JPH05172108A - Hydraulic circuit - Google Patents
Hydraulic circuitInfo
- Publication number
- JPH05172108A JPH05172108A JP3355649A JP35564991A JPH05172108A JP H05172108 A JPH05172108 A JP H05172108A JP 3355649 A JP3355649 A JP 3355649A JP 35564991 A JP35564991 A JP 35564991A JP H05172108 A JPH05172108 A JP H05172108A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- load
- pressure receiving
- valve
- receiving portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】[0001]
【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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic circuit for supplying pressure oil discharged from one hydraulic pump to a plurality of hydraulic actuators.
【０００２】[0002]
【従来の技術】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ユ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
が供給されなくなってしまう。このことで解消する油圧
回路として、例えば特公平２−４９４０５号公報に示す
ものが提案されている。2. Description of the Related Art In order to supply the discharge pressure oil of one hydraulic pump to a plurality of hydraulic actuators, a plurality of operation valves are provided in the discharge passage of the hydraulic pump, and the operation valves are switched to change the pressure oil to each hydraulic actuator. However, when supplying pressure oil to multiple hydraulic actuators at the same time, pressure oil is supplied only to the hydraulic actuator with a small load, and pressure oil is not supplied to the hydraulic actuator with a large load. Will end up. As a hydraulic circuit to be solved by this, for example, the one shown in Japanese Patent Publication No. 2-49405 has been proposed.
【０００３】かかる油圧回路を模式的に示すと図１に示
すようになる。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
い圧力をチェック弁６で負荷圧検出路７に検出し、その
検出した負荷圧を各圧力補償弁５の受圧部５ａ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。A schematic diagram of such a hydraulic circuit is shown in FIG. 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 connecting 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 check valve 6 in the load pressure detection path 7, and the detected load pressure is applied to the pressure receiving portion 5a of each pressure compensating valve 5 and set to a pressure corresponding to the load pressure. When the pressures on the outlet side of the valves 2 are made equal and the respective operating valves 2 are simultaneously operated, the pressure oil can be supplied to the respective hydraulic actuators 3 at a flow dividing ratio proportional to the opening area of each operating valve.
【０００４】かかる油圧回路であると、圧力補償弁５の
機能によって各油圧アクチュエータ３の負荷の大小に無
関係に操作弁２の開口面積に比例した流量分配ができる
から、１つの油圧ポンプ１の吐出圧油を操作弁２の操作
量に比例して各油圧アクチュエータ３にそれぞれ供給で
きる。With such a hydraulic circuit, the function of the pressure compensating valve 5 allows the flow rate distribution to be proportional to the opening area of the operating valve 2 regardless of the load of each hydraulic actuator 3, so that the discharge of one hydraulic pump 1 can be performed. The pressure oil can be supplied to each hydraulic actuator 3 in proportion to the operation amount of the operation valve 2.
【０００５】[0005]
【発明が解決しようとする課題】前述の圧力補償弁５は
第１の受圧部５ａに作用する最高負荷圧ＰLSとばね力で
閉じ側に押され、第２の受圧部５ｂに作用する操作弁出
口圧（メータイン後流圧）Ｐ0 で開き側に押されると共
に、前記第１の受圧部５ａと第２の受圧部５ｂの受圧面
積が同一であるから操作弁出口圧Ｐ0 は最高負荷圧ＰLS
と等しくなる。このために、油圧アクチュエータが左右
の走行用油圧モータである場合に、一方（図１で左側）
の操作弁２の開度を大として駆動側とし、他方（図１で
右側）の操作弁２の開度を小として従動側として旋回走
行する際に制動側の圧力補償弁５の第１の受圧部５ａに
作用する負荷圧ＰLSと駆動側の負荷圧ＰLS1 が等しけれ
ば左右の走行用油圧モータへの供給流量が両方の操作弁
２の開度比に比例した値となり、その両方の操作弁２の
開度比により旋回半径がコントロールされる。しかしな
がら、制動側の圧力補償弁５の第１の受圧部５ａに作用
する負荷圧ＰLSは漏れ等による圧損が生じ駆動側の負荷
圧ＰLS1 より低くなってしまうので、制動側の走行用モ
ータへの流入量が増大し旋回半径が両方の操作弁２の開
度比に見合う値と異なって旋回走行しずらくなる。The above-mentioned pressure compensating valve 5 is pushed toward the closing side by the maximum load pressure P LS acting on the first pressure receiving portion 5a and the spring force, and operates on the second pressure receiving portion 5b. The operation valve outlet pressure P 0 is the maximum load because it is pushed to the open side by the valve outlet pressure (meter-in post-flow pressure) P 0 and the pressure receiving areas of the first pressure receiving portion 5a and the second pressure receiving portion 5b are the same. Pressure P LS
Is equal to For this reason, when the hydraulic actuator is the left and right traveling hydraulic motors, one side (left side in FIG. 1)
Of the pressure compensating valve 5 on the braking side when the vehicle travels around as the driven side with the opening of the operation valve 2 set to the large side and the other (right side in FIG. 1) opening to the small side. If the load pressure P LS acting on the pressure receiving portion 5a and the load pressure P LS1 on the drive side are equal, the flow rate supplied to the left and right traveling hydraulic motors becomes a value proportional to the opening ratio of both operating valves 2, and both The turning radius is controlled by the opening ratio of the operation valve 2. However, since the load pressure P LS acting on the first pressure receiving portion 5a of the pressure compensating valve 5 on the braking side becomes lower than the load pressure P LS1 on the driving side due to pressure loss due to leakage or the like, the traveling motor on the braking side is reduced. The amount of inflow into the valve increases, and the turning radius becomes different from the value corresponding to the opening ratio of both operation valves 2 and it becomes difficult for the vehicle to turn.
【０００６】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 problems.
【０００７】[0007]
【課題を解決するための手段】油圧ポンプ１の吐出路１
ａに複数の操作弁２を設け、各操作弁２と油圧アクチュ
エータ３を接続する回路４に圧力補助弁５をそれぞれ設
け、前記各アクチュエータ３の負荷圧をの最高圧を検出
する負荷圧検出路７を設け、この負荷圧検出路７を前記
各圧力補償弁５の受圧部５ａに接続した油圧回路におい
て、前記圧力補償弁５を第１の受圧部５ａに作用する負
荷圧で閉じ側に押され、第２の受圧部５ｂに作用する入
口側圧力で開き側に押される形状とし、その第１の受圧
部５ａの受圧面積Ａ1 を第２の受圧部５ｂの受圧面積Ａ
0 より大きくした油圧回路。Means for Solving the Problems Discharge passage 1 of hydraulic pump 1
a load pressure detection path for detecting the maximum pressure of the load pressure of each actuator 3 by providing a plurality of operation valves 2 on a and a pressure auxiliary valve 5 on a circuit 4 connecting each operation valve 2 and the hydraulic actuator 3 respectively. In the hydraulic circuit in which the load pressure detection passage 7 is connected to the pressure receiving portion 5a of each pressure compensating valve 5, the pressure compensating valve 5 is pushed to the closing side by the load pressure acting on the first pressure receiving portion 5a. The pressure receiving area A 1 of the first pressure receiving portion 5a is the pressure receiving area A 1 of the second pressure receiving portion 5b.
Hydraulic circuit greater than 0 .
【０００８】[0008]
【作 用】２つの操作弁を操作して左右の走行用モー
タに圧油を供給して旋回走行する場合に、負荷圧ＰLSの
低下を圧力補償弁５の第１・第２の受圧部５ａ，５ｂの
受圧面積差で相殺できるから、２つの操作弁の開度比に
見合う旋回半径でスムーズに旋回走行できる。[Operation] When operating the two operating valves to supply pressure oil to the left and right traveling motors for turning, the load pressure P LS is reduced by the first and second pressure receiving portions of the pressure compensating valve 5. Since the difference in the pressure receiving areas of 5a and 5b can be offset, it is possible to smoothly turn by the turning radius corresponding to the opening ratio of the two operation valves.
【０００９】[0009]
【実 施 例】基本回路は図１に示す油圧回路と同様で
あり、その圧力補償弁５は図２に示すようになってい
る。すなわち、圧力補償弁５は弁本体１０に入口ポート
１１と出口ポート１２と負荷圧導入ポート１３を形成
し、その入口ポート１１と出口ポート１２を開閉するポ
ペット１４及びそのポペット１４を閉じ側に押すスプー
ル１５を設け、そのスプール１５をばね１６で閉じ側に
押すと共に、後端面１５ａを負荷圧導入ポート１３に開
口して第１の受圧部５ａとし、ポペット１４を入口ポー
ト１１の圧力で開き側に押するようにして第２の受圧部
５ｂとしてあり、ホペット１４の入口ポート側圧力が作
用する部分の面積、つまり第２の受圧部５ｂの受圧面積
Ａ0 をスプール１５の負荷圧導入ポート圧力が作用する
部分の面積、つまり第１の受圧部５ａの受圧面積Ａ1 よ
り小さくしてある（Ａ0 ＜Ａ1 ）。これによって、前述
の負荷圧ＰLSの低下量を受圧面積差Ａ1 −Ａ0 によって
相殺して制動側の走行用モータに操作弁の開度に見合う
流量が供給されるので、両方の操作弁２の開度比に見合
う旋回半径でスムーズに旋回走行できる。[Example] The basic circuit is the same as the hydraulic circuit shown in FIG. 1, and the pressure compensation valve 5 is as shown in FIG. That is, the pressure compensating valve 5 forms an inlet port 11, an outlet port 12, and a load pressure introducing port 13 in the valve body 10, and pushes the poppet 14 that opens and closes the inlet port 11 and the outlet port 12 and the poppet 14 to the closing side. A spool 15 is provided, the spool 15 is pushed toward the closing side by a spring 16, and the rear end surface 15a is opened to the load pressure introducing port 13 to form the first pressure receiving portion 5a, and the poppet 14 is opened at the pressure of the inlet port 11. The second pressure receiving portion 5b is formed by pushing the area of the portion of the hoppet 14 on which the inlet port side pressure acts, that is, the pressure receiving area A 0 of the second pressure receiving portion 5b is the load pressure introducing port pressure of the spool 15. Is smaller than the area of the portion where A acts, that is, the pressure receiving area A 1 of the first pressure receiving portion 5a (A 0 <A 1 ). As a result, the amount of decrease in the load pressure P LS is offset by the pressure-receiving area difference A 1 -A 0 , and a flow amount commensurate with the opening of the operating valve is supplied to the traveling motor on the braking side. A turning radius can be smoothly achieved with a turning radius commensurate with the opening ratio of 2.
【００１０】[0010]
【発明の効果】２つの操作弁を操作して左右の走行用モ
ータに圧油を供給して旋回走行する場合に、負荷圧ＰLS
の低下を圧力補償弁５の第１・第２の受圧部５ａ，５ｂ
の受圧面積差で相殺できるから、２つの操作弁の開度比
に見合う旋回半径でスムーズに旋回走行できる。When the two operation valves are operated to supply the pressure oil to the left and right traveling motors to perform the turning traveling, the load pressure P LS
Decrease in the first and second pressure receiving portions 5a and 5b of the pressure compensating valve 5.
Since it can be offset by the difference in the pressure receiving area, it is possible to smoothly turn in a turning radius corresponding to the opening ratio of the two operation valves.
【図１】油圧回路図である。FIG. 1 is a hydraulic circuit diagram.
【図２】圧力補償弁の断面図である。FIG. 2 is a sectional view of a pressure compensation valve.
１…油圧ポンプ、１ａ…吐出路、２…操作弁、３…油圧
アクチュエータ、４…回路、５…圧力補償弁、５ａ…第
一の受圧部、５ｂ…第２の受圧部。DESCRIPTION OF SYMBOLS 1 ... Hydraulic pump, 1a ... Discharge path, 2 ... Operation valve, 3 ... Hydraulic actuator, 4 ... Circuit, 5 ... Pressure compensation valve, 5a ... 1st pressure receiving part, 5b ... 2nd pressure receiving part.
Claims (1)
弁２を設け、各操作弁２と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、前記各油圧
アクチュエータ３の負荷圧の最高圧を検出する負荷圧検
出路７を設け、この負荷圧検出路７を前記各圧力補償弁
５の受圧部５ａに接続した油圧回路において、 前記圧力補償弁５を第１の受圧部５ａに作用する負荷圧
で閉じ側に押され、第２の受圧部５ｂに作用する入口側
圧力で開き側に押される形状とし、その第１の受圧部５
ａの受圧面積Ａ1 を第２の受圧部５ｂの受圧面積Ａ0 よ
り大きくした油圧回路。1. A plurality of operating valves 2 are provided in a discharge passage 1a of a hydraulic pump 1, a pressure compensating valve 5 is provided in a circuit 4 connecting each operating valve 2 and a hydraulic actuator 3, and a load of each hydraulic actuator 3 is provided. In a hydraulic circuit in which a load pressure detection path 7 for detecting the maximum pressure is provided, and the load pressure detection path 7 is connected to the pressure receiving portion 5a of each pressure compensation valve 5, the pressure compensation valve 5 is connected to the first pressure receiving portion. The first pressure receiving portion 5 has a shape in which it is pushed toward the closing side by the load pressure acting on 5a and is pushed toward the opening side by the inlet side pressure acting on the second pressure receiving portion 5b.
hydraulic circuit pressure receiving area A 1 that is larger than the pressure receiving area A 0 of the second pressure receiving portion 5b of a.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35564991A JP3301544B2 (en) | 1991-12-24 | 1991-12-24 | Hydraulic circuit |
| US08/244,439 US5481872A (en) | 1991-11-25 | 1992-11-25 | Hydraulic circuit for operating plural actuators and its pressure compensating valve and maximum load pressure detector |
| PCT/JP1992/001540 WO1993011364A1 (en) | 1991-11-25 | 1992-11-25 | Hydraulic circuit for operating plural actuators and its pressure compensating valve and maximum load pressure detector |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP35564991A JP3301544B2 (en) | 1991-12-24 | 1991-12-24 | Hydraulic circuit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05172108A true JPH05172108A (en) | 1993-07-09 |
| JP3301544B2 JP3301544B2 (en) | 2002-07-15 |
Family
ID=18445059
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP35564991A Expired - Fee Related JP3301544B2 (en) | 1991-11-25 | 1991-12-24 | Hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3301544B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007092774A (en) * | 2005-09-27 | 2007-04-12 | Kayaba Ind Co Ltd | Load sensing control unit |
-
1991
- 1991-12-24 JP JP35564991A patent/JP3301544B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007092774A (en) * | 2005-09-27 | 2007-04-12 | Kayaba Ind Co Ltd | Load sensing control unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3301544B2 (en) | 2002-07-15 |
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