示する操作指示手段とを備えた油圧駆
動装置において、 前記操作指示手段の低速指示位置に従つて押除
け容積をその最大値とすべく前記設定手段を制御
し、前記操作指示手段の高速指示位置に従つて、
前記油圧モータの負荷が所定値より大きいときに
押除け容積を最大値とし、その負荷が所定値以下
では負荷が小さくなるにつれて押除け容積を小さ
くすべく前記設定手段を制御する押除け容積制御
手段を具備し、該押除け容積制御手段は、前記操
作指示手段が高速指示位置でかつ前記油圧モータ
の負荷が前記所定値以下のとき前記油圧モータの
負荷圧力の変化に基づいて絞り量が変化する絞り
切換弁を備え、前記高速指示位置かつ前記油圧モ
ータの負荷が前記所定値以下のときに当該絞り切
換弁から出力される前記油圧モータの負荷圧力に
基づいて前記設定手段を制御することを特徴とす
る油圧駆動装置。 ２ 前記押除け容積設定手段は、前記油圧モータ
の負荷圧力が前記絞り切換弁を介して一方の油室
へ導かれ、前記油圧モータの負荷圧力が前記絞り
切換弁を迂回して他方の油室へ導かれる油圧シリ
ンダであることを特徴とする特許請求の範囲第１
項記載の油圧駆動装置。[Scope of Claims] 1. A hydraulic pump, a variable displacement hydraulic motor rotationally driven by pressure oil from the hydraulic pump, a displacement volume setting means for setting the displacement volume of the hydraulic motor, and the setting means. and an operation instruction means for instructing a displacement volume to be set by: controlling the setting means to set the displacement volume to its maximum value according to a low speed instruction position of the operation instruction means; According to the high speed instruction position of the operation instruction means,
Displacement volume control means for controlling the setting means to set the displacement volume to a maximum value when the load of the hydraulic motor is greater than a predetermined value, and to reduce the displacement volume as the load decreases when the load is less than a predetermined value. The displacement volume control means changes the amount of throttling based on a change in the load pressure of the hydraulic motor when the operation instruction means is at the high speed instruction position and the load of the hydraulic motor is less than or equal to the predetermined value. It is characterized by comprising a throttle switching valve, and controlling the setting means based on the load pressure of the hydraulic motor output from the throttle switching valve when the high-speed instruction position and the load of the hydraulic motor are below the predetermined value. Hydraulic drive device. 2 The displacement volume setting means is configured such that the load pressure of the hydraulic motor is guided to one oil chamber via the throttle switching valve, and the load pressure of the hydraulic motor bypasses the throttle switching valve and is directed to the other oil chamber. Claim 1 characterized in that it is a hydraulic cylinder guided to
Hydraulic drive device as described in section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60272883A JPS62132002A (en) | 1985-12-04 | 1985-12-04 | Hydraulic driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60272883A JPS62132002A (en) | 1985-12-04 | 1985-12-04 | Hydraulic driving device |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4258355A Division JP2545180B2 (en) | 1992-09-28 | 1992-09-28 | Control device for variable displacement hydraulic motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62132002A JPS62132002A (en) | 1987-06-15 |
| JPH0517961B2 true JPH0517961B2 (en) | 1993-03-10 |
Family
ID=17520085
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60272883A Granted JPS62132002A (en) | 1985-12-04 | 1985-12-04 | Hydraulic driving device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62132002A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0160004U (en) * | 1987-10-09 | 1989-04-17 | ||
| JPH0160003U (en) * | 1987-10-09 | 1989-04-17 | ||
| JP2651079B2 (en) * | 1991-07-24 | 1997-09-10 | 日立建機株式会社 | Hydraulic construction machinery |
| JP2545180B2 (en) * | 1992-09-28 | 1996-10-16 | 日立建機株式会社 | Control device for variable displacement hydraulic motor |
| JP4166604B2 (en) * | 2003-03-26 | 2008-10-15 | 日立住友重機械建機クレーン株式会社 | Winch speed control device and crane |
| JP5896675B2 (en) * | 2011-09-30 | 2016-03-30 | 株式会社タダノ | Crane equipment |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5320080A (en) * | 1976-08-04 | 1978-02-23 | Kawasaki Heavy Ind Ltd | Two speed motor hydraulic control system |
| JPS57195089A (en) * | 1981-05-21 | 1982-11-30 | Kaiyo Giken Kk | Hydraulic motor circuit |
| JPS60191993A (en) * | 1984-03-13 | 1985-09-30 | 株式会社福島製作所 | Controller for hydraulic winch |
-
1985
- 1985-12-04 JP JP60272883A patent/JPS62132002A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5320080A (en) * | 1976-08-04 | 1978-02-23 | Kawasaki Heavy Ind Ltd | Two speed motor hydraulic control system |
| JPS57195089A (en) * | 1981-05-21 | 1982-11-30 | Kaiyo Giken Kk | Hydraulic motor circuit |
| JPS60191993A (en) * | 1984-03-13 | 1985-09-30 | 株式会社福島製作所 | Controller for hydraulic winch |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62132002A (en) | 1987-06-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |