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EP1762535A2 - Engin roulant du type muni d'un bras et procédé pour celui-ci - Google Patents

Engin roulant du type muni d'un bras et procédé pour celui-ci Download PDF

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Publication number
EP1762535A2
EP1762535A2 EP06120251A EP06120251A EP1762535A2 EP 1762535 A2 EP1762535 A2 EP 1762535A2 EP 06120251 A EP06120251 A EP 06120251A EP 06120251 A EP06120251 A EP 06120251A EP 1762535 A2 EP1762535 A2 EP 1762535A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
boom
hydraulic cylinder
control unit
sensor
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
EP06120251A
Other languages
German (de)
English (en)
Other versions
EP1762535B1 (fr
EP1762535A3 (fr
Inventor
Marcus Bitter
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 EP1762535A2 publication Critical patent/EP1762535A2/fr
Publication of EP1762535A3 publication Critical patent/EP1762535A3/fr
Application granted granted Critical
Publication of EP1762535B1 publication Critical patent/EP1762535B1/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
    • 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
    • B66F9/065—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 non-masted
    • B66F9/0655—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 non-masted with a telescopic boom
    • 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
    • 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 and a method for a charger with a hydraulic arrangement for raising and lowering a boom, wherein the hydraulic arrangement comprises at least one hydraulic conveying means, a hydraulic tank, a hydraulic cylinder with a lifting and a vertical supply line, a control device connected to the supply lines for controlling the hydraulic cylinder, a first hydraulic line connecting the hydraulic cylinder to the hydraulic tank and provided with a first switching valve, a second hydraulic line connecting the hydraulic cylinder to the hydraulic tank or the vertical supply line and a second switching valve, a lifting-side load-holding valve device and a control unit for Switching the switching valves includes.
  • Chargers are known, for example, wheel loaders, telescopic loaders or other construction, agricultural or forestry vehicles, which have a hydraulic arrangement for a hydraulic cylinder for raising and lowering a boom, with a floating position for the hydraulic cylinder can be realized.
  • the floating position may be advantageous if work should be done with the charger, in which the working tool should be performed on the ground and as contour true to the ground surface.
  • a hydraulic arrangement for a telescopic loader which has a hydraulic cylinder for raising and lowering a boom and for which a floating position is feasible.
  • the hydraulic arrangement further has a load-holding valve arrangement, as is required for telescopic loader to secure the boom against hose break or unintentional lowering.
  • hydraulic lines are provided, which connect the two chambers of a hydraulic cylinder electronically controllable with a hydraulic tank. At the same time the safety function of the load-holding valve arrangement is maintained.
  • a disadvantage is that an activation of the floating position is possible, even if the boom is in a position not supported on the ground. In such a case, the fact that the lifting side of the hydraulic cylinder is connected in the floating position with the hydraulic tank, the boom would fall uncontrollably and possibly cause or take damage.
  • the problem underlying the invention is seen to provide a charger with a hydraulic arrangement for a boom, in which an activation of the floating position takes place without the boom can fall uncontrollably.
  • a charger of the type mentioned in which a at least one position of the boom or hydraulic cylinder signalizing sensor and Activation means for switching to a floating position for the hydraulic cylinder and controllable control means for lowering the boom are provided, wherein the control unit is designed such that the lowering of the boom and / or switching to the floating position in response to a signal supplied by the sensor , After activation of the floating position by activating means, it is first determined whether the boom is in a raised position or position. This determination is made by detecting and processing the position of the cantilever signal sensor signal.
  • the controllable control means for lowering the boom and the switching valves are controlled by the control unit accordingly until the boom assumes its preferably fully lowered position. Only then does the control unit perform a circuit and / or control of the corresponding components of the hydraulic arrangement in a floating position for the hydraulic cylinder or boom. However, if the control unit, after activation for switching to a floating position, determines that the boom is in its preferably fully lowered position or position, which is signaled by a corresponding sensor signal, then the control unit directly, ie without performing a controlled lowering operation executed for the boom, the circuit and / or control of the corresponding components of the hydraulic arrangement in a floating position for the hydraulic cylinder or boom. This ensures that when an activation of the floating position is made, the boom is in a lowered position or position before the corresponding switching or control operations for a floating position.
  • the hydraulic line connecting the hydraulic cylinder to the hydraulic tank on the vertical side preferably leads directly from the first switching valve into the hydraulic tank, but it is also conceivable to establish the connection via the control unit so that the hydraulic line is connected to the supply line on the stroke side between the load holding valve device and the control unit , In this case, the control valve in its neutral position produces the lift-side connection to the tank, wherein the load on the hydraulic cylinder is still held by the load-holding valve device.
  • the first switching valve is brought into a closed position, so that the connection to the rod side of the hydraulic cylinder is interrupted.
  • controllable control means for lowering the boom comprise a controllable pressure limiting device, wherein preferably a manually switchable control device for the hydraulic arrangement is used.
  • control unit can also be formed electrically or hydraulically switchable.
  • a pressure limiting device can be realized by a controllable pressure relief valve or pressure relief valve, which can be brought from a closed valve position preferably proportionally adjustable in an open position. In this case, preferably in a closed position, a hydraulic flow is interrupted, whereas in a fully open position an unhindered hydraulic flow is permitted. Appropriate intermediate position (not fully open positions) provide a throttled hydraulic flow.
  • a volume flow passed through the pressure limiting valve be controlled or regulated in proportion to a control signal.
  • a correspondingly adjustable throttle valve in which the passage cross-section can be controlled or regulated correspondingly in proportion to a control signal.
  • Other types of valves or devices are conceivable with which a control of the volume flow can be carried out in response to a control signal.
  • the controllable pressure limiting device is arranged such that when the first and second switching valve open a stroke-side hydraulic oil flow is adjustable or controllable.
  • a positioning of the pressure limiting device between the lifting side of the hydraulic cylinder and the hydraulic tank is critical, ie the pressure limiting device can be arranged both between the lifting side of the hydraulic cylinder and the first or second switching valve and between the first or the second switching valve and the hydraulic tank, so that at open switching valves, the outflow from the stroke side of the hydraulic cylinder to the hydraulic tank can be controlled or controlled or regulated.
  • a corresponding closing control value is set at the pressure limiting device, in which the pressure limiting device is closed or almost closed.
  • both switching valves are opened.
  • a control process for the pressure limiting device is initiated so that the pressure limiting device opens slowly.
  • a designed as a pressure relief valve pressure limiting device of the set or regulated pressure limiting value a value below the stroke pressure in the hydraulic cylinder, the boom begins to lower.
  • This lowering can be detected and utilized by the sensor as a change in the position or position of the arm, so that the pressure limiting device can be controlled such that a certain lowering speed is not exceeded.
  • independence from the load condition of the boom is achieved. If the boom does not lower further, it can be assumed that the boom is resting on the ground.
  • a corresponding opening control value can be set at the pressure limiting device, in which the pressure limiting device is fully or almost completely opened.
  • the pressure limiting device is fully or almost completely opened.
  • the boom can move freely or floating, with an unimpeded hydraulic flow between the hydraulic cylinder and hydraulic tank can take place.
  • a pressure limiting device designed as a throttle valve instead of a pressure limiting value, the passage cross section of the throttle valve is regulated from a closed to an open passage cross section value. It is conceivable as an additional safety measure to provide speed monitoring during the floatation operation which prevents the boom from exceeding a certain speed.
  • the pressure relief device can be closed to not allow a certain maximum permissible speed exceed.
  • the maximum permissible speed can additionally be made dependent on the extension length of the lifting cylinder, for example, to limit the lowering of the boom from high working heights to lowering the boom from lower working heights with regard to the lowering speed.
  • controllable control means for lowering the boom comprise a proportionally controllable control of the control device.
  • control of the control unit can be dispensed with a separate pressure limiting device.
  • the control unit is automatically controlled directly or indirectly by the control unit and placed in a lowered position, wherein the switching valves are closed.
  • the hydraulic cylinder empties in the conventional manner via the existing load-holding valve device, so that the boom is lowered.
  • the lowering is detected as a change in the boom position metrologically and utilized by the control unit such that the control or regulation of the control unit does not allow falling below a predetermined lowering speed.
  • This can be supported by the use of pressure compensators in the control unit, which correspond to the prior art and are usually used to keep the volume flow of a control unit load-independent and pump speed independent constant.
  • pressure compensators in the control unit which correspond to the prior art and are usually used to keep the volume flow of a control unit load-independent and pump speed independent constant.
  • independence from the loading state of the boom is achieved. Does the boom no longer sink? continue from, it can be assumed that the boom rests on the ground and the control unit is switched to its neutral position. Subsequently or simultaneously, the two switching valves are opened, so that sets a floating position.
  • control of the control unit may be a purely electrical control or even a pneumatic or hydraulic control
  • the control signals for lowering the boom are limited to a suitable value to limit the lowering speed accordingly.
  • speed monitoring during the floatation operation which prevents the boom from exceeding a certain speed when lowered. Should the boom drop too quickly, the switching valves can be closed and the lowering process can be actively carried out again via the control unit.
  • the maximum permissible speed can additionally be made dependent on the extension length of the lifting cylinder.
  • the position indicating or signaling sensor is designed as a position or angle sensor, so that the position or position of the boom or the hydraulic cylinder can be measured directly.
  • a position sensor may be directly connected to the rod stroke of the piston rod of the hydraulic cylinder, or another variable distance to be recorded or monitored in conjunction with the hydraulic cylinder or the boom.
  • An angle sensor can, for example, at the pivot points on the boom or on the hydraulic cylinder be arranged and record or scan or monitor a corresponding tilt angle.
  • a pressure sensor can also be used, wherein at least one position of the arm or of the hydraulic cylinder can be signaled as a function of the pressure.
  • the position or position of the boom is not directly measured, but instead the pressure on the stroke side of the lifting cylinder or determined whereby a conclusion on the position of the boom is possible.
  • the lowering of the boom takes place here not by control of a pressure limiting device, but by a direct, initiated by the control unit control of the control unit in its lowered position. It is thus dispensed with a pressure limiting device. If the boom is resting on the ground, the pressure on the lifting side of the lifting cylinder drops as it no longer has to bear the load of the boom.
  • the decrease in pressure indicates or indirectly indicates a position or position of the arm, whereby the drop in pressure below a predeterminable value (preferably the lowest possible pressure for holding an unloaded arm) indirectly indicates or indicates the lowered position or position of the arm can signal.
  • a predeterminable value preferably the lowest possible pressure for holding an unloaded arm
  • the control unit assumes that the boom is in a non-lowered position. Only when the corresponding pressure is reached or fallen below, an opening of the two switching valves for the realization of the floating position is initiated by the control unit.
  • the pressure sensor can also be replaced by a pressure switch.
  • the activation means for activating the floating position can be designed for example as a switch, with which an activation signal is given to the control unit. Such switches are preferably housed in the cab of a charger or on the control panel. Furthermore, the activation means can also be designed as a joystick or be integrated in the positions of a joystick, so that the joystick with integrated floating position, which is detected electronically, is formed.
  • the switching valves are preferably designed as electrically actuated switching valves, in which case also pneumatically or hydraulically switchable valves can be used.
  • FIG. 1 shows an example of a hydraulic arrangement of a semi-active suspension for a boom, wherein in addition to a suspension function and a floating position function is given.
  • FIG. 1 shows a hydraulic cylinder 10 with a hydraulic piston 12 which serves to lift and lower a boom 70 of a charger 61 (both shown in FIG. 3).
  • the hydraulic cylinder 10 has a lifting-side chamber 14 and a lowering-side chamber 16.
  • the lift-side chamber 14 is connected via a stroke-side hydraulic line 18 and the lowering-side chamber 16 via a vertical hydraulic line 20 with a manually switchable control unit 22.
  • the controller 22 may also be electrically or hydraulically switchable.
  • the control unit 22 is connected via a drain line 24 to a hydraulic oil tank 28.
  • a hydraulic oil pump 30 delivers hydraulic oil via the control unit 22 into the respective hydraulic lines 18, 20.
  • the control unit 22 is switchable in three positions, in a closed position, in which no flow for both hydraulic lines 18, 20 takes place, in a stroke position in which the stroke-side hydraulic line 18 is supplied with hydraulic oil, wherein the vertical-side hydraulic line 20 hydraulic oil to the hydraulic tank 28th emits, and in a lowering position, in which the vertical-side hydraulic line 20 is supplied with hydraulic oil, wherein the stroke-side hydraulic line 18 emits hydraulic oil to the hydraulic tank 28.
  • the lift-side hydraulic line 18 contains a load-holding valve 34, which allows a hydraulic oil flow in the direction of the hydraulic cylinder 10 via a bypass line 36. Via control lines 38, the load-holding valve 34 can be opened in the direction of the hydraulic oil tank 28, so that a hydraulic oil flow to the hydraulic oil tank 28 can take place.
  • a connecting line 40 which contains an electrically switchable switching valve 42.
  • the switching valve 42 includes a blocking position in which no flow takes place in both directions and an open position in which a flow in both directions is made possible.
  • the connecting line 40 contains a controllable pressure limiting device 43 with a controllable pressure limiting valve 44, which opens via a control line 46 in the direction of the vertical hydraulic line 20.
  • the control pressure or pressure threshold value for opening the pressure-limiting valve 44 can be regulated via a regulator 48 of the pressure-limiting device 43.
  • a pressure relief valve 44 instead of a pressure relief valve 44 and the use of a variable throttle or aperture is possible.
  • a position sensor 50 is connected to a piston rod 52 of the hydraulic cylinder 10 and provides a sensor signal representing the position of the hydraulic piston 12 to a control unit 54.
  • the control unit 54 is connected to a switching device 56, via which the control unit 54 and thus the hydraulic suspension are activated can.
  • a second vertical-side hydraulic line 58 is provided which extends from the first vertical-side hydraulic line 20 leads to the hydraulic tank 28 and is provided with a further switching valve 60, wherein the switching valves 42, 60 may be of identical construction.
  • an activation switch 56 ' is provided, which is in communication with the control unit 54.
  • the hydraulic semi-active suspension is designed as an on-demand suspension system in which, if necessary, a volume flow from the control unit 22 via a load-holding valve 34 to the hydraulic cylinder 10 of the boom 70 flows.
  • the controller 22 is thus in the closed position and is switched as needed by the control unit 54 in the corresponding other positions.
  • the control for semi-active suspension is activated by the switching unit 56, the original position of the boom 70 is recorded as the reference variable to be observed and the control unit 54 determines the deviation (control difference) from this reference variable and the current, measured position (controlled variable). from each other to perform on this basis, the regulation of the pressure relief valve 44 and adjust the height of the flow rate of the control unit 22 by means of further control variables.
  • the switching valves 42, 60 In order for the hydraulic piston 12 of the hydraulic cylinder 10 to move due to disturbances acting on it, the switching valves 42, 60 must be switched to their open positions.
  • the pressure which is to act on the lifting side of the hydraulic cylinder 10 is regulated by the control unit 54 as required via the electrically controllable pressure limiting valve 44.
  • the pressure limiting valve 44 is set to a higher value and the control unit 22 is opened so that the pressure on the lifting side of the hydraulic cylinder 10 increases due to the flowing volume flow and the hydraulic cylinder 10 is extended.
  • the pressure limiting valve 44 is set to a lower value, so that the pressure on the lifting side of the hydraulic cylinder 10 is reduced and the hydraulic piston 12 is retracted.
  • the hydraulic oil which then flows from the lifting side of the hydraulic cylinder 10 via the pressure limiting valve 44 and the first switching valve 42 to the lowering side of the hydraulic cylinder 10, flows from there via the second switching valve 60 to the hydraulic tank 28.
  • the hydraulic oil from the stroke side of the hydraulic cylinder 10 is displaced by the hydraulic piston 12 and flows through the pressure relief valve 44 and via the switching valves 42, 60 from. Due to the displaced oil volume of the boom 70 decreases, which in turn is detected by the control unit 54 as a control difference, whereupon the control unit 54 increases the opening pressure of the pressure relief valve 44 and the control unit 22 brings into the stroke position, so that a volume flow to the stroke side of the hydraulic cylinder 10 flows where the manipulated variables through the control unit 54 can be determined according to the control difference. Due to the increase in the opening pressure and the volume flow flowing from the control unit 22, the boom 70 is raised again until the control difference has reduced again to zero or to a presettable threshold value.
  • control unit 54 switches the control unit 22 back into the closed position. Due to the reduction in the opening pressure, hydraulic oil flows from the lift side of the hydraulic cylinder 10 via the pressure relief valve 44, and the boom 70 descends until the control difference has decreased to zero or to a presettable threshold.
  • a detection of the position or position of the arm 70 or of the hydraulic cylinder 10 by the sensor 50 which supplies a corresponding sensor signal to the control unit 54, follows immediately.
  • the pressure limiting valve 44 will be slowly started up from a high pressure limit or downshifted to lower pressure limit values so that the boom 70 begins to lower.
  • the hydraulic oil flowing out of the lift-side chamber 14 can flow into the hydraulic tank 28 via the open switching valves 42, 60.
  • the position or position of the arm 70 is further registered by the control unit 54 via the sensor signal.
  • the pressure relief valve 44 is fully opened, so that sets a floating position for the boom through the open switching valves 42, 60.
  • the control device 22 shown in FIG. 1 and the switching valves 42, 60 are shown electrically switchable.
  • a pressure sensor 50 ' can also be used.
  • the pressure sensor 50 ' is arranged in pressure connection to the lift-side chamber 14. It is assumed that the pressure with lowered boom 70 assumes a minimum value. The boom 70 is brought into its lowered position by a control of the control device 22 which is brought into its lowered position by the electrical control unit 54. A pressure limiting device 43 is not used here. If this minimum pressure value is signaled by the pressure sensor 50 ', then it is assumed that the boom 70 is in its lowered position. If a pressure deviating from the preset minimum value is signaled by the pressure sensor 50 ', it is assumed that the boom 70 has to be lowered.
  • the pressure sensor 50 'thus allows a conclusion as to which position or position the boom 70 is located.
  • a preset control procedure is carried out by the control unit 54 with which the pressure limiting valve 44 is slowly opened, or the boom 70 is slowly lowered, ie when the pressure value drops, the pressure limiting valve 44 is controlled accordingly, so that at Reaching a preset minimum pressure value, a corresponding signal sent by the pressure sensor 50 'signal is assumed by the control unit 54 as a signal to fully open the pressure limiting valve 44.
  • Figure 2 shows another hydraulic arrangement without suspension function, but with floating position function.
  • the hydraulic arrangement shown in Figure 2 differs from the arrangement of Figure 1 described above, first, in that in the connecting line 40 no pressure limiting unit 43 is provided, with which in the example shown in Figure 1, the suspension function has been realized, on the other hand, in that, instead of the switchable control device 22, a controllable control device 22 'controlled by the control unit 54 is arranged.
  • the activation switch 56 arranged in FIG. 1 for activating a suspension function can be used to activate the floating position.
  • a floating position is activated in the example shown in FIG. 2 by actuating the activation switch 56, the position or position of the arm 70 or of the hydraulic cylinder 10 is detected by the sensor 50, which supplies a corresponding sensor signal to the control unit 54 the switching valves 42, 60 are closed.
  • the control unit 22 ' is controlled by the control unit 54 and brought into lowered position, wherein an adjustable control procedure provides that a predetermined lowering speed is not exceeded. This is achieved in that the proportionally controllable control unit 22 'only allows a presettable volume flow.
  • the hydraulic oil can flow out of the first chamber 14 of the hydraulic cylinder 10 into the hydraulic tank via the load-holding valve 34 opened by the vertical-side pressure and the boom 70 can be lowered.
  • the position or position of the arm 70 is further registered by the control unit 54 via the sensor signal.
  • the controller 22 ' is brought into the neutral position and at the same time the switching valves 42, 60 are opened, so that sets a floating position for the boom.
  • the activation switch 56 deactivate
  • the floating position can be deactivated, so that the switching valves 42, 60 are closed again and the hydraulic arrangement can be operated in a normal operating mode.
  • control unit 22 'and the switching valves 42, 60 shown in FIG. 2 are shown electrically switchable. However, they can also be designed to be controllable as pneumatic, hydraulic or in another way.
  • FIG. 3 shows a charger 61 in the form of a telescopic handler, which may have a hydraulic arrangement according to the form shown in FIGS. 1 or 2.
  • the charger 61 has a frame 62 which is supported by a front axle 64 provided with front drive wheels 63 and by a rear axle 68 provided with rear drive wheels 66.
  • the charger 61 has a boom 70, which is pivotally hinged about a parallel to the drive axles 64, 68 arranged pivot axis 72 on the frame 62.
  • the boom 70 is designed as a telescopic boom and has at its free end 74 on a working head 76, by means of a pivotally mounted on the working head 76 tool holder 78, a loading tool 80 is receivable.
  • the boom 70 can be telescopically extended or extended via adjusting cylinders (not shown) arranged in the interior of the boom 70.
  • adjusting cylinders (not shown) arranged in the interior of the boom 70.
  • the hydraulic cylinder 10 is pivotally connected at a first end, preferably piston crown side about a pivot axis 82 to the frame 62 and at a second end about a pivot axis 84 with the boom 70.
  • a further hydraulic cylinder 86 arranged in the interior of the arm 70 is formed.
  • the hydraulic cylinder 86 serves as a tipping cylinder for the pivotally mounted on the working head 76 tool holder 78, wherein the tool holder 78 is pivotable by means of a working head 76 and connected to the hydraulic cylinder 86 Kippgestfites 88.
  • the hydraulic cylinder 10 arranged for pivoting the arm 70 is provided on its lifting side with a pressure sensor 50 ', by means of which a pressure prevailing in the stroke-side chamber of the hydraulic cylinder 10 can be detected. Furthermore, the hydraulic cylinder 10 is provided on the rod side with the position sensor 50, by means of which an extended position of the hydraulic cylinder 10 can be detected. By way of the extended position detected by the position sensor 50, the pivot position (swivel angle) of the arm 70 can be determined. Alternatively, a position sensor (not shown) designed as a rotary encoder can also be arranged on the pivot axis 72 of the arm 70 in order to detect the pivot position of the arm 70.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)
EP06120251.1A 2005-09-13 2006-09-07 Engin roulant du type muni d'un bras et procédé pour celui-ci Not-in-force EP1762535B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005043447A DE102005043447A1 (de) 2005-09-13 2005-09-13 Ladegerät sowie Verfahren für ein Ladegerät

Publications (3)

Publication Number Publication Date
EP1762535A2 true EP1762535A2 (fr) 2007-03-14
EP1762535A3 EP1762535A3 (fr) 2009-01-07
EP1762535B1 EP1762535B1 (fr) 2014-07-16

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EP06120251.1A Not-in-force EP1762535B1 (fr) 2005-09-13 2006-09-07 Engin roulant du type muni d'un bras et procédé pour celui-ci

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US (1) US7430953B2 (fr)
EP (1) EP1762535B1 (fr)
DE (1) DE102005043447A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1897847A3 (fr) * 2006-09-08 2009-06-17 Deere & Company Appareil de chargement
IT201900005056A1 (it) * 2019-04-04 2020-10-04 Nem S R L Circuito idraulico di azionamento per macchina operatrice con articolazione meccanica dotata di funzione flottante.

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007018405B4 (de) * 2007-04-17 2022-09-15 Alpha Fluid Hydrauliksysteme Müller GmbH Elektrohydraulische Ansteuerung
US8474254B2 (en) * 2008-11-06 2013-07-02 Purdue Research Foundation System and method for enabling floating of earthmoving implements
US8631651B2 (en) * 2009-01-21 2014-01-21 Manitowoc Crane Companies, Llc Hydraulic system thermal contraction compensation apparatus and method
US8858151B2 (en) * 2011-08-16 2014-10-14 Caterpillar Inc. Machine having hydraulically actuated implement system with down force control, and method
US20130168073A1 (en) * 2011-12-30 2013-07-04 Cnh America Llc Work vehicle fluid heating system
WO2013103954A2 (fr) * 2012-01-05 2013-07-11 Parker-Hannifin Corporation Système électro-hydraulique avec fonction de flottement
AU2017248349B2 (en) 2016-04-08 2021-11-11 Oshkosh Corporation Leveling system for lift device
IT201700047745A1 (it) * 2017-05-03 2018-11-03 Cnh Ind Italia Spa Veicolo provvisto di un braccio comprendente un circuito di controllo idraulico avente una valvola di controllo di carico
JP6960585B2 (ja) * 2018-12-03 2021-11-05 Smc株式会社 流量コントローラ及びそれを備えた駆動装置
DE102020131046A1 (de) 2020-11-24 2022-05-25 Buchholz Hydraulik Gmbh Hydraulisches Hubsystem

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1450048A1 (fr) 2003-02-21 2004-08-25 Deere & Company Agencement de vanne
EP1496009A1 (fr) 2003-07-05 2005-01-12 Deere & Company Suspension hydraulique

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472127A (en) * 1967-12-12 1969-10-14 Caterpillar Tractor Co Control circuit for bulldozers used in pushing
US5415076A (en) * 1994-04-18 1995-05-16 Caterpillar Inc. Hydraulic system having a combined meter-out and regeneration valve assembly
DE19853523C1 (de) * 1998-11-20 2000-03-09 Schaeff Karl Gmbh & Co Fahrbarer Schaufellader
DE10006908A1 (de) * 2000-02-16 2001-08-23 Caterpillar Sarl Genf Geneva Hydraulische Kolbenzylindereinheit für landwirtschaftliche Arbeitsmaschinen
DE10149787B4 (de) * 2000-10-23 2012-06-06 Linde Material Handling Gmbh Ventilanordnung mit Schwimmstellung
DE10340504B4 (de) * 2003-09-03 2006-08-24 Sauer-Danfoss Aps Ventilanordnung zur Steuerung eines Hydraulikantriebs

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1450048A1 (fr) 2003-02-21 2004-08-25 Deere & Company Agencement de vanne
EP1496009A1 (fr) 2003-07-05 2005-01-12 Deere & Company Suspension hydraulique

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1897847A3 (fr) * 2006-09-08 2009-06-17 Deere & Company Appareil de chargement
US7845896B2 (en) 2006-09-08 2010-12-07 Deere & Company Loader
IT201900005056A1 (it) * 2019-04-04 2020-10-04 Nem S R L Circuito idraulico di azionamento per macchina operatrice con articolazione meccanica dotata di funzione flottante.

Also Published As

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DE102005043447A1 (de) 2007-03-15
US7430953B2 (en) 2008-10-07
EP1762535B1 (fr) 2014-07-16
EP1762535A3 (fr) 2009-01-07
US20070056280A1 (en) 2007-03-15

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