JP2005331011A - Hydraulic control system - Google Patents

Hydraulic control system Download PDF

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Publication number
JP2005331011A
JP2005331011A JP2004148967A JP2004148967A JP2005331011A JP 2005331011 A JP2005331011 A JP 2005331011A JP 2004148967 A JP2004148967 A JP 2004148967A JP 2004148967 A JP2004148967 A JP 2004148967A JP 2005331011 A JP2005331011 A JP 2005331011A
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Prior art keywords
flow path
pump
group
circuit system
switching valve
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JP2004148967A
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JP4139352B2 (en
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Atsushi Fujii
篤 藤井
Takeshi Sugano
剛 菅野
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KYB Corp
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Kayaba Industry Co Ltd
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Priority to JP2004148967A priority Critical patent/JP4139352B2/en
Priority to DE200560003980 priority patent/DE602005003980T2/en
Priority to EP20050010782 priority patent/EP1598561B1/en
Priority to CNB2005100727619A priority patent/CN100516555C/en
Publication of JP2005331011A publication Critical patent/JP2005331011A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/167—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load using pilot pressure to sense the demand
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2282—Systems using center bypass type changeover valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To avoid loss in driving a pump, and decrease an engine load. <P>SOLUTION: The hydraulic control system includes a plurality of pumps, and circuit systems to each of which an open-center-type transfer valve is connected. Out of the circuit systems, the downstream paths of a 1st group and a 2nd group B, C respectively are allowed to gather in a confluence path 41, in which an auxiliary transfer valve 16 is provided to supply pressure oil from the plurality of pumps to an actuator of the auxiliary transfer valve 16. In the hydraulic control system, an open control valve 42 is provided upstream of the confluence path 41 and in the downstream path of the 2nd-group circuit system C. In accordance with the pump discharge pressure of the 1st-group circuit system B and the pump discharge pressure of the 2nd-group circuit system C, the open control valve 42 opens the downstream path to a discharge flow path 10 communicating with a tank. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、油圧ショベル等の建設車両に用いる油圧制御装置に係わり、ポンプを接続した回路系統を複数備えた油圧制御装置に関する。   The present invention relates to a hydraulic control device used for a construction vehicle such as a hydraulic excavator, and relates to a hydraulic control device including a plurality of circuit systems to which a pump is connected.

図２に示す従来の装置は、第１〜３ポンプＰ１〜Ｐ３を備えるとともに、これら第１〜３ポンプＰ１〜Ｐ３のぞれぞれには、第１〜３回路系統ａ〜ｃを接続している。   The conventional apparatus shown in FIG. 2 includes first to third pumps P1 to P3, and first to third circuit systems a to c are connected to each of the first to third pumps P1 to P3. ing.

第１回路系統ａは、第１ポンプＰ１に接続した第１供給流路１に、オープンセンタータイプの第１〜３切換弁１１〜１３を接続している。これら第１〜３切換弁１１〜１３は、図示する中立位置にあるときに、第１中立流路２を介して第１ポンプＰ１とタンク流路１０とを連通させる。そして、第１切換弁１１を切り換えると、その切換弁に接続したアクチュエータに直接に圧油を供給する。また、第２、３切換弁１２、１３のいずれかを切り換えると、その切換弁に接続したアクチュエータに第１パラレル流路３を介して圧油を供給するようにしている。なお、第１ポンプＰ１の最大吐出量は、第１〜３切換弁１１〜１３に接続する３台のアクチュエータの最大必要流量に基づいて設定している。   In the first circuit system a, open center type first to third switching valves 11 to 13 are connected to a first supply flow path 1 connected to a first pump P1. The first to third switching valves 11 to 13 communicate the first pump P1 and the tank flow path 10 via the first neutral flow path 2 when they are in the neutral position shown in the figure. When the first switching valve 11 is switched, the pressure oil is directly supplied to the actuator connected to the switching valve. Further, when any one of the second and third switching valves 12 and 13 is switched, pressure oil is supplied to the actuator connected to the switching valve via the first parallel flow path 3. The maximum discharge amount of the first pump P1 is set based on the maximum required flow rates of the three actuators connected to the first to third switching valves 11-13.

第２回路系統ｂは、第２ポンプＰ２に接続した第２供給流路４に、オープンセンタータイプの第４〜６切換弁１４〜１６を接続している。これら第４〜６切換弁１４〜１６は、図示する中立位置にあるときに、第２中立流路５を介して第２ポンプＰ２とタンク流路１０とを連通させる。そして、第４切換弁１４を切り換えると、その切換弁に接続したアクチュエータに直接に圧油を供給する。また、第５、６切換弁１５、１６のいずれかを切り換えると、その切換弁に接続したアクチュエータに第２パラレル流路６を介して圧油を供給するようにしている。   In the second circuit system b, open center type fourth to sixth switching valves 14 to 16 are connected to the second supply flow path 4 connected to the second pump P2. The fourth to sixth switching valves 14 to 16 communicate the second pump P2 and the tank channel 10 via the second neutral channel 5 when in the neutral position shown in the figure. When the fourth switching valve 14 is switched, pressure oil is directly supplied to the actuator connected to the switching valve. Further, when any one of the fifth and sixth switching valves 15 and 16 is switched, pressure oil is supplied to the actuator connected to the switching valve via the second parallel flow path 6.

この第６切換弁１６は、予備用の切換弁であり、この予備用切換弁１６は、特殊なアクチュエータを用いる建設車両に対して予め用意したものである。すなわち、第２回路系統ｂによって制御するアクチュエータが２台だけの場合には、予備用切換弁１６は使用しないが、特殊なアクチュエータがあって、第２制御系統ｂに接続するアクチュエータが合計３台となる場合には、特殊なアクチュエータを予備用切換弁１６に接続する。そして、この予備用切換弁１６によって特殊なアクチュエータを制御するようにしている。なお、特殊なアクチュエータは常設するものではないので、第２ポンプＰ２の最大吐出量は、第４、５切換弁１４，１５に接続する２台のアクチュエータの最大必要流量に基づいて設定している。   The sixth switching valve 16 is a spare switching valve, and this spare switching valve 16 is prepared in advance for a construction vehicle using a special actuator. That is, when only two actuators are controlled by the second circuit system b, the standby switching valve 16 is not used, but there are special actuators and a total of three actuators connected to the second control system b. In such a case, a special actuator is connected to the spare switching valve 16. A special actuator is controlled by the auxiliary switching valve 16. Since a special actuator is not permanently installed, the maximum discharge amount of the second pump P2 is set based on the maximum required flow rate of the two actuators connected to the fourth and fifth switching valves 14 and 15. .

第３回路系統ｃは、第３ポンプＰ３に接続した第３供給流路７に、オープンセンタータイプの第７〜９切換弁１７〜１９を接続している。これら第７〜９切換弁１７〜１９は、図示する中立位置にあるときに、第３中立流路８を介して第３ポンプＰ３とその下流側とを連通し、第７切換弁１７を切り換えると、その切換弁に接続したアクチュエータに直接に圧油を供給する。また、第８、９切換弁１８、１９のいずれかを切り換えると、その切換弁に接続したアクチュエータに第３パラレル流路９を介して圧油を供給するようにしている。なお、第３ポンプＰ３の最大吐出量は、第７〜９切換弁１７〜１９に接続する３台のアクチュエータの最大必要流量に基づいて設定している。   In the third circuit system c, open center type seventh to ninth switching valves 17 to 19 are connected to the third supply flow path 7 connected to the third pump P3. These seventh to ninth switching valves 17 to 19 communicate with the third pump P3 and its downstream side via the third neutral flow path 8 to switch the seventh switching valve 17 when in the illustrated neutral position. Then, pressure oil is supplied directly to the actuator connected to the switching valve. When any one of the eighth and ninth switching valves 18 and 19 is switched, pressure oil is supplied to the actuator connected to the switching valve via the third parallel flow path 9. The maximum discharge amount of the third pump P3 is set based on the maximum required flow rates of the three actuators connected to the seventh to ninth switching valves 17-19.

また、第３中立流路８の下流側を、第２回路系統ｂの第２中立流路５に接続するとともに、この第３中立流路８を接続する流路に油圧パイロット式の合流切換弁２０を設けている。この合流切換弁２０は、操作者によって切り換えられ、閉位置にあるときは、第３中立流路８がタンク流路１０に連通して第２中立流路５と遮断され、第３ポンプＰ３の吐出油が第２回路系統ｂに供給されない。また、合流切換弁２０が図示の開位置に切り換えられると、第３中立流路８と第２中立流路５とが連通され、第３ポンプＰ３の吐出油が第２回路系統ｂに供給される。   Further, the downstream side of the third neutral flow path 8 is connected to the second neutral flow path 5 of the second circuit system b, and a hydraulic pilot type confluence switching valve is connected to the flow path connecting the third neutral flow path 8. 20 is provided. When this confluence switching valve 20 is switched by the operator and is in the closed position, the third neutral flow path 8 communicates with the tank flow path 10 and is disconnected from the second neutral flow path 5, and the third pump P3 The discharged oil is not supplied to the second circuit system b. When the merging switching valve 20 is switched to the open position shown in the figure, the third neutral flow path 8 and the second neutral flow path 5 are communicated, and the discharge oil of the third pump P3 is supplied to the second circuit system b. The

このように合流切換弁２０を設けたのは、予備用切換弁１６に接続した特殊なアクチュエータに供給する流量が、不足しないようにするためである。すなわち、予備用切換弁１６には、第２ポンプＰ２の吐出油を供給しているが、この第２ポンプＰ２の最大吐出量は、第４，５切換弁１４，１５に接続するアクチュエータの最大必要流量に基づいて設定されており、予備用切換弁１６に接続するアクチュエータを作動させた場合に、供給流量不足が生じることがある。そこで、このような場合に、合流切換弁２０によって第３ポンプＰ３の吐出油を合流させることによって、その供給流量不足を補うようにしている（例えば、特許文献１）。
特開２００２−２７６６０７号公報 The reason why the merging switching valve 20 is provided in this manner is to prevent the flow rate supplied to the special actuator connected to the standby switching valve 16 from being insufficient. In other words, the auxiliary switching valve 16 is supplied with the discharge oil of the second pump P2, and the maximum discharge amount of the second pump P2 is the maximum of the actuator connected to the fourth and fifth switching valves 14 and 15. It is set based on the required flow rate, and when the actuator connected to the auxiliary switching valve 16 is operated, the supply flow rate may be insufficient. Therefore, in such a case, the shortage of the supply flow rate is compensated by joining the discharge oil of the third pump P3 by the merge switching valve 20 (for example, Patent Document 1).
JP 2002-276607 A

しかし、第３ポンプＰ３の吐出油を第２回路系統ｂに供給して予備用切換弁１６に接続した特殊なアクチュエータの作動を行っている場合、その特殊なアクチュエータあるいは第２回路系統ｂのその他のアクチュエータの負荷圧が高く、第２回路系統ｂの圧力が高いときには、第３ポンプＰ３の吐出油が第２回路系統ｂに行かなくなって、第３ポンプＰ３のリリーフ弁２３が開き、その分ロスとなる。建設車両では、作業の仕方等によってアクチュエータの動きが遅くなって回路の圧力が高く上昇してしまうことが多く、したがってこの第３ポンプＰ３の駆動のロス分、エンジンの燃費を悪化させるという問題がある。   However, when the discharge oil of the third pump P3 is supplied to the second circuit system b and the special actuator connected to the standby switching valve 16 is operated, the special actuator or the other of the second circuit system b is operated. When the load pressure of the actuator is high and the pressure of the second circuit system b is high, the discharge oil of the third pump P3 does not go to the second circuit system b, the relief valve 23 of the third pump P3 opens, It becomes a loss. In construction vehicles, the actuator movement is slow due to the way of work, etc., and the circuit pressure often rises high. Therefore, there is a problem that the fuel consumption of the engine is deteriorated by the loss of driving of the third pump P3. is there.

この発明は、このような問題点を解決することを目的としている。   An object of the present invention is to solve such problems.

本発明は、複数のポンプと、それぞれポンプにオープンセンタータイプの切換弁が接続された回路系統とを備え、これら回路系統のうち第１グループ、第２グループの回路系統の下流路を合流させる合流流路に予備用切換弁を設け、複数のポンプからの圧油を予備用切換弁のアクチュエータに供給可能な油圧制御装置において、前記合流流路の上流にて第２グループの回路系統の下流路に、該下流路を、第１グループの回路系統のポンプの吐出圧と第２グループの回路系統のポンプの吐出圧に応じてタンクに通じる排出流路に開放する開放制御弁を設けたことを特徴とするものとした。   The present invention includes a plurality of pumps and a circuit system in which an open center type switching valve is connected to each pump, and joins the lower flow paths of the first group and the second group of these circuit systems. In a hydraulic control apparatus that is provided with a backup switching valve in a flow path and can supply pressure oil from a plurality of pumps to an actuator of the backup switching valve, a lower flow path of a second group of circuit systems upstream of the merging flow path In addition, an opening control valve that opens the lower flow path to a discharge flow path that leads to the tank according to the discharge pressure of the pump of the first group circuit system and the discharge pressure of the pump of the second group circuit system is provided. It was supposed to be a feature.

本発明によると、第２グループの回路系統のポンプの駆動ロスを回避して、予備用切換弁のアクチュエータの所要の作動を確保できると共に、駆動用エンジンの負担を軽減でき、燃費を向上できる。   According to the present invention, it is possible to avoid the driving loss of the pumps of the second group of circuit systems, to ensure the required operation of the actuator of the standby switching valve, to reduce the burden on the driving engine, and to improve the fuel efficiency.

以下、本発明の実施の形態を添付図面に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

図１は油圧ショベルの油圧制御装置の回路図を示す。   FIG. 1 shows a circuit diagram of a hydraulic control device of a hydraulic excavator.

本装置は、第１〜３ポンプＰ１〜Ｐ３を備えるとともに、これら第１〜３ポンプＰ１〜Ｐ３のぞれぞれには、第１〜３回路系統Ａ〜Ｃを接続している。   This apparatus includes first to third pumps P1 to P3, and first to third circuit systems A to C are connected to the first to third pumps P1 to P3, respectively.

第１回路系統Ａは、第１ポンプＰ１に接続した第１供給流路１に、オープンセンタータイプの第１〜３切換弁１１〜１３を接続している。これら第１〜３切換弁１１〜１３は、図示する中立位置にあるときに、第１中立流路２を介して第１ポンプＰ１とタンク流路１０とを連通させる。そして、第１切換弁１１を切り換えると、その切換弁に接続したアクチュエータ（走行用左モータ３１）に直接に圧油を供給する。また、第２、３切換弁１２、１３のいずれかを切り換えると、その切換弁に接続したアクチュエータすなわち第２切換弁１２の場合はブーム用シリンダ３２、第３切換弁１３の場合はバケット用シリンダ３３に第１パラレル流路３を介して圧油を供給するようにしている。なお、第１ポンプＰ１の最大吐出量は、第１〜３切換弁１１〜１３に接続する３台のアクチュエータの最大必要流量に基づいて設定している。図中、２１はリリーフ弁、Ｐａ１、Ｐｂ１〜Ｐａ３、Ｐｂ３はパイロット回路、ＤＲはドレン回路である。   In the first circuit system A, open center type first to third switching valves 11 to 13 are connected to a first supply flow path 1 connected to a first pump P1. The first to third switching valves 11 to 13 communicate the first pump P1 and the tank flow path 10 via the first neutral flow path 2 when they are in the neutral position shown in the figure. When the first switching valve 11 is switched, the pressure oil is directly supplied to the actuator (traveling left motor 31) connected to the switching valve. When one of the second and third switching valves 12 and 13 is switched, the actuator connected to the switching valve, that is, the boom cylinder 32 in the case of the second switching valve 12, and the bucket cylinder in the case of the third switching valve 13. Pressure oil is supplied to 33 via the first parallel flow path 3. The maximum discharge amount of the first pump P1 is set based on the maximum required flow rates of the three actuators connected to the first to third switching valves 11-13. In the figure, 21 is a relief valve, Pa1, Pb1 to Pa3, Pb3 are pilot circuits, and DR is a drain circuit.

第２回路系統Ｂ（第１グループの回路系統）は、第２ポンプＰ２（第１グループの回路系統のポンプ）に接続した第２供給流路４に、オープンセンタータイプの第４〜６切換弁１４〜１６を接続している。これら第４〜６切換弁１４〜１６は、図示する中立位置にあるときに、第２中立流路５を介して第２ポンプＰ２とタンク流路１０とを連通させる。そして、第４切換弁１４を切り換えると、その切換弁に接続したアクチュエータ（走行用右モータ３４）に直接に圧油を供給する。また、第５、６切換弁１５、１６のいずれかを切り換えると、その切換弁に接続したアクチュエータすなわち第５切換弁１５の場合はアーム用シリンダ３５、第６切換弁（予備用切換弁）１６の場合は予備用切換弁１６に接続した特殊なアクチュエータに第２パラレル流路６を介して圧油を供給するようにしている。   The second circuit system B (first group circuit system) is connected to the second supply flow path 4 connected to the second pump P2 (first group circuit system pump), and is an open center type fourth to sixth switching valve. 14 to 16 are connected. The fourth to sixth switching valves 14 to 16 communicate the second pump P2 and the tank channel 10 via the second neutral channel 5 when in the neutral position shown in the figure. When the fourth switching valve 14 is switched, pressure oil is directly supplied to the actuator (traveling right motor 34) connected to the switching valve. Further, when any one of the fifth and sixth switching valves 15 and 16 is switched, in the case of the actuator connected to the switching valve, that is, the fifth switching valve 15, the arm cylinder 35 and the sixth switching valve (preliminary switching valve) 16. In this case, pressure oil is supplied to the special actuator connected to the auxiliary switching valve 16 via the second parallel flow path 6.

特殊なアクチュエータとしては、例えば、ブレーカ、爪等がある。なお、第２ポンプＰ２の最大吐出量は、第４、５切換弁１４，１５に接続する２台のアクチュエータの最大必要流量に基づいて設定している。図中、２２はリリーフ弁、Ｐａ４、Ｐｂ４〜Ｐａ６、Ｐｂ６はパイロット回路である。   Examples of the special actuator include a breaker and a claw. The maximum discharge amount of the second pump P2 is set based on the maximum required flow rates of the two actuators connected to the fourth and fifth switching valves 14 and 15. In the figure, 22 is a relief valve, Pa4, Pb4 to Pa6, and Pb6 are pilot circuits.

第３回路系統Ｃ（第２グループの回路系統）は、第３ポンプＰ３（第２グループの回路系統のポンプ）に接続した第３供給流路７に、オープンセンタータイプの第７〜９切換弁１７〜１９を接続している。これら第７〜９切換弁１７〜１９は、図示する中立位置にあるときに、第３中立流路８を介して第３ポンプＰ３とその下流路４０とを連通し、第７切換弁１７を切り換えると、その切換弁に接続したアクチュエータ（旋回用モータ３７）に直接に圧油を供給する。また、第８、９切換弁１８、１９のいずれかを切り換えると、その切換弁に接続したアクチュエータすなわち第８切換弁１８の場合はブレード用シリンダ３８、第９切換弁１９の場合はスイング用シリンダ３９に第３パラレル流路９を介して圧油を供給するようにしている。なお、第３ポンプＰ３の最大吐出量は、第７〜９切換弁１７〜１９に接続する３台のアクチュエータの最大必要流量に基づいて設定している。図中、２３はリリーフ弁、Ｐａ７、Ｐｂ７〜Ｐａ９、Ｐｂ９はパイロット回路である。   The third circuit system C (second group circuit system) is connected to the third supply flow path 7 connected to the third pump P3 (second group circuit system pump), and the open center type seventh to ninth switching valves. 17 to 19 are connected. The seventh to ninth switching valves 17 to 19 communicate with the third pump P3 and the lower flow path 40 via the third neutral flow path 8 when in the illustrated neutral position. When switched, the pressure oil is directly supplied to the actuator (rotation motor 37) connected to the switching valve. Further, when any one of the eighth and ninth switching valves 18 and 19 is switched, an actuator connected to the switching valve, that is, the blade cylinder 38 in the case of the eighth switching valve 18, and a swing cylinder in the case of the ninth switching valve 19. The pressure oil is supplied to 39 through the third parallel flow path 9. The maximum discharge amount of the third pump P3 is set based on the maximum required flow rates of the three actuators connected to the seventh to ninth switching valves 17-19. In the figure, 23 is a relief valve, Pa7, Pb7 to Pa9, and Pb9 are pilot circuits.

この第３回路系統Ｃの第３中立流路８の下流路４０を、予備用切換弁１６の上流の第２回路系統Ｂの第２中立流路５、第２パラレル流路６に接続する。すなわち、第２回路系統Ｂの下流路と第３回路系統Ｃの下流路４０とを合流させる合流流路４１に予備用切換弁１６を設けている。   The lower flow path 40 of the third neutral flow path 8 of the third circuit system C is connected to the second neutral flow path 5 and the second parallel flow path 6 of the second circuit system B upstream of the standby switching valve 16. That is, the standby switching valve 16 is provided in the merged flow channel 41 that merges the lower flow channel of the second circuit system B and the lower flow channel 40 of the third circuit system C.

そして、この合流流路４１の上流にて第３回路系統Ｃの下流路４０に、第２回路系統Ｂの第２ポンプＰ２の吐出圧と第３回路系統Ｃの第３ポンプＰ３の吐出圧に応じて動作する開放制御弁４２を設ける。   Then, upstream of the merging flow path 41, the discharge pressure of the second pump P2 of the second circuit system B and the discharge pressure of the third pump P3 of the third circuit system C are set in the lower flow path 40 of the third circuit system C. An open control valve 42 that operates in response is provided.

開放制御弁４２は、第２回路系統Ｂの第２ポンプＰ２の吐出圧が第３回路系統Ｃの第３ポンプＰ３の吐出圧よりも設定圧以上高いときは第３回路系統Ｃの下流路４０をタンク流路１０に開放し、その設定圧以内のときは第３回路系統Ｃの下流路４０を合流流路４１に開通するようになっている。   When the discharge pressure of the second pump P2 of the second circuit system B is higher than the set pressure by the open control valve 42 than the discharge pressure of the third pump P3 of the third circuit system C, the open control valve 42 is a downstream channel 40 of the third circuit system C. Is opened to the tank flow path 10, and the lower flow path 40 of the third circuit system C is opened to the merge flow path 41 when the pressure is within the set pressure.

このように構成したので、第２回路系統Ｂの第２ポンプＰ２の吐出圧と第３回路系統Ｃの第３ポンプＰ３の吐出圧とがほぼ同等のとき、予備用切換弁１６をいずれかの方向に切り換えると、第２回路系統Ｂの第２中立流路５と第２パラレル流路６を介して第２ポンプＰ２の圧油および開放制御弁４２を介して第３回路系統Ｃの第３ポンプＰ３の圧油が、予備用切換弁１６に接続したアクチュエータに供給され、そのアクチュエータが作動する。   With this configuration, when the discharge pressure of the second pump P2 of the second circuit system B is substantially equal to the discharge pressure of the third pump P3 of the third circuit system C, the auxiliary switching valve 16 is When switching in the direction, the third circuit system C of the third circuit system C via the pressure oil of the second pump P2 and the release control valve 42 through the second neutral channel 5 and the second parallel channel 6 of the second circuit system B. The pressure oil of the pump P3 is supplied to the actuator connected to the auxiliary switching valve 16, and the actuator is activated.

そして、予備用切換弁１６に接続したアクチュエータの作動中、そのアクチュエータあるいは第２回路系統Ｂのその他のアクチュエータの負荷圧が高くなり、第２回路系統Ｂの第２ポンプＰ２の吐出圧力が上昇してくると、第３回路系統Ｃの第３ポンプＰ３の吐出圧力も上昇してくるが、その第２回路系統Ｂの第２ポンプＰ２の吐出圧力が第３回路系統Ｃの第３ポンプＰ３の吐出圧力よりも設定圧以上高くなると、開放制御弁４２が第３ポンプＰ３の吐出油をタンク流路１０に開放する。   During the operation of the actuator connected to the standby switching valve 16, the load pressure of the actuator or other actuators of the second circuit system B increases, and the discharge pressure of the second pump P2 of the second circuit system B increases. As a result, the discharge pressure of the third pump P3 of the third circuit system C also increases, but the discharge pressure of the second pump P2 of the second circuit system B becomes higher than that of the third pump P3 of the third circuit system C. When the discharge pressure becomes higher than the set pressure, the release control valve 42 opens the discharge oil of the third pump P3 to the tank flow path 10.

このため、第３ポンプＰ３の吐出油がリリーフ弁２３よりリリーフすることによる第３ポンプＰ３の駆動ロスを回避でき、したがってエンジンの負担を軽減でき、燃費を向上できる。   For this reason, the drive loss of the 3rd pump P3 by the discharge oil of the 3rd pump P3 relieving from the relief valve 23 can be avoided, Therefore, the burden of an engine can be reduced and a fuel consumption can be improved.

そして、予備用切換弁１６に接続したアクチュエータあるいは第２回路系統Ｂのその他のアクチュエータの負荷圧が低く、第２回路系統Ｂの第２ポンプＰ２の吐出圧力が設定圧以内の低いときには、第２ポンプＰ２の圧油に加え、開放制御弁４２を介して第３回路系統Ｃの第３ポンプＰ３の圧油が、予備用切換弁１６に接続したアクチュエータに供給される。   When the load pressure of the actuator connected to the auxiliary switching valve 16 or the other actuator of the second circuit system B is low and the discharge pressure of the second pump P2 of the second circuit system B is low within the set pressure, the second In addition to the pressure oil of the pump P2, the pressure oil of the third pump P3 of the third circuit system C is supplied to the actuator connected to the standby switching valve 16 via the release control valve 42.

したがって、第３ポンプＰ３の圧油を予備用切換弁１６に接続したアクチュエータに適切に供給でき、そのアクチュエータの所要の作動を確保できる。   Therefore, the pressure oil of the third pump P3 can be appropriately supplied to the actuator connected to the auxiliary switching valve 16, and the required operation of the actuator can be ensured.

本発明は、建設機械の各種油圧制御装置に利用できる。   The present invention can be used in various hydraulic control devices for construction machines.

実施の形態の油圧ショベルの油圧制御装置の回路図である。1 is a circuit diagram of a hydraulic control device for a hydraulic excavator according to an embodiment. FIG. 従来例の回路図である。It is a circuit diagram of a conventional example.

符号の説明Explanation of symbols

Ａ〜Ｃ 第１〜３回路系統
Ｐ１〜Ｐ３ 第１〜３ポンプ
５ 第２中立流路
６ 第２パラレル流路
８ 第３中立流路
１６ 予備用切換弁
４０ 下流路
４１ 合流流路
４２ 開放制御弁 A to C 1st to 3rd circuit systems P1 to P3 1st to 3rd pump 5 2nd neutral flow path 6 2nd parallel flow path 8 3rd neutral flow path 16 Preliminary switching valve 40 Lower flow path 41 Merge flow path 42 Open control valve

Claims (2)

複数のポンプと、それぞれポンプにオープンセンタータイプの切換弁が接続された回路系統とを備え、これら回路系統のうち第１グループ、第２グループの回路系統の下流路を合流させる合流流路に予備用切換弁を設け、複数のポンプからの圧油を予備用切換弁のアクチュエータに供給可能な油圧制御装置において、
前記合流流路の上流にて第２グループの回路系統の下流路に、該下流路を、第１グループの回路系統のポンプの吐出圧と第２グループの回路系統のポンプの吐出圧に応じてタンクに通じる排出流路に開放する開放制御弁を設けたことを特徴とする油圧制御装置。 A plurality of pumps and a circuit system each having an open center type switching valve connected to the pumps are provided, and a reserve flow path is provided in a merge flow path that merges the lower flow paths of the first group and the second group of these circuit systems. In the hydraulic control device that is provided with a switching valve for supplying pressure oil from a plurality of pumps to the actuator of the standby switching valve,
Upstream of the merging channel, the lower channel is connected to the lower channel of the second group circuit system according to the discharge pressure of the pump of the first group circuit system and the discharge pressure of the pump of the second group circuit system. A hydraulic control device comprising an open control valve that opens to a discharge passage that communicates with a tank. 前記開放制御弁は、第１グループの回路系統のポンプの吐出圧が第２グループの回路系統のポンプの吐出圧よりも設定圧以上高いときは第２グループの回路系統の下流路を前記排出流路に開放し、その設定圧以内のときは第２グループの回路系統の下流路を前記合流流路に開通することを特徴とする請求項１に記載の油圧制御装置。   When the discharge pressure of the pumps of the first group of circuit systems is higher than the set pressure by the discharge pressure of the pumps of the second group of circuit systems, the release control valve causes the discharge flow in the lower flow path of the second group of circuit systems. 2. The hydraulic control device according to claim 1, wherein the hydraulic control device opens to the road and opens the lower flow path of the second group of circuit systems to the merging flow path when the pressure is within the set pressure.
JP2004148967A 2004-05-19 2004-05-19 Hydraulic control device Expired - Fee Related JP4139352B2 (en)

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EP20050010782 EP1598561B1 (en) 2004-05-19 2005-05-18 Hydraulic control apparatus
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EP1598561A2 (en) 2005-11-23
DE602005003980T2 (en) 2008-04-30
DE602005003980D1 (en) 2008-02-07
CN100516555C (en) 2009-07-22
EP1598561A3 (en) 2005-12-14
JP4139352B2 (en) 2008-08-27
EP1598561B1 (en) 2007-12-26
CN1699761A (en) 2005-11-23

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