EP3939930A1 - Entraînement de levage hydraulique d'une machine de travail mobile - Google Patents

Entraînement de levage hydraulique d'une machine de travail mobile Download PDF

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Publication number
EP3939930A1
EP3939930A1 EP21181382.9A EP21181382A EP3939930A1 EP 3939930 A1 EP3939930 A1 EP 3939930A1 EP 21181382 A EP21181382 A EP 21181382A EP 3939930 A1 EP3939930 A1 EP 3939930A1
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EP
European Patent Office
Prior art keywords
valve
lifting drive
lowering
container
line
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.)
Pending
Application number
EP21181382.9A
Other languages
German (de)
English (en)
Inventor
Markus Schwab
Britta Natrop
Niko Siemering
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.)
STILL GmbH
Original Assignee
STILL GmbH
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 STILL GmbH filed Critical STILL GmbH
Publication of EP3939930A1 publication Critical patent/EP3939930A1/fr
Pending legal-status Critical Current

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Classifications

    • 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

Definitions

  • the invention relates to a hydraulic lifting drive of a mobile working machine, in particular an industrial truck, for raising and lowering a load handling device, the lifting drive having a lifting cylinder device and a control valve device for controlling the lowering operation and the lifting operation of the lifting drive, the control valve device being connected to a consumer line leading to the lifting cylinder device , is connected to a container line leading to a container and to a conveying line connected to a pump.
  • a load handling device For handling loads, industrial trucks are provided with a load handling device, which is generally formed by a lifting carriage that can be raised and lowered on the lifting frame and an attachment attached thereto.
  • the attachment can be designed, for example, as a load fork consisting of forks, by means of which a load, for example a pallet, can be driven under.
  • the deflection of the control valve in lowering mode determines the lowering speed of the load-carrying device.
  • a limit value of 0.6 m/s for a maximum lowering speed of the load handling device or a load has been established in recent years.
  • a discharge pressure compensator in the tank line leading from the control valve device to the tank, which is controlled by a spring device and the pressure present in the tank line between the control valve device and the discharge pressure compensator in the direction of a flow position and is acted upon by the pressure present in the consumer line in the direction of a blocking position. If a lifted load or an empty load-carrying means is to be lowered with such lifting drives, the control valve device is actuated into an open position in which the consumer line is connected to the container line.
  • the discharge pressure compensator is in series with the control valve device switched.
  • a sink volume flow begins to flow from the lifting cylinder device to the container via the control valve device and the discharge pressure compensator, and the load-receiving means is lowered.
  • the maximum flow rate for lowering the load handling attachment is limited by the adjustment of the discharge pressure compensator.
  • the pressure in the consumer line before the control valve device acts on the discharge pressure compensator on one side in the direction of a blocking position, and the spring force of the spring device and the pressure in the container line between the control valve device and the discharge pressure compensator and thus the pressure downstream on the other side in the direction of a flow position the control valve device.
  • the sink volume flow increases until a maximum pressure drop of 4 bar, for example, occurs at the control valve device, which corresponds to the spring force of the discharge pressure compensator.
  • the discharge pressure compensator goes into the control position and moves in the direction of the blocking position until this pressure drop of 4 bar, for example, is kept constant at the control valve device.
  • lifting frames with several lifting stages for example a lifting frame with a free lift as the first lifting stage and a mast lift as the second lifting stage, result in too low maximum lowering speeds when lowering with low load pressures, for example load pressures below approx. 30 bar, in the first lifting stage because the control valve device does not open far enough for this operating state or the series connection of the control valve device and discharge pressure compensator represents too great a resistance.
  • the low load pressure for lowering the load handling attachment is therefore not sufficient to achieve the required maximum lowering speed.
  • control valve device In the case of generic lifting drives, the control valve device would have to open much further for this operating state of lowering with low load pressures, so that higher lowering speeds can be achieved. However, this would mean that with higher load pressures, for example load pressures above 30 bar, impermissibly high lowering speeds of the load-receiving means would occur.
  • the present invention has for its object to provide a linear actuator of the type mentioned are available in which in a simple manner at low Last pressures higher lowering speeds of the load handling device can be achieved.
  • a bypass line leading to the container is connected to the consumer line, in which a bypass valve is arranged, the bypass valve having a lowering valve designed as a proportional valve and a release valve designed as a switching valve, the bypass valve being designed in such a way that in the lowering operation of the lifting drive below a limit load pressure of the lifting drive, a lowering volume flow flowing out of the lifting drive flows away via the control valve device and the bypass valve into the container and in the lowering operation of the lifting drive above the limiting load pressure of the lifting drive, a lowering volume flow flowing out of the lifting drive flows out exclusively via the control valve device into the container .
  • the idea according to the invention is therefore to provide the bypass line branching off from the consumer line with the bypass valve arranged therein parallel to the control valve device. It is also essential to the invention that the bypass valve is designed in such a way that in lowering operation of the lifting drive below a limit load pressure of the lifting drive, a lowering volume flow flowing out of the lifting drive flows out via the control valve device and the bypass valve into the container and in lowering operation of the lifting drive above the limiting load pressure of the lifting drive Lift drive outflowing sink volume flow flows out exclusively via the control valve device in the container. Below the limit load pressure, a sink volume flow can thus flow off via the control valve device and an additional sink volume flow can flow off via the bypass valve to the container.
  • the bypass valve has a lowering valve designed as a proportional valve and a release valve designed as a switching valve. This will A high level of operational reliability is achieved, since in the event of a fault in one of the two valves, for example the proportional valve or release valve jammed in the open position, the lowering movement can be stopped at any time via the other valve of the bypass valve.
  • the lowering valve designed as a proportional valve has a blocking position and a flow position.
  • a proportional valve of this type requires little construction work and makes it possible to release and shut off the bypass line in a simple manner.
  • the release valve designed as a switching valve has a blocking position and a flow position.
  • Such a switching valve requires little structural effort and makes it possible to release and shut off the bypass line in a simple manner.
  • the lowering valve is electrically actuated and the release valve is electrically actuated, and the lowering valve and the release valve are operatively connected to an electronic control device for actuation. This enables simple and safe control of the lowering valve and the release valve.
  • the lowering valve is preferably acted upon by a spring device in the direction of the blocking position and by means of an electrical actuating device, in particular a proportional magnet, in the direction of the flow position. This achieves a high level of operational reliability, since the lowering valve is actuated by the spring device into the blocking position when it is not actuated.
  • the release valve is preferably acted upon by a spring device in the direction of the blocking position and by means of an electrical actuating device, in particular a switching magnet, in the direction of the flow position. This achieves a high level of operational reliability, since the release valve is actuated by the spring device into the blocking position in the non-actuated state.
  • the electronic control device is operatively connected to a pressure sensor device that detects the load pressure of the lifting drive in the consumer line, the electronic control device being designed in such a way that in lowering operation below the limit load pressure of the lifting drive, the release valve and the lowering valve are actuated into the flow positions and in the lowering operation above the load limit pressure of the lifting drive, the release valve and the lowering valve are actuated into the blocking positions.
  • the load pressure of the lifting drive can be easily detected by the electronic control device in order to control the proportional valve and the release valve in the flow positions in lowering operation below the limit load pressure.
  • the bypass valve has a shut-off valve which has a blocking position and a flow position, the shut-off valve being actuated by a spring device in the direction of the flow position and by the load pressure of the lifting drive present in the consumer line in the direction of the blocking position , wherein the spring device of the shut-off valve is set to the limit load pressure of the lifting drive.
  • shut-off valve With such a shut-off valve, whose spring device is set to the limit load pressure, it is achieved in a simple manner - without having to use a pressure sensor device to detect the load pressure of the lifting drive - that the bypass line is open in lowering operation below the limit load pressure, so that via the open proportional valve and the open release valve, an additional sink volume flow can flow from the lifting drive to the container.
  • the shut-off valve In lowering operation above the limit load pressure, the shut-off valve is actuated in the blocking position, which reliably prevents a lowering volume flow from flowing out via the proportional valve and the release valve to the container in lowering operation above the limit load pressure and resulting in impermissibly high lowering speeds of the load handling equipment.
  • the invention has a number of advantages.
  • the parallel connection of the bypass valve to the control valve device enables the lowering speed of the To increase load handling equipment with and without partial load, especially in the free lift of a mast. As a result, an increase in the handling capacity of the working machine can be achieved.
  • bypass line with the bypass valve arranged therein can be easily connected to the consumer line, so that the bypass line with the bypass valve can be easily retrofitted to existing lifting drives.
  • bypass valve can be used in a simple manner on different lifting drives, for example different work machines with different masts, since the limit load pressure can be easily adapted to the respective lifting drive.
  • FIG 1 is a schematic structure of a hydraulic lifting drive 1 according to the invention of a mobile working machine, not shown in detail, for example an industrial truck.
  • the elevating drive 1 has a mast 2 on which a lifting device 3 is arranged such that it can be raised and lowered.
  • the load handling device 3 consists of a lifting carriage 4 that can be moved vertically on the mast 2 and to which, for example, a load fork 5 formed by forks is attached as an attachment.
  • the mast 2 consists of a standing mast 2a and an extension mast 2b which can be raised and lowered on the standing mast 2a and on which the load handling device 3 is arranged so that it can be raised and lowered.
  • the mast 2 of figure 1 has at least two lifting stages.
  • a hydraulic lifting cylinder device 10a is provided for raising and lowering the load handling device 3 relative to the extending mast 2b.
  • the lifting cylinder device 10a forms a first lifting stage (free lift).
  • a flexible traction device 6, for example a lifting chain is provided figure 1 is attached at a first end to the lifting carriage 4, is guided via a deflection roller 7 on the extendable piston rod of the lifting cylinder device 10a and is attached at a second end to the extension mast 2b.
  • a hydraulic lifting cylinder device 10b is used to raise and lower the extension mast 2b relative to the stationary mast 2a.
  • the lifting cylinder device 10b forms a second lifting stage (mast lift).
  • the lifting cylinder device 10a is connected to the lifting cylinder device 10b by means of a pressure medium line 11 .
  • the lifting cylinder device 10a, 10b can be actuated by means of a control valve device 12, with which the lowering operation and the lifting operation of the load handling device 3 can be controlled.
  • the control valve device 12 is designed as a proportional valve 13 which throttles in intermediate positions and has a blocking position 13a designed as a neutral position, a lifting position 13b and a lowering position 13c.
  • the control valve device 12 is connected to a delivery line 14 of a pump 15, which sucks in pressure medium from a container 17 by means of an intake line 16, to a container line 18 leading to a container 17 and to a pressure medium line 19 leading to the lifting cylinder device 10a, 10b.
  • the blocking position 13a of the control valve device 12 the connection between the consumer line 19 and the delivery line 14 and the container line 18 is blocked.
  • the delivery line 14 is connected to the consumer line 19.
  • the lowered position 13c of Control valve device 12 is the consumer line 19 with the tank line 18 in connection.
  • the control valve device 12 can be operated manually by means of a lever or electrically by means of an electronic control device 20 .
  • control valve device 12 can have a separate lifting valve for controlling the lifting operation of the load-carrying means 3 and a separate lowering valve for controlling the lowering operation of the load-carrying means 3 .
  • a drain pressure compensator In the tank line 18 leading from the control valve device 12 to the tank 17, a drain pressure compensator, not shown in detail, can be arranged.
  • the outflow pressure compensator is preferably designed as a proportional valve that throttles in intermediate positions with a flow position and a blocking position and is controlled by a spring device and the pressure present in the tank line 18 between the control valve device 12 and the outflow pressure compensator and thus the pressure present in the tank line 18 downstream of the control valve device 12 the flow position is actuated and actuated by the load pressure of the linear actuator 1 present in the consumer line 19 and thus by the pressure present in the consumer line 19 upstream of the control valve device 12 in the direction of the blocking position.
  • a bypass line 30 leading to the container 17 is connected to the consumer line 19 according to the invention, in which a bypass valve 31 is arranged.
  • the bypass valve 31 has a lowering valve 32 designed as a proportional valve and a release valve 33 designed as a switching valve, which are connected into the bypass line 35 .
  • the additional bypass valve 31 is thus arranged parallel to the control valve device 12 and is connected via the bypass line 30 to the consumer line 19 connecting the control valve device 12 and the lifting cylinder device 10a, 10b.
  • the lowering valve 32 designed as a proportional valve has a blocking position 32a and a flow position 32b.
  • the Blocking position 32a is leak-tight and has a non-return valve blocking in the direction of container 17 .
  • the release valve 33 designed as a switching valve has a blocking position 33a and a flow position 33b.
  • the blocking position 33a is designed to be leak-proof and has a non-return valve blocking in the direction of the container 17 .
  • the lowering valve 32 and the release valve 33 are each actuated electrically and are operatively connected to the electronic control device 20 for actuation.
  • the lowering valve 32 can be acted upon by a spring device 35 in the direction of the blocking position 32a and by means of an electrical actuating device 36, for example a proportional magnet, in the direction of the flow position 32b.
  • the release valve 33 can be acted upon by a spring device 37 in the direction of the blocking position 33a and by means of an electrical actuating device 38, for example a switching magnet, in the direction of the flow position.
  • the bypass valve 31 is designed in such a way that when the lifting drive 1 is lowering below a load limit pressure of the lifting drive 1, a lowering volume flow flowing out of the lifting drive 1 flows via the control valve device 12 and the bypass valve 31 into the container 17 and when the lifting drive 1 is lowering above the load limit pressure of the lifting drive 1, a sink volume flow flowing out of the lifting drive 1 flows out into the container 17 exclusively via the control valve device 12 .
  • the electronic control device 20 is operatively connected to a pressure sensor device 40 that detects the load pressure of the lifting drive 1 that is present in the consumer line 19 .
  • the electronic control device 20 is designed such that the release valve 33 and the lowering valve 32 each in the lowering operation below the limit load pressure of the lifting drive Flow position 32a, 33a are actuated and the release valve 33 and the proportional valve 32 are each actuated in the blocking position 32b, 33b in lowering operation above the limit load pressure of the linear actuator 1.
  • the lifting drive figure 1 works as follows.
  • the bypass valve 31 is not active.
  • the release valve 33 and the lowering valve 32 of the bypass valve 31 are not controlled by the control device 20 and are in the blocking positions 32a, 33a, so that the lowering operation of the lifting drive 1 takes place exclusively via the control valve device 12 actuated in the lowering position 13c.
  • no sink volume flow flows from the lifting cylinder device 10a, 10b to the container 17 via the bypass valve 30 .
  • the bypass valve 31 is active.
  • the release valve 33 and the lowering valve 32 of the bypass valve 31 are controlled by the control device 20 in the flow positions 32b, 33b.
  • the lowering operation of the lifting drive 1 thus takes place via the control valve device 12 and additionally via the bypass valve 31.
  • an additional lowering volume flow is thus established, which is supplied by the lifting cylinder device 10a, 10b flows to the container 17.
  • This additional lowering volume flow via the bypass valve 30 enables higher lowering speeds at partial loads below the limit load pressure.
  • a further lowering movement can be stopped at any time via the release valve 33 actuated into the blocking position 33a. If the release valve 33 should remain in the flow position 33b after the lowering operation has been stopped in the event of a fault, it can be adjusted accordingly a further lowering movement can be stopped at any time via the lowering valve 32 actuated into the blocking position 32a.
  • the bypass valve 31 is also designed in such a way that in the lowering mode of the lifting drive 1 below a limit load pressure of the lifting drive 1, a lowering volume flow flowing out of the lifting drive 1 flows via the control valve device 12 and the bypass valve 31 into the container 17 and in the lowering mode of the lifting drive 1 above the limit load pressure of the Lifting drive 1 flows out of the lifting drive 1 outflowing sink volume flow exclusively via the control valve device 12 into the container 17 .
  • the bypass valve 31 provided with a shut-off valve 60 having a blocking position 60a and a flow position 60b.
  • the shut-off valve 60 is actuated by a spring device 61 in the direction of the flow position 60b and by the load pressure of the lifting drive 1 present in the consumer line 19 in the direction of the blocking position 60a.
  • a control line 63 is routed from the bypass line 30 upstream of the shut-off valve 60 to a control surface of the shut-off valve 60 acting in the direction of the blocking position 60a.
  • the spring device 61 of the shut-off valve 60 is set to the load limit pressure of the lifting drive 1 .
  • the lifting drive figure 2 works as follows.
  • the bypass valve 31 is not active because the load pressure of the lifting drive 1 is above the switching point of the shut-off valve 60 and the shut-off valve 60 is actuated by the load pressure of the lifting drive 1 into the blocking position 60a.
  • the bypass valve 31 is thus shut off, so that the lowering operation of the lifting drive 1 takes place exclusively via the control valve device 12 actuated into the lowering position 13c.
  • no sink volume flow flows from the lifting cylinder device 10a, 10b to the container 17 via the bypass valve 30.
  • the shut-off valve 60 actuated by the load pressure of the lifting drive 1 thus prevents an inadmissibly high sink volume flow from being able to set in via the bypass valve 31 at higher load pressures above the limit load pressure.
  • the lowering valve 32 and the release valve 33 of the bypass valve 31 can be controlled independently of the load pressure of the lifting drive 1 in the flow positions 32b, 33b during each lowering process.
  • the bypass valve 31 is active since the load pressure of the lifting drive 1 is below the switching point of the shut-off valve 60 is located and the shut-off valve 60 is actuated by the spring device 61 into the open position 60b.
  • the release valve 33 and the lowering valve 32 of the bypass valve 31 are controlled by the control device 20 in the flow positions 32b, 33b. The lowering operation of the lifting drive 1 thus takes place via the control valve device 12 and also via the bypass valve 31.
  • a further lowering movement can be stopped at any time via the release valve 33 actuated into the blocking position 33a will. If the release valve 33 should remain in the flow position 33b after the lowering operation has been stopped in the event of a fault, a further lowering movement can be stopped at any time via the lowering valve 32 actuated into the blocking position 32a.
  • control valve device 12 is arranged in a directional control valve block 70 .
  • Further control valves, not shown in detail, of a working hydraulic system of the mobile working machine can also be arranged in the directional control valve block 70, for example a control valve of a tilting drive for tilting the mast 2 and a control valve for controlling an additional consumer, for example a sideshift of the load handling device 3.
  • the bypass valve 31 in the figure 1 the lowering valve 32 and the release valve 33 includes or in the figure 2 the lowering valve 32 comprising the release valve 33 and the shut-off valve 60 is arranged in a valve housing 71 . This enables the bypass valve 31 and the bypass line 30 to be retrofitted to existing lifting drives 1 in a simple manner.
  • the invention is not limited to the exemplary embodiments shown.
  • the lowering valve 32 and the release valve 33 of the bypass valve 31 can be designed as seat valves or slide valves.
  • shut-off valves can also be installed in the bypass valve 31 for service and/or maintenance purposes.
  • additional valves can be designed as switching or proportional valves, preset or adjustable, manually switchable electrically and hydraulically. Examples of such additional valves are a discharge pressure compensator, a lowering brake valve, shut-off valves, line breakage protection, pressure relief valves, pressure control valves, sequence valves, orifices/throttles.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Forklifts And Lifting Vehicles (AREA)
EP21181382.9A 2020-07-09 2021-06-24 Entraînement de levage hydraulique d'une machine de travail mobile Pending EP3939930A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020118144.2A DE102020118144A1 (de) 2020-07-09 2020-07-09 Hydraulischer Hubantrieb einer mobilen Arbeitsmaschine

Publications (1)

Publication Number Publication Date
EP3939930A1 true EP3939930A1 (fr) 2022-01-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP21181382.9A Pending EP3939930A1 (fr) 2020-07-09 2021-06-24 Entraînement de levage hydraulique d'une machine de travail mobile

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EP (1) EP3939930A1 (fr)
DE (1) DE102020118144A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011053960A1 (de) * 2011-09-27 2013-03-28 Still Gmbh Hydraulikanlage für ein Flurförderzeug

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011053960A1 (de) * 2011-09-27 2013-03-28 Still Gmbh Hydraulikanlage für ein Flurförderzeug

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DE102020118144A1 (de) 2022-01-13

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