EP1369598A1 - Elektrohydraulische Hubsteuervorrichtung für Flurförderfahrzeuge - Google Patents
Elektrohydraulische Hubsteuervorrichtung für Flurförderfahrzeuge Download PDFInfo
- Publication number
- EP1369598A1 EP1369598A1 EP20030002659 EP03002659A EP1369598A1 EP 1369598 A1 EP1369598 A1 EP 1369598A1 EP 20030002659 EP20030002659 EP 20030002659 EP 03002659 A EP03002659 A EP 03002659A EP 1369598 A1 EP1369598 A1 EP 1369598A1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- pilot
- way
- valve
- tank
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/008—Valve failure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/20—Means for actuating or controlling masts, platforms, or forks
- B66F9/22—Hydraulic devices or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40576—Assemblies of multiple valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/4159—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source, an output member and a return line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/465—Flow control with pressure compensation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
- F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
Definitions
- the invention relates to an electro-hydraulic stroke control device in the preamble of claim 1 specified Art.
- the lifting line is because the Speed of the hydraulic cylinder is controlled by the speed of the pump, only one black / white 2/2-way solenoid valve provided.
- the invention has for its object an electrohydraulic stroke control device of this type to indicate their operational safety against malfunctions due to contamination of the hydraulic medium or developing mechanical Damage to hydraulic switching elements is increased with minimal effort.
- an additional activatable braking function may be possible, or is a deliberate active activation of one or both current controllers desirable, or should the supply pressure for at least one other hydraulic consumer easy to set lower with minimal effort than e.g. for the Lifting control.
- the effort mentioned relates mainly to magnets as a valve actuator.
- the operational safety of the electrohydraulic stroke control device is increased because the redundancy switching element then actively intervenes when at least one other is electrically actuable switching element should no longer function properly.
- the active intervention of the redundancy switching element is primarily uncontrolled Avoid load movements or an unwanted lowering of the load.
- the proportional pressure control valve for lowering control or lifting control hang, so that it is no longer due to its proportional magnet can be adjusted (the lifting hydraulic cylinder would then either retract under the load or extend against the load), then this brings effective redundancy switching element in the open position either the pressure compensator of the two-way flow controller in the load-holding shut-off position (stopping the descending lifting hydraulic cylinder) or the pressure compensator of the three-way flow controller in the open position (Deriving the current to the tank so that the lifting hydraulic cylinder stops). If the proportional pressure control valve functions properly, the redundancy switching element takes over no influence in the respective pilot circuit, since it is powered of the respective proportional magnet is energized and holds its closed position.
- the redundancy switching element is an easy to integrate safety component and requires minimal effort. For this function is for the control electronics only the solenoid of the switching element and hydraulically a simple, small valve required for the pilot oil.
- the redundancy switching element offers further advantageous thanks to its arrangement Possibilities, but it must be assumed that in modern industrial trucks Electronic control provided contains a microprocessor that offers many possibilities for individual program routines or functions.
- the redundancy switching element By adjusting of the redundancy switching element in the open position during the lowering control
- the lowering movement can also be braked individually by the pressure compensator of the two-way flow controller to the closed position in another way is brought in as by the pressure difference of the proportional pressure control valve.
- a similar individual braking could also be done with the lift control via the Pressure balance of the three-way current regulator.
- the redundancy switching element Activate the two-way current controller or the three-way current controller actively, i.e. the respective pressure compensator in the closed position or full open position bring.
- the redundancy switching element can be used as a variable pressure relief valve the pilot pressure of the pressure compensator of the three-way flow controller change the supply pressure for at least one other hydro consumer that is lower than that of the lift hydraulic cylinder. It opens that up Redundancy switching element in interaction with the control electronics a more universal control of the industrial truck, the given per se Performance of the higher-level electronics is used without additional effort.
- the redundancy switching element should be between the tank and either the opening pilot side the pressure compensator of the two-way flow controller and / or the closing pilot side the pressure compensator of the three-way flow controller. In this Position, the redundancy switching element relieves the pilot pressure when it is activated for the respective pressure compensator, so that it is forced into its closed position or through position.
- the redundancy switching element For a sensitive regulation of the pressure relief by the redundancy switching element To be able to adjust, it is advisable to use this as a 2/2-way control valve with pressure pilot control in the opening direction and a proportional magnet as an actuator for Adjust in the closing direction. This interpretation is advantageous if the redundancy switching element as the variable pressure relief valve the pilot pressure has to be adjusted individually. However, it is sufficient for the desired security aspect off, the redundancy switching element only between one opening and one To be able to change the closed position (black / white function).
- redundancy switching elements are only sufficient for increased safety requirements a 2/2-way valve with pressure pilot control in the opening direction and one Black / white magnets as actuators for adjustment in the closing direction.
- a 2/2-way valve this design is inexpensive and reliable.
- the redundancy switching element here is a poppet valve that is characterized by a leak-free Distinguished closed position.
- the pressure pre-control of the redundancy switching element with which the Redundancy switching element is brought into its open position with the opening pilot side the pressure compensator of the two-way flow controller or the closing pilot side the pressure compensator of the three-way flow controller.
- pilot pressure is present at the respective pressure compensator, the redundancy switching element in the direction of its open position, which it only then is able to take if it is not actively electrically adjusted to its closed position is.
- a further increase in operational safety can be achieved if the redundancy switching element is assigned to both current regulators and its function for the respective Current regulator fulfilled depending on the pressure. That is, the shuttle valve connects each the working pressure compensator with the redundancy switching element, the then selected pilot pressure or the higher pilot pressure is present.
- the redundancy switching element thus works automatically with the lifting control with the three-way current regulator, on the other hand, together with the two-way current controller for lowering control.
- the redundancy switching element can expediently be connected in parallel with a control pressure pressure relief valve be arranged. This offers structural advantages because anyway a pilot pressure channel via the pressure relief valve to the tank or to the return line runs. If the redundancy switching element than by a proportional magnet Actuatable pressure control valve is formed, which with varying current supply the function of a pressure relief valve, the pressure relief valve can may be omitted.
- the redundancy switching element guided by the control electronics and, as mentioned, when designed as a proportional pressure control valve, the function of an electrical adjustable pressure relief valve to meet the pressure compensator of the three-way flow regulator sets a lower supply pressure for other hydraulic consumers. All of the above functions can be done with a small valve and a Achieve magnets.
- the redundancy switching element arranged in the pilot control circuit for example, in the event of a fault of the three-way current controller when lowering is in its open position goes as soon as the proportional magnet of the three-way current controller is de-energized, the lifting hydraulic cylinder could operate via the pilot control circuit despite the load holding function give in to the pressure compensator very slowly. For this reason, it is advisable the redundancy switching element as a 4/2-way switching valve with a switching magnet as Train actuator and the pilot line to the lowering branch at least forklift-tight shut off while opening the pilot side of the pressure compensator directly to the tank is relieved. This results in a perfect load holding function of the pressure compensator, so that the lifting hydraulic cylinder even with a stuck proportional directional pressure control valve remains reliably stopped.
- the redundancy switching element In order to be able to guarantee this high security standard even if that Redundancy switching element the function of pressure reduction for other consumers it is advisable to execute the redundancy switching element even as a 4/3-way proportional pressure control valve with a proportional magnet as an actuator and the two pilot lines from the lowering branch and from the closing pilot side the pressure compensator of the two-way flow controller separately. If the 4/3-way proportional pressure control valve is canceled when lowering control is canceled de-energized, then it assumes its switch-off position, in which the opening pilot side the pressure compensator of the two-way flow regulator to the tank and the pressure compensator is set for load holding. This switch position is also assumed when the lifting control is canceled.
- the closing pre-tax side is the Pressure balance of the three-way flow regulator to the tank is relieved, so that the pressure balance, if supply pressure is present, set to the closed position.
- the proportional solenoid of the 4/3-way proportional pressure control valve is energized fully energized.
- the switching position thus created provides the pilot line from the lowering branch to the opening pilot side of the pressure compensator of the two-way current controller on continuity and interrupts the connection of the Pilot line to the closing pilot side of the pressure compensator of the three-way flow controller to the tank.
- the 4/2-way switching valve or the 4/3-way proportional pressure control valve is useful designed as a slide valve in a forklift-tight design. This means, that the valve meets the requirement for the forklift tightness criterion.
- the electro-hydraulic stroke control device is suitable for both Lift trucks with an internal combustion engine and an electric motor can be used.
- the lift control device can be used with an electric motor-driven lift truck can be used with or without energy recovery (utility sinks).
- energy recovery utility sinks
- For lowering operation where the electric motor is operated as a generator via the pump, it is only necessary to place the lower branch upstream of the pressure compensator of the two-way flow regulator to connect to the suction side of the pump via a useful line, and Place a check valve between the pump and the tank.
- At high Load pressure and without additional hydraulic consumers switched on can handle the full amount (controlled by the pressure compensator of the two-way flow controller) by the pump be promoted.
- the redundancy switching element does not intervene if it functions properly, but only if there is a fault, and occasionally when reducing the pressure for other consumers.
- the electrically active actuable components of the stroke control device should be included an electronic containing a microprocessor or logic circuit Control connected to the different actuation routines as needed, as chosen, or according to an automated scheme.
- a hydraulic cylinder Z for lifting control from a pressure source P (hydraulic pump), which e.g. is driven by an electric motor or diesel engine M and, if no other hydraulic consumers are to be supplied when lowering the hydraulic cylinder Z can stand, or (Fig. 4) then runs for energy recovery as a motor.
- the hydraulic pump sucks in from a tank T and acts on a lifting strand 1, in which a three-way current regulator R1 is provided.
- the three-way current regulator R1 consists of a proportional pressure control valve 3, with which the lifting speed is set by a proportional magnet 4, and a pressure compensator 5 between the lifting line 1 and the tank T.
- the pressure control valve 3 is spring loaded acted towards the shut-off position. Between the hydraulic cylinder Z and the pressure control valve 3 branches a pilot line 6 to the closing pilot side (on which a control spring also acts) the pressure compensator 5. From the lifting strand 1 branches a further pilot line 7 upstream of the pressure control valve 3 Opening pilot side of the pressure compensator 5 from.
- the two-way flow controller R2 consists of a pressure control valve 8, with which the lowering speed by means of a proportional magnet 9 can be set, and a pressure compensator 10.
- the pressure control valve 8 is by Spring force is applied towards the shut-off position, in which there is the load pressure is able to keep leak-free.
- pilot line 11 to the closing pilot pressure side 22 of the pressure compensator 10
- pilot line 12 to the opening pilot side 19 of the pressure compensator 10 leads.
- a pilot line branches from the pilot line 12 12a to the tank T, in the z. B. a pressure relief valve 13 is included.
- the two-way current regulator R2 is an electrically actuated redundancy switching element Assigned to A, which energizes when the proportional magnet 9 is energized becomes.
- this is a 2/2-way valve 14 in seat valve construction, i.e. with a leak-free closed position by a black and white magnet 15 against the on its opening pilot side 21 of the pilot pressure in the pilot line 12a derived pressure can be brought into the closed position shown is.
- the redundancy switching element A is e.g. parallel to the pressure relief valve 13 in whose wiring harness is arranged.
- the load pressure is held by the pressure control valve 8.
- the proportional magnet 9 receives current, the strength of which is the desired one Lowering speed corresponds.
- a not shown parent control of the black / white magnet 15 energized, so that the redundancy switching element A assumes its shut-off position (as shown).
- the pressure control valve 8 allows the proportional magnet 9 to be energized via an orifice opening Pressure medium flow out, the pressure compensator 10 using the pressure difference keeps the orifice aperture and thus the lowering speed constant.
- the Pressure compensator 10 sets itself in a position that depends on the pilot pressures in the pilot lines 11 and 12 and its control spring (load independence).
- the redundancy switching element is A assigned to the three-way current regulator R1 for lifting control. That is, the redundancy switching element A is in one of the pilot line 6 to the closing pilot side 20 of the pressure compensator 5 branching pilot line 6a to the tank and offers a possibility to actively intervene in the event of a malfunction.
- the pressure compensator 5 should be in a middle position due to a fault get stuck, this could cause the hydraulic cylinder Z to extend further be prevented that the pressure control valve 3 by means of the proportional magnet 4 in its closed position is brought.
- the proportional magnet is de-energized 4 also de-energized black / white magnet 15, the 2/2-way valve 14 from the pilot pressure brought quickly into its open position in the pilot line 6, 6a, see above that the pilot pressure is suddenly reduced to the tank and the pressure compensator 5 by the pressure prevailing in the lifting line 1 via the pilot line 7 into the is brought to the full open position, in which the pressure medium from the lifting strand 1 to the tank and the hydraulic cylinder Z is brought to a standstill.
- the Redundancy switching element A could be used with repeated energization and de-excitation to make the stuck pressure compensator 5 common again.
- the electro-hydraulic stroke control device S is combined with additional controls SH, SH 'for other hydraulic consumers of the industrial truck with a common Supply from the pressure source P is present.
- the control SH serves, for example for actuating a further hydraulic consumer Z ', for example one Tilt cylinder or a gripper cylinder that has a lower supply pressure needs as the hydraulic cylinder Z.
- the load pressure becomes a pilot line 6b to the pilot line 6 and then brought to the closing pilot side 20 of the pressure compensator 5, namely via a shuttle valve 16, which the higher control pressure to the Closing pilot control side 20 of the pressure compensator 5 transmits.
- the pressure compensator 5 regulates the required pressure.
- the redundancy switching element A is functionally alternating in this embodiment both the two-way current regulator R2 and the three-way current regulator R1 assigned, namely via a shuttle valve 17 (or, as shown in Figs. 4 and 5 via two separate pilot lines). From the pilot line 12 of the two-way current regulator R2 branches off a pilot line 12 'to the shuttle valve 17. The other On the side of the shuttle valve 17, a pilot line 6 'leads from the pilot line 6 of the three-way current regulator R1 branches. The higher the pilot pressure is transferred to the pilot line 18, in which the pressure relief valve, if applicable 13 and the redundancy switching element A are arranged.
- the redundancy switching element A is a 2/2-way proportional pressure control valve in FIG. 3 14 ', which is due to the pilot pressure in the pilot line 18 in the opening direction its opening pilot side 21 is acted upon, and by a proportional magnet 15 'in the direction of the closed position shown.
- the proportional magnet 15 ' is energized simultaneously with the lifting control with the energization of the proportional magnet 4, however with the lowering control simultaneously with the energization of the proportional magnet 9.
- the proportional magnet 15 ' is not only the closed position of the redundancy switching element Set A, but can also be adjusted depending on a weaker one Power supply with sole or additional actuation of the hydraulic cylinder Z 'intermediate positions adjust the pilot pressure in the pilot line 18 for the Lower pressure compensator 5.
- the redundancy switching element fulfills the function of a electrically adjustable pressure relief valve for setting the pilot pressure on the closing pilot side 20 of the pressure compensator 5, e.g. around for the other hydro consumer Z 'to set a lower supply pressure. It could be the redundancy switching element A with this design also for the intended reduction of the pilot pressure level can be used for lifting and / or lowering control.
- the shuttle valve 17 In the lifting control, the shuttle valve 17 is in its left position, so that in the pilot line 18 the pilot pressure prevails from the pilot line 6. Should the pressure control valve 3 remains stuck although the proportional magnet 4 is de-energized, the proportional magnet 15 'is also de-energized, so that the redundancy switching element A Abruptly its opening position via the pilot pressure in the pilot line 18 takes and reduces the pilot pressure to the tank.
- the pressure compensator 5 goes abruptly into its open position, in which the pressure medium is discharged directly to the tank is and the hydraulic cylinder Z stops its extension movement, the Load pressure from a check valve downstream of the pressure control valve 3 and the Pressure control valve 8 is held. If necessary, the proportional magnet 15 ' then only de-energized after a program routine, in which it is determined that the Lift cylinder Z did not stop properly.
- the shuttle valve 17 With the lowering control, the shuttle valve 17 assumes the position shown, so that the pressure of the pilot line 12 or 12 'prevails in the pilot line 18. Should the pressure control valve 8 get stuck, then, as explained at the beginning, in its opening position going redundancy switching element A the pressure compensator 10 in their Bring closed position and thus the load pressure of the hydraulic cylinder Z is maintained.
- the higher-level electronic control CU which is expedient contains a microprocessor or other logic circuit that Proportional magnet 15 'only so strongly energized that the pressure control valve 14' an intermediate position occupies and regulates part of the pressure medium from the pilot pressure line 18 drains to the tank to the pilot pressure on the closing pilot side 20 to reduce the pressure compensator 5, so that the pressure compensator 20 now controls relatively more pressure medium to the tank and the supply pressure in the pressure line 1 'decreased.
- a redundancy switching element A is provided in FIGS. 4 and 5, the with de-energized switching magnet 15 or proportional solenoid 15 'the pilot line 12 to lower branch 2 and the opening pilot side 19 of the pressure compensator 10 Relieved directly to the tank via a pilot line 12b.
- the redundancy switching element A is a 4/2-way switching valve 14 "with a Switching magnet 15 as an actuator against a spring 26.
- the redundancy switching element A does not serve to set a lower supply pressure for other hydraulic consumers, but to protect the current regulator R1, R2 in the event of a Fault and, if necessary, for the arbitrary activation of the respective pressure compensator for other reasons, e.g. for individual braking or from others security reasons.
- the 4/2-way switching valve 14 " is a slide valve with a valve slide 27, the is pressure balanced with respect to the tank pressure.
- the switching valve 14 " is between the two pilot lines 12 (from the lower leg 2) and 6a (from the closing pilot side 20) the pressure compensator 5 and, if necessary, the shuttle valve 16 and the tank T and the pilot line 12b to the opening pilot side 19 of the Pressure compensator 10 arranged.
- With deenergized switching magnet 15 (this can be a simple one Black / white switching magnet) there is the switching position shown, in which the Pilot lines 12, 12b separated from one another and pilot lines 6a and 12b jointly relieved to the tank T in a bypass 24 in the valve slide 27 are.
- a switching position is set in which the Pilot line 6a separated from tank T and pilot lines 12, 12b with each other are connected.
- a useful lowering line 2a is shown in dash-dotted lines between the proportional pressure control valve 8 and the pressure compensator 10 branches off from the lower strand 2 and to the Suction side of pump P is connected.
- a check valve V is indicated, which in the direction of The tank locks the pressure medium pushed out by the pump when the utility is lowered P to promote and this as a motor for the electric motor then working as a generator to drive for energy recovery.
- the pressure medium then flows over the pressure compensator 20 to the tank, or if other hydraulic consumers are connected and be cared for, further.
- a variable speed pump P is used, when lowering the pressure compensator 10 in the case of the connection of additional hydraulic consumers set the required quantity by pump P.
- the option of lowering the usefulness can be easily achieved in every embodiment shown integrate.
- the redundancy switching element A is a 4/3 proportional pressure control valve 14 "' with the proportional magnet 15 'as an actuator of the valve slide 27' against the Force of a spring 26 and the pilot pressure in a pilot line 6c by the Pilot line 6a branches.
- the further connection corresponds to that shown in FIG. 4 and already explained.
- the valve spool 27 ' is related to the tank pressure via the pilot line 25 pressure-balanced, expediently over the entire surface, while the pilot pressure from the pilot line 6c expediently only a partial area of the surface of the valve slide 27 against the proportional magnet 15 ', a weak and compact or inexpensive proportional magnet 15 'to be able to use.
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- Fluid-Pressure Circuits (AREA)
- Forklifts And Lifting Vehicles (AREA)
Abstract
Description
- Fig. 1
- ein Blockschaltbild einer elektrohydraulischen Hubsteuervorrichtung mit einem Redundanz-Schaltglied, das der Senksteuerung zugeordnet ist,
- Fig. 2
- ein Blockschaltbild einer elektrohydraulischen Hubsteuervorrichtung mit einem Redundanz-Schaltglied, das der Hebesteuerung zugeordnet ist,
- Fig. 3
- ein Blockschaltbild einer elektrohydraulischen Hubsteuervorrichtung mit weiteren Hydroverbraucher, mit einem Redundanz-Schaltglied, das der Hebesteuerung und der Senksteuerung zugeordnet ist, und bei Zuordnung zur Hebesteuerung zusätzlich als elektrisch verstellbares Druckbegrenzungsventil zur Druckminderung für die weiteren Hydroverbraucher dient,
- Fig. 4
- ein Blockschaltbild einer weiteren Ausführungsvariante, und
- Fig. 5
- ein Blockschaltbild einer noch weiteren Ausführungsvariante.
Claims (14)
- Elektrohydraulische Hubsteuervorrichtung (S) für Flurförderfahrzeuge, insbesondere Hubstapler, mit einem einen zumindest zur Hebesteuerung elektrisch betätigbaren Dreiwege-Stromregler (R1) mit einem Proportional-Magneten und einer Druckwaage (5) enthaltenden Hebestrang (1) zwischen einer Druckquelle (P) und einem Hydraulikzylinder (Z), und einem vom Hebestrang (1) zum Tank abzweigenden Senkstrang (2), der zur Senksteuerung einen elektrisch betätigbaren Zweiwege-Stromregler (R2) mit einem Proportional-Magneten und einer Druckwaage (10) enthält, dadurch gekennzeichnet, dass zwischen dem Vorsteuerdruckkreis des Zweiwege-Stromreglers (R2) oder/und dem Vorsteuerdruckkreis des Dreiwege-Stromreglers (R1) und dem Tank (T) ein aktiv elektrisch zwischen Schließ- und Offenstellungen betätigbares Redundanz-Schaltglied (A) vorgesehen ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Redundanz-Schaltglied (A) zwischen dem Tank (T) und einer Öffnungs-Vorsteuerseite (19) der Druckwaage (10) des Zweiwege-Stromreglers (R2) oder/und einer Schließvorsteuerseite (20) der Druckwaage (5) des Dreiwege-Stromreglers (R1) angeordnet ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Redundanz-Schaltglied (A) ein 2/2-Wege-Regelventil (14') mit Druckvorsteuerung (21) in Öffnungsrichtung ist und mit einem Proportionalmagneten (15') als Aktuator für die Schließrichtung ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Redundanz-Schaltglied (A) ein 2/2-Wegeventil (14) mit Druckvorsteuerung (21) in Öffnungsrichtung und mit einem Schwarz/Weiß-Magneten (15) als Aktuator für die Schließrichtung ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Druckvorsteuerung (21) des Redundanz-Schaltgliedes (A) mit der Öffnungs-Vorsteuerseite (19) der Druckwaage (10) des Zweiwege-Stromreglers (R2) oder der Schließvorsteuerseite (20) der Druckwaage (5) des Dreiwege-Stromreglers (R1) verbunden ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die Druckvorsteuerung (21) des Redundanz-Schaltglieds (A) über ein Wechselventil (17) druckabhängig mit der Öffnungs-Vorsteuerseite (19) der Druckwaage (10) des Zweiwege-Stromreglers (R2) oder der Schließvorsteuerseite (20) der Druckwaage (5) des Dreiwege-Stromreglers (R1) verbindbar ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 2, adurch gekennzeichnet, dass die Druckwaage (5) des Dreiwege-Stromreglers (R1) zusätzlich zur lastunabhängigen Steuerung wenigstens eines weiteren, aus derselben Druckquelle (P) versorgten Hydroverbrauchers (Z') angeordnet ist, und dass über das Redundanz-Schaltglied (A) und die Druckwaage (5) des Dreiwege-Stromreglers (R1) ein niedrigerer Versorgungsdruck für den weiteren Hydroverbraucher (Z') einstellbar ist als zumindest zur Hebesteuerung des Hydraulikzylinders (Z).
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass das Redundanz-Schaltglied (A) ein zwischen getrennten Vorsteuerleitungen (12, 6a) zum Senkstrang (2) und zur Schließvorsteuerseite (20) der Druckwaage (5) des Dreiwege-Stromreglers (R1) sowie dem Tank (T) und einer Vorsteuerleitung (12b) zur Öffnungsvorsteuerseite (19) der Druckwaage (10) des Zweiwege-Stromreglers (R2) eingesetztes 4/2-Wege-Schaltventil (14") mit einem Schwarz/Weiß-Magneten (15) als Aktuator für eine Schaltrichtung ist, das in einer Schaltstellung die Vorsteuerleitung (6a) vom Tank (T) trennt und die Vorsteuerleitungen (12, 12b) verbindet, und in einer anderen Schaltstellung die Vorsteuerleitungen (12, 12b) trennt und die Vorsteuerleitungen (6a, 12b) mit dem Tank verbindet.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 2 und 7, dadurch gekennzeichnet, dass das Redundanz-Schaltglied ein zwischen getrennten Vorsteuerleitungen (12, 6a) zum Senkstrang (2) und zur Schließvorsteuerseite (20) der Druckwaage (5) des Dreiwege-Stromreglers (R1) sowie dem Tank (T) und einer Vorsteuerleitung (12b) zur Öffnungsvorsteuerseite (19) der Druckwaage (10) des Zweiwege-Stromreglers (R2) eingesetztes 4/3-Wege-Proportional-Druckregelventil (14"') mit einem Proportional-Magneten (15') als Aktuator für eine Schaltrichtung gegen die Kraft einer Feder (26) und den Vorsteuerdruck in der Vorsteuerleitung (6a) ist, das in einer Endschaltstellung die Vorsteuerleitung (6a) vom Tank (T) trennt und die Vorsteuerleitungen (12, 12b) verbindet, in einer anderen Endschaltstellung die Vorsteuerleitungen (12, 12b) trennt und die Vorsteuerleitungen (6a, 12b) mit dem Tank (T) verbindet, und ihn durch Bestromen des Proportionalmagneten nach Maßgabe des Vorsteuerdrucks in der Vorsteuerleitung (6a) variierbaren Zwischenschaltstellungen zwischen den Endschaltstellungen zur Vorsteuerdruckeinstellung die Vorsteuerleitungen (12, 12b) miteinander und die Vorsteuerleitung (6a) mit dem Tank (T) verbindet.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass das 4/2-Wege-Schaltventil (14") oder das 4/3-Wege-Proportional-Druckregelventil (14"') ein Schieberventil in staplerdichter Ausführung ist.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass das 4/2-Wege-Schaltventil (14") einen an beiden Enden großflächig zum Tank (T) druckausgeglichenen Ventilschieber (27) enthält.
- Elektrohydraulische Hubsteuervorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass das 4/3-Wege-Proportional-Druckregelventil (14"') einen beidendig vollflächig zum Tank (T) druckausgeglichenen Ventilschieber (27') enthält, der vom Vorsteuerdruck in der Vorsteuerleitung (6a) nur teilflächig gegen den Proportionalmagneten (15') beaufschlagt ist.
- Elektrohydraulische Hubsteuervorrichtung nach wenigstens einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Druckquelle (B) eine drehzahlregelbare Pumpe mit einem Elektromotor (M) aufweist, der über die Pumpe bei der Senksteuerung zur Energierückgewinnung als Generator betreibbar ist, dass zwischen der Pumpe und dem Tank (T) ein zum Tank sperrendes Rückschlagventil (V) vorgesehen ist, und dass eine stromauf der Druckwaage (10) des Zweiwege-Stromreglers (R2) vom Senkstrang (2) abzweigende Nutzsenkleitung (2a) stromab des Rückschlagventils (V) an die Pumpe angeschlossen ist.
- Elektrohydraulische Hubsteuervorrichtung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die elektrisch aktiv betätigbaren Komponenten (4, 9, 15, 15', M) der Hubsteuervorrichtung (S) mit einer einen Mikroprozessor oder eine Logikschaltung enthaltenden elektronischen Steuerung (CU) verbunden sind.
Applications Claiming Priority (2)
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DE20208577U | 2002-06-03 | ||
DE20208577U DE20208577U1 (de) | 2002-06-03 | 2002-06-03 | Elektrohydraulische Hubsteuervorrichtung für Flurförerfahrzeuge |
Publications (3)
Publication Number | Publication Date |
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EP1369598A1 true EP1369598A1 (de) | 2003-12-10 |
EP1369598B1 EP1369598B1 (de) | 2007-09-26 |
EP1369598B2 EP1369598B2 (de) | 2015-08-19 |
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EP03002659.5A Expired - Fee Related EP1369598B2 (de) | 2002-06-03 | 2003-02-11 | Elektrohydraulische Hubsteuervorrichtung für Flurförderfahrzeuge |
Country Status (4)
Country | Link |
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US (1) | US6837045B2 (de) |
EP (1) | EP1369598B2 (de) |
JP (1) | JP3785159B2 (de) |
DE (2) | DE20208577U1 (de) |
Cited By (8)
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EP1754682A1 (de) | 2005-08-11 | 2007-02-21 | HAWE Hydraulik GmbH & Co. KG | Elektrohydraulische Vorrichtung |
DE102007034746A1 (de) | 2007-07-25 | 2009-01-29 | Still Gmbh | Hydrostatisches Antriebssystem |
EP2236452A1 (de) | 2009-04-03 | 2010-10-06 | HAWE Hydraulik SE | Hubmodul |
EP2985473A1 (de) | 2014-08-11 | 2016-02-17 | HAWE Hydraulik SE | Hubmodul |
EP3037678A1 (de) * | 2014-12-23 | 2016-06-29 | HAWE Hydraulik SE | Hubmodul |
DE102016003972A1 (de) * | 2016-04-01 | 2017-10-05 | Hydac System Gmbh | Steuervorrichtung |
DE10303385B4 (de) | 2003-01-29 | 2018-11-29 | Buchholz Hydraulik Gmbh | Steuereinrichtung für eine Hub- und Senksteuerung |
DE10357631B4 (de) | 2003-01-29 | 2019-05-16 | Buchholz Hydraulik Gmbh | Steuereinrichtung für eine Hub- und Senksteuerung |
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DE10344480B3 (de) * | 2003-09-24 | 2005-06-16 | Sauer-Danfoss Aps | Hydraulische Ventilanordnung |
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DE202004014030U1 (de) | 2004-09-08 | 2006-01-12 | Hawe Hydraulik Gmbh & Co. Kg | Elektrohydraulische Steuervorrichtung |
DE102006003414B3 (de) * | 2006-01-24 | 2007-08-02 | Sauer-Danfoss Gmbh & Co Ohg | Hydraulische Schaltungsanordnung |
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DE102007028864A1 (de) * | 2007-03-27 | 2008-10-02 | Robert Bosch Gmbh | Hydraulische Steueranordnung |
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DE10303385B4 (de) | 2003-01-29 | 2018-11-29 | Buchholz Hydraulik Gmbh | Steuereinrichtung für eine Hub- und Senksteuerung |
DE10357631B4 (de) | 2003-01-29 | 2019-05-16 | Buchholz Hydraulik Gmbh | Steuereinrichtung für eine Hub- und Senksteuerung |
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Also Published As
Publication number | Publication date |
---|---|
EP1369598B2 (de) | 2015-08-19 |
US20030221548A1 (en) | 2003-12-04 |
US6837045B2 (en) | 2005-01-04 |
DE20208577U1 (de) | 2003-12-11 |
JP2004044795A (ja) | 2004-02-12 |
EP1369598B1 (de) | 2007-09-26 |
JP3785159B2 (ja) | 2006-06-14 |
DE50308262D1 (de) | 2007-11-08 |
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