EP1699727B1 - Systeme de levage servant a lever et abaisser et/ou deplacer de grosses charges - Google Patents

Systeme de levage servant a lever et abaisser et/ou deplacer de grosses charges Download PDF

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Publication number
EP1699727B1
EP1699727B1 EP04803767A EP04803767A EP1699727B1 EP 1699727 B1 EP1699727 B1 EP 1699727B1 EP 04803767 A EP04803767 A EP 04803767A EP 04803767 A EP04803767 A EP 04803767A EP 1699727 B1 EP1699727 B1 EP 1699727B1
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EP
European Patent Office
Prior art keywords
cylinder
pressure
lifting
piston
housing
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.)
Not-in-force
Application number
EP04803767A
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German (de)
English (en)
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EP1699727A1 (fr
Inventor
Herbert Kallenberger
Günther MOSCHUNG
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Individual
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Individual
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Publication of EP1699727A1 publication Critical patent/EP1699727A1/fr
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    • 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
    • B66F3/00—Devices, e.g. jacks, adapted for uninterrupted lifting of loads
    • B66F3/24—Devices, e.g. jacks, adapted for uninterrupted lifting of loads fluid-pressure operated
    • 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
    • B66F3/00—Devices, e.g. jacks, adapted for uninterrupted lifting of loads
    • B66F3/46—Combinations of several jacks with means for interrelating lifting or lowering movements
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1466—Hollow piston sliding over a stationary rod inside the cylinder
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and 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
    • F15B2211/20—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
    • 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
    • F15B2211/305—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
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional 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
    • F15B2211/405—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
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to 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
    • F15B2211/428—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
    • F15B2211/45—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
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/50—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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure 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
    • F15B2211/70—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
    • F15B2211/7055—Linear output members having more than two chambers
    • 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
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a lifting system for raising and lowering and / or moving large loads, which has a number of individually controllable, simultaneously to several activatable lifting modules, each having a hydraulic lifting cylinder with a piston, which forms a one-sided movable boundary of a drive pressure chamber the pressurization of the piston to perform a working stroke is displaceable relative to the housing of the cylinder, and in the pressure relief of the piston in the sense of performing a return to a basic position in the opposite direction is displaceable, each lifting cylinder is equipped with a displacement sensor, the input signals generated, the units of the piston stroke are evaluable.
  • Lifting systems of this type are z. B. for lifting and / or lowering of bridge segments, generally used for positioning of building parts or buildings, possibly to position corrections z. B. be required if in the foundation area of a building subsidence and associated inclinations of building parts occur that can lead to damage.
  • a group of lifting cylinders which should be accessible to a "synchronous" mode of operation, ie essentially operable simultaneously and with the same stroke, is assigned a common pressure supply unit, which is hydraulically connected to the individual lifting cylinders via a control valve block.
  • the means flexible pressure hoses are connected to their individually associated control valves of the control valve block.
  • the object of the invention is therefore to improve a lifting system of the type mentioned in such a way that both the time required for its installation is reduced, as well as a comparatively faster change in position of the load by means of the lifting system is made possible.
  • each lifting cylinder is equipped with its own pressure supply unit and its own electro-hydraulic stroke control unit
  • the lifting cylinder, the pressure supply unit including its reservoir and the electro-hydraulic control unit constructively form a compact lifting module whose function control is done exclusively by electrical control signals
  • the pressure supply unit a high-pressure pump, an electric motor driving this, a pressure limiting valve and a reservoir
  • the electro-hydraulic control unit as an assembly laterally mounted on Hubzylindergephase whose measured in the direction of the central longitudinal axis of the lift cylinder expansion is smaller than that measured between the support planes of the lift cylinder minimum height of the same.
  • the lifting system is divided into a number of virtually autonomous lifting modules, which do not require any hydraulic connection with each other, but only require a suitable electrical control in terms of their interaction only a coordinated, "simultaneous" function. Thanks to the - systemic - elimination of hydraulic connections of the lifting modules with each other, the installation of the lifting system according to the invention is much easier and also subject to a much lower risk of installation defects and therefore less prone to damage to one of the lifting cylinder in operation, as no hydraulic functional coupling between the consists of individual lifting modules. Therefore, the lifting system according to the invention also offers a relatively higher reliability in comparison to the known system.
  • a lifting system according to the features of claim 2 with the lifting cylinders individually assigned rapid traction drives, which are expediently designed so that the pistons of the lifting cylinder can indeed be quickly moved into contact with the object to be moved, but their driving force is not sufficient, the load To provide lifting operation, has the advantage that regardless of an initial position of Hubzylinderkolben this can be brought very quickly in a "common" starting position, from which only the load-stroke is to monitor, leading to a desired positioning of the load should lead. For a precise stroke control, it is therefore not necessary that the individual lifting cylinders are brought into a defined starting position; it is selected as the starting point for the stroke measurement, the contact position of the Hubzylinderkolbens on the load and the hub as it were selected from this position.
  • the lifting modules of the rapid traction drive is designed as an integrated in the respective lifting cylinder hydraulic rapid traverse cylinder, preferably as a double-acting hydraulic cylinder, which takes along the piston of the lifting cylinder as it were in retraction operation.
  • the Hubzylinderkolben compared to the rapid traverse cylinders can perform tilting movements with small angular deflections. This can be compensated for each large-scale support of the Hubzylindergeophuses on a flat abutment surface or Hubzylinderkolbens on a flat support surface of the load, slight deviations of a parallel course of these surfaces in terms of a large distribution of feed and reaction forces.
  • the pressure supply unit of the respective lifting module is designed as a zero-metric high-pressure pump, counts in particular as a piston pump, as provided according to claim 9, this z. B. by controlling the speed of a drive motor of the pump in a simple way to control the express and load gear movements of the rapid traverse drive or the lifting cylinder of the respective Hubmoduls be exploited.
  • a simple possibility in this regard is given by the features of claim 10, which also allows at least approximately an evaluation of the drive signals for the motor or the pump in units of the executed or the stroke to be executed.
  • a total of 10 designated shear module is intended for a lifting system, with the very heavy and the volume of large loads, z. B. sections of bridges, can be raised and lowered, wherein such a system may include a plurality (N) of such hydraulic lifting modules 10.
  • the lifting module 10 in turn comprises a generally designated 11 linear lifting cylinder, a total of 12 designated pressure supply unit with an electrically driven high-pressure pump 13 and a total of 14 designated electro-hydraulic control unit, by means of which the various functions of the lifting module 10 and other, not shown lifting modules of the system are controllable.
  • the lifting cylinder 11 is formed as a single-acting linear cylinder, which has a cylindrical-drip-shaped housing 17 in which a piston 18 is arranged pressure-tight, which forms an axially movable delimitation of a drive pressure chamber 19, the housing fixed axially through the bottom 21 of the cup-shaped cylinder housing 17 is formed.
  • the piston 18 is rotationally symmetrical with respect to the central longitudinal axis 22 of the lifting cylinder 11 is formed.
  • a generally designated 28 rapid traverse cylinder is structurally integrated, which makes it possible to use the provided by the pump 13 hydraulic media flow rate for a quick start of that configuration of the lifting cylinder 11, in which this as it were between the abutment and the Load 24 each supporting arranged - "clamped” - is and the lifting process can be initiated by the fact that now the "large" drive pressure chamber 19 of the lifting cylinder 11 is acted upon by drive pressure.
  • the rapid traverse cylinder 28 is realized as a double - acting linear cylinder with one side exiting from the housing piston rod 29, which starts from a flat-cylindrical, flange-shaped piston 31, within a cylindrical cavity of the piston 18 of the lifting cylinder 11 a cylindrical cup-shaped drive pressure chamber 32 against a Annulus 33 pressure-tight demarcated, which is penetrated axially by the piston rod 29 which is fixedly connected in the central region of the bottom of the Hubzylindergeophusses 17 with the cylinder housing, so that upon pressurization of the cylindrical drive pressure chamber 32 of the rapid traverse cylinder 28 on the piston 18 of the lifting cylinder 17 a the piston 18 is urged out of the housing 17 urging force, which, seen in itself, causes a displacement of the piston 17 in the direction of the arrow 23.
  • the rapid traverse cylinder 28 is designed and arranged such that its central axis coincides with the central longitudinal axis 22 of the lifting cylinder 11.
  • a ring seal 34 is provided, which of a Ring groove of an annular disc-shaped cover member 36 is received, by means of which the annular space 33 of the rapid traverse cylinder 28 pressure-tight with respect to the - in turn annular - drive pressure chamber 19 of the lifting cylinder 11 is delimited.
  • additionally required sealing elements are, for the sake of simplicity of illustration, not specifically shown.
  • the annular drive pressure 19 of the lift cylinder 11 is pressurized, wherein pressure medium by means of the high-pressure pump 13 of the pressure supply unit 12 via the stroke control terminal 37in the - limited area - Drive pressure chamber 19 of the lifting cylinder is initiated.
  • the electrohydraulic control unit 14 has a high pressure supply port 46, via which the output pressure of the pressure supply unit 12 can be coupled into the electrohydraulic control unit 14 and a return port 47, which is directly connected to the unpressurized reservoir 48 of the pressure supply unit 12.
  • the high-pressure pump 13 of the pressure supply unit 12 is connected in a conventional manner via an input check valve 49 to the reservoir 48 and an exit check valve 51 to the high-pressure supply port 46 of the electro-hydraulic control unit 14, provided that these and the pressure supply unit 12 to a building - And functional unit are summarized, in which the pressure supply unit 12 conveys control function.
  • the pressure supply unit 12 is equipped with a pressure relief valve 52 which is connected between the high-pressure supply port 46 and the reservoir 48.
  • the value of the pressure to which the outlet pressure of the pressure supply unit is limited is by adjusting the bias of a valve spring 53 of the pressure relief valve 52 adjustable.
  • the presettable by adjusting the valve spring 53 maximum output pressure of the pressure supply unit 12 is 660 bar.
  • the electro-hydraulic control unit 14 comprises an electrically controllable function control valve 54, which has two alternative functional positions 0 and I, which are associated with the alternative directions of relative movements, which can perform the piston 18 of the lifting cylinder 11 relative to the housing 17.
  • the function control valve 54 is designed as a 3/2-way solenoid valve, which operates as a changeover valve, in whose alternative functional positions 0 and I defined opening cross sections of the respective open flow paths are given.
  • the function control valve 54 is - in the de-energized state of its control solenoid 56 - urged by the action of a biased valve spring 57 in its normal position 0, in which the connected to the high-pressure supply port of the pressure supply unit 12 P-supply port 58 via a released in this functional position 0 flow path 59th communicating with the A-control port 61 of the function control valve 54 which is connected via an output check valve 62 to the high-pressure output 42 of the electro-hydraulic control unit 14, this output check valve 62 by relatively higher pressure at the A control output of the function control valve 54 than the high-pressure Output 42 or the control pressure port 41 of the rapid traverse cylinder 28 is driven in the opening direction and otherwise blocking.
  • the high-pressure output 42 of the electro-hydraulic control unit 14 is further connected via a connection check valve 63 to the retreat control terminal 44 of the rapid traverse cylinder 28 of Hubzyliners 11, this terminal check valve 63 by relatively higher pressure at the high-pressure output 42 of the electric cylinder 28 in his Open position controlled and otherwise blocking.
  • the connection check valve 63 is acted upon by the high outlet pressure of the pump 13 in the opening direction.
  • the high-pressure output of the electro-hydraulic control unit 14 is connected via a pressure reducing valve 64 shown as a check valve with the stroke control port 37 of the "large" annulus 19 of the lifting cylinder 11, via which this annulus 19, a pressure can be coupled, the pressure by a defined amount ⁇ is lower than that via the high-pressure outlet 42 in the large-area limited "bottom-side” drive pressure chamber 32 of the rapid traverse cylinder 28 einkoppelbare pressure which substantially corresponds to the output pressure of the pressure supply unit 12.
  • a check valve illustrated filling valve 66 connected via which, when the piston 18 of the lifting cylinder 11 is displaced by activating the rapid traverse cylinder 28 in the sense of increasing the annular space 19 of the lifting cylinder 11, pressure medium from the reservoir 48 of the pressure supply unit 12 in this annulus 19 - and this filled can hold.
  • the basic position 0 of the functional control valve 54 is assigned to those operating phases of the lifting cylinder 11, in which the piston 18 is moved in rapid traverse to the load 24 or this lifts or shifts in the load lifting operation.
  • a rapid traverse discharge valve 69 is provided, can escape from the pressure medium from its annulus 19 to the pressure supply unit through the pressure medium in the emergency retreat operation of the lifting cylinder 11.
  • the "load” exhaust valve 68 is designed as a pressure-controlled 2/2-way switching valve with blocking basic position and open switch position.
  • the - movable - valve body of the load dump valve 68 is urged on the one hand by the bias of a valve spring 71 and on the other hand by acting on a control surface 72 with the prevailing at the A-control output 61 of the function control valve 54 pressure p A in the blocking basic position 0; by applying a small p x control surface of the valve body of the load relief valve 68 to the output pressure of the pressure supply unit 12, a switching force directed counter to the force of the valve spring 71 is achieved which moves the valve body to the open position 1 of the load relief valve 68 urges.
  • the control surface 72 by the application of the control pressure p A a valve is forced to its normal position "closing" force is greater in magnitude than the control surface 73, which is the output pressure p x of the pressure supply unit 12 interchangeable.
  • the rapid traverse drain valve 69 is also formed as a pressure-controlled 2/2-way switching valve with blocking basic position 0 and continuous switching position 1.
  • the in turn represented by the 2/2-way valve symbol valve body of the rapid traverse valve 69 is on the one hand by the bias of a valve spring 74 and the other by pressurization of a control surface 76 with the prevailing in the "large" annulus 19 of the lifting cylinder 11 pressure in the blocking basic position of the valve and urged by pressurizing a counter-surface 77 with the output pressure p x of the pressure supply unit in its forward position 1, wherein analogous to the load-discharge valve 68, the amount of acted upon by the output pressure of the pressure supply unit
  • Counter surface 77 is significantly smaller than the amount of the acted upon by the pressure in the annular space 19 control surface 76th
  • the lifting module 10 is equipped with an electromagnetic or electronic pressure sensor 78 which generates an evaluable by means of the electronic control unit 16 and indirectly for controlling the Hubmoduls 10 electrical output signal which is a measure of the prevailing pressure in the annular space 19 of the lifting cylinder 11.
  • the lifting module 10 is further equipped with a merely schematically indicated, generally designated 79 path-measuring system that generates characteristic electrical output signals for the position of the piston 18 in the lifting cylinder 11, from the processing of the information about the hub can be obtained, the the load 24 experiences in the course of a work cycle. It is expedient if the distance measuring system 79 is formed as an absolute measuring system whose output signals are a measure of the deflection of the piston 18 from a z. B. minimum volume of the annular space 19 corresponding basic position.
  • Deviating from the schematic "diagram" representation of Fig. 1 are in the lifting module 10, as schematically simplified in the Fig. 2 illustrated, the lifting cylinder 11, the electro-hydraulic control unit 14 and the pressure supply unit 12 combined into a compact unit, such that the electro-hydraulic control unit 14 and the pressure supply unit 12 are arranged laterally of the lifting cylinder 11, in particular such that the electro-hydraulic control unit 14 and the pressure supply unit 12 are housed in a fixed to the housing 17 of the lifting cylinder 11 mounted common housing.
  • connecting channels 172 and 173 which connect the control block designed as an electro-hydraulic control unit 14 with the lifting cylinder 11, seen in the direction of the central axis 22 of the lifting cylinder 11, arranged at a distance from the outer surface 129 of the cylinder base 21, with the lifting module 10 z , B. on a load-bearing foundation can be supported, and there are arranged the electro-hydraulic control unit 14 and the pressure supply unit 12 housing parts between the - parallel - levels 81 and 82 arranged whose distance h min minimum height of the lifting cylinder 11 corresponds, the height of the laterally arranged housing parts is less than this minimum height h min of the lifting cylinder 11.
  • a load 24 should first be raised by a stroke H a , z. B. for the purpose of being able to arrange this load temporarily supporting supports, then raise the load 24 again to remove the supports again and then lower the load again by a defined amount H s in an end position in which they can remain and then lower the piston 18 of the lifting cylinder 11 so far that the lifting module 10 can be easily removed from the area below the supported load 24.
  • the pump 13 If, starting from this "resting" state, the pump 13 is activated, it is - in the initial position of the function control valve 54-pressure medium conveyed into the pressure chamber 32 of the input cylinder 28, and pressure medium from the annular space 33 of the input cylinder 28 displaced, with the result in that the piston 18 of the lifting cylinder 11 moves in the direction of the arrow 23.
  • the pressure medium displaced out of the annular space 33 flows back to the high-pressure supply connection 46 of the electro-hydraulic control unit 14 and is added to the pressure medium flowing from the pump 13 to the drive pressure chamber 32 of the express cylinder.
  • the rapid traverse down valve 69 can not get into its flow position, the valve spring 74 is biased so far that you the opening-acting force caused by the pressurization of the "small” control surface 77th with the output pressure of the pump 13 results, overcompensated and thereby the valve 69 can hold in its blocking position 0, as long as the pump outlet pressure acts on the "small” control surface 77.
  • the rapid traverse discharge valve 69 With increasing pressure in the annular space 19, the rapid traverse discharge valve 69 remains reliably closed, since this pressure due to its effect on the larger control surface 76 an additional “closing" force unfolds, which holds the rapid traverse discharge valve 69 in the blocking position 0.
  • the "load” bleed valve 68 remains in its operating position in its blocking position, if only because the outlet pressure p A acts on both control surfaces 72 and 73 of the valve and the greater control force resulting from the pressurization of the larger control surface 72 relieves the load Discharge valve 68 reliably holds in its blocking position, regardless of which "closing" force deployed by its control spring 71, which can be designed accordingly to a magnitude smaller closing force than the valve spring 74 of the rapid traverse relief valve 69th
  • the function control valve 24 is switched by driving its control magnet 56 with an output signal of the electronic control unit 16 in its functional position I, in the now the P supply port 56 against the control terminal 61st the function control valve 54 is shut off and this, however, connected to the tank return port 65 via the flow path 70, which has the consequence that the "larger" control surface 72 of the load-discharge valve 68 is relieved of pressure and - due to the low presumed restoring force of his Valve spring 71 - a correspondingly low control pressure p x , which is applied to the counter surface 73, is sufficient to switch the load-discharge valve 68 in its flow position I.
  • Pressure medium which is displaced from the bottom-side drive pressure chamber 32 of the rapid traverse cylinder 28 to the high-pressure outlet 42 of the electro-hydraulic control unit 14, flows via the pressure reducing valve 64 "back" into the annular space 19 of the lifting cylinder 11 and from this via the return port 38, the throttle 67 and the load dump valve 68 to the forward reservoir 48.
  • the rapid traverse discharge valve 69 remains, as long as the load acts on the piston 18 of the lifting cylinder 11 and because of the throttling of the output current a significant pressure in the annular space 19 of the lifting cylinder 17 prevails, locked and as long as this pressure is sufficient to the piston of the drain valve 69 with the assistance of the valve spring 74 against the force resulting from the application of the counter surface 77 with the output pressure of the pump 13 is deployed to hold in the locked position, which is possible by suitable design of the rapid traverse drain valve 69 due to common expert actions.
  • lifting cylinder is the structure and function of the basis of the Fig. 1 explained lifting cylinder 11 largely analog and can also with the basis of Fig. 1 described, electro-hydraulic peripheral, namely the pressure supply unit 12 and the electro-hydraulic control unit 14 are operated appropriately.
  • a cylindrical-cup-shaped, generally designated 117, housing is provided, within which a load drive associated piston 118 is arranged pressure-tightly displaceable and forms the axially movable boundary of a load drive pressure chamber 119 which is fixed to the housing through the housing bottom 112.
  • the piston 118 has the shape of a truncated cone externally; wherein the cone angle, which includes a surface line of the conical surface 123 with the central longitudinal axis 22/1, is comparatively small and a typical value between 2 and 3 °, z. B. has a value of 2.5 °; in the immediate vicinity of the diameter of the larger "inner" flat boundary surface 124 of the piston 118 of this has a peripheral annular groove 126 which receives a generally designated 127 annular seal, by means of which the drive piston 118 is slidably sealed in the housing shell 117/1.
  • the ring seal assembly 127 is configured to be under a stretch bias when inserted into the groove 126 and, when the piston 118 is inserted into the housing 117, to be radially compressed to the extent that both between the housing shell 117 / 1 and the outer sealing ring 127/1 as well as between the outer sealing ring 127/1 and the inner sealing ring 127/2 and also between this and the base 126/1 of the annular groove 126 a good sealing effect is achieved and that this seal is also preserved when the piston in the housing 117 is slightly tilted within a predetermined and limited by the cone angle range.
  • This tilting degree of freedom makes it possible that the piston 118 can invest with its free end face 122 over a large area of a limited load 24, when the lift cylinder can be supported over a large area with the lower boundary surface 129 of the housing bottom 112 on a flat limited foundation as an abutment, too if its support surface is not exactly parallel to the planar underside of the load 24.
  • a total of 128 designated rapid traverse cylinder again training as a double-acting linear cylinder is assumed, with one side exiting from the housing 131 piston rod 132 which is fixedly connected to the housing 117 of the load-lifting cylinder 111 and a flange-shaped piston 133, the inside of the rapid traverse cylinder housing 131 a pressure-tight and axially movable delimited by the piston rod 132, rod-side annular space 134 against a cup-cylindrical drive pressure chamber 136 radially through a cylindrical-tubular housing member 137 and axially by a tight in the tubular housing part 137 inserted bottom part 138 is completed.
  • the flange-shaped piston 133 of the rapid-action cylinder 128 is formed by a threaded ring 133/1, which is screwed onto a thread extension 133/2 of the piston rod 132, whereby a sufficiently dense connection between the piston threaded ring 133/1 and the piston rod 132 is achieved by the screw connection becomes.
  • the piston 133 is sealed by means of an outer, piston-tight annular sealing arrangement 139 against the central, in each case the housing-fixed radial boundary of the pressure chambers 134 and 136 of the rapid traverse cylinder 128 forming housing bore 141 of the rapid traverse cylinder housing 131.
  • a housing-fixed "inner" ring seal assembly 142 is provided, which is disposed within the short bore portion 143 of the bottom portion 138 opposite end wall 144 of the housing 131 through which the piston rod 132 of the rapid traverse cylinder piston passes.
  • the housing 131 of the rapid traverse cylinder 128 is disposed within the piston 118 of the load-lifting cylinder 111 in a generally cup-shaped cavity 146, which by a piston 118 in the axial direction passing through, designated overall with 147 stepped bore and one on one side - at the Load-facing side - occlusive terminating flange is generally designated 148, on the inside 149 of the housing 131 of the rapid traverse cylinder 128 with the flat-calotte-shaped outer surface of the formed in the manner of a plano-convex lens bottom portion 138 is axially supported on one side.
  • the bottom part 138 is supported via an elastic sealing ring 153, preferably an O-ring, on a narrow, inner annular shoulder 154 of the housing 131 of the rapid-action cylinder 128, which mediates between the housing bore 141 and a short, inner bore final stage 156 of the cylinder housing 131.
  • an elastic sealing ring 153 preferably an O-ring
  • the diameter d / 1 is slightly smaller than the diameter d / 2 of the short bore output stage 156, so that between this and the bottom portion 138 a small radial clearance is present, the amount of which is only a small fraction of the radial width of the inner annular shoulder 154 of the housing 131, z. B. 1/20 to 1/10 of the same.
  • the diameter d / 3 of a short in the axial direction "disc-shaped" centering insert 158 of the outside arched bottom portion 138 is smaller by a comparable amount than the slight diameter d / 4 of the central bore 141 of the rapid traverse cylinder housing 131, so that there is a game is that thanks to the elasticity of the sealing ring 153 small relative movements of the bottom portion 138 relative to the shell portion 137 of the rapid traverse cylinder housing 131 allows.
  • the rapid traverse cylinder 128 is arranged in a generally pot-shaped, in the radial direction through the stepped bore 147 and in the axial direction on one side - the load side - limited by the end flange 148 receiving space 159.
  • the curved bottom part 138 and the tubular housing part 137 comprising housing 131 of the rapid traverse cylinder 128 between the end flange 148 of the piston 118 and the annular shoulder 151 of the stepped bore 137 as it were elastically clamped, said clamping comes about by the elastic compression of the sealing ring 153 , which is slightly compressed in the axial direction during assembly of the lifting cylinder 111.
  • the end flange 148 is in turn designed cup-shaped in the basic form, such that a one-sided by a circular flange plate 148/1 upstanding, tubular shell portion 148/2 is provided, which is radially outwardly surrounded by an annular fixing portion 148/3 of the end flange 148, the can be supported on an annular shoulder 161 of the stepped bore 147, which mediates between the - last patenten - outermost hole level 147/1 of the - largest - diameter D / 1 of the stepped bore 147 and the bore stage 147/2 slightly smaller diameter D / 2, opposite which the end flange 148 by means of an outer groove 162 of his tubular skirt portion 148/2 used annular seal 163 is sealed.
  • the outer diameter D / a of the end face wall region 144 of the cylindrically tubular housing part 137 of the rapid traverse cylinder 128 passing through the smallest bore step 147/4 and the outer diameter D / m of the tubular housing part 137 of the rapid traverse cylinder 128 are compared with the diameters D / 4 and D / 2 of the surrounding bore walls chosen so much smaller than their clear diameter, that the tilting movements of the Hubzylinderkolbens 118 are not limited by the design of the rapid traverse cylinder 128.
  • the piston 118 is inserted into the cylinder housing 117, exactly centered with respect to the central longitudinal axis 22.
  • a suitable position of the piston 118 for this is its support on the inside of the bottom 112 of the cylinder housing 117th
  • the cylindrical-tubular housing shell 137 of the rapid traverse cylinder housing 131 is inserted into the inner region of the lifting cylinder 111 bordered by the stepped bore 147.
  • the threaded ring 133/1 screwed onto the threaded extension 133/2 of the piston rod 132, wherein the threaded engagement between threaded ring 133/1 and the thread of the threaded extension 133/2 a sufficient sealing effect "inside” mediates, while the ring seal 139 the threaded ring radially outward seals against the tubular housing portion 137 of the rapid traverse cylinder housing 131.
  • a fork-shaped special tool is required, which can be brought into engagement with axial blind bores, not shown, of the threaded ring.
  • the sealing ring 153 is placed on the inner annular shoulder 154 of the rapid traverse cylinder housing 131 and the bottom part 138 is inserted into the bore end stage 156 of the cylindrical tubular shell part 137.
  • the load side disposed end flange 148 is inserted into the bore stages 147/1 and 147/2 and by means of axially symmetrical grouped mounting screws 171, which are supported on the load side of the end flange 148 and engage in armature thread, in the load side Ring shoulder 161 are arranged fixed;
  • the end flange 148 urges the bottom portion 138 of the rapid traction cylinder housing 131 into its tubular shell 137 somewhat, whereby the ring seal 143 enters its sealing, slightly compressed configuration in which it is under a bias that the bottom portion 138 and the shell portion 137 of the rapid traverse -Cylinder housing on the end flange 148, on the one hand, and on the annular shoulder 151 of the Hubzylinderkolbens 118, on the other hand, holds with a minimum force in plant.
  • control channels 39 and 43 according to Fig. 1 corresponding control channels 39/2 and 43/2, via the pressure medium in the pressure chambers 136 and 134 of the rapid traverse cylinder 128 according to Fig. 3 can flow in or out of these are in the embodiment according to FIG. 3 are tightly connected to connection channels 172 and 173, which extend in the housing bottom 112 and lead to the respective control pressure port 41 and the return control port 44 of the electro-hydraulic control unit 14.
  • control terminals 44 and 41 are above the bottom 129 of the housing bottom 112 "laterally” arranged by Hubzylindergeophuse 117.
  • a control connection "corresponding to the stroke control connection 37 and the return control connection 38" is arranged laterally and, if necessary, communicating with the drive pressure space 119 of the lifting cylinder 111, which is likewise not shown - likewise extending in the housing bottom 112.

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Claims (12)

  1. Système de levage pour lever et abaisser et/ou déplacer de grosses charges, comprenant une pluralité de cylindres de levage hydrauliques (11) commandables individuellement, dont plusieurs peuvent être activés simultanément, qui ont chacun un piston (18) qui forme une limite mobile d'un côté pour un espace de pression d'entraînement (19), dont la sollicitation de pression permet de déplacer le piston (18) pour effectuer une course de travail par rapport au boîtier (17) du cylindre (11), et dont la décharge de pression permet de déplacer le piston (18) dans le sens inverse en vue de la réalisation d'un mouvement de retour dans une position de base, chaque cylindre de levage (11) étant équipé d'un capteur de position (79) qui produit des signaux de sortie qui peuvent être analysés dans des unités de la course du piston, caractérisé par les caractéristiques suivantes :
    a) chaque cylindre de levage (11) est équipé d'une unité propre d'alimentation en pression (12) ainsi que d'une unité propre de commande de levage électrohydraulique (14) ;
    b) le cylindre de levage (11), l'unité d'alimentation en pression (12) y compris son réservoir (48) et l'unité de commande électrohydraulique (14) sont réalisés de manière constructive sous forme d'un module de levage compact (10), dont la commande de fonctionnement s'effectue exclusivement par des signaux de commande électriques ;
    c) l'unité d'alimentation en pression (12), qui comprend une pompe haute pression (13), un moteur électrique (15) l'entraînant, une soupape de limitation de la pression (52) et le réservoir (48), et l'unité de commande électrohydraulique (14) sont réalisées sous forme de module monté latéralement sur le boîtier du cylindre de levage (17), dont l'extension mesurée dans la direction de l'axe longitudinal (22) du cylindre de levage (f) est inférieure à sa hauteur minimale mesurée hmin entre les plans de support (81 et 82) du cylindre de levage.
  2. Système de levage selon la revendication 1, caractérisé en ce que le cylindre de levage (11 ; 111) du module de levage respectif (10) est muni d'un entraînement hydraulique à vitesse rapide (17, 18 ; 117, 118), au moyen duquel le piston (18 ; 118) du cylindre de levage peut être déplacé avec une plus faible force d'avance mais relativement rapidement dans la position de sortie requise pour le déclenchement de la course de charge, position à partir de laquelle la pression de la course de charge du cylindre de levage commence à s'établir, durant laquelle l'entraînement d'avance s'effectue par le cylindre de levage (11 ; 111) par sollicitation en pression de son espace de pression d'entraînement (19 ; 119), la vitesse d'avance en mode d'avance en charge étant réduite de manière considérable par rapport à la vitesse rapide, mais la force d'avance étant toutefois augmentée de manière correspondante.
  3. Système de levage selon la revendication 2, caractérisé en ce que l'entraînement à vitesse rapide est réalisé sous forme de cylindre de vitesse rapide hydraulique intégré dans le cylindre de levage (11) (Fig. 1).
  4. Système de levage selon la revendication 3, caractérisé en ce que le cylindre de vitesse rapide (28) est réalisé sous forme de cylindre hydraulique à double effet.
  5. Système de levage selon la revendication 4, caractérisé en ce que le cylindre de vitesse rapide (28) a un piston (31) en forme de bride, qui est connecté fixement au moyen d'une tige de piston (29) au fond (21) d'un boîtier (17) en forme de pot du cylindre de levage (11), et limite de manière étanche à la pression à l'intérieur d'un espace interne cylindrique du piston (18) du cylindre de levage (11) un espace de pression d'entraînement cylindrique (31) par rapport à un espace annulaire (33) traversé axialement par la tige de piston (29), cet espace annulaire étant pour sa part fermé hermétiquement simultanément vis-à-vis de l'espace de pression d'entraînement (19) du cylindre de levage (11) au moyen d'une garniture d'étanchéité de guidage disposée de manière solidaire sur le piston d'entraînement (18) et enserrant la tige de piston.
  6. Système de levage selon la revendication 4, caractérisé en ce que le cylindre de vitesse rapide (128) a un piston (133) connecté fixement au boîtier du cylindre de levage et un élément de boîtier (137) mobile par rapport à celui-ci, qui est ancré de manière résistante en traction et en poussée entre des éléments de butée (148 et 152) du piston (118) du cylindre de levage (111).
  7. Système de levage selon la revendication 6, caractérisé en ce que
    a) le cylindre de vitesse rapide (128) a une enveloppe de boîtier de forme cylindrique tubulaire, dont le diamètre extérieur D/1 est plus petit que le diamètre D/2 d'un gradin d'alésage (147/3) central du piston de cylindre de levage (118) limitant radialement un espace interne (146) du cylindre de levage (111) en forme de pot cylindrique, mais est plus gros que le diamètre D/4 d'un gradin d'extrémité d'alésage (147/4) qui se raccorde par le biais d'un gradin annulaire radial (152) à la portion d'alésage centrale (147/3) du diamètre D/2, contre lequel la partie de boîtier (137) peut s'appuyer axialement,
    b) l'alésage à gradin du piston du cylindre de levage est fermé du côté de la charge par une bride de terminaison (148), contre le côté interne de laquelle s'appuie - essentiellement de manière ponctuelle - la partie de boîtier mobile (137) du cylindre de vitesse rapide au moyen d'une partie de fond de configuration en forme de calotte du côté extérieur, cette partie de fond formant la limite du côté de la charge de l'espace de pression de commande (136) du cylindre de vitesse rapide (128), et
    c) le piston du cylindre de levage est disposé dans son boîtier de manière mobile de telle sorte que son axe central puisse prendre une orientation s'écartant de l'axe longitudinal central (22) du boîtier (117) du cylindre de levage dans une petite plage de variation.
  8. Système de levage selon la revendication 7, caractérisé en ce que le piston (118) du cylindre de levage (111) a la forme d'un tronc de cône avec un petit angle de conicité (entre 2° et 3°), ce piston ayant, à proximité immédiate de la surface de base (124) plane de plus grand diamètre, une rainure annulaire périphérique (126), dans laquelle est insérée une garniture d'étanchéité annulaire (127), au moyen de laquelle le piston d'entraînement est rendu hermétique vis-à-vis du boîtier (117) à l'intérieur de sa plage de basculement possible par rapport à l'axe longitudinal central (22) du boîtier tout en pouvant glisser.
  9. Système de levage selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la pompe haute pression (13) de l'unité d'alimentation en pression (12) est réalisée sous forme de pompe à piston, dont le volume de refoulement par rotation du moteur d'entraînement (15) a une valeur définie.
  10. Système de levage selon l'une quelconque des revendications 1 à 9, caractérisé en ce que la pompe (13) et/ou le moteur d'entraînement électrique (15) de l'unité d'alimentation en pression respective (12) sont équipés d'un compteur de cycles qui produit à lui seul dans une unité de commande électronique (16) du système de levage un signal de sortie électrique analysable, caractéristique du nombre des rotations du rotor effectuées ou des courses de refoulement de la pompe (13).
  11. Système de levage selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'un capteur de pression électronique ou électromécanique (78) est prévu, lequel produit un signal de sortie électrique caractéristique de la pression dans l'espace de pression d'entraînement (19) du cylindre de levage (11), lequel est acheminé à l'unité électronique (16) du système de levage (10) sous forme de signal d'entrée d'information.
  12. Système de levage selon l'une quelconque des revendications 1 à 11, caractérisé en ce qu'une capteur de pression est prévu, lequel produit un signal de sortie électrique caractéristique de la pression de sortie pA de la pompe (13) de chaque unité d'alimentation en pression (12), lequel est acheminé à l'unité de commande électronique (16) du système de levage (10) sous forme de signal d'entrée d'information.
EP04803767A 2003-12-30 2004-12-11 Systeme de levage servant a lever et abaisser et/ou deplacer de grosses charges Not-in-force EP1699727B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10361807A DE10361807A1 (de) 2003-12-30 2003-12-30 Hubsystem zum Anheben und Absenken und/oder Verschieben grosser Lasten
PCT/EP2004/014126 WO2005066062A1 (fr) 2003-12-30 2004-12-11 Systeme de levage servant a lever et abaisser et/ou deplacer de grosses charges

Publications (2)

Publication Number Publication Date
EP1699727A1 EP1699727A1 (fr) 2006-09-13
EP1699727B1 true EP1699727B1 (fr) 2009-03-11

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EP04803767A Not-in-force EP1699727B1 (fr) 2003-12-30 2004-12-11 Systeme de levage servant a lever et abaisser et/ou deplacer de grosses charges

Country Status (4)

Country Link
EP (1) EP1699727B1 (fr)
AT (1) ATE425117T1 (fr)
DE (2) DE10361807A1 (fr)
WO (1) WO2005066062A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069384A1 (fr) * 2022-09-27 2024-04-04 Automa By Magic S.R.L. Dispositif de déplacement de moules et procédé associé

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202009004608U1 (de) * 2009-04-03 2010-08-12 Khd Humboldt Wedag Gmbh Hydraulikflachzylinder mit verschwenkbarem Kolben und Rückstellvorrichtung
DE102010015115A1 (de) * 2010-04-16 2011-10-20 Georg Kramp Gmbh & Co. Kg Mobiles Hebegerät mit elektro-hydraulischem Antrieb
CN103318799A (zh) * 2012-03-23 2013-09-25 程曼华 矮型机械锁紧式液压千斤顶
DE102013103458A1 (de) * 2013-04-08 2014-10-09 Peri Gmbh Schalungssystem zur Herstellung einer Betondecke
CN103925257B (zh) * 2014-04-08 2017-01-04 奇瑞汽车股份有限公司 顶起装置
CN104879344B (zh) * 2015-05-21 2017-02-01 黄杰 防尘型顶压装置
CN114319382B (zh) * 2022-01-07 2023-09-05 上海巨鲲科技有限公司 基坑钢支撑液压轴力盒
CN114920162B (zh) * 2022-05-24 2023-06-13 柳州欧维姆机械股份有限公司 一种千斤顶防窝缸保护方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2325212B (en) * 1997-05-07 2001-04-11 Humberside Lifting Services Lt Improvements in or relating to a lifting apparatus and a method of lifting
ITRM20010646A1 (it) * 2001-11-02 2003-05-02 Roberto Maggiori Dispositivo di sollevamento integrato auto livellante.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069384A1 (fr) * 2022-09-27 2024-04-04 Automa By Magic S.R.L. Dispositif de déplacement de moules et procédé associé

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ATE425117T1 (de) 2009-03-15
EP1699727A1 (fr) 2006-09-13
WO2005066062A1 (fr) 2005-07-21
DE502004009163D1 (de) 2009-04-23

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