EP1067296B1 - Module de levage électrohydraulique - Google Patents

Module de levage électrohydraulique Download PDF

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Publication number
EP1067296B1
EP1067296B1 EP00112802A EP00112802A EP1067296B1 EP 1067296 B1 EP1067296 B1 EP 1067296B1 EP 00112802 A EP00112802 A EP 00112802A EP 00112802 A EP00112802 A EP 00112802A EP 1067296 B1 EP1067296 B1 EP 1067296B1
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EP
European Patent Office
Prior art keywords
pressure
consumer
function
control
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.)
Expired - Lifetime
Application number
EP00112802A
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German (de)
English (en)
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EP1067296A1 (fr
Inventor
Martin Heusser
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Hawe Hydraulik GmbH and Co KG
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Hawe Hydraulik GmbH and Co KG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • 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
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant 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
    • F15B2211/405—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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/40—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
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the 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
    • F15B2211/50—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief 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
    • F15B2211/50—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
    • 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the invention relates to an electro-hydraulic lifting module of the type specified in the preamble of claim 1.
  • an important aspect is to use electrical energy sparingly or to use a load-related pressure potential of the hydraulic pressure medium to recover electrical energy.
  • Modern industrial trucks contain a speed-adjustable supply pump that is driven by an electric motor.
  • a load-related pressure potential of the pressure medium is used for energy recovery by the supply pump driving the electric motor as a generator.
  • the electrical energy obtained is returned to the battery.
  • industrial trucks such as reach trucks, for energy recovery e.g. the consumer of the main lifting function in question.
  • a reach truck for example, the so-called initial lifting cylinder, which should also be operable during the energy-saving mode of the supply pump.
  • an electrohydraulic lifting module known from EP 0 669 281 A for an industrial truck with a lifting mast
  • a single pump is provided which can lower a main consumer in a lowering line monitored by a pressure compensator and drive a generator.
  • a common control valve device is also provided for all consumers to operate a secondary function, which works with the pressure compensator as a two-way flow controller.
  • a pilot pressure-controlled bypass valve is provided between a return connection to the pump and the tank connected to the tank, switches to a position in which the lowering branch is connected directly to the tank.
  • the lowering branch is permanently connected to the suction side of the single pump for a regeneration operating mode of the pump upstream of the bypass valve.
  • the invention has for its object to provide an electro-hydraulic lifting module of the type mentioned with an efficient energy saving mode of the supply pump.
  • the entire pressure difference between the pressure level of the consumer of the main lifting function and the tank pressure level is used for energy recovery.
  • Only a single supply pump enables a relatively simple hydraulic control circuit with a special connection anyway for the functions of the necessary components and thus a structurally simple electrohydraulic lifting module, which is particularly useful for reach trucks.
  • the electric motor of the single supply pump is used in the energy-saving mode on the control side in such a way that it either supplies electricity as a generator or additionally consumes electricity.
  • the consumer pressure supply lines are connected to the outputs of a three-way proportional flow control device, and the control valve component for lifting the consumer of the main lifting function is arranged downstream of the three-way proportional flow control device and in the direct connection to the tank. As such, the control valve component controls the lifting process of the consumer of the main lifting function when the supply pump is driven.
  • the three-way proportional flow control device allocates the required amount to the consumer of the secondary function.
  • the first and second control pressures for the pressure balance of the flow control device are tapped from the pressure supply line for the consumer of the secondary function, so that here the pressure conditions in the direct connection to the tank, in which direct connection the control valve component for lifting the consumer of the main lifting function have no influence. This enables smooth transitions between the energy-saving mode and the supply mode to be controlled.
  • the proportional measuring orifice in the pressure supply line of this consumer sets exactly the required pressure difference as required, which is maintained by the pressure compensator for supplying the consumer of the secondary function.
  • the at least one consumer of the secondary function is controlled via a proportional control valve, a representative load pressure being tapped off as the first control pressure for the pressure compensator downstream of the proportional directional control valve. This saves a separate proportional measuring orifice. It is obvious that several consumers for secondary functions can each be controlled with a proportional control valve and the highest load pressure is then supplied to the pressure compensator as the first control pressure, expediently via shuttle valve devices.
  • the control valve component can be a simple 2/2 directional or directional control valve or, if appropriate, a 2/2 proportional control valve.
  • the speed control of the supply pump can be used for a clean ramp control of the consumer of the main lifting function.
  • a clean ramp function can be performed using the proportional directional control valve can be controlled without the supply pump having to make any significant contribution.
  • the crossing point at which the pressure supply line to the consumer of the main lifting function is connected can also be arranged in the control valve component (position: lifting) arranged in the direct connection to the tank.
  • the control valve component should then expediently be a structurally simple 3/2-way control valve in black / white construction (two switching positions: open to the tank or open to the consumer) or a 3/2-proportional control valve that controls a ramp function.
  • control valve component in the secondary line should be a 2/2-way proportional control valve.
  • a simple 2/2 black / white control valve can also suffice here, because if necessary the flow control device and / or the control valve component cooperate in the direct connection when lowering.
  • the system pressure is - as usual - secured by a pressure relief valve on the pressure side of the supply pump.
  • pressure protection is also expedient for the possibly lower pressure level of the consumer of the secondary function provided, namely by a second, provided between the pressure supply line to the consumer of the secondary function and the tank, then set lower pressure relief valve, or a pressure relief valve positioned in the control line for the first control pressure of the pressure compensator.
  • the second pressure relief valve is bypassed by a relief line containing a throttle for the first control pressure.
  • the throttle in the relief line is dimensioned so that even the first low pilot pressure is properly reported to the pressure compensator.
  • the consumer VH is, for example, the lifting cylinder, while the consumer VN e.g. is the so-called initial stroke cylinder.
  • a single supply pump P is provided which is driven by a speed-controllable electric motor M for lifting control. In addition to the supply mode for energy recovery (electrical energy) or energy saving, this supply pump P can also be operated in an energy-saving mode.
  • the supply pump P with pressure medium displaced from the consumer VH drives the electric motor M as a generator and generates energy, or the electric motor M only just absorbs the energy that is not present in the displaced pressure medium of the consumer VH for actuating the consumer VN. If the energy in the displaced pressure medium is sufficient for the secondary function, then electrical energy is recovered or, despite the secondary function, no electrical energy needs to be supplied.
  • a line 1 leads from the pressure side of the supply pump P to the input of a three-way proportional current control device SR, which can be adjusted by a proportional magnet m1p.
  • a direct connection 2 to the tank T is connected to a first oil side of the flow control device SR, while a pressure supply line 15 to the at least one consumer VN or its directional or directional control valve W is connected to the other oil side.
  • the system pressure is monitored by a pressure relief valve 3.
  • a pressure supply line 5 to the consumer VH is connected, in which a check valve 6 is arranged, which blocks in the backflow direction.
  • a control valve component 10 for lifting control of the consumer VH is arranged in the direct connection 2, which in the embodiment of FIG. 1 is designed as a 2/2 proportional directional control valve 30 and with a proportional magnet m3p for adjustment Is provided.
  • a return line 11 leads from the consumer VN to the tank T.
  • a second pressure relief valve 3a is provided in a control line 12.
  • the second pressure relief valve 3a is bypassed by a control line loop 13 in which a throttle point 14 is provided.
  • the second pressure relief valve 3a and the control line 12 are provided here as an expedient option.
  • the consumer VH for the main lifting function is monitored by a so-called lowering brake B, which is also responsible for limiting the maximum outflow quantity when lowering.
  • a lowering brake B which is also responsible for limiting the maximum outflow quantity when lowering.
  • a further control valve component 9 for lowering control is contained, namely a 2/2-way proportional control valve with a proportional magnet m2p.
  • the secondary line 8 leads between a check valve R blocking in the direction of the tank T and the supply pump P to the suction side of the supply pump 3.
  • Each directional control valve W (a simple directional or directional control valve in FIG. 1) of a consumer VN for the secondary function is connected to the pressure supply line 15 with a pressure line 16, and to the return line 11 with a return line 17th
  • the control valve component 10 is adjusted for lifting from the open position in the direction of the shut-off position when the supply pump P is driven (by means of of the proportional magnet m3p), so that 5 pressure builds up in the pressure supply line.
  • the flow control device SR directs the pressure and the quantity only to the crossing point 4.
  • the control valve component 9 remains in the shut-off position shown.
  • the lowering brake B is bypassed by the check valve that opens; the consumer VH extends in the lifting direction.
  • the control takes place depending on the energization of the proportional magnet m3p; if necessary, the speed of the electric motor M used to control a clean ramp function and set the desired speed. If an auxiliary function is controlled at the same time, then the pressure medium required for this is provided in the pressure supply line 15 by energizing the proportional magnet m1p, the speed of the electric motor M then also being increased if necessary.
  • control valve component 10 is again adjusted in the direction of the open position and, if no secondary function has to be controlled, the electric motor M is also switched off. If a secondary function is also to be controlled, this can be done by regulating the speed of the supply pump P and energizing the proportional solenoid m1p. Optionally, the control valve component 10 is also held in the shut-off position.
  • the flow control device SR only opens at the crossing point 4, the control valve component 10 is held in the open position, and becomes Control valve component 9 adjusted from the shut-off position shown in the direction of the through position, by means of the proportional magnet m2p. Since the check valve R then closes, the pressure medium displaced by the secondary line 8 is pressed by the supply pump P, which drives the electric motor M as a hydraulic motor as a generator for energy recovery. The pressure medium passing the supply pump P flows through the line 1, the flow control device SR and the direct connection 2 via the control valve component 10 to the tank T.
  • the proportional magnet m1p is energized accordingly in order to lead the required quantity into the pressure supply line 15, from which the consumer VN is then actuated via its directional or directional control valve W.
  • Pressure medium displaced from a consumer VN flows via the return line 17 and the return line 11 directly to the tank.
  • FIG. 2 differs from that of FIG. 1 in that the control valve component 10 for the lifting control is a simple 2/2-way control valve 31 with a simple switching magnet m3.
  • the speed control of the electric motor M is used.
  • the rest of the structure is the same. 1, the three-way proportional flow control device SR is shown in detail, namely with a pressure compensator D and a measuring orifice MB arranged downstream of the pressure compensator D in the pressure supply line 15 and adjustable by the proportional magnet m1p.
  • the pressure compensator D holding the pressure difference set on the measuring orifice MB is set by first and second control pressures and a control spring 20 and holds the set pressure difference even in the event of pressure fluctuations in line 1 and / or 15.
  • the first control pressure acts together with the control spring 20 in the opening direction the pressure compensator D from the line 1 to the pressure supply line 15.
  • the first control pressure comes from a control line 12a, which branches off from the control line 12 branching off from the pressure supply line 15 at the intersection 18 with the second pressure relief valve 3a.
  • the crossing point 18 is located downstream of the measuring orifice MB.
  • the second control pressure is tapped at a crossing point 21 upstream of the measuring orifice MB in the pressure supply line 15, transmitted via a control line 22 to the other side of the pressure compensator D and acts on it in the opening direction from the pressure line 1 to the direct connection 2 to the tank T. Since the first and second control pressures are tapped only in the circuit of the secondary function, the pressure conditions in lines 1, 2 or in the pressure supply line 5 to the consumer VH have no influence on the control intervention of the current control device SR.
  • the line loop 13 with the throttle point 14, which should be narrower than a throttle point 19 in the control line 12a, serves to relieve the control line 12a if the measuring orifice MB is adjusted into its shut-off position and no secondary function can be controlled.
  • FIG. 3 differs from the two aforementioned embodiments in that the control valve component 10 for lifting control contains the crossing point 4 'between the direct connection 2 and the pressure supply line 5 and for this purpose as a 3/2-way control valve 32 without a proportional function and is formed with a switching magnet m3.
  • the symbolism shows that it is a 3/2-way seat valve that replaces the check valve 6 with the seat valve function 6 '.
  • the directional and directional control valves W of the consumer VN for the secondary functions are simple directional control valves without a proportional function, each consumer VN being connected to the directional or directional control valve W via working lines 23, 24.
  • FIG. 4 corresponds functionally to the embodiment of FIG. 2 with the control valve component 10 designed as a simple 2/2-way control valve 31, which is adjustable by means of a switching magnet m3.
  • the measuring orifice required for the pressure compensator D is not contained in the pressure supply line 15, but the proportionally adjustable measuring orifice is formed by a directional or directional control valve WP for the consumer VN of the secondary function, which is a proportional control valve with the proportional solenoids m1p (and, if necessary, an inflow regulator, not shown).
  • the first control pressure for the pressure compensator D results in the working line 23, 24 that is acted upon, which is transmitted via the control line 12a and is tapped, for example, at a shuttle valve 25 between the working lines 23, 24.
  • the first control pressure is transferred from the shuttle valve 25 directly to the control line 12a via a control line 26.
  • their control lines 26, 28 are linked via at least one additional shuttle valve 27, which transmits the highest first control pressure into the control line 12a.
  • the second control pressure is tapped from the pressure supply line 15 via the control line 22.
  • control valve component 10 for the lifting control is a 3/2-way control valve of simple design with a switching magnet m3.
  • this is not a poppet valve, but a slide valve, which also contains the crossing point 4 'to the pressure supply line 5.
  • control valve component 9 (lowering) in the secondary line 8 could be a simple 2/2-way black / white directional control valve with a simple switching magnet (without proportional function).
  • control valve component 10 for lifting control is a 3/2-way proportional control valve 34 with at least one proportional magnet m3p in slide valve design and with a control function (indicated by the parallel lines).

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  • Engineering & Computer Science (AREA)
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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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Claims (10)

  1. Module de levage électro-hydraulique (S), en particulier pour un chariot de manutention tel qu'un chariot élévateur à fourche rétractable, avec une pompe d'alimentation unique (P) entraînable par un moteur électrique (M), pouvant fonctionner dans un mode alimentation et un mode gain d'énergie, et à laquelle peuvent être raccordées sélectivement des conduites d'alimentation en pression (5, 15) d'au moins un consommateur (VH) d'une fonction de levage principale et d'au moins un consommateur (VN) d'une fonction secondaire, et avec un tronçon secondaire (8), bloqué dans la direction de reflux vers le réservoir, menant du consommateur (VH) de la fonction de levage principale, par l'intermédiaire de la pompe d'alimentation (P), à une liaison directe (2) avec le réservoir, le consommateur (VN) de la fonction secondaire étant également actionnable en mode gain d'énergie de la pompe d'alimentation (P), caractérisé en ce que le consommateur (VN) de la fonction secondaire, en mode gain d'énergie de la pompe d'alimentation (P), est actionnable au moins proportionnellement, par l'intermédiaire d'un régulateur de débit proportionnel à trois voies (SR) prévu sur le côté refoulement de la pompe (P), par de l'agent sous pression refoulé du consommateur (VH) de la fonction de levage principale au travers du tronçon secondaire (8) et par la pompe d'alimentation (P), régulateur auquel sont raccordées côté échappement les conduites d'alimentation en pression (5, 15) de tous les consommateurs (VH, VN) et la liaison directe (2) avec le réservoir (T), et en ce qu'il est prévu pour la commande de levage de la fonction de levage principale un composant distributeur (10), contrôlant la liaison directe (2) avec le réservoir et disposé dans la direction d'écoulement dans le tronçon secondaire en aval du régulateur de débit proportionnel à trois voies (SR).
  2. Module de levage suivant la revendication 1, caractérisé en ce que le régulateur de débit proportionnel à trois voies (SR) présente une balance de pression (D) et un diaphragme de mesure proportionnel (MB), et en ce que la balance de pression est sollicitée, en direction d'ouverture vers la conduite d'alimentation en pression (15) du consommateur (VN) de la fonction secondaire, par un ressort de réglage (20) et par une première pression de commande en aval du diaphragme de mesure proportionnel (MB) et, en direction d'ouverture vers la conduite d'alimentation en pression (5) du consommateur (VH) de la fonction de levage principale, par une seconde pression de commande en amont du diaphragme de mesure proportionnel (MB).
  3. Module de levage suivant la revendication 2, caractérisé en ce que le diaphragme de mesure proportionnel (MB) est disposé dans la conduite d'alimentation en pression (15) du consommateur (VN) de la fonction secondaire, pour lequel est prévu un simple distributeur (W).
  4. Module de levage suivant la revendication 2, caractérisé en ce qu'un distributeur proportionnel (WP) est prévu pour le consommateur (VN) de la fonction secondaire, et en ce que la pression de charge du consommateur (VN) en aval du distributeur proportionnel (WP) est prélevée en tant que première pression de commande pour la balance de pression (D).
  5. Module de levage suivant la revendication 1, caractérisé en ce que le composant distributeur (10) du consommateur (VH) de la fonction de levage principale est un distributeur par tout ou rien 2/2 (31) ou un distributeur proportionnel 2/2 (30) prévu dans la liaison directe (2) avec le réservoir en aval d'un point d'intersection (4), à partir duquel la conduite d'alimentation en pression (5) mène au consommateur (VH) de la fonction de levage principale.
  6. Module de levage suivant la revendication 1, caractérisé en ce que le composant distributeur (10) du consommateur (VH) de la fonction de levage principale est un distributeur par tout ou rien 3/2 (33) ou un distributeur proportionnel 3/2 (34), prévu dans la liaison directe (2) avec le réservoir et qui renferme un point d'intersection (4'), à partir duquel la conduite d'alimentation en pression (5) mène au consommateur (VH) de la fonction de levage principale.
  7. Module de levage suivant la revendication 1, caractérisé en ce que le consommateur (VH) de la fonction de levage principale est protégé par un frein de descente (B) limitant la vitesse de descente maximale en charge.
  8. Module de levage suivant l'une au moins des revendications précédentes, caractérisé en ce qu'un distributeur proportionnel 2/2 (9) ou un distributeur par tout ou rien 2/2 est prévu dans le tronçon secondaire (8) pour contrôler la descente du consommateur (VN).
  9. Module de levage suivant la revendication 1, caractérisé en ce que, en supplément d'une soupape de limitation de pression (3) en aval du régulateur de débit proportionnel à trois voies (SR), adaptée au niveau de pression de la fonction de levage principale du consommateur (VH), il est prévu une seconde soupape de limitation de pression (3a) adaptée au niveau de pression, éventuellement plus faible, du consommateur (VN) de la fonction secondaire, disposée entre la conduite d'alimentation en pression (15) du consommateur (VN) de la fonction secondaire et le réservoir (T) ou dans une conduite pilote (12, 12a) pour prélever la première pression de commande.
  10. Module de levage suivant la revendication 9, caractérisé en ce que la seconde soupape de limitation de pression (3a) est contournée en direction du réservoir (T) par une conduite de décharge (13), renferment un point d'étranglement (14), pour la première pression de commande.
EP00112802A 1999-07-06 2000-06-16 Module de levage électrohydraulique Expired - Lifetime EP1067296B1 (fr)

Applications Claiming Priority (2)

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DE29911686U DE29911686U1 (de) 1999-07-06 1999-07-06 Elektrohydraulischer Hubmodul
DE29911686U 1999-07-06

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EP1067296A1 EP1067296A1 (fr) 2001-01-10
EP1067296B1 true EP1067296B1 (fr) 2004-12-29

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Publication number Priority date Publication date Assignee Title
DE10010670C2 (de) * 2000-03-04 2003-11-06 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
DE10224730B4 (de) * 2001-06-29 2012-09-27 Linde Material Handling Gmbh Hydraulische Steuereinrichtung
DE102004011913B4 (de) 2004-03-11 2005-12-29 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
DE102006003414B3 (de) * 2006-01-24 2007-08-02 Sauer-Danfoss Gmbh & Co Ohg Hydraulische Schaltungsanordnung
DE102007010697A1 (de) * 2007-03-06 2008-09-11 Jungheinrich Aktiengesellschaft Flurförderzeug
EP2058270B1 (fr) 2007-11-06 2010-05-26 HAWE Hydraulik SE Dispositif de levage électrohydraulique
DE502007004419D1 (de) 2007-11-21 2010-08-26 Hawe Hydraulik Se Elektrohydraulischer Hubmodul
EP3171039A1 (fr) * 2015-11-18 2017-05-24 HAWE Hydraulik SE Module de levage hydraulique presentant une fonction de levage et d'abaissement
DE102018112835A1 (de) 2018-05-29 2019-12-05 Fsp Fluid Systems Partner Holding Ag Hydrauliksystem, Hydraulikeinheit, Fahrzeug, Verfahren und Verwendung
GB2575480A (en) * 2018-07-11 2020-01-15 Parker Hannifin Emea Sarl A control valve assembly for a load handling vehicle

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GB1365511A (en) 1972-05-04 1974-09-04 Conveyancer Ltd Energy recovery systems
JPS6434627A (en) 1987-07-30 1989-02-06 Tsudakoma Ind Co Ltd Pallet clamp equipment of machine tool
JPH02215700A (ja) 1989-02-14 1990-08-28 Toyota Autom Loom Works Ltd バッテリ式産業車両における油圧装置
DE9218483U1 (de) 1992-11-06 1994-04-28 Honeywell Ag, 63067 Offenbach Hub- und Senkeinrichtung
DE4402653C2 (de) 1994-01-29 1997-01-30 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
DE19744429A1 (de) 1997-10-08 1999-04-22 Still Wagner Gmbh & Co Kg Flurförderfahrzeug mit einer Lastaufnahmevorrichtung und Verfahren zum Absenken der Lastaufnahmevorrichtung

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DE50009076D1 (de) 2005-02-03
DE29911686U1 (de) 1999-09-16

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