JPS5986704A - Capacity compensating device of hydrualic closed circuit - Google Patents
Capacity compensating device of hydrualic closed circuitInfo
- Publication number
- JPS5986704A JPS5986704A JP19681382A JP19681382A JPS5986704A JP S5986704 A JPS5986704 A JP S5986704A JP 19681382 A JP19681382 A JP 19681382A JP 19681382 A JP19681382 A JP 19681382A JP S5986704 A JPS5986704 A JP S5986704A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- circuit
- rod cylinder
- driven
- low pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
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- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、油圧ｄｔｔとこの油圧υｒ、４ Ｋ接続され
た片ロツドシリンダより成る油田閉回路に生じる流ｊｋ
不足を補償する油［Ｌ閉回路の容量補償装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention is based on the hydraulic pressure dtt, this hydraulic pressure υr, and the flow jk generated in an oil field closed circuit consisting of a single-rod cylinder connected to 4K.
This article relates to a capacity compensator for an L closed circuit that compensates for a shortage of oil.
片ロツドシリンダをアクチュエータとする油圧閉回路に
おいては、片ロツドシリンダのヘッド側とロッド側の受
圧面積の差により片ロツドシリンダを駆動したときその
閉回路に流ｔ（の過不足を生じ、過剰分はリリーフ弁を
介してタンクに排出し、不足分は別に設置したチャージ
ポンプ等から供給−号るようになっ″〔いる。以下、図
によりこれを説明する。In a hydraulic closed circuit that uses a single-rod cylinder as an actuator, when the single-rod cylinder is driven due to the difference in the pressure-receiving area between the head side and rod side of the single-rod cylinder, an excess or deficiency of flow t (t) occurs in the closed circuit, and the excess flow is handled by the relief valve. The remaining amount is supplied from a separately installed charge pump or the like.This will be explained below with reference to the drawings.
第１図は従来の片ロツドシリンダの油圧閉回路の系統図
である。FIG. 1 is a system diagram of a conventional hydraulic closed circuit of a single rod cylinder.
図で、１は可変容置油圧ポンプであり、斜板、斜軸等に
よりその吐出方向、吐出量が制御される。In the figure, 1 is a variable displacement hydraulic pump, and its discharge direction and discharge amount are controlled by a swash plate, a diagonal shaft, etc.
２は前記油圧ポンプ１で駆動される片ロツドシリンダ、
３は油出ポンプ１と片ロツドシリンダ２とを接続する油
圧回路、４は油圧回路３に介在する切換弁、５は油圧回
路３のヘッド側とロッド側の間に接続されたフラッシン
グ弁、６は逆止弁である。７は油出回路３に生じる流量
不足を補ｆＪｆするチャージポンプ、８は油圧閉回路３
に生じる過剰流量を排出するリリーフ弁、９は作動油タ
ンク、川はフラッシング弁５により油圧回路３の低圧側
とリリーフ弁８とを接続する低圧回路である。2 is a single rod cylinder driven by the hydraulic pump 1;
3 is a hydraulic circuit connecting the oil pump 1 and the single rod cylinder 2, 4 is a switching valve interposed in the hydraulic circuit 3, 5 is a flushing valve connected between the head side and the rod side of the hydraulic circuit 3, and 6 is a hydraulic circuit connecting the oil pump 1 and the single rod cylinder 2; It is a check valve. 7 is a charge pump that compensates for the flow shortage occurring in the oil output circuit 3; 8 is a hydraulic closed circuit 3;
9 is a hydraulic oil tank, and 9 is a low pressure circuit that connects the low pressure side of the hydraulic circuit 3 and the relief valve 8 through a flushing valve 5.
このような片ロッドシリンダ２０油工回路３においては
、前述の如く片ロツドシリンダ２の受圧面積の差による
駆動時の容積変化やリークにより流量に過不足を生じる
。この場合、もし、油圧回路３のいずれ１１１１１かに
流量不足を生じたときは、チャージポンプ７からの圧油
が逆止弁６を介して、又、フラッシング弁５、低圧回路
１０．逆止弁６を介して、流蓋不足側の油圧回路３に供
給されて流量不足を袖ｆＡする。逆に、油圧回路３のい
ずれ側かに流星過剰を生じたときは、フラッシング弁５
．１氏出回路１０を介して過剰流量が流れ、このとき低
圧回路１０σ）圧力がリリーフ弁８のリリーフ設定圧す
る。In such a single rod cylinder 20 hydraulic circuit 3, excess or deficiency in flow rate occurs due to volume changes and leaks during driving due to the difference in pressure receiving areas of the single rod cylinders 2, as described above. In this case, if a flow shortage occurs in any one of the hydraulic circuits 3 11111, the pressure oil from the charge pump 7 will flow through the check valve 6, the flushing valve 5, the low pressure circuit 10. It is supplied via the check valve 6 to the hydraulic circuit 3 on the side where there is insufficient flow cover to prevent insufficient flow fA. Conversely, if an excess of meteor occurs on either side of the hydraulic circuit 3, the flushing valve 5
．． Excess flow flows through the 1°C output circuit 10, and at this time, the pressure in the low pressure circuit 10σ) becomes the relief setting pressure of the relief valve 8.
このように、従来、油圧ポンプ１と片ロツドシリンダ２
とで油１１−閏回路を構成する場合、片ロツドシリンダ
２の駆動による流量不足の発生に備え、その不足を補償
するチャージポンプ７の設置が不可欠となっていた。し
かしながら、チャージポンプ７には通常、定警犀型の油
圧ポンプが用（・られているため、油圧回路３で流量不
足が生じな℃・ときは、チャージポンプ７の圧油はリリ
ーフ弁８を介してタンクに放出されてしまい、極めて不
紗済であった。このため、チャージポンプ７に代えてチ
ャージ専用のｉ＋Ｊ変容振ポンプを用（・ることカー提
案されているが、このよ５な勇変宕証ポンプは非常に高
価であり、実用に適さないという欠点があった０
本発明σ）目的目１、−に記従来の問題を解決し、チャ
ージポンプ、ｒｉＪ変容祉ポンプ等を別途設置すること
なく不足流量を補償することができる油圧閉回路の容量
袖償佐匝を提供するにある。In this way, conventionally, the hydraulic pump 1 and the single rod cylinder 2
When constructing an oil 11-leap circuit, it is essential to install a charge pump 7 to compensate for the insufficient flow rate due to the drive of the single rod cylinder 2. However, since the charge pump 7 is usually a constant-warning type hydraulic pump, when there is insufficient flow in the hydraulic circuit 3, the pressure oil in the charge pump 7 is supplied to the relief valve 8. Therefore, it was proposed that an i+J transducer pump exclusively for charging should be used in place of the charge pump 7. The Yuhengosho pump had the disadvantage of being extremely expensive and unsuitable for practical use.The present invention σ) Objective 1. - Solve the conventional problems stated in -, and separately install charge pumps, RIJ transformation pumps, etc. The purpose is to provide a hydraulic closed circuit capacity compensation system that can compensate for insufficient flow without installation.
この目的を達成するため、本発明は、複数の油圧源と、
これら油圧源にそれぞれ接続されたアクチュエータとを
備え、これらアクチュエータの少なくとも１つは油圧源
とともに閉回路を構成する片ロツドシリンダであり、片
ロツドシリンダが駆！［ｉｌ＋されるときに、駆動され
ていない他の油圧ｄ９を、駆動されている片ロツドシリ
ンダの閉回路に接続して、この接続された油圧源により
閉回路の不足流量を補償するようにしたことを特徴とす
る。To achieve this objective, the present invention comprises a plurality of hydraulic sources;
and actuators connected to each of these hydraulic power sources, at least one of these actuators is a single-rod cylinder that forms a closed circuit with the hydraulic power source, and the single-rod cylinder is driven! [When il + is applied, the other hydraulic pressure d9 which is not driven is connected to the closed circuit of the driven single rod cylinder, and the insufficient flow rate of the closed circuit is compensated by this connected hydraulic pressure source. It is characterized by
以下、本発明を第２図に示す実施例に基づいて説明する
。The present invention will be explained below based on the embodiment shown in FIG.
第２図で、１１は可変容量油圧ポンプ（以下単に油出ポ
ンプという。）であり、その吐出量および吐出方向は斜
板、斜軸等（以下斜板で代表する。）により制御される
。１２は油圧ポンプ１１で駆動される片ロツドシリンダ
、１３は油圧ポンプ１１と片ロツドシリンダｊ２とを接
続して閉回路を構成する油圧回路である。１４は油圧回
路１３に介在する第１の切換弁であり、中立位置Ｃ２左
１ｊｌｌ１位（候り、右側位置口・に切換えられ、中立
位置、Ｃで油圧ポンプ１１と片ロツドシリンダ１２を遮
断し、左側位１ｇ蔓りで両者を導通状態とする。右側位
置Ｊ−１については後述する。In FIG. 2, reference numeral 11 denotes a variable displacement hydraulic pump (hereinafter simply referred to as oil pump), the discharge amount and discharge direction of which are controlled by a swash plate, a slant shaft, etc. (hereinafter referred to as swash plate). 12 is a single rod cylinder driven by the hydraulic pump 11, and 13 is a hydraulic circuit that connects the hydraulic pump 11 and the single rod cylinder j2 to form a closed circuit. Reference numeral 14 designates a first switching valve interposed in the hydraulic circuit 13, which is switched from a neutral position C2 to a left position (C2) and a right position (opening), and shuts off the hydraulic pump 11 and the single-rod cylinder 12 at the neutral position C. Both are brought into conduction state by the left position 1g.The right position J-1 will be described later.
１５は油圧回路Ｉ３のヘッド側とロッド側の間に接続さ
れたフラッシング弁、］６は逆止弁、１７は上側位置Ｕ
と下側位置、１〕に切換えられる第２の切換弁である。15 is a flushing valve connected between the head side and rod side of the hydraulic circuit I3,] 6 is a check valve, and 17 is an upper position U.
and the lower position, 1].
１８は油圧ポンプ１１の斜板の傾転量、傾転方向を検出
する傾転量検出装置、１９は油圧ポンプ１１の斜板を駆
動する斜板駆動装置である。Reference numeral 18 denotes a tilting amount detection device that detects the amount and direction of tilting of the swash plate of the hydraulic pump 11, and 19 a swash plate drive device that drives the swash plate of the hydraulic pump 11.
以上述べた油ＬＥ閉回路と同じ油圧閉回路が第２図で右
側に示されている。即ち、２１は油圧ポンプ、２２は片
ロツドシリンダ、詔は油圧回路、囚は第１の切換弁、５
はフラッシング弁、２６は逆止弁、２７は第２の切換弁
、甜は傾転量検出装置、２９は斜板駆動装置である。A hydraulic closed circuit similar to the oil LE closed circuit described above is shown on the right side of FIG. That is, 21 is a hydraulic pump, 22 is a single rod cylinder, 1 is a hydraulic circuit, 2 is a first switching valve, 5
26 is a flushing valve, 26 is a check valve, 27 is a second switching valve, 甜 is a tilting amount detecting device, and 29 is a swash plate driving device.
第１図に示すＩＪ ＩＪ−フ弁８、作動油タンク９゜低
圧回路用は、本実施例においては左右の油田回路に対し
て共通に設けられている。低圧回路１０からは、各第１
の切換弁１４、冴のボートに接続する分岐回路１０ａ、
、 ＩＵａＩおよび各第２の切換弁１７．２７と一方
の逆止弁１６、あの中間に接続する分岐回路１０ｂ、
、 Ｊｏｂ、が分岐している。In this embodiment, the IJ valve 8 and the hydraulic oil tank 9 for the low pressure circuit shown in FIG. 1 are provided in common for the left and right oil field circuits. From the low voltage circuit 10, each first
a switching valve 14, a branch circuit 10a connected to Sae's boat,
, IUaI and each second switching valve 17, 27 and one check valve 16, a branch circuit 10b connected to that intermediate,
, Job, are branching.
加は片ロツドシリンダ１２を操作する操作レバー、ぷ）
は片ロツドシリンダ２２を操作する操作レバーである。In addition, there is an operation lever for operating the single rod cylinder 12.
is an operating lever for operating the single rod cylinder 22.
３１は左右の油圧閉回路の作動を制御する制御装置であ
り、操作レバー加、（ト）、傾転量検出装置俯６１８、
あの信号を入力し、この信号に基づいて油圧ポンプ１１
．２１の斜板の傾転方向、傾転量、および第１の切換弁
１４、別、第２の切換弁１７．２７の切換えを制御する
。制御装置３１は演算回路又はマイクロコンビ二一夕を
用いて構成されている。31 is a control device that controls the operation of the left and right hydraulic closed circuits;
Input that signal, and based on this signal, the hydraulic pump 11
．． It controls the direction and amount of tilting of the swash plate 21, and the switching of the first switching valve 14, another switching valve 17, and the second switching valve 17.27. The control device 31 is constructed using an arithmetic circuit or a microcombiner.
次に、本実施例の動作を、第３図に示すフローチャート
を参照しながら説明する。Next, the operation of this embodiment will be explained with reference to the flowchart shown in FIG.
制御装［，３１に堀源が投入されると、制御装置３Ｉに
おいては、まず、操作レバー加からの操作信号が入力さ
れているか否かを判断する（第１のステップＳ１゜以下
各ステップを符号８．、Ｓ、・・・・・・・・・で表ず
。）。操作レバー加からの操作信号がなければ、今度は
操作レバー加からの操作信号が入力されているか否かを
判断する（Ｓ、）。操作レバー（資）からの信号もない
場合、即ち、操作レバー別、（資）のいずれも操作され
ていない場合、制御装置３１がらは第１の切換弁１４、
冴を中立位置Ｃとする信号および第２の切換弁１７．２
７を下側位１ｔｆｆｉ Ｄとする信号が出力される（Ｓ
３）。これにより、油圧ポンプ１１と片ロヅドシリンダ
１２との間は遮断され、低圧回路１０の分岐回路１０１
１． 、 ｌＯｂ、は逆止弁１６、がを介して油圧回路
１３、田に接続される。この状態では当然ながら左右の
両油Ｌ［閉回路は全く作動しない。When the control device 31 is turned on, the control device 3I first determines whether an operation signal from the operation lever is input (first step S1 and subsequent steps are performed). It is not represented by the code 8., S, ......). If there is no operation signal from the operation lever, it is then determined whether or not an operation signal from the operation lever is input (S,). When there is no signal from the operating lever (equipment), that is, when none of the operating levers (equipment) is operated, the control device 31 switches the first switching valve 14,
Signal to set Sae to neutral position C and second switching valve 17.2
A signal with 7 as the lower position 1tffiD is output (S
3). As a result, the hydraulic pump 11 and the single-rod cylinder 12 are cut off, and the branch circuit 101 of the low pressure circuit 10 is disconnected.
1. , lOb, are connected to the hydraulic circuit 13 through the check valve 16, respectively. Naturally, in this state, both the left and right oil L [closed circuits] do not operate at all.
これとは逆に、操作レバー加、３０の両者が同時に操作
された場合、まず、操作レバー加が操作されていると判
断され（Ｓ、）、次いで、操作レバーよ）も操作されて
いると判断される（Ｓ４）。そうすると、前述の操作レ
バー加、刃とも操作されていない場合と同じく８α３の
ステップＳ３に移行し、さきに述べたと同（））ｔＶＣ
ｌ、−、右の両油圧閉回路を不作動状態とし、流量不足
による事故発生を防止するようになっている。On the contrary, if both the operating levers 30 are operated at the same time, it is determined that the operating lever 30 is operated first, and then it is determined that the operating lever 30 is also operated. A determination is made (S4). Then, the process moves to step S3 of 8α3, which is the same as when neither the operation lever nor the blade is operated, and the same ())tVC as mentioned earlier is reached.
Both the l, - and right hydraulic closed circuits are rendered inactive to prevent accidents due to insufficient flow.
次に、いずれかのＩＶ：作レバー、例えば操作レバー２
０が操作されて片ロツドシリンダ１２が駆動されている
場合を考える。この場合、制御装置３１では、第１のス
テップＳＩで操作レバー九の操作信号が入力されている
と判断し、第４のステップＳ４で操作レバー（資）の信
号は入力されていないと判断スる。Next, press any IV: operation lever, for example operation lever 2.
Let us consider the case where the single rod cylinder 12 is driven by the operation of the cylinder 0. In this case, the control device 31 determines in the first step SI that the operation signal of the control lever 9 has been input, and in the fourth step S4 it determines that the signal of the control lever (9) has not been input. Ru.
そうすると、制御装置ｉ！７３１からは、第１の切換弁
１４を左側位１ｔｌ’ｆ Ｌに切換える信号、第１の切
換弁別を右側位置几に切換える信号、第２の切換弁１７
を下側位置ＤＫ切換える信号、第２の切換弁２７を上側
位朧、Ｕに切換える信号が出力される（Ｓｓ）。これに
より、各切換弁は第２図に示す状態となり、油ＩＥポン
プ１１と片ロツドシリンダ１２．および分岐回路１０
ｂ 、と油圧回路１３がそれぞれ接続される。一方、油
田ポンプ２１と片ロツドシリンダ２２、および分岐回路
１（ｌ ｂ 、と油圧回路おがそれぞれ遮断状態になる
とともに、第１の切換弁２４により油圧ポンプ１１の一
方側は作Ｈｉｌ＋油タンク９に接続され、他方側は分岐
回路１（ｌａｙに接続される。次に、制御装置３１は傾
転Ｍ検出装置ｋ１Ｂの信号を取入れて油圧ポンプ１１の
斜板の傾転量、傾転方向を検出する（Ｓ＠）。そして、
斜板の傾転方向から、油圧ポンプ１１が片ロツドシリン
ダ１２を、油圧回路１３に流量不足を生じる方向に駆動
してぃイ）が否かを判断する（ｓ７）。負荷により異な
るものの、一般的に番オ１、片ロツドシリンダのロッド
が伸長する方向の駆動の場合に油圧回路１３に流量不足
を生じる。なお、流用、過剰の場合は、その過刺分かリ
リーフ弁８がら作動油タンク９に排出されるので問題は
生じない。さて、ステップＳ、で油圧回路１３に流量不
足が生じないと判断された場合、制御装置３１がらは斜
板駆動装置〆１゜２９に対して油圧ボンダ２１の斜板な
中立位置とするような指令信号が出力される（ｓ８）。Then, the control device i! From 731, a signal to switch the first switching valve 14 to the left position 1tl'f L, a signal to switch the first switching valve to the right position, and a signal to switch the first switching valve 14 to the right position 1tl'f L, the second switching valve 17
A signal for switching the second switching valve 27 to the lower position DK and a signal for switching the second switching valve 27 to the upper position, U, are output (Ss). As a result, each switching valve becomes the state shown in FIG. 2, and the oil IE pump 11, single rod cylinder 12. and branch circuit 10
b and the hydraulic circuit 13 are connected to each other. On the other hand, the oil field pump 21, the single-rod cylinder 22, the branch circuit 1 (lb), and the hydraulic circuit are each cut off, and the first switching valve 24 switches one side of the hydraulic pump 11 to the active Hil+oil tank 9. The other side is connected to the branch circuit 1 (lay).Next, the control device 31 receives the signal from the tilt M detection device k1B and detects the tilt amount and tilt direction of the swash plate of the hydraulic pump 11. (S@).And,
Based on the tilting direction of the swash plate, it is determined whether the hydraulic pump 11 is driving the single rod cylinder 12 in a direction that causes a flow shortage in the hydraulic circuit 13 (s7). Although it varies depending on the load, in general, a flow shortage occurs in the hydraulic circuit 13 when the rod of the No. 1 single-rod cylinder is driven in the direction of extension. In addition, in the case of diversion or excess, the overfill is discharged from the relief valve 8 into the hydraulic oil tank 9, so no problem occurs. Now, if it is determined in step S that there is no shortage of flow in the hydraulic circuit 13, the control device 31 moves the hydraulic bonder 21 to the neutral position of the swash plate with respect to the swash plate drive device 〆1゜29. A command signal is output (s8).
これにより、油田ポンプ２１は不作動状態となり、圧油
は吐出されない。ステップＳ、で油Ｉｆ回路１３りし流
量不足が生じると判断された場合、制御装Ｊｊ、ｉ ３
１がらは斜板駆動装置２９に対し“〔油Ｌ１−ポンプ２
１の斜板の傾転ｉｔを油圧ポンプ１１の斜板の傾転量と
等しくする指令信号が出力される（Ｓｏ）。これにより
、油圧ポンプ２１の斜板は油圧ポンプ１１０余ｌ板と等
ｈ１だけ傾転し、油圧ポンプ２１からはこれに応じた圧
油（流ｉｔ不足に見合った童の圧油）が吐出される。即
ち、作動油タンク９の油は第２の切換弁２４、油圧回路
るを経て油圧ポンプ２１の一方側に吸入され、他方側か
ら吐出される。吐出された油は第１の切換弁別、分岐回
路１０ａ７、低圧回路１０、分岐回路１０ｂ’、、逆止
弁１６又は第２の切換弁１７と逆止弁１６を経て流量不
足側の油圧回路１３に供給される。このため、油圧回路
１３の流量不足は完全に補償される。この圧油の［Ｊｔ
、給回路において、第２の切換弁２７は、分岐回路Ｊｏ
ｂ、を介する低圧回路１０と作動油タンク９との連通を
遮断するものであり、前記連通により圧油がポンプ２１
を循環して圧油回路１３のｖｔｔ 址不足側へ供給され
な（なるのを防止している。As a result, the oilfield pump 21 becomes inactive, and no pressure oil is discharged. If it is determined in step S that insufficient flow occurs in the oil If circuit 13, the control device Jj, i3
1 to the swash plate drive device 29.
A command signal that makes the tilting amount of the swash plate of the hydraulic pump 11 equal to the amount of tilting of the swash plate of the hydraulic pump 11 is output (So). As a result, the swash plate of the hydraulic pump 21 is tilted by an amount h1 equal to the plate of the hydraulic pump 110, and the hydraulic pump 21 discharges a corresponding amount of pressure oil (pressure oil commensurate with the lack of flow). Ru. That is, the oil in the hydraulic oil tank 9 is sucked into one side of the hydraulic pump 21 via the second switching valve 24 and the hydraulic circuit, and is discharged from the other side. The discharged oil passes through the first switching valve, the branch circuit 10a7, the low pressure circuit 10, the branch circuit 10b', the check valve 16, or the second switching valve 17 and the check valve 16, and then enters the hydraulic circuit 13 on the side where the flow rate is insufficient. supplied to Therefore, the insufficient flow rate of the hydraulic circuit 13 is completely compensated for. This pressure oil [Jt
, in the supply circuit, the second switching valve 27 is connected to the branch circuit Jo.
The communication between the low pressure circuit 10 and the hydraulic oil tank 9 via the
This prevents the VTT from being circulated and supplied to the VTT insufficient side of the pressure oil circuit 13.
操作レバー３０が操作され、操作レバー四が操作されて
いない場合も、左右の油圧閉回路の各要素の動作が入れ
換わるのみで他はステップＳ、〜ステップＳ９と同じ動
作を行って油圧回路乙の流量不足を油圧ポンプ１１で補
償する。この動作がステップ８）６〜ステツプ８１４に
示されている。この場合、油圧ポンプ２Ｉで片ロツドシ
リンダ２２が駆動され、第１の１７Ｊ換弁１４は右側位
置）ＬＫ、第１の切換弁２４は左側位置りに、第２の切
換弁１７は上側位置Ｕに、れ、油圧ポンプ１１がらの圧
油は分岐回路１０ａ、、低圧回路１０、分岐回路１０ｂ
、を経て油ＥＥ回路乙の流Ｊ「４゜不足側に供給される
。ステップＳ、。〜ステップ８１４の動作の詳細な説明
は省略する。Even when the operating lever 30 is operated and the operating lever 4 is not operated, the operations of the respective elements of the left and right hydraulic closed circuits are simply switched, and the other operations are the same as steps S to S9, and the hydraulic circuit B is closed. The hydraulic pump 11 compensates for the insufficient flow rate. This operation is shown in steps 8)6 to 814. In this case, the single rod cylinder 22 is driven by the hydraulic pump 2I, the first 17J switching valve 14 is in the right position (LK), the first switching valve 24 is in the left position, and the second switching valve 17 is in the upper position U. The pressure oil from the hydraulic pump 11 is transferred to a branch circuit 10a, a low pressure circuit 10, and a branch circuit 10b.
, and is supplied to the 4° deficient side of the oil EE circuit B.A detailed explanation of the operations from step S to step 814 will be omitted.
このように、本実施例では、２つの同じ片ロツドシリン
ダの油圧閉回路を備え、部層１されている油圧閉回路に
流１不足が生じたとき、駆動されていない油圧閉回路の
油ｏニポンプから不足流量に見合った圧油が供給２≦れ
るので、チャージポンプ、可変容置ポンプ等を別途設置
することなく流量不足を補償することができ、このため
全体の構成がｆｆ１ｉ易になり、安価と１．イ）。又、
不足流量に見合った圧油を供給するので、リリーフ弁か
らのエネルギ損失も少なり７．Ｘる。In this way, this embodiment has two hydraulic closed circuits of the same single-rod cylinder, and when a shortage of flow 1 occurs in the hydraulic closed circuit in which the hydraulic closed circuit is connected to Since pressure oil commensurate with the insufficient flow rate is supplied from 2≦, it is possible to compensate for the insufficient flow rate without separately installing a charge pump, variable displacement pump, etc. This makes the entire configuration easier and cheaper. and 1. stomach). or,
Since pressure oil is supplied in proportion to the insufficient flow rate, energy loss from the relief valve is also reduced.7. X Ru.
なお、前記実施例においては、片ロツドシリンダの２つ
の油圧閉囲ｌｌ′１１の相互の芥量補イハについて示し
たが、３つ以上の油圧閉回路相互の容箪袖償も可能であ
るのは明らかであり、又、開回路の油−１源を用いるこ
とができるのも明らかである。さらに、前記実施例では
、駆動されていない油圧源を駆動されている片ロンドシ
リンダの油圧閉回路に接続するため通常の切換弁にポー
トを増設しているが、前記接続のための切換弁を通常の
切換弁とは別に設置するとともできる。さらに又、前記
実施例では、２つの油圧ポンプと２つの片ロツドシリン
ダが同じであることから、駆動されていない油圧ポンプ
の傾転量を駆動されている油圧ポンプの傾転量と等しく
なるような制御としたが、これらが同じでない場合には
、駆動されている片ロツドシリンダの圧力を検出し、こ
の検出された値とその片ロツドシリンダのロッド測とヘ
ッド側の受圧面積比から補償すべき流量は直ちに演算で
きるので、この演算結果に応じて駆動されていない油圧
ポンプの傾転量を制御すればよい。この場合、駆動され
ていない油圧ポンプが複数あれば、補償すべぎ流量ｔに
応じてそれらすべての油圧ポンプの傾転量を制御しても
よいし、又は、任意のものを選択して制御しても差支え
ない。In the above embodiment, mutual compensation of the capacity of the two hydraulic closed circuits 11'11 of a single rod cylinder was shown, but it is also possible to compensate the capacity of three or more closed hydraulic circuits. It is clear that it is also possible to use an open circuit oil-1 source. Furthermore, in the above embodiment, a port is added to the normal switching valve in order to connect the hydraulic pressure source that is not being driven to the hydraulic closed circuit of the driven single cylinder. It can also be installed separately from a normal switching valve. Furthermore, in the above embodiment, since the two hydraulic pumps and the two single-rod cylinders are the same, the amount of tilting of the hydraulic pump that is not driven is made equal to the amount of tilting of the hydraulic pump that is being driven. However, if these are not the same, the pressure of the single-rod cylinder being driven is detected, and the flow rate to be compensated for is determined from this detected value, the rod measurement of the single-rod cylinder, and the pressure-receiving area ratio on the head side. Since the calculation can be performed immediately, the amount of tilting of the hydraulic pump that is not being driven can be controlled in accordance with the calculation result. In this case, if there are multiple hydraulic pumps that are not driven, the tilting amount of all the hydraulic pumps may be controlled according to the compensation flow rate t, or an arbitrary one may be selected and controlled. There is no problem.
以上述べたように、本発明では、油圧閉回路を構成する
片ロツドシリンダが駆動され、その油圧閉回路に流量不
足を生じたとき、駆動されていない他の油圧源から圧油
を供給するようにしたので、チャージポンプ、０■変容
伍ポンプ等を別途設置することなく流４．不足を補供す
ることができ、このｔこめ全体の構成が簡易になり、安
価となる。As described above, in the present invention, when a single rod cylinder forming a hydraulic closed circuit is driven and a flow shortage occurs in the hydraulic closed circuit, pressure oil is supplied from another hydraulic source that is not driven. Therefore, flow 4. without separately installing a charge pump, 0■ conversion pump, etc. The shortage can be compensated for, and the overall structure of this T-filler becomes simple and inexpensive.
第１図は従来の片ロツドシリンダの油圧閉回路の系統図
、第２１ネ１は本発明の実施例に係る片ロツドシリンダ
の油上閉回路の容量補償装置の油圧回路および′電気回
路の系統図、第３図は第２図に示す容量補償装置ａ−の
動作を説明するフローチャートである。
１１．２１・・・・・・ｎ」変容社油圧ボンノ、１２．
２２・・・・・・片ロツドシリンダ、［４，２４・・・
・・第１の切換弁、１７．２７・・・・・・第２の切換
弁、１８、昂・・・・・・傾転量検出装置、１９．２９
・・・・・・斜板駆動装置、２Ｕ、３０・・・・・・操
作レバー、３１・・・・・・制御装置。Fig. 1 is a system diagram of a conventional hydraulic closed circuit of a single rod cylinder, and 21st page 1 is a system diagram of a hydraulic circuit and an electric circuit of a capacity compensator for an oil closed circuit of a single rod cylinder according to an embodiment of the present invention. FIG. 3 is a flowchart illustrating the operation of the capacitance compensator a- shown in FIG. 11.21...n'' Henshinsha Hydraulic Bonno, 12.
22... Single rod cylinder, [4, 24...
...First switching valve, 17.27...Second switching valve, 18, Length...Tilt amount detection device, 19.29
... Swash plate drive device, 2U, 30 ... Operation lever, 31 ... Control device.
Claims (1)
るとともに少なくとも１つが閉回路で接続された片ロツ
ドシリンダである複数のアクチュエータと、前記片ロツ
ドシリンダが駆動されるとき駆動されていない前記油圧
源を前記駆動されている片ロツドシリンダの駆動回路に
接続する接続手段とで構成されることを特徴とする油圧
閉回路の容量補償装置。 ２、特ｒｒ ｉ＋／ｉ求の範囲第１項において、前記接
続手段は、ｊｓＩＪ ｆｆｄ片ロ片ロッドシリンダッド
側回路およびロッド側回路に接続された低圧回路と、こ
の低圧回路に駆動されていない前記油圧劇を接続する１
４）１の切換弁と、前記片ロツドシリンダを駆動する油
圧酋が前記第１の切換弁により前記低圧回路に接続され
たときこの低圧回路と作動油タンクを遮断する第２の切
換弁とより成ることを特徴とする油圧閉回路の容量補償
装置。[Claims] 1. A plurality of hydraulic power sources, a plurality of actuators each connected to these hydraulic power sources and at least one of which is a single rod cylinder connected in a closed circuit, and driven when the single rod cylinder is driven. and connecting means for connecting the hydraulic power source that is not being driven to the drive circuit of the single-rod cylinder that is being driven. 2. Particular range of rr i+/i In Item 1, the connecting means is connected to a low pressure circuit connected to the jsIJ ffd single rod single rod cylinder pad side circuit and the rod side circuit, and to a low pressure circuit that is not driven by this low pressure circuit. Connecting the hydraulic drama 1
4) comprising a switching valve 1 and a second switching valve that cuts off the low pressure circuit and the hydraulic oil tank when the hydraulic machine that drives the single rod cylinder is connected to the low pressure circuit by the first switching valve. A hydraulic closed circuit capacity compensation device characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19681382A JPS5986704A (en) | 1982-11-11 | 1982-11-11 | Capacity compensating device of hydrualic closed circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19681382A JPS5986704A (en) | 1982-11-11 | 1982-11-11 | Capacity compensating device of hydrualic closed circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5986704A true JPS5986704A (en) | 1984-05-19 |
Family
ID=16364079
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19681382A Pending JPS5986704A (en) | 1982-11-11 | 1982-11-11 | Capacity compensating device of hydrualic closed circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5986704A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990007031A1 (en) * | 1988-12-19 | 1990-06-28 | Kabushiki Kaisha Komatsu Seisakusho | Service valve circuit in a hydraulic excavator |
| CN105074230A (en) * | 2013-09-02 | 2015-11-18 | 日立建机株式会社 | Drive device for work machine |
| KR20220014888A (en) * | 2019-08-14 | 2022-02-07 | 파커-한니핀 코포레이션 | An electro-hydraulic drive system for a machine, a machine equipped with an electro-hydraulic drive system, and a control method of the electro-hydraulic drive system |
-
1982
- 1982-11-11 JP JP19681382A patent/JPS5986704A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990007031A1 (en) * | 1988-12-19 | 1990-06-28 | Kabushiki Kaisha Komatsu Seisakusho | Service valve circuit in a hydraulic excavator |
| US5148676A (en) * | 1988-12-19 | 1992-09-22 | Kabushiki Kaisha Komatsu Seisakusho | Confluence valve circuit of a hydraulic excavator |
| CN105074230A (en) * | 2013-09-02 | 2015-11-18 | 日立建机株式会社 | Drive device for work machine |
| KR20220014888A (en) * | 2019-08-14 | 2022-02-07 | 파커-한니핀 코포레이션 | An electro-hydraulic drive system for a machine, a machine equipped with an electro-hydraulic drive system, and a control method of the electro-hydraulic drive system |
| JP2022539184A (en) * | 2019-08-14 | 2022-09-07 | パーカー－ハネフィン コーポレーション | Electrohydraulic drive system for machines, machines with electrohydraulic drive systems, and methods for controlling electrohydraulic drive systems |
| US11781289B2 (en) | 2019-08-14 | 2023-10-10 | Parker-Hannifin Corporation | Electro-hydraulic drive system for a machine |
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