JPH086721B2 - Hydraulic circuit - Google Patents
Hydraulic circuitInfo
- Publication number
- JPH086721B2 JPH086721B2 JP12295590A JP12295590A JPH086721B2 JP H086721 B2 JPH086721 B2 JP H086721B2 JP 12295590 A JP12295590 A JP 12295590A JP 12295590 A JP12295590 A JP 12295590A JP H086721 B2 JPH086721 B2 JP H086721B2
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- Prior art keywords
- pressure
- valve
- load
- hydraulic
- compensating valve
- Prior art date
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Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、１つの油圧ポンプの吐出圧油を複数の油圧
アクチュエータに供給する油圧回路に関する。Description: TECHNICAL FIELD The present invention relates to a hydraulic circuit that supplies the hydraulic fluid discharged from one hydraulic pump to a plurality of hydraulic actuators.
１つの油圧ポンプの吐出圧油を複数の油圧アクチュエ
ータに供給するには、油圧ポンプの吐出路に複数の操作
弁を設け、その操作弁を切換えることで各油圧アクチュ
エータに圧油を供給すれば良いが、このようにすると複
数の油圧アクチュエータに圧油を同時に供給する際に、
負荷の小さな油圧アクチュエータにのみ圧油が供給され
て負荷の大きな油圧アクチュエータに圧油が供給されな
くってしまう。In order to supply the pressure oil discharged from one hydraulic pump to the plurality of hydraulic actuators, a plurality of operation valves may be provided in the discharge passage of the hydraulic pump, and the pressure oil may be supplied to each hydraulic actuator by switching the operation valves. However, in this way, when supplying pressure oil to multiple hydraulic actuators simultaneously,
The pressure oil is supplied only to the hydraulic actuator having a small load, and the pressure oil is not supplied to the hydraulic actuator having a large load.
このことを解消する油圧回路として、例えば特開昭59
−197603号公報に示すものが提案されている。As a hydraulic circuit for solving this, for example, Japanese Patent Laid-Open No.
-197603 has been proposed.
かかる油圧回路を模式的に示すと第２図に示すように
なる。A schematic view of such a hydraulic circuit is shown in FIG.
つまり、油圧ポンプ１の吐出路1aに複数の操作弁２を
設け、各操作弁２と各油圧アクチュエータ３を接続する
回路４に圧力補償弁５をそれぞれ設けると共に、各回路
４の圧力、つまり負荷圧における最も高い圧力をシヤト
ル弁６で検出し、その検出した負荷圧を各圧力補償弁５
に作用してその負荷圧に見合う圧力にセットし、各操作
弁２の出口側圧力を等しくして各操作弁２を同時操作し
た時に各操作弁の開口面積に比例した分流比で各油圧ア
クチュエータ３に圧油を供給できるようにしてある。That is, a plurality of operating valves 2 are provided in the discharge passage 1a of the hydraulic pump 1, a pressure compensating valve 5 is provided in each circuit 4 that connects each operating valve 2 and each hydraulic actuator 3, and the pressure of each circuit 4, that is, the load. The highest pressure among the pressures is detected by the shuttle valve 6, and the detected load pressure is detected by each pressure compensation valve 5.
To set the pressure corresponding to the load pressure, and when the operating valves 2 are operated at the same time by making the outlet pressures of the operating valves 2 equal, each hydraulic actuator is operated at a diversion ratio proportional to the opening area of each operating valve. The pressure oil can be supplied to 3.
第２図に示した従来技術は、複数の油圧アクチュエー
タ３を有する油圧回路において、油圧アクチュエータ３
に作用する負荷の大きさによらず、操作弁２の操作量に
比例した圧油を、複数の油圧アクチュエータ３に供給し
ようとすることを目的とするものであるが、第２図の構
成では、以下の問題点がある。The conventional technique shown in FIG. 2 is a hydraulic circuit having a plurality of hydraulic actuators 3.
The purpose of the present invention is to supply pressure oil proportional to the operation amount of the operation valve 2 to a plurality of hydraulic actuators 3, regardless of the magnitude of the load acting on the. However, there are the following problems.
第２図において、右の油圧アクチュエータ（シリン
ダ）３を高負荷側、左の油圧アクチュエータ（モータ）
３が低負荷側であるとすると、右の油圧アクチュエータ
３の負荷圧がシャトル弁６で選択されて油圧ポンプ１の
制御装置に導入されるとともに、自らの圧力補償弁（右
側）５と低負荷側の圧力補償弁（左側）５に作用する。In FIG. 2, the right hydraulic actuator (cylinder) 3 is on the high load side, and the left hydraulic actuator (motor) is
Assuming that 3 is on the low load side, the load pressure of the right hydraulic actuator 3 is selected by the shuttle valve 6 and introduced into the control device of the hydraulic pump 1. It acts on the side pressure compensation valve (left side) 5.
自らの圧力補償弁（右側）５には、圧力補償弁５の開
口を絞る側に、自らの負荷圧P3と弱いバネ力（番号を指
示せず）が作用し、開口を開く側に圧力補償弁５の入口
側圧力P2が作用する。圧力補償弁５には若干の通路抵抗
が存在するため入口側圧力P2と出口側圧力（負荷圧）P3
の関係はP2＞P3であるから自らの圧力補償弁５は、 （P2による開き方向の力）＝（P3による閉じ方向の力） ＋（弱いバネ力）＋（フローフォース） というバランス状態となり、ほぼ全開に近い状態で流量
Q1の圧油を右の油圧アクチュエータ３（シリンダ）に供
給する。The pressure compensating valve 5 (right side) of the pressure compensating valve 5 has its own load pressure P 3 and a weak spring force (without indicating the number) acting on the side where the opening of the pressure compensating valve 5 is narrowed, and pressure is applied to the side where the opening is opened. The inlet side pressure P 2 of the compensating valve 5 acts. Since there is some passage resistance in the pressure compensation valve 5, the inlet side pressure P 2 and the outlet side pressure (load pressure) P 3
The relationship own pressure compensating valve 5 because it is P 2> P 3, that (the direction of the force to open by P 2) = (P 3 by closing direction force) + (weak spring force) + (flow force) The balance is reached, and the flow rate is almost full
Supplies pressure oil for Q 1 to the right of the hydraulic actuator 3 (cylinder).
一方、低負荷側の圧力補償弁５には、開口を絞る側に
高負荷側の負荷圧P3が作用するため、圧力補償弁５の開
口は絞られて、その入口側圧P2は結果としてP3の圧力ま
で昇圧する。（より正確には、弱いバネのバネ力分もプ
ラスされる） つまり高負荷側の圧油の流量Q1は （Ｃは常数、a1は操作弁２の開口面積、P1は油圧ポンプ
１の吐出圧力） 低負荷側の圧油の流量Q2は、 （Ｃは常数、a2は操作弁２の開口面積、P1は油圧ポンプ
１の吐出圧力） となり、開口面積a1＝a2としても、それぞれの油圧アク
チュエータ３への供給流量は、Q1＝Q2とならない。On the other hand, in the pressure compensation valve 5 on the low load side, the load pressure P 3 on the high load side acts on the side that throttles the opening, so the opening of the pressure compensation valve 5 is throttled, and the inlet side pressure P 2 is consequently It boosted to a pressure of P 3. (More accurately, the spring force of the weak spring is also added.) In other words, the flow rate Q 1 of the pressure oil on the high load side is (C is a constant, a 1 is the opening area of the operation valve 2, P 1 is the discharge pressure of the hydraulic pump 1) The flow rate Q 2 of the pressure oil on the low load side is (C is a constant, a 2 is the opening area of the operation valve 2, P 1 is the discharge pressure of the hydraulic pump 1), and even if the opening area is a 1 = a 2 , the supply flow rate to each hydraulic actuator 3 is Q 1 = Q 2 is not achieved.
すなわち、低負荷側の操作弁２の出口圧力（圧力補償
弁５の入口側圧力）P2は、高負荷側の操作弁２の出口圧
力（圧力補償弁５の入口側圧力）P2とならず、それより
低い高負荷側の圧力補償弁５の出口側圧力（負荷圧）P3
となるため、操作弁２の開口面積が同じでも低負荷側の
油圧アクチュエータ３への供給流量の方が多くなってし
まう。That is, if the outlet pressure of the operation valve 2 on the low load side (the inlet side pressure of the pressure compensation valve 5) P 2 is the same as the outlet pressure of the operation valve 2 on the high load side (the inlet side pressure of the pressure compensation valve 5) P 2. No pressure, lower than that, the outlet side pressure (load pressure) P 3 of the pressure compensating valve 5 on the high load side.
Therefore, even if the opening area of the operation valve 2 is the same, the flow rate supplied to the hydraulic actuator 3 on the low load side becomes larger.
この問題を解消するため、負荷圧を圧力補償弁５の出
口側の回路４ではなく、圧力補償弁５の入口側（P2部）
で検出するという案もあるが、こうすると自ら（高圧
側）の圧力補償弁５には、開口を開く方向に入口側圧力
P2が、また閉じる方向に入口側圧力P2が作用するため、
自らの圧力補償弁５は開弁できなくなってしまう。In order to solve this problem, the load pressure is not applied to the circuit 4 on the outlet side of the pressure compensating valve 5, but to the inlet side of the pressure compensating valve 5 (P 2 part).
There is also a plan to detect it with this method, but if this is done, the pressure compensating valve 5 on its own (high pressure side) will have pressure on the inlet side in the direction of opening the opening.
Since P 2 acts on the inlet side pressure P 2 in the closing direction again,
The pressure compensation valve 5 of its own cannot be opened.
あるいは、負荷圧として検出する圧力は操作弁２と圧
力補償弁５の間で入口側圧力P2を検出する位置より、圧
力補償弁５に近い側で検出（すなわち負荷圧P3を入口側
圧力P2よりわずかに低い圧力Ｐ′２として検出）し、自
らの圧力補償弁５が開弁するようにしたとしても、圧力
補償弁５には圧油の通過によるフローフォースが作用す
るため、自らの圧力補償弁５はより開口が絞られる位置
に動いてしまい、その結果P2、Ｐ′２はより上昇してし
まう。Alternatively, the pressure detected as the load pressure is detected closer to the pressure compensating valve 5 than the position where the inlet pressure P 2 is detected between the operation valve 2 and the pressure compensating valve 5 (that is, the load pressure P 3 is the inlet pressure P 2). detected) as a slightly lower pressure P '2 from P 2, even 5 themselves of the pressure compensating valves so as to open, to act the flow force due to the passage of the pressure oil in the pressure compensating valve 5, itself The pressure compensating valve 5 is moved to a position where the opening is further narrowed, and as a result, P 2 and P ′ 2 are further raised.
するとP2、Ｐ′２と負荷圧P3の圧力差は大きくなり、
フローフォースは圧力差に応じて大きくなるので圧力補
償弁５はさらに絞られてP2、Ｐ′２はさらに上昇してし
まう結果となり、高圧側の圧力補償弁５は、本来若干の
通過抵抗で全開に近い状態でいるべきものが絞られて、
大きな圧力差を発生してしまい、パワーロスを生じてし
まうためこの方式も採用できない。Then, the pressure difference between P 2 and P ′ 2 and the load pressure P 3 becomes large,
Since the flow force increases in accordance with the pressure difference, the pressure compensating valve 5 is further throttled and P 2 and P ′ 2 are further raised, and the pressure compensating valve 5 on the high pressure side originally has a slight passage resistance. Things that should be in a state close to full open are squeezed,
This method cannot be used because it causes a large pressure difference and power loss.
そこで、本発明は前述の課題を解決できるようにした
油圧回路を提供することを目的とする。Therefore, an object of the present invention is to provide a hydraulic circuit capable of solving the above-mentioned problems.
本発明に係る油圧回路は、油圧ポンプ10の吐出路10a
に複数の操作弁15を設け、各操作弁15と各油圧アクチュ
エータ16の接続回路に圧力補償弁18をそれぞれ設け、各
圧力補償弁18を各油圧アクチュエータ16の負荷圧におけ
る最高圧でセットするようにした油圧回路において、 前記各油圧アクチュエータ16の負荷圧として、圧力補
償弁18の入口側圧力と出口側圧力の中間の圧力をそれぞ
れ検出し、 前記圧力補償弁18を第１受圧部19の圧力と第２受圧部
20の圧力の差圧によってセットされる構成とし、 その第１受圧部19に圧力補償弁18の入口側圧力を供給
し、第２受圧部20に各油圧アクチュエータ16の負荷圧に
おける最も高い負荷圧を供給するようにしたものであ
る。The hydraulic circuit according to the present invention includes a discharge passage 10a of the hydraulic pump 10.
A plurality of operating valves 15 are provided in each, and a pressure compensating valve 18 is provided in the connection circuit of each operating valve 15 and each hydraulic actuator 16, and each pressure compensating valve 18 is set to the maximum pressure of the load pressure of each hydraulic actuator 16. In the hydraulic circuit described above, as the load pressure of each hydraulic actuator 16, an intermediate pressure between the inlet side pressure and the outlet side pressure of the pressure compensation valve 18 is detected, and the pressure compensation valve 18 is set to the pressure of the first pressure receiving portion 19. And the second pressure receiving part
The pressure is set according to the differential pressure of 20. The inlet pressure of the pressure compensating valve 18 is supplied to the first pressure receiving section 19 and the second pressure receiving section 20 has the highest load pressure of the hydraulic actuators 16. Is to be supplied.
これにより、低負荷側の圧力補償弁18の第１受圧部19
の圧力と第２受圧部20の圧力との差圧は、圧力補償弁18
の入口側圧力と油圧ポンプの吐出圧力との差圧が小さく
なって低負荷側の油圧アクチュエータ16の流量と高負荷
側の油圧アクチュエータ16の流量との差が小さくなり、
高負荷側の圧力補償弁18の第１受圧部19の圧力は第２受
圧部の圧力よりも必ず高くなり、その圧力補償弁18がほ
ぼ全開に近い状態に開弁する。As a result, the first pressure receiving portion 19 of the pressure compensation valve 18 on the low load side is provided.
The pressure difference between the pressure of the pressure compensation valve 18 and the pressure of the second pressure receiving portion 20 is
The pressure difference between the inlet side pressure and the discharge pressure of the hydraulic pump decreases, and the difference between the flow rate of the low load hydraulic actuator 16 and the high load hydraulic actuator 16 decreases.
The pressure of the first pressure receiving portion 19 of the pressure compensating valve 18 on the high load side is always higher than the pressure of the second pressure receiving portion, and the pressure compensating valve 18 opens in a state of being almost fully opened.
第１図に示すように、油圧ポンプ10は斜板11の角度を
変更することで容量、つまり１回転当たり吐出流量が変
化する可変容量型の油圧ポンプとなり、その斜板11は大
径ピストン12で容量減方向に傾動し、小径ピンストン13
で容量増方向に傾動する。As shown in FIG. 1, the hydraulic pump 10 is a variable displacement type hydraulic pump in which the displacement, that is, the discharge flow rate per rotation is changed by changing the angle of the swash plate 11. The swash plate 11 has a large-diameter piston 12 It tilts in the direction of decreasing capacity with
It tilts in the capacity increasing direction.
前記大径ピストン12の受圧室12aは切換弁14で油圧ポ
ンプ10の吐出路10aに連通・遮断され、小径ピントン13
の受圧室13aは前記吐出路10aに接続してある。The pressure receiving chamber 12a of the large-diameter piston 12 is connected to and cut off from the discharge passage 10a of the hydraulic pump 10 by the switching valve 14, and the small-diameter pinton 13
The pressure receiving chamber 13a is connected to the discharge passage 10a.
前記油圧ポンプ10の吐出路10aには複数の操作弁15が
設けてあり、各操作弁15と油圧アクチュエータ16を接続
する回路17に圧力補償弁18がそれぞれ設けてあり、該圧
力補償弁18は第１受圧部19の圧油で開口を開き低圧セッ
ト側に押され、第２受圧部20の圧油で開口を絞り高圧セ
ット側に押される構成としてあり、第１受圧部19は圧力
補償弁18の入口側に接続されて入口側圧力が供給され、
第２受圧部20はシャトル弁21を経て各負荷圧導入路22に
接続されて最も高い負荷圧が供給される。A plurality of operating valves 15 are provided in the discharge passage 10a of the hydraulic pump 10, and a pressure compensating valve 18 is provided in a circuit 17 connecting each operating valve 15 and the hydraulic actuator 16, and the pressure compensating valve 18 is The opening is opened by the pressure oil of the first pressure receiving portion 19 and pushed toward the low pressure set side, and the opening is narrowed by the pressure oil of the second pressure receiving portion 20 and pushed toward the high pressure setting side. The first pressure receiving portion 19 is a pressure compensating valve. Connected to the inlet side of 18 to supply inlet pressure,
The second pressure receiving portion 20 is connected to each load pressure introducing passage 22 via the shuttle valve 21 so that the highest load pressure is supplied.
前記切換弁14は吐出路10a内の圧力で連通方向に押さ
れ、バネ23と前記負荷圧でドレーン方向に押されて、吐
出圧力P1が高くなると大径ピストン12の受圧室12aに吐
出圧を供給して斜板11を容量減方向に傾動し、吐出圧力
P1が低くなると大径ピストン12の受圧室12aをタンク側
に流出して斜板11を容量増方向に傾動する。The switching valve 14 is pushed in the communication direction by the pressure in the discharge passage 10a, and is pushed in the drain direction by the spring 23 and the load pressure, and when the discharge pressure P 1 becomes high, the discharge pressure is supplied to the pressure receiving chamber 12a of the large-diameter piston 12. Is supplied to tilt the swash plate 11 in the capacity decreasing direction, and the discharge pressure
When P 1 becomes low, the pressure receiving chamber 12a of the large-diameter piston 12 flows out to the tank side and the swash plate 11 tilts in the capacity increasing direction.
前記操作弁15はパイロット制御弁24よりのパイロット
圧油に比例して開口面積が増大する方向に操作され、そ
のパイロット圧油はレバー25の操作ストロークに比例す
る。The operation valve 15 is operated in a direction in which the opening area increases in proportion to the pilot pressure oil from the pilot control valve 24, and the pilot pressure oil is proportional to the operation stroke of the lever 25.
前記負荷圧導入路22は圧力補償弁18の入口側と出口側
とに接続し、かつ第１・第２絞り26,27とチェック弁28
が設けてあり、圧力補償弁18の入口側圧力P2と出口側圧
力P3の中間の圧力が負荷圧PLSとしてシャトル弁21に導
入されるようにしてある。The load pressure introducing passage 22 is connected to the inlet side and the outlet side of the pressure compensating valve 18, and the first and second throttles 26 and 27 and the check valve 28 are connected.
Is provided so that an intermediate pressure between the inlet side pressure P 2 and the outlet side pressure P 3 of the pressure compensating valve 18 is introduced into the shuttle valve 21 as the load pressure P LS .
つまり、第１絞り26と第２絞り27との間をシャトル弁
21の入口側に接続し、その第１・第２絞り26,27の絞り
面積比に基づく中間の圧力が負荷圧PLSとしてシャトル
弁21の入口側にそれぞれ流入し、その負荷圧PLSを比較
して高い圧力を出力側より最高負荷圧として出力し、圧
力補償弁５の第２受圧部20に供給する。That is, the shuttle valve is provided between the first throttle 26 and the second throttle 27.
Connected to the inlet side of the 21 flows respectively on the inlet side of the shuttle valve 21 as a first-intermediate pressure is the load pressure P LS based on the aperture area ratio of the second diaphragm 26 and 27, the load pressure P LS By comparison, a higher pressure is output from the output side as the maximum load pressure and is supplied to the second pressure receiving portion 20 of the pressure compensation valve 5.
このようであるから、右の油圧アクチュエータ（シリ
ンダ）16を高負荷側、左の油圧アクチュエータ（モー
タ）16を低負荷側であるとすると、右の圧力補償弁18の
入口側圧力P2と出口側圧力P3の中間の圧力P4が負荷圧と
して検出され、この中間の圧力P4は左右の圧力補償弁18
の第２受圧部20にそれぞれ作用する。Therefore, assuming that the right hydraulic actuator (cylinder) 16 is on the high load side and the left hydraulic actuator (motor) 16 is on the low load side, the inlet pressure P 2 and the outlet of the right pressure compensating valve 18 are An intermediate pressure P 4 of the side pressure P 3 is detected as a load pressure, and this intermediate pressure P 4 is applied to the left and right pressure compensation valves 18
To the second pressure receiving portion 20 of each.
このために、高負荷側（右側）の圧油の流量Q1は、 （Ｃは常数、a1は操作弁２の開口面積、P1は油圧ポンプ
１の吐出圧力） 低負荷側の圧油の流量Q2は、 （Ｃは常数、a2は操作弁２の開口面積、P1は油圧ポンプ
１の吐出圧力） となる。For this reason, the flow rate Q 1 of the pressure oil on the high load side (right side) is (C is a constant, a 1 is the opening area of the operation valve 2, P 1 is the discharge pressure of the hydraulic pump 1) The flow rate Q 2 of the pressure oil on the low load side is (C is a constant, a 2 is an opening area of the operation valve 2, and P 1 is a discharge pressure of the hydraulic pump 1).
ここで、前記の中間の圧力P4は入口側圧力P2より低く
出口側圧力P3より高いので（P1−P4）は（P1−P3）より
も小さくなり、低負荷側の流量Q2は従来よりも少ないか
ら、左右の操作弁２の開口面積が同じ場合に高負荷側の
流量Q1と低負荷側の流量Q2との差が従来よりも小さくな
る。Here, since the intermediate pressure P 4 is lower than the inlet pressure P 2 and higher than the outlet pressure P 3 , (P 1 −P 4 ) becomes smaller than (P 1 −P 3 ), and the low load side Since the flow rate Q 2 is smaller than before, the difference between the flow rate Q 1 on the high load side and the flow rate Q 2 on the low load side becomes smaller than before when the opening areas of the left and right operation valves 2 are the same.
また、高負荷側の圧力補償弁18の第１受圧部19には入口
側圧力P2が作用し、第２受圧部20には中間の圧力P4が作
用し、P2＞P4であるから圧力補償弁５は開弁できる。In addition, the inlet pressure P 2 acts on the first pressure receiving portion 19 of the pressure compensation valve 18 on the high load side, and the intermediate pressure P 4 acts on the second pressure receiving portion 20, so that P 2 > P 4 . Therefore, the pressure compensation valve 5 can be opened.
また、高負荷側の圧力補償弁５がフローフォースによ
り開口を絞られる位置に動くと、入口側圧力P2は若干高
くなるが、出口側圧力P3は一定であるために、中間の圧
力P4が若干高くなる程度であり、結局高負荷側の圧力補
償弁５はほぼ全開に近い状態となり、パワーロスが発生
しない。Further, when the pressure compensation valve 5 on the high load side moves to a position where the opening is throttled by the flow force, the inlet side pressure P 2 becomes slightly higher, but the outlet side pressure P 3 is constant, so the intermediate pressure P 2 4 is slightly high, and the pressure compensating valve 5 on the high load side is in a state of being almost fully opened, so that power loss does not occur.
圧力補償弁18の入口側圧力と出口側圧力の中間の圧力
を油圧アクチュエータ16の負荷圧として検出し、各油圧
アクチュエータの最も高い負荷圧を各圧力補償弁18の第
２受圧部20に供給するので、複数の油圧アクチュエータ
16を同時に操作した時に低負荷側の圧力補償弁18の入口
側圧力と油圧ポンプの吐出圧力との差圧は小さくなる
し、高負荷側の圧力補償弁18の第１受圧部19の圧力は第
２受圧部20の圧力よりも必ず高くなる。An intermediate pressure between the inlet side pressure and the outlet side pressure of the pressure compensating valve 18 is detected as the load pressure of the hydraulic actuator 16, and the highest load pressure of each hydraulic actuator is supplied to the second pressure receiving portion 20 of each pressure compensating valve 18. So multiple hydraulic actuators
When 16 are operated simultaneously, the differential pressure between the inlet side pressure of the low load side pressure compensating valve 18 and the discharge pressure of the hydraulic pump becomes small, and the pressure of the first pressure receiving portion 19 of the high load side pressure compensating valve 18 becomes It is always higher than the pressure of the second pressure receiving portion 20.
したがって、複数の油圧アクチュエータを同時に操作
した時に高負荷側の油圧アクチュエータの流量と低負荷
側の油圧アクチュエータの流量の差が小さくなるし、高
負荷圧側の圧力補償弁18がほぼ全開に近い状態に開弁し
てパワーロスが生じることもない。Therefore, when a plurality of hydraulic actuators are operated simultaneously, the difference between the flow rate of the hydraulic actuator on the high load side and the flow rate of the hydraulic actuator on the low load side becomes small, and the pressure compensation valve 18 on the high load pressure side becomes almost full open. There is no power loss due to valve opening.
第１図は本発明の実施例を示す油圧回路図、第２図は従
来例の油圧回路図である。 10は油圧ポンプ、10aは吐出路、15は操作弁、16は油圧
アクチュエータ、17は回路、18は圧力補償弁、19,20は
第１・第２受圧部。FIG. 1 is a hydraulic circuit diagram showing an embodiment of the present invention, and FIG. 2 is a hydraulic circuit diagram of a conventional example. Reference numeral 10 is a hydraulic pump, 10a is a discharge passage, 15 is an operation valve, 16 is a hydraulic actuator, 17 is a circuit, 18 is a pressure compensating valve, and 19 and 20 are first and second pressure receiving portions.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 山下 光治 神奈川県川崎市川崎区中瀬３―20―１ 株 式会社小松製作所川崎工場内 (72)発明者 篠崎 晋一 神奈川県川崎市川崎区中瀬３―20―１ 株 式会社小松製作所川崎工場内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Koji Yamashita 3-20-1 Nakase, Kawasaki-ku, Kawasaki-shi, Kanagawa Komatsu Ltd. Kawasaki Plant (72) Inventor Shinichi Shinozaki Nakase-ku, Kawasaki-shi, Kanagawa 3- 20-1 Komatsu Manufacturing Co., Ltd. Kawasaki Factory
Claims (1)
5を設け、各操作弁15と各油圧アクチュエータ16の接続
回路に圧力補償弁18をそれぞれ設け、各圧力補償弁18を
各油圧アクチュエータ16の負荷圧における最高圧でセッ
トするようにした油圧回路において、 前記各油圧アクチュエータ16の負荷圧として、圧力補償
弁18の入口側圧力と出口側圧力の中間の圧力をそれぞれ
検出し、 前記圧力補償弁18を第１受圧部19の圧力と第２受圧部20
の圧力の差圧によってセットされる構成とし、 その第１受圧部19に圧力補償弁18の入口側圧力を供給
し、第２受圧部20に各油圧アクチュエータ16の負荷圧に
おける最も高い負荷圧を供給するようにした油圧回路。1. A plurality of operating valves 1 in a discharge passage 10a of a hydraulic pump 10.
In the hydraulic circuit in which 5 is provided, the pressure compensating valve 18 is provided in the connection circuit of each operation valve 15 and each hydraulic actuator 16, and each pressure compensating valve 18 is set at the maximum pressure of the load pressure of each hydraulic actuator 16. As the load pressure of each hydraulic actuator 16, an intermediate pressure between the inlet side pressure and the outlet side pressure of the pressure compensating valve 18 is detected, and the pressure compensating valve 18 is set to the pressure of the first pressure receiving portion 19 and the second pressure receiving portion. 20
Is set by the differential pressure of the pressure, the inlet side pressure of the pressure compensating valve 18 is supplied to the first pressure receiving part 19, and the highest load pressure among the load pressures of the hydraulic actuators 16 is supplied to the second pressure receiving part 20. Hydraulic circuit designed to be supplied.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12295590A JPH086721B2 (en) | 1990-05-15 | 1990-05-15 | Hydraulic circuit |
| KR1019910701937A KR920702755A (en) | 1990-05-15 | 1991-05-15 | Hydraulic system |
| DE69120818T DE69120818T2 (en) | 1990-05-15 | 1991-05-15 | HYDRAULIC SYSTEM |
| DE69132071T DE69132071T2 (en) | 1990-05-15 | 1991-05-15 | Hydraulic system |
| EP91909094A EP0536398B1 (en) | 1990-05-15 | 1991-05-15 | Hydraulic system |
| EP95103115A EP0657656B1 (en) | 1990-05-15 | 1991-05-15 | Hydraulic apparatus |
| PCT/JP1991/000641 WO1991018212A1 (en) | 1990-05-15 | 1991-05-15 | Hydraulic system |
| US07/793,395 US5271227A (en) | 1990-05-15 | 1991-05-15 | Hydraulic apparatus with pressure compensating valves |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12295590A JPH086721B2 (en) | 1990-05-15 | 1990-05-15 | Hydraulic circuit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0419403A JPH0419403A (en) | 1992-01-23 |
| JPH086721B2 true JPH086721B2 (en) | 1996-01-29 |
Family
ID=14848764
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12295590A Expired - Fee Related JPH086721B2 (en) | 1990-05-15 | 1990-05-15 | Hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH086721B2 (en) |
-
1990
- 1990-05-15 JP JP12295590A patent/JPH086721B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0419403A (en) | 1992-01-23 |
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