EP3133043A1 - Module de levage - Google Patents

Module de levage Download PDF

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Publication number
EP3133043A1
EP3133043A1 EP15181346.6A EP15181346A EP3133043A1 EP 3133043 A1 EP3133043 A1 EP 3133043A1 EP 15181346 A EP15181346 A EP 15181346A EP 3133043 A1 EP3133043 A1 EP 3133043A1
Authority
EP
European Patent Office
Prior art keywords
pressure
way valve
lifting module
valve
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.)
Withdrawn
Application number
EP15181346.6A
Other languages
German (de)
English (en)
Inventor
Recep Macit
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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 Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP15181346.6A priority Critical patent/EP3133043A1/fr
Publication of EP3133043A1 publication Critical patent/EP3133043A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • 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
    • 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
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • 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
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a lifting module specified in the preamble of claim 1. Art.
  • Fig. 1 schematically shows a known lifting device, which in the document EP 2 058 270 A1 is described.
  • FIG. 1 Lifting device shown, for example, in a battery-powered industrial truck, such as a forklift, for actuating a lifting cylinder V, for example, arranged for a lifting mast.
  • the lifting cylinder V is secured by a Senkdrossel 102 when connecting a working line 103.
  • the pressure in the working line 103 is detected by a pressure sensor 134.
  • the working line 103 branches at a node 104 into a lifting string 105 and a lowering string 109.
  • the lifting string 105 is connected to a pump 106, wherein the pump 106 is operated in battery-operated industrial trucks by a motor M '.
  • the pump 106 is connected to a tank T 'via a check valve 110 which blocks the tank.
  • a proportional pressure control valve 115 is arranged with a proportional solenoid 116 in the lifting strand 105.
  • the proportional pressure control valve 115 is optionally assisted by a speed control of the pump 106 during lifting.
  • a proportional pressure regulating valve 117 with a proportional magnet 118 is arranged downstream of the node 104 for regulating the lowering speed of the lifting cylinder V.
  • a tank string 113 is provided by a manually operable emergency valve 113N forms a junction of the node 104 with the tank T '.
  • lifting devices such as the known lifting device described above, to meet the following requirements: neutral, lift, sink with load on energy return, sinks without load, dissipation of excess energy, redundant sink, parallel operation for lifting and tipping in several Lifting modules, emergency lowering and possibility to carry out an LB test.
  • the present invention provides a lifting module, in particular for industrial trucks such as forklifts, masts, mobile hydraulic devices, work vehicles or the like, with a lifting strand and a Senkstrang to which a hydraulic consumer, in particular a hydraulic cylinder is connectable.
  • the lifting strand can be acted upon by a pump driven by a motor with a pressure medium under load pressure.
  • a lowering valve is arranged to set, for example, a lowering speed.
  • the Senkstrang has downstream of the lowering valve on a branch at which branches of the Senkstrang in a return strand and a drain line.
  • the lifting module downstream of the branching has a 2/2-way valve arranged in the outlet line with a shut-off position in which a fluid connection between the suction line and the outlet line is shut off, and a passage position in which the pressure medium guided in the suction line via the outlet line can drain to the tank.
  • the 2/2-way valve is acted upon by a blocking pressure derived via a throttle from the load pressure in a direction to the shut-off of the 2/2-way valve and the 2/2-way valve is in a state relieved of the blocking pressure in the passage position applied.
  • the lifting module further comprises an electrically controlled 2/2-way valve, through which the blocking pressure acting on the branching in the shut-off position of the 2/2-way valve can be relieved to the discharge line.
  • the electrically controlled 2/2-way valve is configured as a s / w solenoid valve. This represents a simple and cost-effective implementation of the 2/2-way valve.
  • the electrically controlled 2/2-way valve in the de-energized state is acted upon by a spring in a leak-free blocking position.
  • the electrically controlled 2/2-way valve is configured so that it is not switchable at a load pressure of 50 bar or more. This allows a simple control of the 2/2-way valve, which is independent of a pressure measurement in the sunk strand.
  • the lifting module further comprises a hydraulically controlled 2/2-way valve designed as a pressure compensator, by which the blocking pressure acting on the 2/2-way valve downstream of the branch in the shut-off position can be relieved to the discharge line if the load pressure in the drawstring is a limit value below.
  • a hydraulically controlled 2/2-way valve is implemented as an alternative to the electrically controlled 2/2-way valve.
  • the pressure compensator is biased by a spring in the open-control direction, in which the barrier pressure is relieved to the discharge line, and the pressure compensator can be counteracted in the Zu-control direction of the spring counter to a control pressure derived from the load pressure, wherein the barrier pressure in Zu-control direction can be applied to the 2/2-way valve.
  • the 2/2-way valve is spring-loaded at the junction in the direction of the shut-off position parallel to the barrier pressure.
  • the engine driven by the pump is driven as a generator for energy recovery.
  • the 2/2-way valve is controlled at the junction depending on a voltage occurring at the generator or a state of charge of a rechargeable battery coupled to the generator. As a result, overcharging of a battery coupled to the generator to supply the motor can be prevented.
  • the 2/2-way valve is controlled at the branch depending on a load pressure occurring in the drawstring.
  • the lowering valve is designed as a function of the load pressure for limiting a lowering speed during a lowering, wherein the lowering speed is set as a function of a rotational speed of the engine.
  • Fig. 2 schematically shows a part of an electro-hydraulic lifting device with a lifting module H according to a first embodiment of the invention, which is arranged for example in a battery-powered industrial truck, such as a forklift to at least one hydraulic consumer (not shown), for example a lifting cylinder for a mast (not shown), to operate.
  • the hydraulic consumer (not shown) is secured with a connection of the lifting module H to a working line 3 via a lowering throttle (not shown), which is arranged between the lifting module H and the hydraulic consumer (not shown).
  • the working line 3 branches at a node 4 in a lifting strand 5 and a Senkstrang 9.
  • a motor M pump 6 is connected, which in turn is connected to a tank T via a tank-blocking check valve 10.
  • the pump supplies the lifting module H with a hydraulic pressure medium, which is supplied to the lifting module H at a supply connection P of the lifting module H1.
  • the supply connection P is connected in the lifting module H to the lifting strand 5.
  • the lifting module H is connected to the tank T.
  • a pressure occurring in the working line is detected via a pressure sensor 34, which generates instantaneous pressure data and forwards to an electronic control (not shown) of the lifting device and / or outputs via a display device (not shown) for an operator of the lifting device.
  • a proportional pressure regulating valve 15 with a proportional magnet EP01 is arranged for regulating the lifting speed.
  • the proportional pressure control valve 15 may be assisted by a pressure control of the pump 6 in a lifting operation of the lifting device H comprising the lifting module H, if necessary.
  • a proportional pressure regulating valve 17 with a proportional magnet EP02 is arranged downstream of the node 4 for regulating the lowering speed. Furthermore, located in the Senkstrang 9 downstream of the proportional pressure control valve 17, a node 18 at which the Senkstrang 9 branches into a return strand 13 'and a branch 18'. The branch 18 'passes into a discharge line 13 which is connected to the discharge port R of the lifting module.
  • the return train 13 ' is connected to a return port ER of the lifting module H.
  • a pressure medium conducted via the return line 13 ' can be fed directly to the pump 6 for energy recovery.
  • the pump 6 is operated by a via the return line 13 'recycled hydraulic pressure medium.
  • the pump 6 in turn drives the motor M, which is designed to act as a generator in a generator mode.
  • a voltage is now induced, e.g. can be tapped to charge a battery (not shown) or other storage medium for electrical energy.
  • the lifting device From the charged battery or storage medium, e.g. the lifting device relate the electrical energy required for a lifting device to the operation of the motor M.
  • supply of electric and / or electronic units of the lifting device for example pressure sensor 34 and / or electronic control unit
  • electrical energy by the battery or by the storage medium for example pressure sensor 34 and / or electronic control unit
  • a 2/2-way valve 19 is disposed between the branch 18 'and the discharge line, wherein in the illustrated shut-off position of the 2/2-way valve 19, a fluid connection between the Senkstrang 9, in particular between the branch 18' and the discharge line 13, the fluid connection between the branch 18 'and the discharge line 13 is interrupted, in particular, a flow through the 2/2-way valve 19 is shut off leak-free).
  • the pressure medium guided in the suction line 9 is discharged through the 2/2-way valve 19 via the discharge line 13 to the tank T.
  • a pilot valve 30 is disposed downstream of the 2/2-way valve 19, which is formed for example as a solenoid pilot valve (eg, a s / w solenoid valve).
  • the pilot valve 30 has a magnet ES01 which, when de-energized, holds the pilot valve 30 in the blocking control illustrated.
  • the control line 14 is connected to a tank line 24 via which a lateral outlet 111 of the 2/2-way valve 19 output pressure medium is supplied to the tank port R of the lifting module H, whereby a pressure relief of the guided in the lowering strand 9 pressure medium to the tank T is made possible.
  • the 2/2-way valve 19 in an annular chamber 110 comprises a displaceably guided, sealed movable stepped piston 112 with a valve closing member defining a piston extension 117 which cooperates with an axial valve seat 113 in poppet design.
  • a barrier pressure control chamber 114 is provided, in which, preferably, a spring 115 is included, which urges the stepped piston 112 in the direction of the shut-off position shown.
  • the barrier pressure control chamber 114 is connected to the control line 14.
  • the loading surface of the stepped piston 112 in the annular chamber 110 and in the barrier pressure control chamber 114 are at least substantially the same size and in particular larger than the loading surface of the piston shoulder 117 on the valve seat 113.
  • a bypass from the annular chamber 110 to the barrier pressure control chamber 114, which includes a throttle 116 runs.
  • the throttle 116 could be housed in a bypass passage in the housing of the 2/2-way valve 19.
  • the lowering valve 17 in the closed position it is possible by an appropriate control of the lowering valve 17 in the closed position to prevent uncontrolled lowering of a load.
  • the valves 17 and 19 are in this respect a redundant system.
  • the barrier pressure control chamber 114 of the 2/2-way valve 19 is relieved and a cross-sectional size Abströmweg by means of the drain line 13 to the tank T out is released, which allows relief of a guided in the Senkstrang 9 pressure fluid to the tank T.
  • a mechanical limit may be provided for the maximum opening stroke of the stepped piston 112 in the 2/2-way valve 19, so that the 2/2-way valve 19 may operate as a lowering brake having a maximum lowering rate of a hydraulic load on e.g. limited to 0.6 m / s under load.
  • a limitation of the lowering speed by a suitable control of the magnets EP02 and ES01 depending on a speed of the pump 6 and / or the motor M take place.
  • the speed of the pump 6 and / or the motor M via a speed sensor (not shown) is monitored, which controls depending on the speed deflections of the lowering valve 17 and / or the pilot valve 30 via the magnets EP02, ES01 suitable.
  • This in Fig. 2 Lifting module H shown also has an emergency discharge N, by which manually at the node 4, a connection between the working line 3 and the drain port R (and thus to the tank T) can be made.
  • the lifting module H furthermore comprises a circulating valve UL, by means of which a neutral circulation (for example in idling operations of an industrial truck) is provided.
  • a neutral circulation for example in idling operations of an industrial truck
  • the circulation valve UL energy destruction when lowering under load in which, for example, in the case of a fully charged battery through the hydraulic resistance of the circulation valve UL dissipation of excess energy can be achieved can.
  • the recirculation valve UL may provide a pressure drop ⁇ p of 10 bar.
  • FIG. 2 illustrated embodiment shows a lifting module with Senkstrang 9, which is unthrottled in particular when lowering under load connected to the return strand 13 '.
  • FIG. 3a shows a further illustrative embodiment of the lifting module H, with respect to the 2/2-way valve 19 'of the in Fig. 2 illustrated 2/2-way valve 19 is different.
  • the same reference numerals in FIG Fig. 3a denote components of the lifting device H previously described with reference to FIG Fig. 2 have been described and accordingly in Fig. 3a are used.
  • Fig. 3a For a corresponding description, reference is made to the above description to avoid repetition.
  • a description is given Fig. 3a in terms of differences too Fig. 2 ,
  • a throttle arranged in the 2/2-way valve see throttle 116 in FIG Fig. 2
  • it is a blocking pressure upstream of the lowering valve 17 between the lowering valve 17 and node 4 via a line SD and a arranged in the line SD throttle D1 derived.
  • a arranged between branch 18 'and drain line 13 2/2-way valve 19' is for better understanding in Fig. 3b illustrated by a check valve 210.
  • the check valve 210 is arranged in a housing 217 with a closing element 204, which can establish or separate a connection between a first fluid port 206 and a second fluid port 207. Via a control connection 208, the separation or connection of the first and second fluid connection 206, 207 can be controlled.
  • the closing element 204 can be held in the illustrated closed position by means of an optional spring 203.
  • the first fluid port 206 is connected to a first pressure chamber 212 in the interior of the valve housing 217, while the second fluid port 207 is connected to a second pressure chamber 209.
  • the control port 208 is connected to a barrier pressure-pressure space 211 inside the valve housing 217. In the illustrated closed state, the pressure chambers 209, 212 and the pressure chamber 2011 are separated from each other by the closing element 204.
  • control port 208 is depressurized (eg by opening the pilot valve 30) and is at the first port 206, a pressure, then the pressure surface 212-1 on the closing element 204 with Pressure applied so that the closing element 204 in the representation of Fig. 3b pushes upwards, as rest on the opposite pressure surface 211-1 in the barrier pressure-pressure chamber 211 no pressure forces and the spring force of the spring 203 is usually negligible relative to the pressure force in the first pressure chamber 212. that is, the valve opens and the first port 206 and the second fluid port 207 are connected to each other.
  • a pressure acts in the barrier pressure pressure chamber 211, which acts on the pressure surface 211-1 and exerts a force on the closure element which exceeds a force which is caused by a pressure which is opposite to the pressure surface 211 -1 smaller pressure surface 212-1 acts (the pressure surface 212-1 in the first pressure chamber 212 is smaller than the pressure surface 211-1 in the barrier pressure-pressure chamber 211, so that a resultant force on the closure member 204 in the in Fig. 3b shown representation, which acts downward).
  • the check valve 210 is closed.
  • the throttle D1 is designed with a load applied of 200 bar for a maximum flow of 3I.
  • the pilot valve 30 may be configured such that it is switchable only when it falls below an applied limit pressure, for example, 50 bar or less. In this way it can be ensured in a simple manner that the pilot valve 30 can be opened only at a sufficiently low pressure in Senkstrang 9, while at normal pressures when lowering under load, for example, 200 bar, an opening of the pilot valve 30 is excluded.
  • the pressure sensor 34 can thus be dispensed with, whereby a simple design of the lifting module without a pressure sensor 34 can be achieved (in FIG Fig. 3a indicated by circle around pressure sensor 34).
  • FIG. 4 is a further illustrative embodiment of the lifting module H described, with respect to the 2/2-way valve 19 'of the in Fig. 2 illustrated 2/2-way valve 19 is different.
  • the same reference numerals in FIG Fig. 4 denote components of the lifting device H previously described with reference to FIG Fig. 2 have been described and accordingly in Fig. 4 are used.
  • Fig. 4 For a corresponding description, reference is made to the above description to avoid repetition.
  • a description is given Fig. 4 in terms of differences too Fig. 2 , This in Fig. 4 shown 2/2-way valve 19 'further corresponds to the foregoing with respect to the FIGS. 3a and 3b described 2/2-way valve 19 'and is therefore denoted by the same reference numerals.
  • Fig. 4 shows instead of an electrically controlled 2/2-way valve as a pilot valve 30, a hydraulically controlled pilot valve 30 '.
  • a pressure is derived, which is based on chokes D2, D3 to a hydraulic pressure compensator 30 'is applied.
  • the hydraulic pressure compensator 30 ' is configured such that the pressure compensator 30' is biased by a spring in the reverse direction, in which a flow of a pressure fluid through the pressure balance via a line SD 'to a control port of the 2/2 Directional valve 19 '(corresponds to 2/2-way valve 19' in Fig. 2 ) is tapped.
  • Fig. 5 shows a further illustrative embodiment of the lifting module H, wherein instead of in the Fig. 2 to 4 illustrated 2/2-way valve 19, 19 'is designed as a slide valve 2/2-way valve 19 "is shown Fig. 2 to 4 illustrated embodiments here is no 100% leak-free seal in the locked state of the 2/2-way valve 19 "given.
  • the 2/2-way valve 19 is preferably biased by a spring in an open direction, with a node 18 connected to a drain line 13. Downstream of the lowering valve 17 is a barrier pressure via a line SD" and a nozzle arranged in the line SD " D4 to the 2/2-way valve 19 "applied so that the derived via the throttle D4 barrier pressure produces a force on the 2/2-way valve 19 ", which counteracts the spring and leads to a deflection of the 2/2-way valve in the control direction opposite to the spring action when the spring force is exceeded -Wegeventils 19 ", in particular upstream of the node 18 in the drawstring 9, a pressure is tapped via a node 31, which on a control valve 30 'on the control side, ie parallel to the force of the spring, to the 2/2-way valve 19" is applied.
  • the pilot valve 30 ' may be formed according to illustrative embodiments as electrically controlled 2/2-way valve, which is controlled by means of a s / w magnet ES02. According to illustrative examples herein, the pilot valve 30 'in the de-energized case in the blocking position, wherein upon energization of the solenoid ES02 an up-regulation of the pilot valve 30' takes place in the up direction and a connection between the node 31 and the 2/2-way valve 19 "is made in the up direction ,
  • the throttle D4 is in Fig. 5 designed such that at a load pressure in the positive train 9 above a certain pressure value (ie, a pressure exerted on the 2/2-way valve 19 "in the direction of control a force against the spring can connect the Senkstrangs 9 with the drain line 13 by the 2/2-way valve is interrupted, provided that the pilot valve 30 'in the in Fig. 5 is shown shut-off position.
  • a certain pressure value ie, a pressure exerted on the 2/2-way valve 19 "in the direction of control a force against the spring can connect the Senkstrangs 9 with the drain line 13 by the 2/2-way valve is interrupted, provided that the pilot valve 30 'in the in Fig. 5 is shown shut-off position.
  • the solenoid ES02 When the solenoid ES02 is energized, the 2/2-way valve 19 "is activated, so that a connection between the node 18 and the discharge line 13 is controlled by the pilot valve 30 'independently of the pressure
  • Illustrated illustrative embodiments show lifting and lowering operations.
  • lifting the lowering valve 17 is in the illustrated de-energized state, while the lifting valve 15 is turned on, in particular by energizing the magnet EP01.
  • a lifting operation is set, wherein the lifting speed depends on a slide position of the lifting valve 15.
  • Senkoperationen carried out in that the lifting valve 15 is kept de-energized, in particular the magnet EP01 is not energized and the lifting valve 15 held in the illustrated closed position position, while the lowering valve is switched in the forward direction, in particular by energizing the magnet EP 02.
  • lowering may be done under load or without load.
  • the lowering with load can be limited to a certain lowering speed, for example, to a lowering speed of a maximum of 0, 6 m / s.
  • a pressure sensor see pressure sensor 34 in FIG Fig. 2 and optional in Fig. 3a ) detects the prevailing in the sunk strand 9 load pressure and depending on the detected pressure, energization of the magnets EP02 and ES01 done (alternatively without pressure sensor 34 in Fig. 3a can the pilot valve 30 only at pressures below a threshold, for example. Below 50 bar (ie, no or low load) be switched).
  • Senkstrang 9 a pressure much smaller than a load pressure (pressure under load condition, especially much less than 200 bar), eg 50 bar or less, are detected and depending on this pressure with respect to a predetermined limit, ie below the limit, a
  • energization of the magnet ES01 may depend on a state of charge of a battery operating the motor of the pump 6, so that, for example, the magnet is energized
  • the magnet ES01 may be kept de-energized upon detection of a sufficiently high state of charge of the battery, and instead a circulation operation for energy dissipation by the circulation valve UL may be provided.
  • a redundant lowering can be implemented, in the event of malfunction of the lowering valve 17, for example, clogging by dirt particles (metal chips from hydraulic cylinder) an undesirable lowering is avoided by the fact that the 2/2-way valve is kept closed, especially the magnet ES01 de-energized and the pump is kept off. For example, it is detected via a seat contact in the seat of an operator of a material handling vehicle when it rises from the seat, so that in case of insufficient weight load of the seat no energization of the magnet ES01 and thus no opening of the 2/2-way valve can be done.
  • the modular design makes it possible to flange several parallel modules to interfaces on the lifting module, so that additional lifting and tilting is possible.
  • Each of the in the Fig. 2 to 5 illustrated embodiments shows an emergency lowering.
  • LB test is conventionally carried out by the manufacturer in a test box and serves to set a stroke limiter or countersunk brake in such a way that, when the hose breaks, a maximum lowering of maximum speed is less than a predetermined limit speed.
  • current is applied to the magnets EP02, ES01 under load, ie application of, for example, a voltage of 1000 mV to the magnet ES01, in order to make it possible to relieve the drawstring from the tank T.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)
EP15181346.6A 2015-08-18 2015-08-18 Module de levage Withdrawn EP3133043A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15181346.6A EP3133043A1 (fr) 2015-08-18 2015-08-18 Module de levage

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EP15181346.6A EP3133043A1 (fr) 2015-08-18 2015-08-18 Module de levage

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EP3133043A1 true EP3133043A1 (fr) 2017-02-22

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020011957A1 (fr) * 2018-07-11 2020-01-16 Parker Hannifin Emea S.À.R.L. Ensemble soupape de commande pour véhicule de manutention de charge

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10010670A1 (de) * 2000-03-04 2001-09-13 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
EP2058270A1 (fr) 2007-11-06 2009-05-13 HAWE Hydraulik SE Dispositif de levage électrohydraulique
EP2799389A1 (fr) * 2011-12-26 2014-11-05 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique destiné à un chariot élévateur à fourche
EP2818446A1 (fr) * 2013-06-17 2014-12-31 Kabushiki Kaisha Toyota Jidoshokki Dispositif d'entraînement hydraulique pour véhicule de manutention de cargaison
WO2015190307A1 (fr) * 2014-06-12 2015-12-17 株式会社豊田自動織機 Dispositif d'entraînement hydraulique pour véhicule de transport

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10010670A1 (de) * 2000-03-04 2001-09-13 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
EP2058270A1 (fr) 2007-11-06 2009-05-13 HAWE Hydraulik SE Dispositif de levage électrohydraulique
EP2799389A1 (fr) * 2011-12-26 2014-11-05 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique destiné à un chariot élévateur à fourche
EP2818446A1 (fr) * 2013-06-17 2014-12-31 Kabushiki Kaisha Toyota Jidoshokki Dispositif d'entraînement hydraulique pour véhicule de manutention de cargaison
WO2015190307A1 (fr) * 2014-06-12 2015-12-17 株式会社豊田自動織機 Dispositif d'entraînement hydraulique pour véhicule de transport

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020011957A1 (fr) * 2018-07-11 2020-01-16 Parker Hannifin Emea S.À.R.L. Ensemble soupape de commande pour véhicule de manutention de charge

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