WO2000029752A1 - Dispositif hydraulique de commande pour machines de travaux - Google Patents
Dispositif hydraulique de commande pour machines de travaux Download PDFInfo
- Publication number
- WO2000029752A1 WO2000029752A1 PCT/JP1999/006250 JP9906250W WO0029752A1 WO 2000029752 A1 WO2000029752 A1 WO 2000029752A1 JP 9906250 W JP9906250 W JP 9906250W WO 0029752 A1 WO0029752 A1 WO 0029752A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- flow rate
- control
- pump
- hydraulic pump
- Prior art date
Links
Classifications
-
- 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
-
- 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
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
- E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
-
- 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
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
-
- 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
- E02F9/2285—Pilot-operated systems
-
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
-
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
- B60Y2200/412—Excavators
-
- 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
-
- 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
- F15B2211/32—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
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a 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
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6654—Flow rate 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
- F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
-
- 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
Definitions
- the present invention belongs to the technical field of a hydraulic control device for a working machine such as a hydraulic shovel.
- working machines such as hydraulic excavators include a plurality of hydraulic actuators, a hydraulic pump for supplying hydraulic oil to these hydraulic actuators, and a hydraulic oil supply control for each hydraulic actuator.
- a control valve that operates and a control unit that inputs an operation signal of an operating tool and outputs a control command to an operation unit of the control valve.
- a closed sensor system that prevents oil from bleeding when the control valve is in neutral.
- the opening amount (spool position) of each control valve is determined according to the operation amount of the corresponding operation tool regardless of the operation state of other operation tools. Was configured to be controlled.
- the sum of the required flow rates of the hydraulic actuators required by operating the operating tools becomes larger than the flow rate that can be supplied by the hydraulic pump.
- the flow rate supplied to the hydraulic actuator through each control valve is smaller than the required flow rate, but the opening amount of each control valve at this time is determined by operating the corresponding operating tool as described above. Since the control is performed according to the flow rate, the opening degree may be larger than the supply flow rate from the hydraulic pump. In such a case, the hydraulic actuator may not be able to operate properly due to the vacuum. There is a problem that the smooth operation is hindered when the tucking is interlocked and the operability is reduced, and there is a problem to be solved by the present invention. Disclosure of the invention
- the present invention has been made in view of the above-described circumstances, and has been created with the object of solving these problems.
- the present invention provides a plurality of hydraulic actuators and supplies hydraulic oil to these hydraulic actuators.
- a working machine comprising: a hydraulic pump, a control valve for controlling hydraulic oil supply to each hydraulic actuator, and valve operating means for operating each control valve.
- the control unit includes: Based on an input signal from the operation state detecting means, a distribution flow rate for distributing the output flow rate of the hydraulic pump to each hydraulic actuator is calculated, and the distribution flow rate is calculated for each hydraulic actuator. (D) A control command is output to the valve actuation means so as to be supplied overnight.
- control valve is operated to supply the distribution flow rate to each of the hydraulic factories, and when the hydraulic valves are operated in combination, the hydraulic pump
- the output flow rate can be appropriately distributed to each hydraulic factor, and the opening of the control valve can be prevented from becoming larger than the flow rate supplied from the hydraulic pump, thereby improving the combined operability.
- the output flow rate of the hydraulic pump can be calculated based on the maximum torque of the hydraulic pump, the engine speed, and the pump discharge pressure at the present time. If the sum of the required flow rates of the hydraulic actuators obtained from the operating conditions of the operating tools is smaller than the output flow rate of the hydraulic pump, the required flow rate of each hydraulic actuator is set to be the distribution flow rate. By doing so, it is possible to avoid such a problem that the distribution flow rate becomes larger than the required flow rate.
- FIG. 1 is a side view of a hydraulic excavator.
- FIG. 2 is a schematic diagram of a hydraulic circuit showing supply of pressurized oil to a hydraulic factory.
- FIG. 3 is a block diagram showing input and output of the control unit.
- FIG. 4 is a control block diagram showing a calculation procedure of a pump required flow rate.
- FIG. 5 is a control block diagram showing a procedure for calculating the allowable pump flow rate.
- FIG. 6 is a control block diagram showing a procedure for calculating a distribution flow rate.
- reference numeral 1 denotes a hydraulic excavator
- the hydraulic excavator 1 includes a lower traveling body 2 of a crawler type, an upper revolving body 3 rotatably supported above the lower traveling body 2, and an upper revolving body.
- the front attachment 4 includes a boom 5 whose base end is swingably supported by the upper revolving unit 3 and a front end of the boom 5.
- the basic configuration is the same as that of the related art, including a member 6 such as a stick 6 supported swingably and a bucket 7 supported swingably at the tip of the stick 6.
- the hydraulic excavator 1 further includes left and right traveling motors 8 and 9, a boom cylinder 10 for swinging the boom 5, a stick cylinder 11 for swinging the stick 6, and a bucket.
- Various hydraulic actuators such as a bucket cylinder 12 for swinging the unit 7 and an actuator cylinder 13 for operating an attachment (not shown), are provided. The operation is performed based on the supply of pressurized oil from a hydraulic pump P driven by the power of the engine.
- FIG. 2 is a schematic diagram of the hydraulic oil supply circuit to the hydraulic actuators 8 to 13.
- 14 to 19 indicate the hydraulic oil supply control to each hydraulic actuator 8 to 13.
- This is a control valve for attachment, and these control valves 14 to 19 are constituted by pilot operated three-position switching valves.
- the control valve 14 to 19 When the pilot pressure oil is not supplied to the pie port 14a to 19a or the 14b to 19b, the control valve 14 to 19 is actuated by the hydraulic actuator. Evening Although it is located in the neutral position N where oil is not supplied to 8 to 13, the oil pressure is supplied to the pipe port 14a to 19a or 14b to 19b. As a result, the spool moves, and the valve path for supplying the hydraulic oil from the hydraulic pump P to one of the oil chambers 8a to l3a of the corresponding hydraulic actuator 8 to 13 and the hydraulic actuator
- the configuration is such that the pressure oil supply position X or Y is switched to the position where the valve for flowing the oil discharged from the other oil chambers 8 b to 13 b of 8 to 13 to the oil tank is opened.
- the opening amount (spool position) of the valve path of the control valve 14 to 19 is determined by the pipe pressure supplied to the pilot port 14 a to 19 a or 14 b to 19 b. More controlled.
- 20 A to 25 A and 20 B to 25 B correspond to the control valves 14 to: L9 pipe ports 14 a to 19 a and 14 b to 19 b. These are solenoid proportional pressure reducing valves for left-hand running, right-hand running, boom, stick, packet, and attachments that output pressure oil at the pie mouth, respectively.
- the output pressures of 25 A and 20 B to 25 B are controlled based on a command from a control unit 26 described later.
- reference numeral 27 denotes an electromagnetic switching valve for hydraulic locking, and the electromagnetic switching valve 27 is provided with the electromagnetic proportional pressure reducing valves 2OA to 25 when the lock switch 28 is open.
- A, 20 B to 25 B The pilot supply oil passage to B is closed, and this allows the hydraulic switches 8 to 13 to be activated, but the lock switch 28 In the closed state, the above-mentioned oil supply passage is opened so that the operation of the hydraulic actuators 8 to 13 is allowed.
- 29 to 34 indicate the operation amounts of the operating levers and pedals for left running, right running, boom, stick, bucket, and attachment, respectively.
- This is an operation amount detection means that is composed of an angle sensor and the like. The detection signals output from these operation amount detection means 29 to 34 are configured to be input to the control unit 26. ing.
- the control unit 26 is configured using a microcomputer or the like.
- the control unit 26 includes the operation amount detection units 29 to 34, a pressure sensor 35 that detects the discharge pressure of the hydraulic pump P, and an accelerator dial. 36, input signals from the lock switch 28, etc., and output control commands to the electromagnetic proportional pressure reducing valves 20A to 25A, 20B to 25B, and the hydraulic lock electromagnetic switching valve 27 based on the input signals. It is configured as follows.
- the accelerator dial 36 is an operation dial for setting the engine speed.
- the accelerator dial 36 can be set in 10 stages [1] to [10]. Setting to [1] sets the engine speed to 850 rpm, setting to [5] sets it to 1450 rpm, and setting to [10] sets it to 2200 rpm.
- the control procedure in the control unit 26 will be described. First, based on the operation amount values of the operating tools input from the operation amount detection means 29 to 34, the corresponding hydraulic actuators 8 to 13 correspond. to calculate the operating speed required to obtain the required flow rate shed-shed 6 necessary to obtain the operating speed, respectively. Then, the hydraulic Akuchi Yue Isseki 8 calculates the sum of the absolute value of the required flow rate shed-shed 6 of 13, this one, the pump required flow Hitosuru.
- the current Calculate pump allowable flow 5 (maximum flow that hydraulic pump P can output).
- the pump flow rate increases when the discharge pressure of the hydraulic pump P decreases, but the first limit value 37 is reduced because the discharge pressure becomes extremely small.
- the allowable flow rate? Of the pump is larger than the maximum flow rate that can be output by the hydraulic pump P. It is restricted so that it does not fall.
- the ratio (? / Hi) of the pump allowable flow rate 5 to the required pump capacity is obtained, and this ratio is multiplied by the required flow rate i to hi 6 of each of the hydraulic actuators 8 to 13 to obtain each hydraulic pressure.
- Calculate the distribution flow a i to a 6 (r 1 to a 6 hi to hi e X? / Hi) distributed to 8 to 13 days.
- the ratio (5 /) becomes larger than "1”
- the distribution flow rate to each hydraulic actuator 8 to 13! ⁇ e becomes larger than the required flow rate ⁇ , ⁇ 6 .
- a second limiter 38 for limiting the ratio to “1” is provided.
- demanded flow rate shed-shed 6 of the hydraulic Akuchiyue Isseki 8-1 3 is set to be distributed flow ⁇ 6.
- control unit 26 controls the opening degree of the control valves 14 to 19 so that the flow rate of the pressure oil supplied to each hydraulic actuator 8 to 13 becomes the above-mentioned distribution flow rate a to a 6.
- control commands are output to the electromagnetic proportional pressure reducing valves 20 A to 25 A and 2 ⁇ B to 25 B. Opening degree of Thus to control valves 1 4-1 9, it would correspond to the distribution flow ⁇ ⁇ ⁇ 6 that distributes the output flow rate of the hydraulic pump P to the hydraulic Akuchiyue Isseki 8-1 3, and the distribution The flow rates to 6 6 are supplied to each hydraulic actuator 8 to 13 ⁇ ⁇ .
- each hydraulic actuator 8 to 13 is performed by supplying hydraulic oil from the hydraulic pump P based on the operation of the operating tool.
- the opening amount of the control valves 14 to 19 for controlling the hydraulic oil supply of the hydraulic actuators 8 to 13 is determined by the flow rate supplied to the hydraulic actuators 8 to 13 by the hydraulic pump P
- the output flow rate is controlled so as to be the distribution flow rates i i to a 6 distributed in accordance with the operation amount of the operating tool.
- the opening amount of the control valves 14 to 19 is determined based on the output flow rate of the hydraulic pump P based on the operation amount of each operating tool. dispensed will correspond to the distribution flow ⁇ ⁇ ⁇ 6, and ⁇ exiled amount ⁇ t ⁇ ⁇ 6 each hydraulic Akuchiyue Isseki 8 such that supplied to the 1 3 connection, the output flow rate of the hydraulic pump P Hydraulic factories can be appropriately distributed to 8 to 13 days.
- the control valve that performs the control of the supply of the hydraulic oil to each hydraulic factor unit corresponds to the distribution flow rate calculated based on the output flow rate of the hydraulic pump.
- the output flow of the hydraulic pump can be appropriately distributed to the hydraulic actuators, and the opening of the control valve is larger than the supply flow from the hydraulic pump. It is possible to avoid sharpening, improve composite operability, and have industrial applicability in this respect.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/582,942 US6393838B1 (en) | 1998-11-12 | 1999-11-10 | Hydraulic control device for working machines |
EP99972293A EP1048853A4 (en) | 1998-11-12 | 1999-11-10 | HYDRAULIC CONTROL DEVICE OF A WORKING MACHINE |
KR1020007007222A KR20010033699A (ko) | 1998-11-12 | 1999-11-10 | 작업기계에 있어서의 유압제어장치 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32235098A JP3750841B2 (ja) | 1998-11-12 | 1998-11-12 | 作業機械における油圧制御装置 |
JP10/322350 | 1998-11-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000029752A1 true WO2000029752A1 (fr) | 2000-05-25 |
Family
ID=18142670
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1999/006250 WO2000029752A1 (fr) | 1998-11-12 | 1999-11-10 | Dispositif hydraulique de commande pour machines de travaux |
Country Status (6)
Country | Link |
---|---|
US (1) | US6393838B1 (ja) |
EP (1) | EP1048853A4 (ja) |
JP (1) | JP3750841B2 (ja) |
KR (1) | KR20010033699A (ja) |
CN (1) | CN1288507A (ja) |
WO (1) | WO2000029752A1 (ja) |
Families Citing this family (33)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE525818C2 (sv) * | 2002-10-08 | 2005-05-03 | Volvo Constr Equip Holding Se | Förfarande och anordning för styrning av ett fordon samt datorprogramprodukt för att utföra förfarandet |
JP3985756B2 (ja) * | 2003-09-05 | 2007-10-03 | コベルコ建機株式会社 | 建設機械の油圧制御回路 |
KR101009838B1 (ko) * | 2003-12-29 | 2011-01-19 | 두산인프라코어 주식회사 | 유압펌프의 전자식 비례 밸브 제어장치 |
KR100621980B1 (ko) * | 2004-03-22 | 2006-09-14 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | 조이스틱을 이용한 중장비 주행 제어방법 |
US7260931B2 (en) * | 2005-11-28 | 2007-08-28 | Caterpillar Inc. | Multi-actuator pressure-based flow control system |
JP4721353B2 (ja) * | 2006-06-29 | 2011-07-13 | キャタピラー エス エー アール エル | 弁制御装置 |
JP2008032175A (ja) * | 2006-07-31 | 2008-02-14 | Shin Caterpillar Mitsubishi Ltd | 流体圧回路 |
JP4931048B2 (ja) | 2006-07-31 | 2012-05-16 | キャタピラー エス エー アール エル | 作業機械の制御装置 |
US7908853B2 (en) * | 2007-09-28 | 2011-03-22 | Caterpillar Inc. | Hydraulic balancing for steering management |
US7748279B2 (en) * | 2007-09-28 | 2010-07-06 | Caterpillar Inc | Hydraulics management for bounded implements |
KR100919436B1 (ko) * | 2008-06-03 | 2009-09-29 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | 복수의 가변용량형 유압펌프 토오크 제어시스템 및 그제어방법 |
WO2011140184A2 (en) * | 2010-05-04 | 2011-11-10 | Parker Hannifin Corporation | Pump power control method for preventing stall |
JP5719440B2 (ja) | 2010-09-09 | 2015-05-20 | ボルボ コンストラクション イクイップメント アーベー | 建設機械用可変容量型油圧ポンプの流量制御装置 |
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JPH053601U (ja) * | 1991-07-04 | 1993-01-19 | 住友建機株式会社 | ロードセンシング油圧回路 |
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DE3546336A1 (de) * | 1985-12-30 | 1987-07-02 | Rexroth Mannesmann Gmbh | Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher |
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EP0515639B1 (de) * | 1990-12-15 | 1995-03-08 | Barmag Ag | Hydrauliksystem |
US5167121A (en) * | 1991-06-25 | 1992-12-01 | University Of British Columbia | Proportional hydraulic control |
US5873244A (en) * | 1997-11-21 | 1999-02-23 | Caterpillar Inc. | Positive flow control system |
US6282891B1 (en) * | 1999-10-19 | 2001-09-04 | Caterpillar Inc. | Method and system for controlling fluid flow in an electrohydraulic system having multiple hydraulic circuits |
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- 1998-11-12 JP JP32235098A patent/JP3750841B2/ja not_active Expired - Fee Related
-
1999
- 1999-11-10 WO PCT/JP1999/006250 patent/WO2000029752A1/ja not_active Application Discontinuation
- 1999-11-10 US US09/582,942 patent/US6393838B1/en not_active Expired - Fee Related
- 1999-11-10 CN CN99802121A patent/CN1288507A/zh active Pending
- 1999-11-10 EP EP99972293A patent/EP1048853A4/en not_active Withdrawn
- 1999-11-10 KR KR1020007007222A patent/KR20010033699A/ko not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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DE3644736A1 (de) * | 1985-12-30 | 1988-07-14 | Rexroth Mannesmann Gmbh | Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher |
JPH04131503A (ja) * | 1990-09-20 | 1992-05-06 | Kayaba Ind Co Ltd | 油圧駆動装置 |
JPH053601U (ja) * | 1991-07-04 | 1993-01-19 | 住友建機株式会社 | ロードセンシング油圧回路 |
Also Published As
Publication number | Publication date |
---|---|
JP3750841B2 (ja) | 2006-03-01 |
EP1048853A1 (en) | 2000-11-02 |
JP2000145720A (ja) | 2000-05-26 |
KR20010033699A (ko) | 2001-04-25 |
CN1288507A (zh) | 2001-03-21 |
EP1048853A4 (en) | 2002-06-05 |
US6393838B1 (en) | 2002-05-28 |
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