EP1616103B1 - Systeme de commande et de reglage pour un mecanisme de levage et d'inclinaison de l'outil d'un engin mobile - Google Patents

Systeme de commande et de reglage pour un mecanisme de levage et d'inclinaison de l'outil d'un engin mobile Download PDF

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Publication number
EP1616103B1
EP1616103B1 EP04733802A EP04733802A EP1616103B1 EP 1616103 B1 EP1616103 B1 EP 1616103B1 EP 04733802 A EP04733802 A EP 04733802A EP 04733802 A EP04733802 A EP 04733802A EP 1616103 B1 EP1616103 B1 EP 1616103B1
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EP
European Patent Office
Prior art keywords
hydraulic
adjusting
lifting
cylinder
control
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.)
Expired - Lifetime
Application number
EP04733802A
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German (de)
English (en)
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EP1616103A1 (fr
Inventor
Jochen Beck
Dieter Roth
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.)
Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Publication of EP1616103A1 publication Critical patent/EP1616103A1/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • 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
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/003—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors with multiple outputs
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to a lifting or tipping mechanism of a mobile working machine according to the preamble of claim 1 or 4.
  • the working hydraulics in mobile machines with a shovel-shaped working tool - for example in wheel loaders, excavators and forklifts - consists of a hoist and a tipping unit.
  • the hoist consists of a boom located between the vehicle body and work tool, which is hydraulically driven by two lifting cylinders and raises or lowers the working tool depending on the pivoting direction by a pivoting movement relative to the vehicle body.
  • the tilting mechanism has one or two bucket cylinders, which are mounted between the vehicle body and the bucket-shaped working tool and drive the bucket tool depending on the tilting direction to an out or tipping tilting movement.
  • EP 0 564 939 B1 shows a hydraulic control device for such a working hydraulic system.
  • the two lifting and bucket cylinders are each connected in parallel.
  • the position and direction of movement of the actuating piston in the lifting cylinders determine the lifting height and the vertical direction of movement of the loading blade relative to the vehicle body.
  • the tilt angle and tilt direction of the bucket are determined by the position and direction of travel of the actuator piston in the bucket cylinders.
  • Position and direction of movement of the actuating piston in the lifting or bucket cylinder are determined by the pressure difference between the piston-side and piston rod-side actuating pressure chamber.
  • the supply of the piston-side and piston rod-side control pressure chambers in the individual Lifting and bucket cylinders with hydraulic fluid determined signal pressure is effected by a common pressure and flow controlled hydraulic pump.
  • control valves in a control block in the hydraulic load circuit between the hydraulic pump and lifting and bucket cylinder.
  • Each of these control valves - one control valve each for the hoist and tilting unit - is controlled via a pilot control unit to which a steering element, for example steering wheel or joystick, is connected, depending on the desired reference values - lifting height, tilt angle, vertical direction of movement and tilting direction.
  • a load-dependent dosage of the hydraulic fluid flow from the hydraulic pump to the individual lifting and bucket cylinders is realized via an intermediate circuit of a control valve (priority valve).
  • the power level for the hydraulic hoist lies in a completely different order of magnitude than the power level for the hydraulic tipper (hoist: approx. 150 to 180 bar, tipping unit: approx. 20 to 50 bar). Since a single hydraulic pump is used for lifting and tilting, whose maximum delivery volume is designed for the hydraulic volume required by the hoist, resulting in the case of hydraulic actuation of the tipper a not insignificant hydraulic energy loss. This hydraulic energy loss generates additional dissipated heat, which unnecessarily degrades the hydraulic efficiency of the working hydraulics.
  • control valves lead due to their adjustable flow cross-section to higher flow resistance in the hydraulic load circuit compared to a normal hydraulic load line between the hydraulic pump and hydraulic cylinder.
  • Flow cross sections in the load circuit cause unnecessary hydraulic losses, which unnecessarily worsen the efficiency of such working hydraulics.
  • the invention is therefore based on the object, the hoist or tilting of a mobile machine according to the preamble of claim 1 or claim 4 such that the required for the desired setpoints of the working hydraulics - lifting height, tilt angle, verticallyssichtung and tilting direction - set pressures in the two actuating pressure chambers of the lifting and bucket cylinder from an adjustable hydraulic pump, directly without the interposition of additional control and adjusting devices, such as control valves in control blocks, are guided in the respective setting pressure chambers.
  • the object of the invention is achieved by a hoist or a tipping mechanism of a mobile machine with the features of claim 1 and of claim 4.
  • An essential feature of the lifting or tilting body according to claim 1 and claim 4 is in contrast to the device in EP 0 564 939 B1, in which an open hydraulic circulation is used, the use of a closed circuit between the hydraulic pump and the respective hydraulic consumer (lifting cylinder the hoist and bucket cylinder of the tipping unit). This presupposes that the delivery volume transported from the hydraulic pump to the hydraulic consumer corresponds to the delivery volume transported back from the hydraulic consumer to the hydraulic pump.
  • a hydraulic pump operating in two-quadrant operation This can be generated by adjusting the hydraulic pump with respect to the direction of current and the pending at its two terminals Stelltikièren any control pressure difference for the two control pressure chambers of the lifting or bucket cylinder.
  • a complex interposition of control blocks with control valves for the generation of any control pressure differences in the two control pressure chambers of the lifting or bucket cylinder from the unidirectional control pressure difference at the two Connections of the hydraulic pump is thus eliminated.
  • the control pressure difference of the two ports of the hydraulic pump can be arbitrarily set with respect to their polarity and their height by an adjustment within the realizable adjustment range of the hydraulic pump. The adjustment of the necessary control pressure differences is thus shifted in this arrangement from the load circuit in the control circuit of the hydraulic pump.
  • the lifting or tilting device according to the invention of a mobile machine thus has the above-mentioned disadvantages - additional piping and Verschraubungsaufwand, increased space requirements, additional Leckölellen, increased installation, maintenance and service costs, lower flow resistance in the load circuit and especially higher system costs - no longer on ,
  • a parallel connection of the two lifting or bucket cylinders as in EP 0 564 939 B1 separates due to the different compression or expansion volumes in the piston-side and piston rod side actuating pressure chambers upon displacement of the actuating piston.
  • the two lifting or bucket cylinders are connected in opposite directions and the two lifting and bucket cylinders have the same expansion as compression volumes when the adjusting pistons are displaced. Same expansion as compression volumes in displacement of the actuating piston in the control pressure chambers of the lifting or bucket cylinder ensure equal delivery volumes in the outward and return lines for the realization of a closed hydraulic circuit.
  • a separate hydraulic pump is advantageous for the realization of a closed hydraulic circuit for the hoist and the tilting mechanism.
  • the required for the control pressure chambers of the lifting or bucket cylinder control pressure differences can be set independently by the respective adjustment of the two hydraulic pumps.
  • a mutual negative influence on the lifting and tilting function as in a realization by means of open hydraulic circuit is no longer available.
  • each hydraulic pump can be adapted in terms of their capacity to the power requirement of the lifting or tilting unit. In an open hydraulic circuit, the capacity of the hydraulic pump must be tailored to the needs of the most powerful consumer.
  • the tipping unit is thus supplied with an open hydraulic circuit with too high a hydraulic power, which can unnecessarily worsen the efficiency of the tipping unit.
  • the control of the control valve for the adjustment of the two hydraulic pumps can be done electrically or hydraulically.
  • a pilot control device which is controlled via a steering element, for example a joystick, in each case in a deflection dimension of the steering element for each hydraulic pump and thus for each hydraulic function - hoist, tilting mechanism.
  • the pilot control device generates at its outputs according to the deflection of the steering member necessary for the deflection of the control valve piston control pressure pairs.
  • the mechanical deflection of the steering member is transformed via a converter into an electrical signal which is supplied to the electric actuating magnet for the deflection of the control valve piston.
  • Advantage of the electrical compared to the hydraulic control is the lower technical Effort - no piping, fittings and hydraulic valves - and the smaller footprint, especially in the cab of the driver.
  • a simple system integration of the electrical control in existing control systems of the mobile work machine - for example, control for hydrostatic drive - is another advantage of the electrical control.
  • electrically or hydraulically controllable (switchable) check valves - so-called “low-leak” valves - are used in one of the two hydraulic load lines to the lifting and bucket cylinders.
  • a hydraulic control arrangement is used for damping the boom, as described, for example, in DE 41 29 509 C2.
  • This hydraulic control arrangement loads the bucket cylinder targeted by adding hydraulic buffer to the expected load pressure and thus leads to a significant damping of pitching vibrations of the working tool.
  • FIG. 1A shows a circuit diagram of a hydraulic control and positioning system for a tilting mechanism 100 of a working tool in a mobile working machine, which comprises a first bucket cylinder 1 and a second bucket cylinder 2.
  • a first bucket cylinder 1 an actuating piston 3 is displaceably guided, which is mechanically coupled to the vehicle body 4.
  • the first bucket cylinder 1 is mechanically connected to the loading bucket 6, which can be deflected relative to the vehicle body 4 in terms of tilt angle and tilting direction.
  • the adjusting piston 5 is slidably guided, which is connected to the loading shovel 6.
  • the second bucket cylinder 2 is mechanically connected to the vehicle body 4.
  • the first bucket cylinder 1 has a piston-side actuating pressure chamber 7 and a piston rod-side actuating pressure chamber 8.
  • the second bucket cylinder 2 also has a piston-side actuating pressure chamber 9 and a piston rod-side actuating pressure chamber 10.
  • the piston side actuating pressure chamber 7 of the first bucket cylinder 1 is connected to the piston rod side actuating pressure chamber 10 of the second bucket cylinder 2 via a hydraulic line 11.
  • the piston rod side actuating pressure chamber 8 of the first blade cylinder 1 via a hydraulic line 12 to the piston-side actuating pressure chamber 9 of the second blade cylinder 2 connected.
  • the piston rod-side actuating pressure chamber 10 of the second blade cylinder 2 or the piston-side actuating pressure chamber 7 of the first blade cylinder 1 is connected via a first hydraulic load line 13 to the first terminal 14 of an adjustable first hydraulic pump 15.
  • the piston-side actuating pressure chamber 9 of the second bucket cylinder 2 or the piston rod-side actuating pressure chamber 8 of the first bucket cylinder 1 is connected via a second hydraulic load line 16 to the second port 17 of the adjustable first hydraulic pump 15.
  • the adjustable first hydraulic pump 15 is driven via a drive shaft 18 by a prime mover (not shown in FIG. 1A), for example a diesel engine.
  • a first actuating pressure chamber 68, 69 adjoins the associated cylinder piston 63, 65 with a pressure application area A1, which is smaller than the pressurization area A2, with which the other second control pressure chamber 67, 70 adjacent to the corresponding cylinder piston 63, 65.
  • Each port 74, 77 the hydraulic pump 75 is connected to a first actuating pressure chamber 68, 69 having a smaller pressurizing area A1 and a second actuating pressure chamber 67, 70 having a larger pressurizing area A2.
  • a first feed pump 19 is also driven via the drive shaft 18 to the prime mover.
  • the first feed pump 19 is a working in one-quadrant operation hydraulic pump whose low-pressure side port 20 is connected via a hydraulic line 21 with the interposition of a filter 22 with a hydraulic tank 23.
  • the high-pressure side port 24 of the first feed pump 19 is connected with respect to a pressure limiting with a pressure relief valve 25 via a hydraulic line 26.
  • One of the two control terminals of the pressure limiting valve 25 is connected to the hydraulic line 26.
  • At the other control input of the pressure relief valve 25 can be adjusted via a spring 27, a certain upper pressure limit. If the pressure in the hydraulic line 26 exceeds the upper pressure limit value set by the spring 27, then the pressure limiting valve 25 opens and connects the hydraulic line 26 to the hydraulic tank 28. The pressure in the hydraulic line 26 then decreases until a pressure in the hydraulic line 26 is reached adjusts the upper pressure limit corresponding pressure and the pressure relief valve 25 goes back to the locked state.
  • the high-pressure side port 24 of the first feed pump 19 is connected via the hydraulic line 26 to a first check valve 29 and a second check valve 30.
  • the first check valve 29 is connected at its second terminal to the first hydraulic load line 13, while the check valve 30 is connected at its second terminal to the second hydraulic load line 16. If the pressure in the first hydraulic load line 13 drops below that in the hydraulic line 26 via the pressure relief valve 25 set pressure level, so opens the check valve 29 and adjusts the pressure in the first hydraulic load line 13 to the pressure prevailing in the hydraulic line 26 pressure. Analogously opens at a pressure drop in the second hydraulic load line 16 under the pressure prevailing in the hydraulic line 26 pressure level, the check valve 30 and adjusts the pressure in the second hydraulic load line 16 to the pressure prevailing in the hydraulic line 26 pressure.
  • a pressure relief valve 31 is connected.
  • This pressure limiting valve 31 compares the pressure value applied to one of its control inputs in the first hydraulic load line 13 with the pressure setpoint set at the other control input via a spring 32 and opens when the pressure in the first hydraulic load line 13 exceeds the set pressure value set by the spring 32.
  • the pressure in the first hydraulic load line 13 is thereby reduced via the pressure relief valve 31 in the hydraulic line 26 until the pressure in the first hydraulic load line 13 corresponds to the pressure setpoint set by the spring 32 on the pressure relief valve 31 and the pressure relief valve 31 again in the locked state passes.
  • a second pressure limiting valve 33 is connected in parallel to the check valve 30. This compares the prevailing pressure in the second hydraulic load line 16, which is guided at one of its control inputs, with a set by a spring 34 at its other control input pressure setpoint and opens when exceeding the pressure in the second hydraulic load line 16 via the spring 34th set pressure setpoint.
  • the pressure in the second hydraulic load line 16 is reduced as long as the second pressure relief valve 33 in the hydraulic line 26 until the pressure in the second hydraulic load line 16 corresponds to the setpoint pressure set by the spring 34 and the pressure relief valve 33 again goes into the locked state.
  • the control of the adjustable first hydraulic pump 15 via a first adjusting device 35, the adjusting piston 36 with the swash plate (not shown in Fig. 1) of the hydraulic pump 15 is mechanically connected.
  • the adjusting piston 36 divides the first adjusting device 35 into a first actuating pressure chamber 37 and into a second actuating pressure chamber 38.
  • the first actuating pressure chamber 37 is connected via a hydraulic line 39 to the first output 40 of a control valve 41, which is designed as a 4/3-way valve.
  • the second control pressure chamber 38 is connected via a hydraulic line 42 to the second output 43 of the control valve 41.
  • the first input 44 of the control valve 41 is connected via a hydraulic line 45 and the hydraulic line 26 to the high pressure side port 24 of the feed pump 19.
  • the second input 46 is connected via a hydraulic line 47 to a hydraulic tank 48.
  • the control of the control valve 41 via a first control input 49 and a second control input 50, which are both designed as electrical actuating magnets.
  • the electric actuating magnet of the first control input 49 is connected to a first output 51 of a converter (not shown in FIG. 1A), which controls the mechanical deflection on a steering member 52 designed as a joystick in the direction of "tilting" in the tilting mechanism 100 determined first deflection dimension converts into a corresponding first electrical signal.
  • the electric actuating magnet of the second control input 50 is connected via an electrical line 53 to a second output 54 of the converter (not shown in FIG. 1A), which controls the mechanical deflection on the steering member 52 in the direction of "tilting out” in the first deflection dimension determined by the tilting mechanism 100 in a corresponding second electrical signal converts.
  • the controlled electric actuating magnet at the second control input 50 leads to a deflection of the control valve 41, so that the second control pressure chamber 38 of the first adjusting device 35 via the hydraulic line 42, 45 and 26 with the high pressure side port 24 of the first feed pump 19 and the first control pressure chamber 37 of the first Adjustment device 35 is connected via the hydraulic line 39 and 47 to the hydraulic tank 48.
  • the adjusting piston 36 of the first adjusting device 35 is then adjusted in the direction of a delivery volume at the first terminal 14 of the adjustable first hydraulic pump 15.
  • This delivery volume at the first port 14 of the adjustable first hydraulic pump 15 is supplied via the first hydraulic load line 13 of the piston rod side actuating pressure chamber 5 of the second blade cylinder 2 and leads to a displacement of the actuating piston 5 in the direction of the piston-side control pressure chamber 9.
  • the higher control pressure in the first hydraulic load line 13 is supplied via the hydraulic line 11 of the piston-side actuating pressure chamber 7 of the first blade cylinder 1, so that the actuating piston 3 is displaced in the direction of the piston rod-side actuating pressure chamber 8.
  • the steering member 52 is deflected in the direction of "tipping over" in the first deflection dimension determined for the tipping unit 100.
  • a first electrical signal is generated by the converter of the steering member 52, which is supplied via the electrical line 59 to the electric actuating magnet at the first control input 49 of the first control valve 41.
  • the first control valve 41 is actuated by the electric actuating magnet at the first control input 49 such that the first control pressure chamber 37 of the first adjusting device 35 via the hydraulic line 39, 45 and 26 with the high pressure side port 24 of the first feed pump 19 and the second control pressure chamber 38 of the first adjustment 35 is connected via the hydraulic line 42 and 47 to the hydraulic tank 48.
  • the adjusting piston 36 of the first adjusting device 35 is adjusted in the direction of a delivery volume or higher setting pressure at the second port 17 of the adjustable first hydraulic pump 15.
  • This delivery volume at the second port 17 of the adjustable first hydraulic pump 15 is guided via the second hydraulic load line 16 in the piston-side actuating pressure chamber 9 of the second blade cylinder 2 and there leads to a deflection of the actuating piston 5 in the direction of the piston rod side actuating pressure chamber 10.
  • the higher control pressure in the second Hydraulic load line 16 is supplied via the hydraulic line 12 of the piston rod-side actuating pressure chamber 8 of the first blade cylinder 1 and there leads to a deflection of the actuating piston 3 in the direction of the piston-side actuating pressure chamber 7.
  • the deflection of the actuating piston 3 of the first blade cylinder 1 as well of the actuating piston 5 of the second blade cylinder 2 lead to a Einkippmony the loading blade. 6
  • a switchable check valve 55 is connected in the first hydraulic load line 13. Via a converter 57 and the electrical line 56, the opener 58 of the switchable check valve 55 is connected to the converter output 54 of the steering member 52.
  • FIG. 1B shows a circuit diagram of a hydraulic control and positioning system for a hoisting gear 200 of a working tool in a mobile working machine, which consists of a first lifting cylinder 61 and a second lifting cylinder 62.
  • a control piston 63 is slidably guided, which is mechanically coupled to the vehicle body 4.
  • the first lifting cylinder 61 is mechanically connected to the boom 64, the angle of rotation relative to the vehicle body 4 determines the lifting height of the arranged at the other end of the bucket 6 and the direction of rotation relative to the vehicle body 4, the vertical direction of movement of the bucket 6.
  • the actuating piston 65 is displaceably guided, which is connected to the loading shovel 6.
  • the second lift cylinder 62 is mechanically connected to the vehicle body 4.
  • the first lifting cylinder 1 has a piston-side adjusting pressure chamber 67 and a piston rod-side adjusting pressure chamber 68.
  • the second lifting cylinder 62 likewise has a piston-side actuating pressure chamber 69 and a piston rod-side actuating pressure chamber 70.
  • the piston-side actuating pressure chamber 67 of the first lifting cylinder 61 is connected to the piston rod-side actuating pressure chamber 69 of the second lifting cylinder 62 via a hydraulic line 71.
  • the piston rod side actuating pressure chamber 68 of the first lifting cylinder 61 is connected via a hydraulic line 72 to the piston-side actuating pressure chamber 70 of the second lifting cylinder 62.
  • the piston rod-side actuating pressure chamber 69 of the second lifting cylinder 62 and the piston-side actuating pressure chamber 67 of the first lifting cylinder 61 is connected via a third hydraulic load line 73 to the first terminal 74 of an adjustable second hydraulic pump 75.
  • the piston-side actuating pressure chamber 70 of the second lifting cylinder 62 or the piston rod-side actuating pressure chamber 68 of the first lifting cylinder 61 is connected via a fourth hydraulic load line 76 to the second port 77 of the adjustable second hydraulic pump 75.
  • the adjustable second hydraulic pump 75 is driven via a drive shaft 78 from a prime mover (not shown in FIG. 1B), for example a diesel engine, which corresponds to the prime mover for the drive shaft 16 of the first hydraulic pump 15.
  • a first actuating pressure chamber 8, 10 adjoins the associated cylinder piston 3, 5 with a pressure application area A1, which is smaller than the pressurization area A2, with which the other second actuating pressure chamber 7, 9 adjacent to the corresponding cylinder piston 3, 5.
  • Each port 14, 17 of the hydraulic pump 15 is connected to a first actuating pressure chamber 8 or 10 with a smaller pressurizing area A1 and a second actuating pressure chamber 7 or 10 with a larger pressurizing area A2.
  • a second feed pump 79 is also driven via the drive shaft 78 to the prime mover.
  • the second feed pump 79 is a one-quadrant operating hydraulic pump whose low-pressure side port 80 is connected via a hydraulic line 81 with the interposition of a filter 82 with a hydraulic tank 83.
  • the high-pressure side port 84 of the second feed pump 79 is connected with respect to a pressure limiting with a pressure relief valve 85 via a hydraulic line 86.
  • One of the two control terminals of the pressure relief valve 85 is connected to the hydraulic line 86.
  • a certain upper pressure limit can be set via a spring 87. If the pressure in the hydraulic line 86 exceeds the upper pressure limit set by the spring 87, then the pressure relief valve 85 opens and connects the hydraulic line 86 to the hydraulic tank 88. The pressure in the hydraulic line 86 then decreases until a pressure in the hydraulic line 86 is reached sets the upper pressure limit corresponding pressure and the pressure relief valve 85 goes back to the locked state.
  • the high-pressure side port 84 of the second feed pump 79 is connected via the hydraulic line 86 to a third check valve 89 and a fourth check valve 90.
  • the third check valve 89 is connected at its second terminal to the first hydraulic load line 73
  • the fourth check valve 90 is connected at its second terminal to the second hydraulic load line 76. If the pressure in the first hydraulic load line 73 drops below the pressure level defined in the hydraulic line 86 via the pressure limiting valve 85, the third check valve 89 opens and adapts the pressure in the first hydraulic Load line 73 to the pressure prevailing in the hydraulic line 86 pressure. Similarly, opens at a pressure drop in the second hydraulic load line 76 under the pressure prevailing in the hydraulic line 86 pressure level, the fourth check valve 90 and adjusts the pressure in the second hydraulic load line 76 to the pressure prevailing in the hydraulic line 86 pressure.
  • a pressure limiting valve 91 is connected. This pressure limiting valve 91 compares the pressure value applied to one of its control inputs in the third hydraulic load line 73 with the pressure setpoint set at the other control input via a spring 92 and opens when the pressure in the third hydraulic load line 73 exceeds the set pressure value set by the spring 92. The pressure in the third hydraulic load line 73 is thereby reduced via the pressure limiting valve 91 in the hydraulic line 86 until the pressure in the third hydraulic load line 73 corresponds to the pressure setpoint set by the spring 92 on the pressure relief valve 91 and the pressure relief valve 91 again in the locked state passes.
  • a pressure limiting valve 93 is connected in parallel to the fourth check valve 90. This compares the prevailing pressure in the fourth hydraulic load line 76, which is guided at one of its control inputs, with a set by a spring 94 at its other control input pressure setpoint and opens when exceeding the pressure in the fourth hydraulic load line 76 through the spring 94th set pressure setpoint. The pressure in the fourth hydraulic load line 76 is reduced as long as the pressure limiting valve 93 in the hydraulic line 86 until the pressure in the fourth hydraulic load line 76 corresponds to the pressure setpoint set by the spring 94 and the Pressure relief valve 93 returns to the locked state.
  • the control of the adjustable second hydraulic pump 75 via a second adjusting device 95, the adjusting piston 96 with the swash plate (not shown in Fig. 1) of the hydraulic pump 75 is mechanically connected.
  • the adjusting piston 96 divides the second adjusting device 95 into a first actuating pressure chamber 97 and into a second actuating pressure chamber 98.
  • the first actuating pressure chamber 97 is connected via a hydraulic line 99 to the first output 101 of a control valve 102, which is designed as a 4/3-way valve.
  • the second actuating pressure chamber 98 is connected via a hydraulic line 103 to the second output 104 of the control valve 102.
  • the first input 105 of the control valve 102 is connected via a hydraulic line 106 and the hydraulic line 86 to the high pressure side port 84 of the feed pump 79.
  • the second input 107 is connected via a hydraulic line 108 to a hydraulic tank 109.
  • the control of the second control valve 102 via a first control input 110 and a second control input 111, which are both designed as electrical actuators.
  • the electric actuating magnet of the first control input 110 is connected to a third output 113 of a converter (not shown in FIGS. 1A or 1B) which controls the mechanical deflection on a steering member 52 (in FIG. 1A) designed as a joystick shown) in the direction of "lifting" in which the hoist 200 determined second deflection dimension converts into a corresponding thereto third electrical signal.
  • the electrical actuating magnet of the second control input 111 is connected via an electrical line 114 to a fourth output 115 of the converter (not shown in FIGS. 1A or 1B), which controls the mechanical deflection on the steering member 52 in the direction of "lowering" in the hoist 200 certain second deflection dimension in a to corresponding fourth electrical signal converts.
  • the controlled electric actuating magnet at the second control input 111 leads to an actuation of the control valve 102, so that the first control pressure chamber 97 of the second adjusting device 95 via the hydraulic line 99 and 106 with the hydraulic tank 109 and the second control pressure chamber 98 of the second adjusting device 95 via the hydraulic line 103, 106 and 86 is connected to the high pressure side port 84 of the second feed pump 79.
  • the adjusting piston 96 of the second adjusting device 95 is then adjusted in the direction of a delivery volume or higher setting pressure at the first port 74 of the adjustable second hydraulic pump 75.
  • This delivery volume at the first port 74 of the adjustable second hydraulic pump 75 is supplied via the third hydraulic load line 73 of the piston rod side actuating pressure chamber 69 of the second lifting cylinder 62 and leads to a displacement of the actuating piston 65 in the direction of the piston-side actuating pressure chamber 70.
  • the higher control pressure in the third hydraulic load line 73 is supplied via the hydraulic line 71 of the piston-side actuating pressure chamber 67 of the first lifting cylinder 61, so that the actuating piston 63 is displaced in the direction of the piston rod-side actuating pressure chamber 68.
  • Lifting cylinder 61 and the deflection of the actuating piston 65 of the second lifting cylinder 62 lead to a rotational movement of the boom 64 down relative to the vehicle body 4 and thus, to a lowering of the loading blade 6 relative to the vehicle body. 4
  • the steering member 52 In a lifting of the loading shovel 6 intended by the driver, the steering member 52 is deflected in the direction of "lifting" in the second deflection dimension determined for the hoist 200.
  • a third electrical signal is generated by the converter of the steering member 52 (shown in Fig. 1A), which is supplied via the electrical line 112 to the electric actuating magnet at the first control input 110 of the control valve 102.
  • the control valve 102 is deflected by the electric actuating magnet at the first control input 110 such that the first control pressure chamber 97 of the second adjusting 95 via the hydraulic line 99, 106 and 86 with the high pressure side port 84 of the second feed pump 79 and the second control pressure chamber 98 of the second adjusting 95th is connected via the hydraulic line 103 and 108 to the hydraulic tank 109.
  • the adjusting piston 96 of the second adjusting device 95 is adjusted in the direction of a delivery volume or higher setting pressure at the second port 77 of the adjustable first hydraulic pump 75.
  • This delivery volume or this higher setting pressure at the second port 77 of the adjustable second hydraulic pump 75 is guided via the fourth hydraulic load line 76 in the piston-side actuating pressure chamber 70 of the second lifting cylinder 62 and leads there to a deflection of the actuating piston 65 in the direction of the piston rod-side actuating pressure chamber 69th
  • Der higher control pressure in the fourth hydraulic load line 76 is supplied via the hydraulic line 72 of the piston rod-side actuating pressure chamber 68 of the first lifting cylinder 61 and leads there to a deflection of the actuating piston 63 in the direction of the piston-side actuating pressure chamber 67th Die Auslenkung des
  • Control piston 63 of the first lifting cylinder 61 as well as the adjusting piston 65 of the second lifting cylinder 62 lead to a rotational movement of the boom 64 upwards relative to the vehicle body 4 and thus to a lifting of the loading blade 6 relative to the vehicle body.
  • a Check valve 116 connected. Via a converter 117 and an electrical line 118, the opener 129 of the switchable check valve 116 is connected to the converter output 115 of the steering member 52.
  • a between the third and fourth hydraulic load line 73 and 76 located 2/2-way valve 119 is opened via an electrical or hydraulic control signal at the second control input 121.
  • This electrical or hydraulic control signal is generated after closing a switch 120 by the operator intentionally planarizing the plane from an electrical transducer disposed on the switch 120 (not shown in FIG. 1B) or from a hydraulic control valve (in FIG. 1B).
  • FIG. 1B not shown
  • the switch 120 When the switch 120 is open, the 2/2-way valve 119 is switched to the locked state by the spring 124 attached to the first control input 123, in which there is no hydraulic connection between the third and fourth hydraulic load lines 73 and 76.
  • Occurring pitching vibrations in particular of the filled loading shovel 6 while the mobile working machine is moving at a higher driving speed, are damped by a hydraulic control arrangement 125.
  • a signal corresponding to the traveling speed of the mobile working machine is guided by the tachogenerator 126 of the vehicle to the input 127 of the hydraulic control arrangement 125. If the vehicle speed is above a certain value and the driver opens a shut-off valve in the interior of the hydraulic control arrangement 125 via a pushbutton, the actuating pressure chambers 68 and 70 of the lifting cylinders 61 and 62 for lifting the loading bucket 6 via the hydraulic load line 73, the hydraulic line 128 and the open shut-off valve is released to a hydraulic accumulator inside the hydraulic control assembly 125.
  • This hydraulic accumulator is charged via a pressure reducing valve in the interior of the hydraulic control arrangement 125 from the second hydraulic pump 75 to the expected load pressure in the lifting cylinders 61 and 62.
  • a sagging of the loading shovel 6 when the hydraulic control arrangement 125 is activated for damping the pitching vibrations of the loading shovel 6 is thus minimized.
  • FIG. 2A and 2B show a second embodiment of the hydraulic control and positioning system according to the invention for a tilting mechanism 100 and for a lifting mechanism 200 with a hydraulic control of the first and second control valves 41 and 102.
  • identical reference numerals are used in Figs. 2A and 2B for like components to Figs. 1A and 1B.
  • the first control input 49 and the second control input 50 of the first control valve 41 and the first control input 110 and the second control input 111 of the second control valve 102 each have a control pressure chamber for the hydraulic control of the first and second control valves 41 and 102.
  • the control pressure chamber of the first control input 49 of the first control valve 41 is supplied via the hydraulic line 51 from the pressure at the first output 129 of the pilot control device 130.
  • the control pressure chamber of the second control input 50 of the first control valve 41 is supplied via the hydraulic line 53 from the pressure at the second output 131 of the pilot control device 130.
  • the control pressure chamber of the first control input 110 of the second control valve 102 is supplied via the hydraulic line 112 from the pressure at the third output 132 of the pilot control device 130.
  • the control pressure chamber of the second control input 111 of the second control valve 102 is supplied via the hydraulic line 114 from the pressure at the fourth output 133 of the pilot control device 130.
  • the first input 134 of the pilot control device 130 is connected via a hydraulic line 135 to the high pressure side port 24 of the first feed pump 19.
  • the second input 136 of the pilot control device 130 is via a Hydraulic line 137 is connected to a hydraulic tank 138.
  • a deflection of designed as a joystick steering member 52 in the first deflection dimension determined for the tilting mechanism 100 the first and second actuating pressures pending at the first and second outlets 129 and 131 are set to control the first control valve 41.
  • the mechanical deflection of the steering member 52 in the first deflection dimension to one of the two control inputs of the two pressure reducing valves 139 and 140 is performed.
  • first control pressure at the first output 129 of the pilot control device 130 is by the pressure reducing valve 139th a ratio pressure between the pressures applied to the first and second inputs 134 and 136 of the pilot control device 130 is switched through to the first output 129 of the pilot control device 130.
  • the hydraulic control and positioning system for a tilting mechanism 100 and a lifting mechanism 200 according to the invention corresponds to the functioning of the corresponding components in the first embodiment of the hydraulic control and positioning system for a tilting mechanism 100 and for a lifting mechanism 200, so that a repeated description of this operation is omitted at this point.
  • the pressure cut 163 consists of the shuttle valve 160 and the pressure relief valve 161.
  • the shuttle valve 160 is connected to the load lines 13 and 16 or 73 and 76 and selects the higher load pressure in the two load lines 13 and 16 or 73 and 76, respectively. This acts as a control pressure for the pressure relief valve 161. If the pressure in the higher load pressure leading load line 13 or 16 or 73 or 76 via a predeterminable by the spring 164 threshold, so opens the pressure relief valve 161 and the pressure in the hydraulic line 45 and 106 is being dismantled. As a result, the hydraulic pump 15 or 75 pivots back to a smaller delivery volume.
  • This function is advantageous in order to avoid a lasting response of the pressure relief valves 31, 33 or 91, 93, when the actuating pistons 3, 5 and 63, 65 run against their stop position.
  • the load pressure would significantly increase upon reaching the stop, so that the pressure relief valves 31, 33 and 91, 93 respond and the load pressure then generating from draining heat into the tank.
  • This is not effective because the hydraulic fluid is unnecessarily heated and the hydraulic pump 15 or 75 unnecessarily performs work. It is therefore more useful when reaching the stop position, strictlyzuschwenken the hydraulic pump 15 and 75.
  • FIG. 3A shows a bucket cylinder hydraulic system of a third embodiment of a hydraulic control and positioning system according to the invention for a working tool in a mobile working machine in which an actuating piston 130 and 131 with a two-sided piston rod is displaceable in each of the first and second bucket cylinders 1 and 2.
  • the adjusting piston 130 is movably guided with its piston-side piston rod through a recess 138 in the first bucket cylinder 1 and in the loading shovel 138 with its body-side piston rod through a recess 139 in the first bucket cylinder 1 and with its body-side end mechanically connected to the body 4.
  • the actuating piston 131 is movably guided with its charge-side piston rod through a recess 140 in the second bucket cylinder 2, mechanically connected at its bucket end with the bucket 6 and movably guided with its body-side piston rod through a recess 141 of the second bucket cylinder 2.
  • the length of the bucket-side piston rod of the actuating piston 130 is dimensioned so that the actuating piston 130 is in contact with the recess 138 at any desired actuating pressure level in the first hydraulic load line 13.
  • the length of the body-side piston rod of the actuating piston 131 is dimensioned such that the actuating piston 131 is in contact with the recess 141 at any desired actuating pressure level in the second hydraulic load line 16.
  • the first bucket cylinder 1 is mechanically connected at its loading bucket end with the loading bucket 6.
  • the second bucket cylinder 2 is mechanically connected with its body-side end with the body 4 so that the actuator piston 131 does not come into contact with the body 4 at any deflection in the second bucket cylinder 2.
  • the displaceable actuating piston 130 separates the first bucket cylinder 1 into a loading-bucket-side positioning chamber 132 and a body-side actuating pressure chamber 133.
  • the displaceable actuating piston 131 separates the second bucket cylinder 2 into a loading-bucket-side positioning chamber 134 and a body-side actuating pressure chamber 135.
  • the two charge-bucket-side positioning pressure chambers 132 and 134 are over a hydraulic line 136, the body-side actuating pressure chambers 133 and 135 connected to each other via a hydraulic line 137.
  • the two charging blade-side actuating pressure chambers 132 and 134 are connected via the first hydraulic load line 13 to the first terminal 14 of the first hydraulic pump 15.
  • the two body-side control pressure chambers 133 and 135 are connected via the second hydraulic load line 16 to the second port 17 of the first hydraulic pump 15.
  • the operation of the further embodiment of the bucket cylinder hydraulic in Fig. 3A corresponds to the operation of the first embodiment of the bucket cylinder hydraulic in Fig. 1A, so that a detailed description thereof can be omitted.
  • the bucket cylinder hydraulic in Fig. 3A differs from the bucket cylinder hydraulic in Fig. 1A solely in the possibility of paralleling the bucket cylinders 1 and 2 due to equal expansion and compression volumes in the two setting pressure chambers 132 and 133, 134 and 135, respectively.
  • Fig. 3B is a Hubzylinderhydraulik shown in a third embodiment of a hydraulic control and positioning system according to the invention for a working tool in a mobile machine in which in the first and second lift cylinders 61 and 62 each have a control piston 142 and 143 is displaceable with a two-sided piston rod.
  • the adjusting piston 142 is movably guided with its boom-side piston rod through a recess 148 in the first lifting cylinder 61 and in the arm 64, with its body-side piston rod through a recess 149 in the first lifting cylinder 61 and with its body-side end mechanically connected to the body 4.
  • the actuating piston 143 is movably guided according to an alternative embodiment with its boom side piston rod through a recess 150 in the second lifting cylinder 62, mechanically connected at its jib end with the boom 64 and movably guided with its body-side piston rod through a recess 151 of the second lifting cylinder 62.
  • the length of the bucket-side piston rod of the actuating piston 142 is dimensioned so that the actuating piston 142 is in contact with the recess 148 at any desired actuating pressure level in the third hydraulic load line 73.
  • the length of the body-side piston rod of the actuating piston 143 is dimensioned such that the actuating piston 143 is in contact with the recess 151 at any desired actuating pressure level in the fourth hydraulic load line 76.
  • the length of the recess 151 in the fourth lifting cylinder 62 is dimensioned such that the actuating piston 143 does not come into contact with the body 4 at any desired pressure ratios in the third and fourth hydraulic load lines 73 and 76.
  • the first lift cylinder 61 is mechanically connected at its boom-side end to the boom 64.
  • the second lifting cylinder 62 is mechanically connected with its body-side end to the body 4 so that the adjusting piston 143 does not come into contact with the body 4 at any deflection in the second lifting cylinder 62.
  • the displaceable actuating piston 142 separates the first lifting cylinder 61 into a boom-side adjusting chamber 144 and a body-side actuating pressure chamber 145.
  • the displaceable actuating piston 143 separates the second lifting cylinder 62 into a boom-side actuating pressure chamber 146 and a body-side actuating pressure chamber 147.
  • the two boom-side actuating pressure chambers 144 and 146 are over a hydraulic line 151, the body-side adjusting pressure chambers 145 and 147 via a hydraulic line 152 connected to each other.
  • the two boom-side control pressure chambers 145 and 146 are connected via the third hydraulic load line 73 to the first port 74 of the second hydraulic pump 75.
  • the two body-side control pressure chambers 145 and 146 are connected via the fourth hydraulic load line 76 to the second port 77 of the second hydraulic pump 75.
  • the operation of the other embodiment of the lifting cylinder hydraulic in Fig. 3B corresponds to the operation of the first embodiment of the lifting cylinder hydraulic in Fig. 1B, so that a detailed description thereof is omitted.
  • the lift cylinder hydraulic in Fig. 3B differs from the lift cylinder hydraulic in Fig. 1B only in the possibility of parallel connection of the lift cylinders 61 and 62 due to equal expansion and compression volumes in the two set pressure chambers 144 and 145 and 146 and 147.

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Claims (23)

  1. Outil de levage (100) destiné à un engin mobile pourvu d'un système de commande et de réglage hydraulique et d'un outil de travail (6), avec au moins un premier et un deuxième cylindre de levage (61, 62), dans lesquels peuvent être déplacés des pistons de cylindre (63, 65), dont la position ou le sens de déplacement dans les cylindres de levage (61, 62) détermine la hauteur de levage ou le sens de déplacement vertical de l'outil de travail (6) par rapport à une carrosserie (4) de l'engin mobile, chaque piston de cylindre (63, 65) séparant le cylindre de levage associé (61, 62) en respectivement deux chambres de pression de commande (67 et 68, 69 et 70), et avec une première pompe hydraulique (75) ajustable en ce qui concerne le volume d'alimentation, dont le premier raccord (74) est relié en fonction du sens de déplacement vertical de l'outil de travail (6) avec une des chambres de pression de commande (67) du premier cylindre de levage (61) et une des chambres de pression de commande (69) du deuxième cylindre de levage (62) et dont le deuxième raccord (77) est relié dans un circuit fermé avec l'autre chambre de pression de commande (68) du premier cylindre de levage (61) et l'autre chambre de pression de commande (70) du deuxième cylindre de levage (62), caractérisé en ce qu'une chambre de pression de commande (67) côté piston du premier cylindre de levage (61) est reliée à une chambre de pression de commande (69) côté tige de piston du deuxième cylindre de levage (62) à l'aide d'une première conduite hydraulique (71) et une chambre de pression de commande (68) côté tige de piston du premier cylindre de levage (61) est reliée avec une chambre de pression de commande (70) côté piston du deuxième cylindre de levage (62) à l'aide d'une deuxième conduite hydraulique (72) et en ce que le premier cylindre de levage (61) et le piston de commande (65, 143) du deuxième cylindre de levage (62) sont reliés à un bras (64) reliant l'outil de travail (6) à la carrosserie (4) de l'engin mobile et le deuxième cylindre de levage (62) et le piston de commande (63, 142) du premier cylindre de levage (61) peuvent être reliés à la carrosserie (4) de l'engin mobile.
  2. Outil de levage selon la revendication 1, caractérisé en ce que chaque première chambre de pression de commande (68 ; 69) est adjacente au piston de cylindre (63 ; 65) correspondant à l'aide d'une surface de génération de pression (A1), qui est plus petite que la surface de génération de pression (A2), avec laquelle chaque autre deuxième chambre de pression de commande (67 ; 70) est adjacente sur le piston de cylindre (63 ; 65) correspondant et en ce que chaque raccord (74 ; 77) de la pompe hydraulique (75) est relié à une première chambre de pression de commande (68 ; 69) présentant une surface de génération de pression (A1) et une deuxième chambre de pression de commande (70 ; 67) présentant une surface de génération de pression (A2) plus grande.
  3. Outil de levage selon la revendication 1 ou 2, caractérisé en ce que les deux chambres de pression de commande côté bras (144, 146) du premier et du deuxième cylindre de levage (61, 62) sont reliées à l'aide d'une première conduite hydraulique (151) et en ce que les deux chambres de pression de commande côté carrosserie (145, 147) du premier et du deuxième cylindre de levage (61, 62) sont reliées à l'aide d'une deuxième conduite hydraulique (152).
  4. Outil d'inclinaison (200) destiné à un engin mobile pourvu d'un système de commande et de réglage hydraulique et d'une pelle de chargement (6) servant d'outil de travail (6) avec au moins un premier et un deuxième cylindre de pelle (1, 2), dans lesquels peuvent se déplacer des pistons de cylindre (3, 5), dont la position ou le sens de déplacement dans les cylindres de pelle (1, 2) détermine l'angle d'inclinaison ou le sens d'inclinaison de la pelle de chargement (6) par rapport à une carrosserie (4), chacun des pistons de cylindre (3, 5) séparant le cylindre de pelle correspondant (1, 2) respectivement en deux chambres de pression de commande (7 et 8, 9 et 10), et une pompe hydraulique (15) ajustable en ce qui concerne le volume d'alimentation, dont le premier raccord (14) est relié en fonction du sens d'inclinaison de la pelle de chargement (6) à une des chambres de pression de commande (7) du premier cylindre de pelle (1) et à une des chambres de pression de commande (10) du deuxième cylindre de pelle (2) et dont le deuxième raccord (17) est relié dans un circuit fermé à l'autre chambre de pression de réglage (8) du premier cylindre de pelle (1) et à l'autre chambre de pression de commande (9) du deuxième cylindre de pelle (2), caractérisé en ce que la chambre de pression de commande côté piston (7) du premier cylindre de pelle (1) est reliée à la chambre de pression de commande côté tige de piston (10) du deuxième cylindre de pelle (2) par une première conduite hydraulique (11) et la chambre de pression de commande côté tige de piston (8) du premier piston de pelle (1) est reliée à la chambre de pression de commande côté piston (9) du deuxième cylindre de pelle (2) à l'aide d'une deuxième conduite hydraulique (12) et en ce que le premier cylindre de pelle (1) et le piston de commande (5, 131) du deuxième cylindre de pelle (2) sont reliés à la pelle de chargement (6) et le deuxième cylindre de pelle (2) et le piston de commande (3, 130) du premier cylindre de pelle (1) peuvent être reliés à la carrosserie (4) de l'engin mobile.
  5. Outil d'inclinaison selon la revendication 4, caractérisé en ce qu'une première chambre de pression de commande (8 ; 10) est adjacente sur le piston de cylindre correspondant (3 ; 5) à l'aide d'une surface de génération de pression (A1), qui est plus petite que la surface de génération de pression (A2), avec laquelle chaque autre deuxième chambre de pression de commande (7 ; 9) est adjacente sur le piston de cylindre correspondant (3 ; 5) et en ce que chaque raccord (14 ; 17) de la pompe hydraulique (15) est relié à une première chambre de pression de commande (10 ; 8) présentant une surface de génération de pression (A1) plus petite et à une deuxième chambre de pression de commande (9 ; 7) présentant une surface de génération de pression (A2) plus grande.
  6. Outil d'inclinaison selon la revendication 4 ou 5, caractérisé en ce que les deux chambres de pression de commande côté pelle de chargement (132, 134) du premier et du deuxième cylindre de pelle (1, 2) sont reliées par une première conduite hydraulique (136) et les deux chambres de pression de commande côté carrosserie (133, 135) du premier et du deuxième cylindre de pelle (1, 2) sont reliées par une deuxième conduite hydraulique (137).
  7. Outil de levage et d'inclinaison selon les revendications 1 et 4, caractérisé en ce que le sens d'alimentation de la première pompe hydraulique (75) en fonctionnement à deux cadrans détermine le sens de déplacement vertical de l'outil de travail (6) ou le sens d'alimentation de la pompe hydraulique (15) en fonctionnement à deux cadrans également détermine le sens d'inclinaison de la pelle de chargement (6).
  8. Outil de levage et d'inclinaison selon les revendications 1 et 4, caractérisé en ce que le volume d'alimentation amené sur le premier et le deuxième raccord (74, 77) de la première pompe hydraulique (75) détermine la hauteur de levage de l'outil de travail (6) ou le volume d'alimentation amené sur le premier et deuxième raccord (14, 17) de la deuxième pompe hydraulique (15) détermine l'angle d'inclinaison de la pelle de chargement (6).
  9. Outil de levage et d'inclinaison selon la revendication 8, caractérisé en ce que le réglage du sens d'alimentation de la deuxième pompe hydraulique (15) et du volume d'alimentation amené sur le premier et deuxième raccord (14, 17) de la deuxième pompe hydraulique (15) s'effectue en fonction d'une déviation appliquée sur un organe dirigeable (52) conçu comme un manche dans une première dimension de déviation et le réglage du sens de rotation de la première pompe hydraulique (75) et de la pression de commande générée sur le premier et deuxième raccord (74, 77) de la première pompe hydraulique (75) s'effectue en fonction d'une déviation appliquée sur un organe dirigeable (52) conçu comme un manche dans une deuxième dimension de déviation.
  10. Outil de levage et d'inclinaison selon la revendication 9, caractérisé en ce qu'une première servovalve (41) est commandée en fonction de la déviation de l'organe dirigeable (52) dans la première dimension de déviation et une deuxième servovalve (102) est commandée en fonction de la déviation de l'organe dirigeable (52) dans une deuxième dimension de déviation.
  11. Outil de levage et d'inclinaison selon la revendication 10, caractérisé en ce que la déviation de la première servovalve (41) s'effectue à l'aide d'aimants de commande électriques sur les raccords de commande (49, 50) de la première servovalve (41), le premier raccord de commande (49) obtenant un premier signal électrique, qui correspond à la déviation de l'organe dirigeable (52) dans le sens correspondant au sens d'inclinaison de la première dimension de déviation, et l'autre raccord de commande (50) obtenant d'un transformateur de l'organe dirigeable (52) un deuxième signal électrique, qui correspond à la déviation de l'organe dirigeable (52) dans le sens correspondant au sens d'inclinaison de la première dimension de déviation, et en ce que la déviation de la deuxième servovalve (102) s'effectue à l'aide d'aimants de commande électriques sur les raccords de commande (110, 111) de la deuxième servovalve (102), le premier raccord de commande (110) obtenant un troisième signal électrique, qui correspond à la déviation de l'organe dirigeable (52) dans le sens correspondant au déplacement de levage dans la deuxième dimension de déviation, et l'autre raccord de commande (111) obtenant d'un transformateur de l'organe dirigeable (52) un quatrième signal électrique, qui correspond à la déviation de l'organe dirigeable (52) dans le sens correspondant au déplacement de descente de la deuxième dimension de déviation.
  12. Outil de levage et d'inclinaison selon la revendication 10, caractérisé en ce que la déviation de la première servovalve (41) s'effectue à l'aide de pressions de commande, qu'un appareil de commande (130) génère à partir de la déviation de l'organe dirigeable (52) dans la première dimension de déviation et alimente les chambres de commande se trouvant sur les deux raccords de commande (49, 50) de la première servovalve (42), et la déviation de la deuxième servovalve (102) s'effectue à l'aide de pressions de commande, que l'appareil de commande (130) génère à partir de la déviation de l'organe dirigeable (52) dans la deuxième dimension de déviation et alimente les chambres de commande se trouvant sur les deux raccords de commande (110, 111) de la servovalve (102).
  13. Outil de levage et d'inclinaison selon la revendication 12, caractérisé en ce que l'appareil de commande (130) génère à partir d'une première paire de réducteurs de pression (143) composée de deux réducteurs de pression (139, 140), dont les entrées sont reliées respectivement à un raccord (24) côté haute pression d'une première pompe d'alimentation (19) et à un réservoir hydraulique (138), les pressions de commande correspondant à la déviation de l'organe dirigeable (52) dans les deux sens de la première dimension de déviation afin de commander la première servovalve (42), et en ce que l'appareil de commande génère à l'aide d'une deuxième paire de réducteurs de pression (144) composé de deux réducteurs de pression (141, 142), dont les entrées sont reliées respectivement à un raccord (24) côté haute pression d'une première pompe d'alimentation (19) et à un premier réservoir hydraulique (138), les pressions de commande correspondant aux deux sens de la deuxième dimension de déviation de l'organe dirigeable (52) pour la deuxième servovalve (102).
  14. Outil de levage et d'inclinaison selon l'une des revendications 10 à 13, caractérisé en ce que la première et la deuxième servovalve (41, 102) sont respectivement une soupape à canaux 4/3, le premier raccord d'entrée (44, 105) de la première servovalve (41) étant relié au raccord côté haute pression (24) de la première pompe d'alimentation (19), le premier raccord d'entrée (105) de la deuxième servovalve (102) étant relié au raccord côté haute pression (84) d'une deuxième pompe d'alimentation (79), le deuxième raccord d'entrée (46, 107) de la première et de la deuxième servovalve (41, 102) étant relié chacun à un réservoir hydraulique (48, 109), le premier raccord de sortie (40) de la première servovalve (41) étant relié à une première chambre de pression de commande (37) d'un premier dispositif de réglage (35), le premier raccord de sortie (101) de la deuxième servovalve (102) étant relié à une première chambre de pression de commande (97) d'un deuxième dispositif de réglage (95), le deuxième raccord de sortie (43) de la première servovalve (41) étant relié à une deuxième chambre de pression de commande (38) d'un premier dispositif de réglage (35) et le deuxième raccord de sortie (104) de la deuxième servovalve (102) étant relié à une deuxième chambre de pression de commande (98) d'un deuxième dispositif de réglage (95).
  15. Outil de levage et d'inclinaison selon la revendication 14, caractérisé en ce que le réglage de la deuxième pompe hydraulique (15) en ce qui concerne le sens d'alimentation et le volume d'alimentation amené sur le premier et le deuxième raccord (14, 17) s'effectue à l'aide du premier dispositif de réglage (35) et le réglage de la première pompe hydraulique (75) en ce qui concerne le sens d'alimentation et le volume d'alimentation amené sur le premier et deuxième raccord (74, 77) s'effectue à l'aide du deuxième dispositif de réglage (95).
  16. Outil de levage et d'inclinaison selon l'une des revendications 13 à 15, caractérisé en ce que la deuxième pompe hydraulique (15) et la première pompe d'alimentation (19) ou la première pompe hydraulique (75) et la deuxième pompe d'alimentation (79) sont entraînées respectivement par un arbre commun (18, 78) d'un engin commun ou distinct, en particulier d'un groupe électrogène diesel.
  17. Outil de levage ou d'inclinaison selon l'une des revendications 13 à 16, caractérisé en ce que un raccord côté basse pression (20) de la première pompe d'alimentation (19) est relié par un filtre (22) à un réservoir hydraulique (23), un raccord côté basse pression (80) de la deuxième pompe d'alimentation (79) est relié par un filtre (82) à un réservoir hydraulique (83), le raccord côté haute pression (24) de la première pompe d'alimentation (19) est relié à l'aide d'un clapet anti-retour (29, 30) à une première conduite de charge hydraulique (13) reliée à un premier raccord (14) de la deuxième pompe hydraulique (15) et à une deuxième conduite de charge hydraulique (16) reliée à un deuxième raccord (17) de la deuxième pompe hydraulique (15) et le raccord côté haute pression (84) de la deuxième pompe d'alimentation (79) est relié à l'aide d'un clapet anti-retour (89, 90) à une troisième conduite de charge hydraulique (73) reliée à un premier raccord (74) de la première pompe hydraulique (75) et à une quatrième conduite de charge hydraulique (76) reliée à un deuxième raccord (77) de la première pompe hydraulique (75).
  18. Outil de levage et d'inclinaison selon la revendication 17, caractérisé en ce qu'un clapet anti-retour (55, 116) pourvu d'un dispositif d'ouverture (58, 129) est prévu dans la troisième et la quatrième conduite de charge hydraulique (13, 73).
  19. Outil de levage et d'inclinaison selon la revendication 18, caractérisé en ce que le deuxième signal de réglage électrique commande après conversion à la pression correspondante un dispositif d'ouverture (58) du clapet anti-retour (55) intégré dans la première conduite de charge hydraulique (13) et le quatrième signal de commande électrique commande après conversion à la pression correspondante un dispositif d'ouverture (129) du clapet anti-retour (116) intégré dans la troisième conduite de charge hydraulique (73).
  20. Outil de levage et d'inclinaison selon la revendication 17, caractérisé en ce que la deuxième pression de commande générée par l'appareil de commande (130) commande un dispositif d'ouverture (58) du clapet anti-retour (55) intégré dans la première conduite de charge hydraulique (13) et la quatrième pression de commande générée par l'appareil de commande (130) commande un dispositif d'ouverture (129) du clapet anti-retour (116) intégré dans la troisième conduite de charge hydraulique (73).
  21. Outil de levage et d'inclinaison selon la revendication 17, caractérisé en ce qu'une soupape à canaux 2/2 (119) se trouve entre la troisième et la quatrième conduite de charge hydraulique (73, 76), laquelle s'ouvre à l'état de fonctionnement « réglage flottant » du bras (64) en appliquant un signal électrique sur un aimant de commande électrique se trouvant à l'entrée de commande (121) de la soupape à canaux 2/2 (119) ou, en variante, en appliquant une pression de réglage dans une chambre de commande se trouvant à l'entrée de commande (121) de la soupape à canaux 2/2 119).
  22. Outil de levage et d'inclinaison selon la revendication 17, caractérisé en ce que la troisième conduite de charge hydraulique (73) est reliée par une conduite hydraulique (128) à une installation de commande hydraulique (125) afin d'atténuer les rotations planes de l'outil de travail (6) au cours du déplacement de l'engin mobile.
  23. Outil de levage et d'inclinaison selon la revendication 22, caractérisé en ce qu'un signal électrique correspondant à la vitesse de l'engin mobile est introduit par une génératrice tachymétrique (126) de l'engin mobile à l'entrée (127) de l'installation de commande hydraulique (125) afin d'atténuer les rotations planes de l'outil de travail (6) au cours du déplacement de l'engin mobile.
EP04733802A 2003-07-11 2004-05-19 Systeme de commande et de reglage pour un mecanisme de levage et d'inclinaison de l'outil d'un engin mobile Expired - Lifetime EP1616103B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10331533A DE10331533B4 (de) 2003-07-11 2003-07-11 Steuer- und Stellsystem für ein Hub- und Kippwerk eines Arbeitswerkzeugs in einer mobilen Arbeitsmaschine
PCT/EP2004/005437 WO2005008075A1 (fr) 2003-07-11 2004-05-19 Systeme de commande et de reglage pour un mecanisme de levage et d'inclinaison de l'outil d'un engin mobile

Publications (2)

Publication Number Publication Date
EP1616103A1 EP1616103A1 (fr) 2006-01-18
EP1616103B1 true EP1616103B1 (fr) 2006-08-23

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EP04733802A Expired - Lifetime EP1616103B1 (fr) 2003-07-11 2004-05-19 Systeme de commande et de reglage pour un mecanisme de levage et d'inclinaison de l'outil d'un engin mobile

Country Status (5)

Country Link
US (1) US20070175210A1 (fr)
EP (1) EP1616103B1 (fr)
JP (1) JP2007506916A (fr)
DE (2) DE10331533B4 (fr)
WO (1) WO2005008075A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8843282B2 (en) * 2011-11-02 2014-09-23 Caterpillar Inc. Machine, control system and method for hovering an implement
CN104929170B (zh) * 2015-05-27 2017-08-25 徐工集团工程机械股份有限公司科技分公司 一种装载机举升动臂节能系统
US10405480B2 (en) 2017-06-28 2019-09-10 Cnh Industrial America Llc Closed-loop dual-pressure position control of an implement stabilizer wheel
CN116689528A (zh) * 2023-06-16 2023-09-05 西南铝业（集团）有限责任公司 薄板拉伸机钳口夹紧控制方法、控制系统及薄板拉伸机

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Also Published As

Publication number Publication date
DE502004001278D1 (de) 2006-10-05
EP1616103A1 (fr) 2006-01-18
WO2005008075A1 (fr) 2005-01-27
US20070175210A1 (en) 2007-08-02
DE10331533A1 (de) 2005-02-10
DE10331533B4 (de) 2005-11-03
JP2007506916A (ja) 2007-03-22

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