JPH0328501A - Work machine cylinder control valve device - Google Patents

Work machine cylinder control valve device

Info

Publication number
JPH0328501A
JPH0328501A JP1160873A JP16087389A JPH0328501A JP H0328501 A JPH0328501 A JP H0328501A JP 1160873 A JP1160873 A JP 1160873A JP 16087389 A JP16087389 A JP 16087389A JP H0328501 A JPH0328501 A JP H0328501A
Authority
JP
Japan
Prior art keywords
port
side chamber
pump
supplied
machine cylinder
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
Application number
JP1160873A
Other languages
Japanese (ja)
Other versions
JP2632728B2 (en
Inventor
Kiyoshi Shirai
白井　清
Teruo Akiyama
照夫 秋山
Shigeru Shinohara
茂 篠原
Naoki Ishizaki
直樹 石崎
Takahide Takiguchi
敬英 瀧口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Komatsu Ltd
Original Assignee
Komatsu Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd filed Critical Komatsu Ltd
Priority to JP1160873A priority Critical patent/JP2632728B2/en
Priority to KR1019910700213A priority patent/KR920701694A/en
Priority to US07/655,351 priority patent/US5218897A/en
Priority to DE69021706T priority patent/DE69021706T2/en
Priority to EP90909396A priority patent/EP0436028B1/en
Priority to PCT/JP1990/000829 priority patent/WO1991000431A1/en
Publication of JPH0328501A publication Critical patent/JPH0328501A/en
Application granted granted Critical
Publication of JP2632728B2 publication Critical patent/JP2632728B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed 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
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

PURPOSE:To reduce pressure loss and increase speed by supplying returning pressure oil in the upper chamber of a cylinder to the lower chamber through an oil hole in a control valve body and a check valve, when pressure oil delivered from a pump is supplied to the lower chamber of a working machine cylinder. CONSTITUTION:When pilot pressure oil is supplied to a second pressure receiving chamber 34 to slide a spool 13 rightward, a first port 15 is connected to a first tank port 14 through a first notch groove 27 and, at the same time, the first port 15 is opened to a regenerating port 16 through a second notch groove 28 and a second pump port 20 is opened to a second outlet port 19 through a fourth notch groove 30. By this, pressure oil delivered from a pump 1 is supplied to the lower chamber 3b of a working machine cylinder 3 and pressure oil in the upper chamber 3a of the cylinder flows into the first tank port 14 and the regenerating port 16, opens a check valve 25, and flows into the lower chamber 3b through an oil line 26 and a second port 22. Thus, since a flow of pump delivery flow + alpha is supplied to the lower chamber 3b, the lowering speed of the working machine cylinder 3 can be increased.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、パワーショベルのブーム、アーム等の作業機
を上下動する作業機シリンダに圧浦を供給する油圧回路
に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a hydraulic circuit that supplies pressure to a cylinder of a working machine that moves up and down a working machine such as a boom or an arm of a power shovel.

〔従来の技術〕[Conventional technology]

ポンプの吐出圧油を操作弁によって作業機シリンダの上
げ側室、下げ側室に供給して作業機シリンダを伸縮作動
するようにした油圧回路が知られている。2. Description of the Related Art Hydraulic circuits are known in which pressure oil discharged from a pump is supplied to a raising side chamber and a lowering side chamber of a working machine cylinder using an operating valve to cause the working machine cylinder to expand and contract.

この油圧回路において作業機シリンダの作動速度を速く
するために、上げ側室よりの戻りの圧油の一部を下げ側
室に供給して作業機シリンダが急速に伸縮作動するよう
にしている。In order to increase the operating speed of the work machine cylinder in this hydraulic circuit, a portion of the return pressure oil from the up side chamber is supplied to the down side chamber so that the work machine cylinder can rapidly expand and contract.

例えば、操作弁のスプール内に浦通路とチェック弁を設
け、作業機シリンダの下げ側室に圧油を供給する際に上
げ側室よりの戻り圧油の一部を浦通路、チェック弁を通
して下げ側室に供給できるようにしたり、操作弁と作業
機シリンダとの接続回路の途中に上げ側室からの戻り圧
油を操作弁を通さずに下げ側室に供給できるようにした
再生弁を設けたりしている。For example, a ura passage and a check valve are provided in the spool of the operating valve, and when supplying pressure oil to the lowering side chamber of the work equipment cylinder, a portion of the return pressure oil from the raising side chamber is routed through the ura passage and the check valve to the lowering side chamber. In addition, a regeneration valve is provided in the connection circuit between the operating valve and the work equipment cylinder so that return pressure oil from the up-side chamber can be supplied to the down-side chamber without passing through the operating valve.

〔発明が解決しようとする課題〕[Problem to be solved by the invention]

前者の場合にはスプール内に設けた油通路がスプール径
の制限を受けるために、その油通路の断面積が小さくな
って圧曲流れの抵抗が大となり、圧力損失が大となる。In the former case, since the oil passage provided in the spool is limited by the spool diameter, the cross-sectional area of the oil passage becomes small, resulting in a large resistance to bending flow and a large pressure loss.

後者の場合には操作弁と再生弁が別置きであるから、そ
の配管が複雑となる。In the latter case, the operation valve and regeneration valve are placed separately, so the piping becomes complicated.

そこで、本発明は前述の課題を解決できるようにした作
業機シリンダの油圧回路を提供することを目的とする。SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a hydraulic circuit for a working machine cylinder that can solve the above-mentioned problems.

〔課題を解決するための手段及び作用〕操作弁の弁本体
にチェック弁と油孔を設け、作業機シリンダの下げ側室
にポンプの吐出圧油を供給する時に前記油孔、チェック
弁を通して上げ側室の戻り圧油を下げ側室に供給できる
ようにして、圧力損失を低減できると共に、特別な配管
を不要にできるようにした作業機シリンダの油圧回路で
ある。[Means and effects for solving the problem] A check valve and an oil hole are provided in the valve body of the operation valve, and when pump discharge pressure oil is supplied to the lower side chamber of the working machine cylinder, the oil is passed through the oil hole and the check valve to the upper side chamber. This is a hydraulic circuit for a working machine cylinder that can supply return pressure oil to the lower side chamber, thereby reducing pressure loss and eliminating the need for special piping.

〔実　施　例〕〔Example〕

第１図に示すように、ポンブ１の吐出路１ａに操作弁２
が設けられ、この操作弁２を切換えることで吐出圧油を
作業機シリンダ３の上げ側室３ａ，下げ側室３ｂに供給
して作業機４を上下動している。As shown in FIG.
is provided, and by switching this operation valve 2, discharge pressure oil is supplied to the raising side chamber 3a and the lowering side chamber 3b of the working machine cylinder 3 to move the working machine 4 up and down.

前記操作弁２は弁本体１１のスプール孔１２にスプール
１３を嵌挿してあり、弁本体１１のスプール孔１２には
第１タンクポート１４、第１ポート１５、再生用ポート
１６、第１ポンプポート１７、第１出口ポート１８、昂
２出ロポート１９、第２ポンプポート２０，第２ポート
２１、第２タンクポート２２が長手方向に間隔を置いて
順次形威され、第１・第２タンクポート１４、２２はタ
ンクに連通し、第１ポートｌ５は作業機シリンダ３の上
げ側室３ａに接続し、第２ポート２１が下げ側室３ｂに
接続し、第１・第２ポンプポート１７，２０にポンプ１
の吐出路１ａが接続してあり，１１出ロポート１８はチ
ェック弁２４を介して第１ポート１５に連通し、第２出
口ポート１９はチェック弁２４を介して第２ポート２１
に連通し、再生用ポート１６はチェック弁２５、油路２
６を経て第２ポート２１に連通している。The operating valve 2 has a spool 13 fitted into the spool hole 12 of the valve body 11, and the spool hole 12 of the valve body 11 has a first tank port 14, a first port 15, a regeneration port 16, and a first pump port. 17, the first outlet port 18, the second outlet port 19, the second pump port 20, the second port 21, and the second tank port 22 are formed in order at intervals in the longitudinal direction, and the first and second tank ports 14 and 22 are connected to the tank, the first port 15 is connected to the upward side chamber 3a of the working machine cylinder 3, the second port 21 is connected to the downward side chamber 3b, and the first and second pump ports 17 and 20 are connected to the pump. 1
The outlet port 18 is connected to the first port 15 via the check valve 24, and the second outlet port 19 is connected to the second port 21 via the check valve 24.
The regeneration port 16 is connected to the check valve 25 and the oil line 2.
6 and communicates with the second port 21.

前記スプール１３には第１タンクポート１４と第１ポー
ト１５を連通する第１切欠講２７、第１ポート１５と再
生用ポート１６を連通ずる第２切欠溝２８、第１ポンブ
ポート１７と第１出口ポート１８を連通する第３切欠溝
２９、第２出口ポート１９と第１ポンプポート２ｏを連
通する第４切欠溝３０、第２ポート２１と第２タンクポ
ート２２を連通する第５切欠溝３１が形成され、スプー
ル１３はバネ３２で中立位置に保持されると共に、第１
受圧室３３に供給されるパイロット圧油で第１作動位置
、第２受圧室３４に供給されるパイロット圧油で第２作
動位置に切換えられる。The spool 13 has a first notch 27 that communicates the first tank port 14 and the first port 15, a second notch 28 that communicates the first port 15 and the regeneration port 16, and a first pump port 17 and a first outlet. A third notch groove 29 that communicates with the port 18, a fourth notch groove 30 that communicates the second outlet port 19 with the first pump port 2o, and a fifth notch groove 31 that communicates the second port 21 with the second tank port 22. The spool 13 is held in a neutral position by a spring 32, and the first
The pilot pressure oil supplied to the pressure receiving chamber 33 is used to switch to the first operating position, and the pilot pressure oil supplied to the second pressure receiving chamber 34 is used to switch to the second operating position.

前記第１タンクポート１４と第１ポート１５は速度可変
弁３５で連通・遮断され、該速度可変弁３５はバルブ３
６をバネ３７でシート座３８に押しつけてある。The first tank port 14 and the first port 15 are communicated with each other by a variable speed valve 35, and the variable speed valve 35 is connected to the valve 3.
6 is pressed against the seat seat 38 by a spring 37.

以上の構或を模式的に示すと第２図のようになる。The above structure is schematically shown in FIG. 2.

次に作動を説明する。Next, the operation will be explained.

第２受圧室３４にパイロット圧油を供給してスプール１
３を第２作動位置に向けて右方に摺動すると、第１切欠
溝２７で第１ポート１５が第１タンクポート１４に連通
すると同時に第２切欠満２８で第１ポート１５が再生用
ポート１６に開口し、第２ポンプポート２ｏは第４切欠
溝３０で第２出口ポート１９に開口する。Pilot pressure oil is supplied to the second pressure receiving chamber 34 and the spool 1
3 to the right toward the second operating position, the first port 15 communicates with the first tank port 14 through the first notch groove 27, and at the same time, the first port 15 communicates with the first tank port 14 through the second notch 28. 16, and the second pump port 2o opens to the second outlet port 19 at a fourth notched groove 30.

これにより、ポンプ１の吐出圧油が作業機シリンダ３の
下げ側室３ｂに供給され、上げ側室３ａ内の圧油は第１
タンクポート１４と再生用ポート１６に流れ、再生用ポ
ート１６よリチェック弁２５を押し開いて油路２６、第
２ポート２２より下げ側室３ｂ内に流入するので、作業
機シリンダ３の下げ側室３ｂにはポンプ吐出流量十αの
流量が供給されて作業機シリンダ３の下降速度は増逸さ
れる。As a result, the discharge pressure oil of the pump 1 is supplied to the lower side chamber 3b of the working machine cylinder 3, and the pressure oil in the upper side chamber 3a is supplied to the first side chamber 3b.
It flows into the tank port 14 and the regeneration port 16, pushes open the recheck valve 25 from the regeneration port 16, and flows into the lowering side chamber 3b through the oil passage 26 and the second port 22, so that the lowering side chamber 3b of the working machine cylinder 3 is supplied with a pump discharge flow rate of 10α, and the descending speed of the working machine cylinder 3 is increased.

つまり、作業機シリンダ３の上げ側室３ａ内には作業機
４の自重で保持圧が生じ、下げ側室３ｂ内の圧力よりも
高くなっているので、上げ側室３ａ内の圧浦が下げ側室
３ｂに供給される。In other words, a holding pressure is generated in the raising side chamber 3a of the work equipment cylinder 3 due to the weight of the work equipment 4, and is higher than the pressure in the lowering side chamber 3b, so that the pressure in the raising side chamber 3a is transferred to the lowering side chamber 3b. Supplied.

また、上げ側室３ｂよりの戻り圧油は第１切欠溝２７で
第１タンクポート１４にも流れるので、その第１切欠溝
２７とｍ２切欠満２８の開口面積を変化させることで下
げ側室３ａに供給される流量をコントロールでき、作業
機シリンダ３の速度を３３整できる。In addition, since the return pressure oil from the upward side chamber 3b also flows through the first notched groove 27 to the first tank port 14, by changing the opening area of the first notched groove 27 and the m2 notch 28, it is returned to the downward side chamber 3a. The supplied flow rate can be controlled and the speed of the working machine cylinder 3 can be adjusted by 33 times.

また、油孔２６の圧力が高くなると速度可変弁３５のバ
ルブ３６が抑されてシート座３８より離れ、第１タンク
ポート１４よりタンクに流れるので、下げ側室３ａへの
供給流量が城少し、油孔２６の圧力によって作業機シリ
ンダ３の速度を可変にできる。Furthermore, when the pressure in the oil hole 26 increases, the valve 36 of the variable speed valve 35 is suppressed, the oil moves away from the seat 38, and the oil flows from the first tank port 14 to the tank. The speed of the working machine cylinder 3 can be varied by the pressure in the hole 26.

また、前記油孔２６にはチェック弁２５が設けてあるか
ら、第２出口ポート２１より再（生用ポート１６への圧
油流れが阻止され、下げ側室３ｂの圧力が上げ側室３ａ
より高くな１った場合に上げ側室３ａに流れることが防
止できる。Further, since the oil hole 26 is provided with a check valve 25, the flow of pressure oil from the second outlet port 21 to the regeneration port 16 is blocked, and the pressure in the lower side chamber 3b is increased.
If the temperature rises higher, it can be prevented from flowing into the raised side chamber 3a.

〔発明の効果〕〔Effect of the invention〕

作業機シリンダ３の下げ側室３ｂにポンプ吐出圧油を供
給する時に、上げ側室３ａ内の圧油を油孔２６より下げ
側室３ｂに供給できるから、下げ側室３ｂにポンプ吐出
流量より多くの圧油を供給して増速できる。When pump discharge pressure oil is supplied to the lowering side chamber 3b of the work equipment cylinder 3, the pressure oil in the raising side chamber 3a can be supplied to the lowering side chamber 3b from the oil hole 26, so that more pressure oil than the pump discharge flow rate is supplied to the lowering side chamber 3b. can be supplied to increase speed.

また、油孔２６、チェック弁２５は操作弁２の弁本体１
１に形成したので、スプール１３の径に制限されずに油
孔２６を大径にできるから圧力損失を低減できると共に
、特別な配管が不要となる。In addition, the oil hole 26 and the check valve 25 are connected to the valve body 1 of the operating valve 2.
1, the diameter of the oil hole 26 can be increased without being limited by the diameter of the spool 13, reducing pressure loss and eliminating the need for special piping.

【図面の簡単な説明】[Brief explanation of drawings]

図面は本発明の実施例を示し、第１図は断面説明図、第
２図は模式的説明図である。 １はポンプ、１ａは吐出路、２は操作弁、３は作業機シ
リンダ、３ａは上げ側室、３ｂは下げ側室、１１は弁本
体、１２はスプール孔、１３はスプール、２５はチェッ
ク弁、２６は油孔。 第１図The drawings show embodiments of the present invention, with FIG. 1 being a sectional explanatory view and FIG. 2 being a schematic explanatory view. 1 is a pump, 1a is a discharge path, 2 is an operating valve, 3 is a work equipment cylinder, 3a is a raising side chamber, 3b is a lowering side chamber, 11 is a valve body, 12 is a spool hole, 13 is a spool, 25 is a check valve, 26 is an oil hole. Figure 1

Claims (1)

【特許請求の範囲】 ポンプ１の吐出路１ａに操作弁２を設け、この操作弁２
を切換えることで作業機シリンダ３の下げ側室３ｂ、上
げ側室３ａに吐出圧油を供給する作業機シリンダの油圧
回路において、前記操作弁２の弁本体１１に形成したス
プール孔１２にスプール１３を、前記下げ側室３ｂに接
続したポートとポンプポートを連通し、かつ上げ側室３
ａに接続したポートとタンクポートを連通する第１作動
位置と、前記下げ側室３ｂに接続したポートとタンクポ
ート連通し、かつ前記上げ側室３ａに接続したポートと
ポンプポートを連通する第２作動位置とに亘って移動可
能に設け、 前記弁本体１１に、スプール１３が第１作動位置の時に
前記上げ側室３ａに接続したポートと前記下げ側室３ｂ
に接続したポートを連通する油孔２６及びチェック弁２
５を設けたことを特徴とする作業機シリンダの油圧回路
。[Claims] An operating valve 2 is provided in the discharge path 1a of the pump 1, and the operating valve 2
In the hydraulic circuit of the work machine cylinder that supplies discharge pressure oil to the lower side chamber 3b and the upper side chamber 3a of the work machine cylinder 3 by switching the spool 13 to the spool hole 12 formed in the valve body 11 of the operation valve 2, The port connected to the lowering side chamber 3b and the pump port are connected to each other, and the pump port is connected to the lowering side chamber 3b.
a first operating position in which the tank port communicates with the port connected to the lower chamber 3b, and a second operating position in which the tank port communicates with the port connected to the lower chamber 3b and the pump port communicates with the port connected to the upper chamber 3a. The valve body 11 is provided with a port connected to the raising side chamber 3a and the lowering side chamber 3b when the spool 13 is in the first operating position.
An oil hole 26 and a check valve 2 that communicate with the port connected to the
5. A hydraulic circuit for a working machine cylinder, characterized in that a hydraulic circuit is provided with a cylinder.
JP1160873A 1989-06-26 1989-06-26 Control valve device for work machine cylinder Expired - Lifetime JP2632728B2 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP1160873A JP2632728B2 (en) 1989-06-26 1989-06-26 Control valve device for work machine cylinder
KR1019910700213A KR920701694A (en) 1989-06-26 1990-06-26 Hydraulic hydraulic circuit device of working cylinder
US07/655,351 US5218897A (en) 1989-06-26 1990-06-26 Hydraulic circuit apparatus for operating work-implement actuating cylinders
DE69021706T DE69021706T2 (en) 1989-06-26 1990-06-26 HYDRAULIC CIRCUIT FOR OPERATING A MACHINE.
EP90909396A EP0436028B1 (en) 1989-06-26 1990-06-26 Hydraulic circuit for operating cylinder of working machine
PCT/JP1990/000829 WO1991000431A1 (en) 1989-06-26 1990-06-26 Hydraulic circuit for operating cylinder of working machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1160873A JP2632728B2 (en) 1989-06-26 1989-06-26 Control valve device for work machine cylinder

Publications (2)

Publication Number Publication Date
JPH0328501A true JPH0328501A (en) 1991-02-06
JP2632728B2 JP2632728B2 (en) 1997-07-23

Family

ID=15724217

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1160873A Expired - Lifetime JP2632728B2 (en) 1989-06-26 1989-06-26 Control valve device for work machine cylinder

Country Status (1)

Country Link
JP (1) JP2632728B2 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995030094A1 (en) * 1994-05-02 1995-11-09 Ube Industries, Ltd. Speed control method and apparatus for hydraulic cylinders
WO1996004481A1 (en) * 1994-08-05 1996-02-15 Komatsu Ltd. Directional control valve
JP2003028101A (en) * 2001-07-12 2003-01-29 Hitachi Constr Mach Co Ltd Hydraulic control device of construction machine
JP2006283975A (en) * 2005-03-30 2006-10-19 Caterpillar Inc Hydraulic system having variable back pressure control
JP2007135517A (en) * 2005-11-21 2007-06-07 Daiwa Seiko Inc Battery support connector device and battery device for electric reel for fishing
CN103352882A (en) * 2013-06-17 2013-10-16 三一汽车起重机械有限公司 Landing leg extension mode switching valve and engineering machinery
CN109808435A (en) * 2019-03-19 2019-05-28 徐工集团工程机械股份有限公司科技分公司 Suspension system and vehicle
CN110332167A (en) * 2019-07-10 2019-10-15 南通翔骜液压润滑设备有限公司 High-precision diverter-collector valve

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5247185A (en) * 1975-10-14 1977-04-14 Nissan Motor Co Ltd Speed controller of travelling liquid actuator
JPS622805U (en) * 1985-06-20 1987-01-09
JPS62105895A (en) * 1985-10-31 1987-05-16 住友重機械工業株式会社 Hydraulic circuit

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5247185A (en) * 1975-10-14 1977-04-14 Nissan Motor Co Ltd Speed controller of travelling liquid actuator
JPS622805U (en) * 1985-06-20 1987-01-09
JPS62105895A (en) * 1985-10-31 1987-05-16 住友重機械工業株式会社 Hydraulic circuit

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995030094A1 (en) * 1994-05-02 1995-11-09 Ube Industries, Ltd. Speed control method and apparatus for hydraulic cylinders
US5832805A (en) * 1994-05-02 1998-11-10 Ube Industries, Ltd. Method and apparatus for controlling speed of hydraulic cylinder
WO1996004481A1 (en) * 1994-08-05 1996-02-15 Komatsu Ltd. Directional control valve
US5832808A (en) * 1994-08-05 1998-11-10 Komatsu Ltd. Directional control valve unit
JP2003028101A (en) * 2001-07-12 2003-01-29 Hitachi Constr Mach Co Ltd Hydraulic control device of construction machine
JP2006283975A (en) * 2005-03-30 2006-10-19 Caterpillar Inc Hydraulic system having variable back pressure control
JP2007135517A (en) * 2005-11-21 2007-06-07 Daiwa Seiko Inc Battery support connector device and battery device for electric reel for fishing
CN103352882A (en) * 2013-06-17 2013-10-16 三一汽车起重机械有限公司 Landing leg extension mode switching valve and engineering machinery
CN103352882B (en) * 2013-06-17 2016-01-20 三一汽车起重机械有限公司 Landing leg stretching pattern switching valve and engineering machinery
CN109808435A (en) * 2019-03-19 2019-05-28 徐工集团工程机械股份有限公司科技分公司 Suspension system and vehicle
CN109808435B (en) * 2019-03-19 2024-03-15 徐工集团工程机械股份有限公司科技分公司 Suspension systems and vehicles
CN110332167A (en) * 2019-07-10 2019-10-15 南通翔骜液压润滑设备有限公司 High-precision diverter-collector valve
CN110332167B (en) * 2019-07-10 2020-11-13 南通翔骜液压润滑设备有限公司 High Precision Diverter and Collector Valve

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