WO2003027505A1 - Circuit hydraulique d'une machine de chantier - Google Patents

Circuit hydraulique d'une machine de chantier Download PDF

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Publication number
WO2003027505A1
WO2003027505A1 PCT/JP2002/009809 JP0209809W WO03027505A1 WO 2003027505 A1 WO2003027505 A1 WO 2003027505A1 JP 0209809 W JP0209809 W JP 0209809W WO 03027505 A1 WO03027505 A1 WO 03027505A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
oil
pilot
oil passage
switching valve
Prior art date
Application number
PCT/JP2002/009809
Other languages
English (en)
Japanese (ja)
Inventor
Masami Kondo
Original Assignee
Yanmar Co.,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 Yanmar Co.,Ltd. filed Critical Yanmar Co.,Ltd.
Publication of WO2003027505A1 publication Critical patent/WO2003027505A1/fr

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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
    • 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
    • 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
    • E02F9/24—Safety devices, e.g. for preventing overload
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/20—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
    • F15B2211/20—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
    • F15B2211/32—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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

Definitions

  • the present invention relates to a technology of a hydraulic circuit of a hydraulic working machine such as an excavation turning vehicle. More specifically, the present invention relates to a lock mechanism technology for preventing an erroneous operation of an operation lever such as turning. Background art
  • An operating lever is provided in the driver's seat to operate the hydraulic actuators in order to perform the turning operation of the pump, arm, bucket, etc., which are the working machines of the excavation and turning work vehicle, and to turn and run. ing.
  • the operation lever is configured to directly operate the spool of the switching valve, or to switch the switching valve by operating the pilot valve.
  • an oil passage 102 is connected to the discharge side of a pump 101 serving as a pilot pressure oil supply source, and the other end of the oil passage 102 is Connect to the safety pulp 103 pump port.
  • the tank port of the safety valve 103 is connected to the oil tank, and when the safety valve 103 locks, the pressure oil from the pump 101 flows into the oil tank. Then, one end of a pilot oil passage 104 is connected to the output port of the safety valve 103.
  • the other end of the pipe oil passage 104 is connected to one end of a pilot oil passage 105 and one end of a branch pilot oil passage 106 from a branch point.
  • the pilot oil passage 105 The other end is connected to a first pilot oil passage 107 and a second pilot oil passage 1 ′ 08 via a branch point, and the first pilot oil passage 107 and the second pilot oil passage 108 are connected to each other.
  • Each is connected to a pilot switching valve (remote control valve) 109/109.
  • the branch pilot oil passage 106 is connected to the pilot port 110 a of the operation section of the unload oil passage switching valve 110.
  • pilot oil passages 90 to 97 from the pilot switching valve 109 * 109 are connected to pilot ports 90 to 97 of the same reference numerals of the respective switching valves 117,.
  • the present invention is configured such that the hydraulic pressure supply control for a plurality of hydraulic factories is performed by each corresponding control valve, and the switching operation of each control valve is performed by both operating means of pilot operating means and other operating means.
  • An unloading oil passage leading to an oil tank, an oil passage to be supplied to a control valve of each of the hydraulic actuators, and an unopening oil passage switching valve are provided between a hydraulic supply source.
  • the unopened oil passage switching valve is loaded as a pilot operated type when the pilot hydraulic pressure is not applied, a discharge oil passage from a pilot hydraulic supply source, an oil tank, and the pilot operation.
  • a direction switching valve interlocking with a safety lever is provided between a supply oil passage to the means and a pilot oil passage connected to an operation portion of the unsealed oil passage switching valve;
  • the safety lever is operated in the non-working state, all the actuators are disabled, and the safety lever is released to the working state to release all the actuators. The evening can be activated.
  • the pilot pressure oil supply source does not operate due to a failure or the like, the unloading oil passage switching valve is switched to the opening side, and pressure oil is supplied to the control valve.
  • the function operated by the pilot operating means stops functioning, but pressure oil is supplied to the control valve operated by other operating means to operate the actuator, and the operation of the actuator is started. It is possible to secure the minimum safety.
  • the turning motor is included in the hydraulic actuator controlled by the above-mentioned pilot operating means, and the traveling motor is included in the hydraulic actuator controlled by the other operating means.
  • the present invention provides a pressure sensor in a discharge oil passage of the above-described pilot pressure oil supply source.
  • the pressure sensor is connected to an alarm and an alarm is issued when the pressure becomes lower than the set pressure.
  • FIG. 1 is an overall side view of an excavation turning work vehicle having a hydraulic circuit according to the present invention.
  • FIG. 2 is a hydraulic circuit diagram when the directional control valve is closed.
  • FIG. 3 is a hydraulic circuit diagram when the direction switching valve is unlocked.
  • FIG. 4 is a hydraulic circuit diagram when a pressure switch and an alarm are provided.
  • FIG. 5 is a conventional hydraulic circuit diagram. BEST MODE FOR CARRYING OUT THE INVENTION
  • the excavating and turning work vehicle supports a turning frame 8 so as to be able to turn via a turning table bearing 7 having a vertical axis at the upper center of the crawler-type traveling device 1.
  • a blade 10 is disposed at one of the front and rear ends of the crawler traveling device 1 so as to be vertically rotatable.
  • a bonnet 9 for covering an engine or the like is arranged, and a seat 22 is attached above the bonnet 9.
  • levers for performing a traveling operation, a turning operation, and an operation of the work machine 2 are provided on a front column 19.
  • a step 20 is arranged between the front column 19 and the hood 9.
  • a work machine 2 is mounted on a front end of the revolving frame 8, and a boom bracket 12 is attached to the work machine 2 so as to be rotatable left and right.
  • the lower end of the boom 6 is attached to the boom bracket 12. It is supported to be able to rotate back and forth.
  • the boom 6 is bent forward at an intermediate portion, and is formed in a substantially “C” shape in a side view.
  • An arm 5 is rotatably supported at the other end of the boom 6, and a bucket 4 as a work attachment is rotatably supported at the end of the arm 5.
  • a boom cylinder 23 is interposed between the boom bracket 12 and a boom cylinder bracket 25 provided at the front of the middle of the boom 6, and a ram cylinder bottom bracket 2 provided at the back of the middle of the boom 6 is provided.
  • An arm cylinder 29 is interposed between a bucket cylinder bracket 27 provided at the base end of the arm 6 and the arm 5, and a stage 11 is connected to the bucket cylinder bracket 27 and the bucket 4.
  • a bucket cylinder 24 is interposed between them.
  • the boom 6 is rotated by the boom cylinder 23, the arm 5 is rotated by the arm cylinder 29, and the bucket 4 is rotated by the bucket cylinder 24.
  • the cylinder 23, the arm cylinder 29, and the bucket cylinder 24 are constituted by hydraulic cylinders as actuators, and each cylinder 23, 29, 24 is an operation provided on the front column 19.
  • the switching valve disposed below is switched, and the hydraulic pressure is supplied from the hydraulic pump to drive the expansion and contraction.
  • a swing cylinder 17 is disposed on the side of the swing frame 8, and its base is pivotally supported by the swing frame, and the tip of the cylinder rod of the swing cylinder 17 is connected to the beam bracket 12.
  • the swing cylinder 17 allows the boom bracket 12 to rotate left and right with respect to the turning frame 8, thereby enabling the work machine 2 to rotate left and right.
  • the turning frame 8 can be turned left and right by 360 degrees by the operation of a turning module 13 provided above the turning table bearing 7. It can be moved up and down by the operation of a blade cylinder 14 interposed between it and the track frame 3 of the traveling device 1.
  • the swing motor 13 is constituted by a hydraulic motor. Further, traveling hydraulic motors are disposed inside the driving sprockets 16-16 disposed on one side of the front and rear of the track frame 3, respectively, so that the traveling device 1 can be driven to travel.
  • the hydraulic cylinder / hydraulic motor which constitutes the hydraulic actuator, can be driven by operating an operation lever or pedal provided on the front column 19 and the step 20.
  • a first hydraulic pump 31 and a second hydraulic pump 32 which are hydraulic pressure sources, are driven in parallel and connected in parallel to an output shaft of an engine E housed in the bonnet 9.
  • An unloading oil passage switching valve 35 is connected to the two output oil passages 3 3 and 3 4 of the first hydraulic pump 31, and a center oil passage 3 is connected to the unloading oil passage switching valve 35.
  • the unloading oil passage 49 leading to the oil tank is connected to 6 ⁇ 40 and the center oil passage 36 ⁇ 40 is connected to each control valve so that each hydraulic actuator can be driven.
  • the unopened oil passage switching valve 35 is configured as a pilot operated type, and when the pilot oil pressure is applied to the pilot port 35 a of the operation unit, the output oil passages 33, 34 are unloaded.
  • the output oil passages 33, 34 are connected to the center oil passage 36, 40, and the hydraulic oil is supplied to each control valve. It is loaded and each actuary is operational.
  • a relief valve (not shown) for setting the output oil pressure is connected in parallel to the first center oil passage 36 on the output side of the output oil passage 33, and the vehicle travels on one of the left and right sides (the right side in this embodiment).
  • a directional switch valve for traveling motor 37 that switches oil supply to the hydraulic motor 45, to the boom cylinder 23, a directional valve for boom 38 that switches oil supply to the cylinder 23 (Fig. 1), and to the swing hydraulic motor 13.
  • a turning direction switching valve 39 for switching the oil supply of the fuel tank is connected in tandem.
  • a pilot port 38 a ⁇ 38-39 a-39 b is formed in the operation part of the boom direction switching valve 38 and the turning direction switching valve 39, and by operating the operation lever 43.
  • a hydraulic valve (boom cylinder 23, swing hydraulic motor 13) can be operated by switching a control valve by switching a pilot valve described later.
  • a second center oil passage 40 can be connected to the output oil passage 34, and a relief valve (not shown) for setting an output oil pressure is connected in parallel to the second center oil passage 40.
  • Directional switching valve 37 L for traveling motor for switching oil supply to the traveling hydraulic motor 46 on the side (left side in this embodiment) and directional switching valve for swing for switching oil supply to swing cylinder 17 (Fig. 1)
  • the directional control valve 42 for switching the oil supply to the arm cylinder 29 (Fig. 1) is connected in tandem with 41.
  • the pilot port is connected to the operating parts of the swing direction switching valve 41 and the arm direction switching valve 42. G 41 a '41 b' 42 a '42 b is formed.
  • the number of the switching valves 37 R, 38, 39, 37 L, 41, and 42 as control valves is six, but the number and the number of hydraulic actuators to be operated are not limited. Other switching valves can be added.
  • the swing direction switching valve 41 and the arm direction switching valve 42 are neutral in that the hydraulic oil from the first and second hydraulic pumps 31 and 32 is not supplied to the hydraulic actuator by operating the operation levers 43 and 44. From position X, it can be switched to pressure oil supply position Y for supplying pressure oil to one input / output port of the corresponding hydraulic actuator or supply position ⁇ ⁇ ⁇ for supplying pressure oil to the other input / output port .
  • the swing, arm, boom, and swing switching valves 41, 42, 38, and 39 which are switched by operating levers 43 and 44, are pilot operated, and each pilot valve described later From 56, 57, 58, 59, each pilot port 38 a-38 b * 39 a-39 b-41 a * 41 b-42 a 'formed on each switching valve 38, 39, 41, 42
  • each pilot pressurized oil By supplying the pilot pressurized oil to 42b, it is configured to switch from the neutral position X to the pressurized oil supply position Y or Z.
  • the left and right traveling motor direction switching valves 37R and 37L can be switched by manual operation, and are distinguished from the pilot-type operation means.
  • This operation means is not limited to manual operation, and is electrically operated. (Electromagnetic valve type).
  • the left and right traveling motor direction switching valves 37R and 37L are connected to the respective switching valves via links and the like, and are operated from the operation levers 37a and 37b to operate from the neutral position X to the hydraulic oil supply position Y or It is configured as a manual type that switches to Z.
  • the pilot hydraulic pressure supply circuit of the present invention will be described with reference to FIG.
  • the second hydraulic pump (hydraulic supply source) 32 is configured so that part of the pressure oil supplied from it is used as pilot oil pressure.
  • the pressure oil discharged from the second hydraulic pump 32 is supplied to a direction switching valve (safety valve) 50 via a pilot hydraulic discharge oil passage 51.
  • the direction switching valve 50 is a 4-port 2-position switching valve, and is a safety valve capable of locking and unlocking the operation of the hydraulic actuator.
  • the directional control valve 50 is provided with a safety lever 50a, and the safety lever 50a can switch between locking and unlocking of the hydraulic actuator.
  • a remotely controllable valve such as an electromagnetic valve to link with the safety switch / safety lever.
  • the pump port of the direction switching valve 50 is connected to the pilot hydraulic discharge oil passage 51, and the tank port is connected to an oil tank.
  • the first port is connected to the oil passage 53 to each pilot valve 56, 57, 58, 59, and the second port is connected to the unload oil passage switching valve 35. Connected to pilot oil passage 52 to pilot port 35a.
  • a branch is formed at the other end of the oil passage 53, and one end of the first oil passage 54 and one end of the second oil passage 55 are connected.
  • the other end of the first oil passage 54 is connected to pump ports of a boom pilot valve 56 and a turning pilot valve 57, and the other end of the second oil passage 55 is connected to a swing pilot valve 58 and an arm pilot.
  • the pump is connected to the pump port of the valve 59, so that the hydraulic oil from the second hydraulic pump 32 can be supplied to each of the pilot valves 56, 57, 58, 59.
  • pilot hydraulic pressure is changed from the direction switching valve 38, 39, 41, for the boom, swing, swing, and arm.
  • pilot ports 38a, 38b-39a-39b-41a-41b-42a-42b of the directional valves 38, 39, 41, 42 have 90 These are designated by pilot valves 56-57-58.
  • each pilot valve 56, 57, 58, 59 is switched, and each control valve 38, 39, 41, 42 Pilot port 38a, 38b, 39a-39b-41a -41 b-42 a-42 b is supplied with pressurized oil.
  • the unload oil passage switching valve 35 is not supplied with the pipe hydraulic pressure from the direction switching valve 50, and the spool is switched to the load side (unopened one-side release side) by the biasing force of the panel.
  • the pressure oil from the first hydraulic pump 31 is supplied to the unopened oil passage switching valve 35 via the output oil passages 33 and 34. Since the unloading oil passage switching valve 35 is switched to the opening side, the pressure oil is supplied to the center oil passages 36 and 40. Therefore, hydraulic oil is applied to each pilot valve 56, 57, 58, 59 and control valve.
  • the control valve is switched by operating each of the operation levers 37 a ⁇ 37 b ⁇ 43 ⁇ 44, the hydraulic actuator can be operated.
  • the hydraulic oil from the second hydraulic pump 32 causes the direction switching valve 50 and The oil is not supplied to the oil passage 53, and the pilot valves 56, 57, 58, 59 become inoperable.
  • control valves of the operation means other than the pilot means are the left and right traveling motor direction switching valves 37 L and 37 R, even if the second hydraulic pump 32 is not operated, The hydraulic actuator connected to the left and right traveling motor direction switching valves 37 L-37 R becomes operable, and a system that enables traveling even when the pilot pressure oil supply source fails can be established.
  • a pressure sensor for example, a pressure switch 60 is provided in the pilot hydraulic discharge oil passage 51 so as to detect the oil pressure.
  • the pressure switch 60 is provided with a lamp, a buzzer, or the like.
  • the second hydraulic pump 32 which is a pilot pressure oil supply source, is connected to the alarm 61, the alarm 61 can be activated.
  • the pressure in the pilot hydraulic discharge oil passage 51 becomes equal to or less than the set value when the second hydraulic pump 32 fails or an oil leak occurs, the pressure connected to the pilot hydraulic discharge oil passage 51 is reduced.
  • the switch 60 When the switch 60 is turned on, the alarm 61 connected to the pressure switch 60 is activated to issue an alarm, thereby notifying that the second hydraulic pump 32 has failed.
  • the alarm 61 operates only when the engine E is operating, and the alarm 61 issues an alarm by light or sound, etc., and is not limited. No.
  • the hydraulic circuit of the hydraulic working machine according to the present invention is suitable for use in a digging and turning work vehicle such as a backhoe.

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

Abstract

L'invention concerne une machine de chantier capable d'empêcher tous les actionneurs d'être immobilisés dans leur fonctionnement lorsqu'une source d'alimentation en pression hydraulique pilote n'assure plus sécurité minimale. A cet effet, l'invention est caractérisée en ce qu'une valve sélectrice de conduite d'huile de déchargement (35) est installée entre une conduite hydraulique de déchargement conduisant à un réservoir d'huile et à des conduites d'huile (36) et (40) d'alimentation en huile des valves de commande des actionneurs hydrauliques, et une première pompe hydraulique (31), et en ce qu'une valve de distribution (50) est montée dans la conduite d'huile de déchargement d'une seconde pompe hydraulique (32) prévue dans la machine de chantier, de sorte que les commandes de pression hydraulique de la pluralité des actionneurs hydrauliques sont effectuées par les valves de commande correspondantes, et que les sélections des valves de commande sont effectuées par des moyens de fonctionnement pilotes et d'autres moyens de fonctionnement tels que des moyens manuels, en ce que la valve de distribution (50) comprend deux orifices à sens d'alimentation d'huile différents l'un de l'autre, et les orifices sont commutables entre un sens pour l'alimentation en huile sous pression, en provenance de la seconde pompe hydraulique (32), et un sens pour l'alimentation en huile sous pression vers le réservoir d'huile par un levier de sécurité (50a).
PCT/JP2002/009809 2001-09-25 2002-09-24 Circuit hydraulique d'une machine de chantier WO2003027505A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001/290610 2001-09-25
JP2001290610A JP2003097505A (ja) 2001-09-25 2001-09-25 作業機械の油圧回路

Publications (1)

Publication Number Publication Date
WO2003027505A1 true WO2003027505A1 (fr) 2003-04-03

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WO (1) WO2003027505A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101974926A (zh) * 2010-09-29 2011-02-16 三一重机有限公司 一种用于挖掘机的自动控制液压油温的回油系统
CN102518170A (zh) * 2011-12-27 2012-06-27 四川大学 装载机工作装置液压系统
CN104061197A (zh) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 一种装载机的液压系统
CN104405006A (zh) * 2014-12-16 2015-03-11 派克汉尼汾流体传动产品（上海）有限公司 装载机半变量液压系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4193830B2 (ja) 2005-09-02 2008-12-10 コベルコ建機株式会社 作業機械の油圧制御装置
CN101946096B (zh) * 2008-03-31 2013-07-17 纳博特斯克株式会社 建筑机械的液压回路
WO2016140378A1 (fr) * 2015-03-02 2016-09-09 볼보 컨스트럭션 이큅먼트 에이비 Engin de chantier comprenant une fonction d'arrêt d'urgence

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JPH09329107A (ja) * 1996-04-11 1997-12-22 Nabco Ltd 油圧回路
JPH11280701A (ja) * 1998-03-30 1999-10-15 Yutani Heavy Ind Ltd 油圧制御装置
JP2000205141A (ja) * 1998-12-17 2000-07-25 Caterpillar Inc ポンプ故障を判断するための方法と装置
EP1022395A1 (fr) * 1998-07-07 2000-07-26 Kabushiki Kaisha Kobe Seiko Sho Dispositif de commande hydraulique d'une machine de chantier
JP2001311407A (ja) * 2000-04-27 2001-11-09 Sumitomo (Shi) Construction Machinery Manufacturing Co Ltd 建設機械の油圧回路

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
JPH09329107A (ja) * 1996-04-11 1997-12-22 Nabco Ltd 油圧回路
JPH11280701A (ja) * 1998-03-30 1999-10-15 Yutani Heavy Ind Ltd 油圧制御装置
EP1022395A1 (fr) * 1998-07-07 2000-07-26 Kabushiki Kaisha Kobe Seiko Sho Dispositif de commande hydraulique d'une machine de chantier
JP2000205141A (ja) * 1998-12-17 2000-07-25 Caterpillar Inc ポンプ故障を判断するための方法と装置
JP2001311407A (ja) * 2000-04-27 2001-11-09 Sumitomo (Shi) Construction Machinery Manufacturing Co Ltd 建設機械の油圧回路

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101974926A (zh) * 2010-09-29 2011-02-16 三一重机有限公司 一种用于挖掘机的自动控制液压油温的回油系统
CN102518170A (zh) * 2011-12-27 2012-06-27 四川大学 装载机工作装置液压系统
CN104061197A (zh) * 2014-06-05 2014-09-24 安徽博一流体传动股份有限公司 一种装载机的液压系统
CN104405006A (zh) * 2014-12-16 2015-03-11 派克汉尼汾流体传动产品（上海）有限公司 装载机半变量液压系统

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