JPH0324302A - Hydraulic circuit - Google Patents
Hydraulic circuitInfo
- Publication number
- JPH0324302A JPH0324302A JP1154437A JP15443789A JPH0324302A JP H0324302 A JPH0324302 A JP H0324302A JP 1154437 A JP1154437 A JP 1154437A JP 15443789 A JP15443789 A JP 15443789A JP H0324302 A JPH0324302 A JP H0324302A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- load pressure
- pump
- discharge
- 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
- 230000006866 deterioration Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 7
- 239000010720 hydraulic oil Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000002542 deteriorative effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、複数のポンプの吐出圧油を複数の操作弁によ
って複数のアクチュエータに供給スる油圧回路に関する
。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic circuit that supplies pressure oil discharged from a plurality of pumps to a plurality of actuators using a plurality of operation valves.
第２図に示すように、第１ポンプ１と第２ポンプ２の吐
出路１ａ，２ａを接続し、その吐出路１ａ，ｌｂに複数
のクローズドセンタ型式の操作弁３を配設し、その操作
弁３とアクチュエータの接続回路４に圧力補償弁５を設
け、各アクチュエータの負荷圧における最高圧をシャト
ル弁６で検出し、その負荷圧を各圧力補償弁５のバネ室
５ａに供給して、その負荷圧に対応するセット圧とする
油圧回路が知られている。、かかる油圧回路であれば、
複数の操作弁３を同時操作した時に複数のアクチュエー
タの負荷圧における最高圧によって圧力補償弁５がセッ
トされ、複数のアクチュエータの負荷圧が累なっても操
作弁３の開口面積比によって複数のアクチュエータに流
量分配できる。As shown in FIG. 2, the discharge passages 1a and 2a of the first pump 1 and the second pump 2 are connected, and a plurality of closed center type operating valves 3 are arranged in the discharge passages 1a and lb, and the operation valves 3 are arranged in the discharge passages 1a and lb. A pressure compensation valve 5 is provided in the connection circuit 4 between the valve 3 and the actuator, the highest pressure among the load pressures of each actuator is detected by the shuttle valve 6, and the load pressure is supplied to the spring chamber 5a of each pressure compensation valve 5. A hydraulic circuit is known that sets a set pressure corresponding to the load pressure. , for such a hydraulic circuit,
When multiple operation valves 3 are operated simultaneously, the pressure compensation valve 5 is set by the highest pressure among the load pressures of multiple actuators, and even if the load pressures of multiple actuators accumulate, the opening area ratio of the operation valves 3 allows the pressure compensation valve 5 to be set. The flow rate can be distributed to
かかる油圧回路であると、複数のアクチュエータを同峙
作動する場合に圧力補償弁は高い方の負荷圧でセットさ
れポンプ吐出圧力はそのセット圧より若干高い高圧とな
るので、アクチュエータの負荷圧の差が大きい場合には
負荷圧の小さいアクチュエータ側の圧力補償弁における
圧力損失が大となり、第１・第２ポンプ１，２を駆動す
る原動機の損失馬力が大となると共に、作動油の温度が
高くなって作動浦の劣化を早めることになる。In such a hydraulic circuit, when multiple actuators are operated simultaneously, the pressure compensation valve is set at the higher load pressure and the pump discharge pressure is slightly higher than the set pressure, so the difference in the load pressures of the actuators is If the pressure is large, the pressure loss in the pressure compensation valve on the actuator side where the load pressure is small will be large, and the horsepower loss of the prime mover that drives the first and second pumps 1 and 2 will be large, and the temperature of the hydraulic oil will be high. This will accelerate the deterioration of the working area.
例えば、パワーショベルのブームシリンダと旋回モータ
に圧油を供給してブーム下降、上部車体旋回する場合に
、ブームは自重降下するから負荷圧は低圧であるが、旋
回モータは上部車体を起動・加速するため負荷圧が高圧
となり、その時のポンプ吐出圧はセット圧より若干高い
高圧となるので、ブームシリンダ側の圧力補償弁では高
圧一低圧の分が圧力損失となり、前述のように負荷圧の
差が大であるから圧力損失が大となってしまう。For example, when supplying pressure oil to the boom cylinder and swing motor of a power excavator to lower the boom and swing the upper car body, the load pressure is low because the boom falls under its own weight, but the swing motor starts and accelerates the upper car body. As a result, the load pressure becomes high, and the pump discharge pressure at that time becomes a high pressure that is slightly higher than the set pressure, so the pressure loss in the pressure compensation valve on the boom cylinder side is the difference between the high pressure and the low pressure, and as mentioned above, the difference in load pressure Since this is large, the pressure loss will be large.
このことは、アームシリンダでアームを上昇させパケッ
トシリンダでパケットをダンブして土砂を排出する場合
に、アームシリンダの負荷圧が高く、パケットシリンダ
の負荷圧が低くなるから同様である。This is true because when the arm cylinder raises the arm and the packet cylinder dumps packets to discharge earth and sand, the load pressure on the arm cylinder is high and the load pressure on the packet cylinder is low.
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 that can solve the above-mentioned problems.
〔課題を解決するための手段及び作用〕第１ポンプの吐
出路と第２ポンプの吐出路を合分流弁で接続し、第１ポ
ンプの吐出路に接続した操作弁の圧力補償弁の負荷圧導
入路と第２ポンプの吐出路に接続した操作弁の圧力補償
弁の負荷圧導入路を合分流弁で接続した油圧回路であり
、これによって、合分流弁によって各吐出路及び各負荷
圧導入路をそれぞれ独立させ、一方の吐出路に接続した
アクチュエータと他方の吐出路に接続したアクチュエー
タを同時操作した時に、それぞれのアクチュエータの負
荷圧で圧力補償弁をセットして、圧力損失を低域できる
ようにできる。[Means and actions for solving the problem] The discharge passage of the first pump and the discharge passage of the second pump are connected by a joint/divide valve, and the load pressure of the pressure compensating valve of the operation valve connected to the discharge passage of the first pump is This is a hydraulic circuit in which the load pressure introduction path of the pressure compensation valve of the operating valve connected to the introduction path and the discharge path of the second pump is connected by a joint/divide flow valve. By making the passages independent and operating the actuator connected to one discharge passage and the actuator connected to the other discharge passage at the same time, the pressure loss can be kept to a low level by setting the pressure compensation valve at the load pressure of each actuator. You can do it like this.
第１ポンプ１の吐出路１ａｔ．：ｍ数の操作弁３、例え
ば旋回モータ１０，アームシリンダ１１，左走行モータ
１２にポンプ吐出圧浦を供給する操作弁３を設け、第２
ポンプ２の吐出路２ａに複数の操作弁３、例えば右走行
モータ１３，ブームシリンダ１４，パケットシリンダ１
５にポンプ吐出圧油を供給する操作弁３を設け、その吐
出路１ａと吐出路２ａを合分流弁１６で合流、分流でき
るようにすると共に、一方の負荷圧導入路１７と他方の
負荷圧導入路１８を合分流弁１っで合流、分流できるよ
うにする。Discharge path 1at. of the first pump 1. : m number of operating valves 3, for example, an operating valve 3 that supplies pump discharge pressure to the swing motor 10, arm cylinder 11, and left travel motor 12, and a second
A plurality of operating valves 3, such as a right travel motor 13, a boom cylinder 14, and a packet cylinder 1, are provided in the discharge path 2a of the pump 2.
5 is provided with an operation valve 3 for supplying pump discharge pressure oil, and the discharge passage 1a and the discharge passage 2a can be merged and separated by a merging/dividing valve 16, and one load pressure introduction passage 17 and the other load pressure The introduction path 18 is made to be able to merge and separate the flows by using the merging and dividing valve 1.
前記合分流弁１６、合分流弁１９はバネ１６ａ，１９ａ
で連通位置■となり、受圧部１６ｂ，１９ｂに供給され
るパイロット圧油で遮断位置Ｈに切換えられる。The joining and dividing valve 16 and the joining and dividing valve 19 are provided with springs 16a and 19a.
The communication position (3) is reached, and it is switched to the cutoff position (H) by pilot pressure oil supplied to the pressure receiving portions 16b, 19b.
しかして、合分流弁１６．１９を連通位置Ｉとすれば第
１ポンプ１の吐出路１ａと第２ポンプ２の吐出路２ａが
連通し、一方の負荷圧導入路１７と他方の負荷圧導入路
１８が連通ずるから、従来と同様にして各アクチュエー
タにポンプ吐出圧油を供給できる。Therefore, if the merging/dividing valve 16.19 is set to the communication position I, the discharge passage 1a of the first pump 1 and the discharge passage 2a of the second pump 2 are communicated, and the load pressure introduction passage 17 on one side and the load pressure introduction passage 17 on the other side are connected. Since the passages 18 are in communication, pump discharge pressure oil can be supplied to each actuator in the same manner as in the prior art.
また、パイロット圧油を受圧部１６ａ，１９ｂに供給し
て合分流弁１６．１９を遮断位置■とすれば第１ポンプ
１の吐出路１ａと第２ポンプ２の吐出路２ａが遮断し、
一方の負荷圧導入路ｌ７と他方の負荷圧導入路１８が遮
断するから、第１ポンプ１の吐出路１ａに設けた複数の
操作弁３と第２ポンプ２の吐出路２ａに設けた複数の操
作弁３が独立する。Further, if pilot pressure oil is supplied to the pressure receiving parts 16a and 19b and the joint/divider valve 16.19 is set to the cutoff position (2), the discharge passage 1a of the first pump 1 and the discharge passage 2a of the second pump 2 are shut off,
Since the load pressure introduction path l7 on one side and the load pressure introduction path 18 on the other side are blocked, the plurality of operation valves 3 provided in the discharge path 1a of the first pump 1 and the plurality of operation valves provided in the discharge path 2a of the second pump 2 The operation valve 3 is independent.
したがって、旋回モータ１０，アームシリンダ１１，左
走行モータ１２のいずれかと右走行モータ１３．ブーム
シリンダ１４．パケットシリンダ１５のいずれかを同時
に作動する場合に、その負荷圧の差が大きい時には合分
流弁１６．１９を遮断位置■とすることで圧力補償弁５
がそれぞれの負荷圧によってセットでき、余分に高い圧
力にセットされることがなくなって圧力損失を低減でき
る。Therefore, one of the swing motor 10, the arm cylinder 11, the left travel motor 12, and the right travel motor 13. Boom cylinder 14. When operating any of the packet cylinders 15 at the same time, if the difference in the load pressures is large, the pressure compensating valve 5
can be set according to each load pressure, and the pressure is not set to an excessively high pressure, reducing pressure loss.
例えば、旋回モータ１０とブームシリンダｌ４に圧浦を
供給して旋回とブーム下げを同時に行なう場合に、旋回
モータ１０の操作弁３に設けた圧力補償弁５は旋回モー
タ１０の負ａｆ圧によって高圧にセットされ、ブームシ
リンダ１４の操作弁３に設けた圧力補償弁５はブームシ
リンダ１４の負荷圧によって低圧にセットされて、従来
のように旋回モータ１０の負荷圧によって高圧にセット
されることがなくなり、圧力損失が低減する。For example, when supplying pressure to the swing motor 10 and the boom cylinder l4 to perform swing and boom lowering at the same time, the pressure compensating valve 5 provided in the operating valve 3 of the swing motor 10 is under high pressure due to the negative af pressure of the swing motor 10. The pressure compensation valve 5 provided in the operation valve 3 of the boom cylinder 14 is set to a low pressure by the load pressure of the boom cylinder 14, and cannot be set to a high pressure by the load pressure of the swing motor 10 as in the conventional case. This reduces pressure loss.
合分流弁１７．１９を連通位置とすれば第１・第２ポン
プ１，２の吐出圧油を合流して複数のアクチュエータに
圧力補償して供給できる。If the merging/dividing valves 17 and 19 are placed in the communicating position, the pressure oil discharged from the first and second pumps 1 and 2 can be combined and supplied to a plurality of actuators with pressure compensation.
合分流弁１７．１９を遮断位置とすれば第１ポンプ１の
吐出路１ａと第２ポンプ２の吐出路２ａが独立し、一方
の負荷圧導入路１７と他方の負荷圧導入路１８が独立す
るので、第１ポンプ１の吐出路１ａに接続したアクチュ
エータを同時操作した時に圧力補償弁５はそのアクチュ
エータの負荷圧によってそれぞれセットされ、負荷圧に
大きな差があっても圧力損失が大きくなることがなく、
ポンプ駆動の原動機の損失馬力を低減できると共に、作
動油の温度が高く上昇することがなく作動油が早く劣化
することを防止できる。When the merging/dividing valve 17.19 is set to the cutoff position, the discharge passage 1a of the first pump 1 and the discharge passage 2a of the second pump 2 become independent, and one load pressure introduction passage 17 and the other load pressure introduction passage 18 become independent. Therefore, when the actuators connected to the discharge path 1a of the first pump 1 are operated simultaneously, the pressure compensation valves 5 are set depending on the load pressure of the actuators, and even if there is a large difference in the load pressures, the pressure loss will increase. There is no
The horsepower loss of the pump-driven prime mover can be reduced, and the temperature of the hydraulic oil does not rise too high, which prevents the hydraulic oil from deteriorating quickly.
第１図は本発明の実施例を示す回路図、第２図は従来の
回路図である。
１は第１ポンプ、１ａは吐出路、２は第２ポンプ、２ａ
は吐出路、３は操作弁、５は圧力補償弁、５ａはバネ室
、１６は合分流弁、１７は一方の負荷圧導入路、１８は
他方の負荷圧導入路、１つは合分流弁。FIG. 1 is a circuit diagram showing an embodiment of the present invention, and FIG. 2 is a conventional circuit diagram. 1 is the first pump, 1a is the discharge path, 2 is the second pump, 2a
1 is a discharge path, 3 is an operating valve, 5 is a pressure compensation valve, 5a is a spring chamber, 16 is a joint/divide flow valve, 17 is one load pressure introduction path, 18 is the other load pressure introduction path, 1 is a joint/divide flow valve .
Claims (1)
操作弁３とアクチュエータの接続回路に圧力補償弁５を
設け、各圧力補償弁５のバネ室５ａにシャトル弁６と一
方の負荷圧導入路１７によって最も高圧の負荷圧を導入
してセットするようにし、 第２ポンプ２の吐出路２ａと複数の操作弁３を設け、各
操作弁３とアクチュエータの接続回路に圧力補償弁５を
設け、各圧力補償弁５のバネ室５ａにシャトル弁６と他
方の負荷圧導入路１８によって最も高圧の負荷圧を導入
してセットするようにし、 前記第１ポンプ１の吐出路１ａと第２ポンプ２の吐出路
２ａを連通・遮断する合分流弁１６及び、前記一方の負
荷圧導入路１７と他方の負荷圧導入路１８を連通・遮断
する合分流弁１９を設けたことを特徴とする油圧回路。[Claims] A plurality of operation valves 3 are provided in the discharge path 1a of the first pump 1, a pressure compensation valve 5 is provided in the connection circuit between each operation valve 3 and the actuator, and a spring chamber 5a of each pressure compensation valve 5 is provided with a pressure compensation valve 5. The highest load pressure is introduced and set by the shuttle valve 6 and one load pressure introduction path 17, and the discharge path 2a of the second pump 2 and a plurality of operation valves 3 are provided, and each operation valve 3 and the actuator are connected to each other. A pressure compensation valve 5 is provided in the connection circuit, and the highest load pressure is introduced and set into the spring chamber 5a of each pressure compensation valve 5 by the shuttle valve 6 and the other load pressure introduction path 18, and the first pump A joint/divide flow valve 16 that communicates/blocks the discharge path 1a of the first pump 2 with the discharge path 2a of the second pump 2, and a joint/divide flow valve 19 that connects/blocks the one load pressure introduction path 17 with the other load pressure introduction path 18. A hydraulic circuit characterized by being provided with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1154437A JPH0792090B2 (en) | 1989-06-19 | 1989-06-19 | Hydraulic circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1154437A JPH0792090B2 (en) | 1989-06-19 | 1989-06-19 | Hydraulic circuit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0324302A true JPH0324302A (en) | 1991-02-01 |
| JPH0792090B2 JPH0792090B2 (en) | 1995-10-09 |
Family
ID=15584175
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1154437A Expired - Lifetime JPH0792090B2 (en) | 1989-06-19 | 1989-06-19 | Hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0792090B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0586002U (en) * | 1992-04-24 | 1993-11-19 | 株式会社小松製作所 | Maximum load pressure detection circuit of hydraulic circuit with pressure compensation valve |
| US6170261B1 (en) | 1997-11-11 | 2001-01-09 | Komatsu, Ltd. | Hydraulic fluid supply system |
| JP2009198006A (en) * | 2008-02-25 | 2009-09-03 | Linde Material Handling Gmbh | Hydrostatic drive system |
| JP2014522465A (en) * | 2011-06-09 | 2014-09-04 | ボルボ コンストラクション イクイップメント アーベー | Hydraulic system for construction machinery |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5330157A (en) * | 1976-08-31 | 1978-03-22 | Kubota Ltd | Waste-water collecting apparatus |
| JPS57116965A (en) * | 1980-11-24 | 1982-07-21 | Linde Ag | Hydraulic pressure driving system with variable discharging pump |
-
1989
- 1989-06-19 JP JP1154437A patent/JPH0792090B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5330157A (en) * | 1976-08-31 | 1978-03-22 | Kubota Ltd | Waste-water collecting apparatus |
| JPS57116965A (en) * | 1980-11-24 | 1982-07-21 | Linde Ag | Hydraulic pressure driving system with variable discharging pump |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0586002U (en) * | 1992-04-24 | 1993-11-19 | 株式会社小松製作所 | Maximum load pressure detection circuit of hydraulic circuit with pressure compensation valve |
| US6170261B1 (en) | 1997-11-11 | 2001-01-09 | Komatsu, Ltd. | Hydraulic fluid supply system |
| JP2009198006A (en) * | 2008-02-25 | 2009-09-03 | Linde Material Handling Gmbh | Hydrostatic drive system |
| JP2014522465A (en) * | 2011-06-09 | 2014-09-04 | ボルボ コンストラクション イクイップメント アーベー | Hydraulic system for construction machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0792090B2 (en) | 1995-10-09 |
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