EP1691084A2 - Hydraulische Anordnung zur Schwingungsdämpfung - Google Patents

Hydraulische Anordnung zur Schwingungsdämpfung Download PDF

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Publication number
EP1691084A2
EP1691084A2 EP05112154A EP05112154A EP1691084A2 EP 1691084 A2 EP1691084 A2 EP 1691084A2 EP 05112154 A EP05112154 A EP 05112154A EP 05112154 A EP05112154 A EP 05112154A EP 1691084 A2 EP1691084 A2 EP 1691084A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
arrangement according
bottom side
boom
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.)
Withdrawn
Application number
EP05112154A
Other languages
German (de)
English (en)
French (fr)
Inventor
Eric R. Anderson
Russell A. Schneidewind
William D. Robinson
Daniel L. Pflieger
Daniel W. Williams
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP1691084A2 publication Critical patent/EP1691084A2/de
Withdrawn legal-status Critical Current

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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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B21/008—Reduction of noise or vibration
    • 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
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential 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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure 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
    • F15B2211/60—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
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic arrangement for a boom-mounted work vehicle, comprising at least one hydraulic cylinder having a piston bottom side and a piston rod side, a hydraulic source, a hydraulic tank, a main control valve which is fluidly connected to the piston bottom side, the piston rod side, the hydraulic pump and the hydraulic tank. and a vibration damping device operable in a first state and in a second state. Furthermore, the invention relates to a work vehicle with a hydraulic arrangement and a method for vibration damping of a work vehicle.
  • vibration damping systems are known and usually include a valve which connects a boom cylinder with a hydraulic accumulator, the hydraulic accumulator ultimately acts as a shock absorber. All of these systems are designed to be flexible and to absorb shocks between the work area and the frame, thereby increasing ride comfort for the driver and vehicle stability. A disadvantage is that such systems are complex and expensive and take up a considerable amount of space on the vehicle.
  • the object underlying the invention is seen to provide a system and a method for improving the handling characteristics, which is based on the use of expensive, complex and space-consuming components such.
  • the system and method for the entire operating conditions of a work vehicle should be optimally used.
  • a hydraulic arrangement of the type mentioned above is provided with a vibration damping device which is fluidly connected to the piston bottom side, the piston rod side, the main control valve and the hydraulic tank, wherein in the first state of the vibration damping device, a hydraulic fluid flow from the piston bottom side is made possible to the hydraulic tank when the hydraulic fluid on the piston bottom side assumes a pressure that is higher, as a limiting pressure of a first stage, wherein the boom moves from a first received position to a second position when the hydraulic fluid flows from the piston bottom side into the hydraulic tank, wherein in the first state of the vibration damping device, the hydraulic fluid flow from the piston bottom side to the hydraulic tank of the vibration damping device is automatically interruptible when the hydraulic fluid on the piston bottom side assumes a pressure which is less than the limiting pressure of the first stage, and wherein the main control valve in a first position automatically allows hydraulic fluid from the hydraulic source to the piston bottom side flows and the boom of the second Position moves toward the first position, wherein the limiting pressure is automatically set to a limiting
  • the hydraulic arrangement comprises a valve arrangement for controlling a hydraulic cylinder, with which a boom or a working tool can be manipulated.
  • the valve assembly includes a proportional pressure relief valve and an electromagnetic switching valve which are connected in parallel with an electro-hydraulic main control valve.
  • the proportional pressure relief valve connects the piston side of the hydraulic cylinder to a hydraulic tank and the electromagnetic switching valve connects the rod side of the hydraulic cylinder to the hydraulic tank.
  • a control unit supplies control signals to the electromagnetic switching valve and to the main electro-hydraulic control valve.
  • the work vehicle 1 shows a side view of an exemplary embodiment of a work vehicle 1 equipped with a hydraulic arrangement according to the invention.
  • the work vehicle 1 comprises a chassis 10 with a cab 34, a front frame part 20, a rear frame part 30, front wheels 22, rear wheels 32, a work tool 70 a boom 50 and a hydraulic cylinder 60 which is pivotally connected to the front frame part 20 at a pivot point 60a and pivotally connected to the boom 70 at a pivot point 60b.
  • the boom 50 and hydraulic cylinder 60 are rigidly connected to the front frame area when the hydraulic cylinder 60 carries a load on the boom 50 without vibration damping.
  • the weight of the boom 50 as well as a linkage 80 and the work implement 70 are carried in a relatively stiff or fixed position with respect to the front frame portion 20, resulting in this load being predominantly taken up by the front wheels 22 and the center of gravity of the Vehicle relocated.
  • the rigidity of the cantilever 50 has the effect that the cantilever 50 is an equivalent rigid part of the front frame portion 20. This may result in the ride characteristics of the vehicle 1 being rough and stability being limited when traveling over uneven terrain at higher speeds.
  • FIG. 2 shows a schematic circuit diagram of an exemplary embodiment of the hydraulic arrangement 100 according to the invention.
  • the hydraulic arrangement 100 comprises a hydraulic cylinder 60, a hydraulic vibration damping device 110, a main electro-hydraulic control valve 120, a hydraulic pump 125, an electronic control unit 130, a mode switch 140 with at least one first and a second shift position, and a load 95, which in this case, the boom 50 and the tool 70 includes.
  • the weight of the load 95 may increase by adding material to be transported to the work implement 70.
  • the hydraulic cylinder 60 includes a piston 67 having first and second piston surfaces 67a, 67b, a piston rod 64, a piston bottom side 61, a piston rod side 62, a cylindrical wall 63, a first end wall 65, and a second end wall 66
  • the piston rod side 62 includes the second piston surface 67b, the second end wall 66, and a second cylindrical portion 63b of the first piston wall 67a cylindrical wall 63, between the second piston surface 67b and the second end wall 66.
  • the volumes of the piston bottom side 61 and the Piston rod side 62, as well as the lengths of the first and second cylindrical portions 63a, 63b, change as the hydraulic cylinder 60 retracts or retracts.
  • the vibration damping device comprises a first valve portion 111, which is hydraulically connected to the piston bottom side 61 and a hydraulic tank 90, and a second valve portion, which is connected to the piston rod side 62 and Hydraulic tank 90 connected electromagnetic switching valve 112 includes.
  • the first valve region 111 comprises an electrohydraulic 3/2-way activation valve 111a, a pilot pressure-controlled 2/2-way valve 111b and an electro-hydraulic, adjustable pressure limiting valve 111c for adjusting the vibration damping.
  • the second valve region comprises the electromagnetic closing valve 112 designed as a solenoid valve, which connects the piston rod side 62 with the hydraulic tank 90.
  • the vibration damping device 110 is hydraulically connected to the piston bottom side 61, the piston rod side 62 and the hydraulic tank 90 at the connection points 110a, 110b and 110c.
  • FIG. 4 schematically shows the signal flow which is received or transmitted by the control unit 130.
  • the control unit 130 sends control signals to the main electro-hydraulic control valve 120 and to the vibration damping device 110, in particular to the electro-hydraulic activation valve 111a for vibration damping, to the electro-hydraulic, controllable
  • the control unit 130 calculates the transmitted signals based on the signals received from a pressure transducer 145, an angle sensor 135, the mode switch 140, and a joystick 150.
  • FIG. 5 schematically shows a part of the hydraulic circuit diagram of FIG. 2.
  • the main electromagnetic control valve 120, the variable hydraulic pump 125 and the hydraulic tank 90 are shown.
  • the electro-hydraulic main control valve 120 is a directional control valve known in the art.
  • the main control valve 120 is hydraulically connected to the piston bottom side 61, the piston rod side 62, the hydraulic pump 125, and the hydraulic tank 90 via the ports 120 a, 120 b, 120 c, and 120 d, and is controlled by signals sent from the control unit 130.
  • the main control valve 120 is controllable via at least two modes: (1) the regular working mode in which the vibration damping function is deactivated and the main control valve 120 is operated as a simple directional control valve for controlling the conventional work functions, and (2) the vibration damping mode in which the main control valve 120 is operated as an addition to the vibration damping device 110.
  • the control unit 130 is known in the art and may be configured as a hardwired system, as a switch relays system, or as a digital electronic system.
  • the controller 130 controls the main electrohydraulic control valve 120 in the regular Operating mode via signals sent to it by a joystick 150.
  • the mode switch 140 is in its second switch position, the main electro-hydraulic control valve 120 is operated according to a second mode, e.g. B. a vibration damping mode.
  • a second mode e.g. B. a vibration damping mode.
  • An exemplary embodiment of the mode switch 140 is a toggle switch operated by an operator that is well known to those skilled in the art.
  • FIG. 7 shows a system according to the prior art, which provides for the use of a hydraulic accumulator 160 for implementing a vibration damping.
  • a hydraulic accumulator 160 has a complex structure and is large in volume.
  • the hydraulic accumulator 160 may include an input 161, a piston 162, a gas chamber 163 containing a gas 163a, a cylindrical hydraulic accumulator wall 164 having an inner surface 164a, a first end wall 165 having one within the hydraulic accumulator 160 located first end surface 165a, a second end wall 166 and a storage chamber 167 and a gas inlet 168 include.
  • the storage chamber 167 includes a first exposed barrel portion 164a ', which is a portion of the inner surface 164a exposed to a hydraulic fluid flowing into the hydraulic accumulator 160, the first end wall 165, and a first piston surface 162a.
  • the gas chamber 163 includes the second end wall 166, a second piston surface 162 b, and a second exposed cylinder portion 164 a ", which is a portion of the inner surface 164 a exposed to the gas 163 a and disposed between the second piston surface 162 a and the second end wall 166.
  • the length of the second exposed cylindrical portion 164a "changes, flows as soon as pressurized hydraulic fluid in the hydraulic reservoir 160 and flows out.
  • the volume of the gas chamber 163 changed under pressure from the inflowing hydraulic fluid from a first volume V 1 to a second volume V 2 as shown in Figures 8 and 9.
  • the accumulator pressure P A corresponds approximately to the fluid pressure P F of the hydraulic fluid in the hydraulic accumulator 160th
  • FIG. 6 shows an exemplary inventive algorithm 200 for the alternative vibration damping described above.
  • the process for this exemplary algorithm 200 includes three essential sections: (1) setting the mode 200a, (2) comparing and calculating 200b, and (3) adjusting 200c.
  • step 201 The setting of the mode 200a for the process begins with step 201 with a check of the position of the mode switch 140. If the mode switch 140 is not in its second switch position, step 205 is proceeded to, in which the vibration damping device 110 is brought into a second state or is deactivated or remains in the second state or disabled, if it was already in the second state or disabled.
  • step 205 is proceeded to, in which the vibration damping device 110 is brought into a second state or is deactivated or remains in the second state or disabled, if it was already in the second state or disabled.
  • steps 210 and 220 In which an angle value A R of the angle sensor 135 and a static initial pressure P S from the pressure transducer 145 is determined and the vibration damping device 110 is brought into a first state.
  • the value for the initial pressure P s is determined from filtered signals of the pressure transducer 145 in order to minimize the influence of recorded instantaneous pressure peaks.
  • the comparing and calculating section 200b starts immediately after the mode setting section 200a, and starts with step 230, where it is determined whether a changed angle value A C for the boom 50 has occurred by operating the joystick 150. If a changed angle value A C has been determined on the basis of an actuation of the joystick 150, then the process proceeds to step 210.
  • step 230 If it is determined in step 230 that the modified angle value A C was not due to an actuation of the joystick 150, then the calculation is continued in step 240.
  • ⁇ A and P s are then used in step 245 to calculate a theoretical accumulator pressure P A based on the model illustrated in FIGS. 8 and 9.
  • the storage pressure P A for this particular hydraulic accumulator 160 is based on the volume changes of the gas chamber 163 as a result of the positional change of the piston 162 with a constant amount of gas 163a in the gas chamber 163.
  • the displacement of the piston 162 is calculated from the amount of hydraulic fluid discharged from the Piston bottom side 61 flows into the hydraulic accumulator 160 and corresponds to a volume which is needed to the Boom 50 to move the angular difference .DELTA.A.
  • the accumulator pressure P A can be calculated differently if other hydraulic accumulators 160 are used as a model.
  • step 250 The adjustment begins in step 250 with the adjustment of the electrohydraulic proportional pressure relief valve 111c to the corresponding calculated accumulator pressure P A.
  • step 260 the main electro-hydraulic control valve 120 is placed in position # 1, and the hydraulic pump 125 is adjusted accordingly to reach P A. If there is no change in the switch position of the mode switch 140 in step 270, the process continues to step 230 and further adjustments are made as needed. If a change in the switch position of the mode switch 140 is detected in step 270, then the process proceeds to step 201.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP05112154A 2005-02-11 2005-12-14 Hydraulische Anordnung zur Schwingungsdämpfung Withdrawn EP1691084A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/056,684 US7165395B2 (en) 2005-02-11 2005-02-11 Semi-active ride control for a mobile machine

Publications (1)

Publication Number Publication Date
EP1691084A2 true EP1691084A2 (de) 2006-08-16

Family

ID=36216801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05112154A Withdrawn EP1691084A2 (de) 2005-02-11 2005-12-14 Hydraulische Anordnung zur Schwingungsdämpfung

Country Status (3)

Country Link
US (1) US7165395B2 (ja)
EP (1) EP1691084A2 (ja)
JP (1) JP2006219975A (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012010097A1 (zh) * 2010-07-21 2012-01-26 湖南山河智能机械股份有限公司 液压挖掘机主阀及具有其的液压挖掘机
CN104153406A (zh) * 2014-08-05 2014-11-19 山河智能装备股份有限公司 一种具有针对不同工况切换液压回路的挖掘机
KR20190131015A (ko) * 2017-03-31 2019-11-25 스미도모쥬기가이고교 가부시키가이샤 쇼벨

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EP1914353A3 (en) * 2006-10-19 2011-04-20 Hitachi Construction Machinery Co., Ltd. Construction machine
GB2445165A (en) * 2006-12-29 2008-07-02 Agco Sa Vibration damping for load carrier
DE102007048697A1 (de) * 2007-10-11 2009-04-16 Deere & Company, Moline Hydraulische Hubeinrichtung
US7793740B2 (en) 2008-10-31 2010-09-14 Caterpillar Inc Ride control for motor graders
CN102869839B (zh) * 2010-12-24 2014-05-07 株式会社小松制作所 轮式装载机的行驶减振器控制装置
US8899143B2 (en) * 2011-06-28 2014-12-02 Caterpillar Inc. Hydraulic control system having variable pressure relief
CA2869935C (en) 2012-04-11 2020-01-07 Clark Equipment Company Lift arm suspension system for a power machine
US9055719B2 (en) * 2012-12-06 2015-06-16 Deere & Company Method and apparatus for ride control activation
US10030364B2 (en) 2015-10-26 2018-07-24 Caterpillar Inc. Hydraulic system having automatic ride control
WO2019014472A1 (en) * 2017-07-14 2019-01-17 Eaton Intelligent Power Limited INTELLIGENT DRIVING CONTROL
CN107989111B (zh) * 2017-11-21 2021-02-19 黎明液压有限公司 装载机液压***自动控制***
US10994778B2 (en) * 2018-12-20 2021-05-04 Rce Equipment Solutions, Inc. Tracked vehicle with steering compensation
US11091899B1 (en) 2020-08-19 2021-08-17 Deere & Company Hydraulic fluid warm-up using ride control circuit
US11421395B1 (en) 2021-02-09 2022-08-23 Deere & Company Pin actuation system and method
US11832543B2 (en) 2021-05-19 2023-12-05 Deere & Company Sprayer boom control for improved ride and control

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Publication number Priority date Publication date Assignee Title
EP0378129B1 (en) * 1989-01-13 1994-11-30 Hitachi Construction Machinery Co., Ltd. Hydraulic system for boom cylinder of working apparatus
US5733095A (en) * 1996-10-01 1998-03-31 Caterpillar Inc. Ride control system
DE10133616A1 (de) * 2001-07-13 2003-01-30 Bosch Rexroth Ag Hydraulische Steueranordnung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012010097A1 (zh) * 2010-07-21 2012-01-26 湖南山河智能机械股份有限公司 液压挖掘机主阀及具有其的液压挖掘机
CN104153406A (zh) * 2014-08-05 2014-11-19 山河智能装备股份有限公司 一种具有针对不同工况切换液压回路的挖掘机
KR20190131015A (ko) * 2017-03-31 2019-11-25 스미도모쥬기가이고교 가부시키가이샤 쇼벨
EP3604692A4 (en) * 2017-03-31 2021-05-26 Sumitomo Heavy Industries, Ltd. SHOVEL
KR102466641B1 (ko) 2017-03-31 2022-11-11 스미도모쥬기가이고교 가부시키가이샤 쇼벨

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Publication number Publication date
US7165395B2 (en) 2007-01-23
JP2006219975A (ja) 2006-08-24
US20060179831A1 (en) 2006-08-17

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