EP1897846A2 - Appareil de chargement - Google Patents

Appareil de chargement Download PDF

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Publication number
EP1897846A2
EP1897846A2 EP07115419A EP07115419A EP1897846A2 EP 1897846 A2 EP1897846 A2 EP 1897846A2 EP 07115419 A EP07115419 A EP 07115419A EP 07115419 A EP07115419 A EP 07115419A EP 1897846 A2 EP1897846 A2 EP 1897846A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
charger
hydraulic cylinder
control pressure
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.)
Granted
Application number
EP07115419A
Other languages
German (de)
English (en)
Other versions
EP1897846B1 (fr
EP1897846A3 (fr
Inventor
Marcus Bitter
Richard Tudor
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 EP1897846A2 publication Critical patent/EP1897846A2/fr
Publication of EP1897846A3 publication Critical patent/EP1897846A3/fr
Application granted granted Critical
Publication of EP1897846B1 publication Critical patent/EP1897846B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/003—Systems with load-holding valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F17/00—Safety devices, e.g. for limiting or indicating lifting force
    • B66F17/003—Safety devices, e.g. for limiting or indicating lifting force for fork-lift trucks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or 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
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a charger with a hydraulically actuated boom, a sensor for monitoring the load condition on the charger and a hydraulic arrangement for actuating the boom and / or attached to the boom tool, wherein the hydraulic arrangement at least one hydraulic cylinder, at least one hydraulically controllable control unit for Controlling the at least one hydraulic cylinder, a hydromechanical actuator for generating hydraulic control pressure signals for the at least one control unit, a hydraulic source, a hydraulic tank and an electronic control unit.
  • the WO 2004/007339 A1 discloses such a system.
  • a tilting moment acting on the vehicle is detected by sensors and fed to an electronic control.
  • several hydraulic cylinders for lifting, lowering and telescoping a telescopic boom and an electro-hydraulic control of the hydraulic cylinder are provided.
  • the system provides that, when approaching a predetermined threshold for the stalling torque, the hydraulic functions to operate the hydraulic cylinders are slowed down before the complete stoppage of the hydraulic cylinders occurs.
  • the load signal is further processed electronically and the operating possibilities are reduced by the operator or the actuation is prevented.
  • the more mature the technique is, for. B. by electronic control units, the easier is the intervention by the electronics.
  • the object underlying the invention is seen to provide a charger of the type mentioned, by which the aforementioned disadvantages are overcome.
  • a charger of the type mentioned above is formed such that with at least one control pressure line extending between the actuator and the control unit, the control pressure varying means are connected, with which, depending on a sensor signal supplied by the sensor, the control pressure generated by the actuator is variable.
  • the control pressure varying means the operability of the hydraulically controlled control device is influenced such that the pressure in the control pressure line is reduced, so that the manipulated variable is reduced at the control unit and thus controlled via the control unit volume flow of hydraulic fluid for the hydraulic cylinder.
  • the control pressure in the control pressure line is thereby reduced more, the closer one approaches a critical value for the load state, which is predetermined by the electronic control unit.
  • the functions of the hydraulic cylinder are first slowed down and then finally completely prevented.
  • control pressure varying means comprise at least one controllable by the electronic control unit electro-hydraulic pressure relief valve.
  • the electrohydraulic pressure relief valve can be increasingly opened depending on the load signal or overload signal supplied by the sensor. The further you approach the preset threshold, the greater the risk that the vehicle will tip over, and the lower you are set the pressure relief valves. Due to the resulting lower control pressure, the valve spool of the control unit is deflected less, whereby the control units send less flow to the hydraulic cylinder, which then slows down to a standstill. In the opposite direction of movement, the control unit can be operated as usual.
  • a plurality of hydraulic cylinders are arranged in the hydraulic arrangement and thus a plurality of control devices can be hydraulically adjustable for controlling the hydraulic cylinder can be used.
  • a plurality of electro-hydraulic pressure relief valves can be used correspondingly, which are adjusted by the electronic control unit in response to the sensor signal.
  • control pressure varying means comprise at least one controllable by the electronic control unit electro-hydraulic pressure reducing valve, which is arranged directly in a control pressure line for the valve spool of the control unit.
  • the electrohydraulic pressure reducing valve can be controlled as a function of the load signal or overload signal supplied by the sensor. The further you approach the preset threshold, the greater the risk that the vehicle tilts, and the higher the control pressure for the valve spool is throttled or reduced by the pressure reducing valve. Due to the resulting lower control pressure, the valve spool of the controller is deflected less, causing the controllers less flow to Send hydraulic cylinder, which then slows down to a stop. In the opposite direction of movement, the control unit can be operated as usual.
  • a plurality of hydraulic cylinders are arranged in the hydraulic arrangement and thus a plurality of control devices can be hydraulically adjustable for controlling the hydraulic cylinder can be used.
  • a plurality of electro-hydraulic pressure reducing valves can be used correspondingly, which are adjusted by the electronic control unit in dependence of the sensor signal.
  • the hydromechanical actuator is designed as a joystick.
  • valves are actuated by appropriate mechanical deflection of a control lever, which are connected to the hydraulic source and the control pressure line and generate a control pressure for the control unit of the hydraulic cylinder.
  • the charger is preferably designed as a telescopic loader, wherein the boom via a first hydraulic cylinder in its angle of attack and a second hydraulic cylinder in its length is variable and wherein a third hydraulic cylinder may be provided with the on Outrigger arranged tool is pivotable.
  • a third hydraulic cylinder may be provided with the on Outrigger arranged tool is pivotable.
  • the charger comprises a front loader, wherein the boom is designed as a rocker of a front loader, which is variable in its angle of attack via a first or a first and a second hydraulic cylinder.
  • a third hydraulic cylinder may be provided, with which a tool provided on the boom, for example a loading shovel or a loading fork, can be pivoted.
  • the senor is designed and arranged such that a critical load condition on the charger can be detected.
  • the sensor may be arranged, for example, on an axle of the vehicle and signal a critical state of charge with a correspondingly high, one-sided load.
  • strain gauges or force sensors can be used.
  • the sensor at one position other suitable location and define, for example, the inclination of a vehicle frame relative to the vehicle axle as a critical state of charge state.
  • FIG. 1 shows a charger 10 is shown in the form of a telescopic loader.
  • the telescopic loader has a frame 12, on which a boom 14 is articulated.
  • the frame is supported by a front axle 16 and a rear axle 18 with respective front and rear wheels 20, 22.
  • the boom 14 is formed as a telescopic boom and is articulated via a hydraulic cylinder 24 in its angle relative to the frame 12 adjustable.
  • a second hydraulic cylinder is arranged inside the boom 14 (not shown) and allows the extension and retraction (telescoping) of the boom.
  • a third hydraulic cylinder is disposed at the free end of the boom 14 in the interior and allows the pivoting or tilting of a loading tool 26th
  • the charger 10 has a hydraulic source 28 and a hydraulic tank 30, which are arranged below the vehicle body and serve to supply the hydraulic components.
  • the hydraulic components are shown substantially in FIG.
  • FIG. 2 shows a hydraulic arrangement 36 provided for the charger 10.
  • the hydraulic arrangement 36 comprises the hydraulic cylinder 24, and optionally the hydraulic cylinder (not shown) for telescoping the boom and tilting the loading tool.
  • the hydraulic cylinder 24 is connected via a first and second hydraulic supply line 38, 40 with a hydraulically controllable control unit 42, via which the connection of the supply lines 38, 40 with the hydraulic pump 28 and the hydraulic tank 30 can be produced.
  • a load-holding valve 44 is arranged in the hub Indeeden chamber of the hydraulic cylinder 24 associated supply line 40.
  • the load-holding valve includes an in the direction of Control unit 42 openable pressure limiting valve 46 which is arranged in the supply line 40 and via control pressure lines 48, 50 which are connected to two supply lines 38, 40 can be opened, and arranged in a bypass line and in the direction of the hydraulic cylinder 24 opening check valve 52.
  • the load-holding valve 44 serves to ensure that in the event of a pipe break on the lifting side of the hydraulic cylinder 24, no hydraulic fluid can escape and the hydraulic cylinder 24 maintains its position.
  • the control unit 42 comprises three slide positions, one for lifting, one for lowering and another for holding the hydraulic cylinder.
  • the control unit 42 is designed as a hydraulically controllable proportional valve and can be hydraulically controlled or adjusted via corresponding control pressure lines 54, 56.
  • the control pressure is generated by the hydromechanical control device 34, which is designed as a joystick.
  • the operating device 34 has mechanically actuatable valves 58, 60, for example by moving the joystick, which establish a connection or disconnection of the hydraulic pump 28 with the control pressure lines 54, 56.
  • the mechanically operable valves 58, 60 are preferably designed as pressure reducing valves.
  • a joystick or operating lever located on the operating device 34 is pushed forward, whereby the actuation of the valve 58 takes place.
  • the control pressure line 56 is acted upon by a hydraulic pressure generated by the hydraulic pump 28, whereupon the control unit 42 is moved to its lifting position and the hydraulic cylinder 24 on the lift side is filled with hydraulic fluid, so it is extended.
  • a corresponding opposite actuation of the actuating lever would cause actuation of the valve 60, whereupon the control pressure line 54 filled with hydraulic fluid and the control pressure valve 42 is moved to the lowering position, so the hydraulic cylinder 24 would be drained.
  • control pressure line 54 is connected to an electrohydraulic pressure relief valve 62 connected to the hydraulic tank 30.
  • the pressure relief valve 62 causes the pressure prevailing in the control pressure line 54 control pressure is reduced. If a preset limit pressure is reached or exceeded by the control pressure, the pressure relief valve 62 opens increasingly, so that more and more hydraulic fluid flows into the hydraulic tank 30, resulting in that the adjustment of the control unit 42 is reduced by the control pressure line 54 and thus the actuation the hydraulic cylinder 24, in this case the lowering of the hydraulic cylinder 24, is slowed down.
  • the other control pressure line 56 may be connected to such a pressure relief valve 62. In this case, then the lifting of the hydraulic cylinder 24 would be slowed down.
  • the control of the pressure relief valve 62 is performed by the electronic control unit 64, which in turn receives control signals from a load sensor 66. Depending on the load condition, the sensor 66 signals a more or less critical load condition. If one approaches the critical load state, the control signal emitted by the electronic control unit 64 also amplifies to adjust the overpressure valve 62, which is then increasingly opened, so that hydraulic fluid from the control pressure line 54 is increasingly drained and the control pressure decreases.
  • the adjustment or the gain of the control signal is preferably proportional to the signal supplied by the sensor.
  • the sensor is preferably arranged on the rear axle 18 of the charger 10.
  • the sensor 66 is designed as a strain gauge and registers or detects the deflection of the rear axle 18. From the signal values for the deflection can then be closed to the loading or unloading of the rear axle 18. If the load on the rear axle 18 decreases progressively, this may indicate a critical load condition, namely at the latest when no load on the rear axle 18 is detected or signaled. In this case, the charger 10 begins to tip over. The same is also conceivable for the front axle 16.
  • FIG 2a shows an alternative embodiment of the hydraulic arrangement, wherein the control pressure line 54 is provided with an electro-hydraulic pressure reducing valve 62 ', wherein the connection line to the hydraulic tank 30, which is provided in the embodiment of Figure 2, omitted.
  • the pressure reducing valve 62 ' also causes here that the pressure prevailing in the control pressure line 54 control pressure is reduced or throttled. Should a preset limit pressure be reached or exceeded by the control pressure, the pressure reducing valve 62 'closes, so that the control pressure in the control pressure line 54 decreases, resulting in that the adjustment of the control unit 42 is reduced by the control pressure line 54 and thus the actuation of the Hydraulic cylinder 24, in this case the lowering of the hydraulic cylinder 24, is slowed down.
  • the other control pressure line 56 may be connected to such a pressure reducing valve 62 '. In this case, then the lifting of the hydraulic cylinder 24 would be slowed down.
  • the control of the pressure reducing valve is also carried out here by the electronic control unit 64, which in turn receives control signals from a load sensor 66. Depending on the load condition, the sensor 66 signals a more or less critical load condition. If one approaches the critical load state, the control signal emitted by the electronic control unit 64 also amplifies to adjust the pressure reducing valve 62 ', which is then increasingly closed, so that the control pressure decreases.
  • the Adjustment or the gain of the control signal is preferably proportional to the signal supplied by the sensor.
  • the sensor is also preferably arranged on the rear axle 18 of the charger 10 and is formed in an analogous manner to the embodiment shown in Figure 2.
  • FIG. 2a likewise shows the arrangement of only one hydraulic cylinder 24.
  • further hydraulic cylinders (not shown) can be used in parallel, which can be actuated in the same way by an actuating device 34 and also in a hydraulic arrangement 36, as described in US Pat Figure 2a is shown, are involved.
  • the control pressure line 56 with which the lifting position of the control unit 42 and thus the lifting of the hydraulic cylinder 24 can be controlled, would also be provided or connected to an electrohydraulic pressure reducing valve 62 '.
  • FIG. 3 shows a further embodiment of a charger 10 in the form of a tractor 68 with front loader 70, wherein for the same components of the charger 10, such as frame 12, front axle 16, rear axle 16, wheels 20, 22, loading tool 26 and cabin 32, the same reference numerals be valid.
  • the rockers 70 which are arranged on both sides of the tractor 68, a boom, by the actuation in certain situations and overcharging critical load conditions of the charger 10 can be caused.
  • the hydraulic cylinders 74 arranged to actuate the rockers 70 and the hydraulic cylinders 76 arranged to actuate the loading tool 26 are operated analogously to the hydraulic arrangement 36 shown in FIG.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Geology (AREA)
  • General Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Transportation (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mining & Mineral Resources (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Component Parts Of Construction Machinery (AREA)
EP07115419A 2006-09-08 2007-08-31 Appareil de chargement Not-in-force EP1897846B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006042370A DE102006042370A1 (de) 2006-09-08 2006-09-08 Ladegerät

Publications (3)

Publication Number Publication Date
EP1897846A2 true EP1897846A2 (fr) 2008-03-12
EP1897846A3 EP1897846A3 (fr) 2009-06-17
EP1897846B1 EP1897846B1 (fr) 2012-06-06

Family

ID=38683492

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07115419A Not-in-force EP1897846B1 (fr) 2006-09-08 2007-08-31 Appareil de chargement

Country Status (5)

Country Link
US (1) US7717664B2 (fr)
EP (1) EP1897846B1 (fr)
JP (1) JP5383985B2 (fr)
DE (1) DE102006042370A1 (fr)
ES (1) ES2389135T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2476641A1 (fr) * 2011-01-18 2012-07-18 Johannes Gerardus Bleekman Un dispositif de levage et un système hydraulique par conséquent, ainsi qu'un procédé pour adapter le même

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4823767B2 (ja) * 2006-05-31 2011-11-24 日立建機株式会社 双腕作業機械
EP2637961B1 (fr) 2010-11-12 2016-04-20 JLG Industries Inc. Système de surveillance de stabilité longitudinale
AU2011353519B2 (en) * 2011-01-04 2015-09-10 Crown Equipment Corporation Materials handling vehicle having a manifold located on a power unit for maintaining fluid pressure at an output port at a commanded pressure corresponding to an auxiliary device operating pressure
ITTO20110399A1 (it) * 2011-05-06 2012-11-07 Merlo Project Srl Veicolo sollevatore
US10611618B2 (en) * 2015-03-27 2020-04-07 Chang Zhou Current Supply Company Of Jiangsu Electric Power Company Amplitude limiting system of insulated aerial work platform
CA170432S (fr) * 2016-04-06 2017-11-23 Manitou Bf Chariot élévateur
US10401249B2 (en) 2016-10-11 2019-09-03 Caterpillar Inc. Methods and systems for detecting unbalanced payload condition in machines
JP2022148641A (ja) * 2021-03-24 2022-10-06 日立建機株式会社 建設機械
USD1122556S1 (en) * 2022-07-06 2026-04-14 Lingong Group Jinan Heavy Machinery Co., Ltd Forklift
USD1001412S1 (en) * 2022-10-11 2023-10-10 Manitou Bf Forklift truck

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05202535A (ja) 1992-01-29 1993-08-10 Komatsu Ltd 油圧ショベルの転倒防止装置
WO2004007339A1 (fr) 2002-07-12 2004-01-22 J.C. Bamford Excavators Limited Systeme de commande pour appareil de manipulation de charge

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
GB1528741A (en) * 1974-10-12 1978-10-18 Liner Concrete Machinery Load handling vehicle
JPS5819825B2 (ja) * 1975-08-29 1983-04-20 株式会社クボタ シヨベルロ−ダテントウボウシソウチ
US4316697A (en) * 1978-12-13 1982-02-23 Kabushiki Kaisha Komatsu Seisakusho Front-loading hydraulic excavator
JP2996762B2 (ja) * 1991-04-16 2000-01-11 株式会社小松製作所 作業機干渉防止回路
JPH08302753A (ja) * 1995-05-12 1996-11-19 Hitachi Constr Mach Co Ltd 油圧建設機械
JPH11293712A (ja) * 1998-04-14 1999-10-26 Hitachi Constr Mach Co Ltd 油圧制御装置
DE19853523C1 (de) * 1998-11-20 2000-03-09 Schaeff Karl Gmbh & Co Fahrbarer Schaufellader
JP2004131208A (ja) * 2002-10-08 2004-04-30 Hitachi Constr Mach Co Ltd ホイール式作業機械
DE102004031248A1 (de) * 2004-06-29 2006-02-09 Plustech Oy Ladegerät
JP4034763B2 (ja) * 2004-07-12 2008-01-16 有限会社ホロキタ セミトレーラ
US7210292B2 (en) * 2005-03-30 2007-05-01 Caterpillar Inc Hydraulic system having variable back pressure control

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05202535A (ja) 1992-01-29 1993-08-10 Komatsu Ltd 油圧ショベルの転倒防止装置
WO2004007339A1 (fr) 2002-07-12 2004-01-22 J.C. Bamford Excavators Limited Systeme de commande pour appareil de manipulation de charge

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2476641A1 (fr) * 2011-01-18 2012-07-18 Johannes Gerardus Bleekman Un dispositif de levage et un système hydraulique par conséquent, ainsi qu'un procédé pour adapter le même
NL2006021C2 (nl) * 2011-01-18 2012-07-19 Johannes Gerardus Bleekman Hefinrichting en hydraulisch systeem daarvoor, alsmede werkwijze voor het aanpassen daarvan.

Also Published As

Publication number Publication date
US7717664B2 (en) 2010-05-18
EP1897846B1 (fr) 2012-06-06
US20080063501A1 (en) 2008-03-13
EP1897846A3 (fr) 2009-06-17
ES2389135T8 (es) 2012-11-08
DE102006042370A1 (de) 2008-03-27
JP2008063935A (ja) 2008-03-21
ES2389135T3 (es) 2012-10-23
JP5383985B2 (ja) 2014-01-08

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