EP1699727B1 - Lift system used to lift and lower and/or displace heavy loads - Google Patents

Lift system used to lift and lower and/or displace heavy loads 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
Other languages
German (de)
French (fr)
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EP1699727A1 (en
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/en
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Publication of EP1699727B1 publication Critical patent/EP1699727B1/en
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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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Abstract

The invention relates to a lift system which is used to lift and lower and/or displace heavy loads, comprising a plurality of individually controllable hydraulic lift cylinders (11) of which several can be activated at the same time, said lift cylinders respectively comprising a piston (18) which forms a unilateral moveable limit for a drive pressure chamber (19), which impinges pressure enabling the piston (18) to be displaced in order to carry out a working lift in relation to the housing (17) of the cylinder (11), when the pressure thereof is relieved, the piston (18) can be displaced in a counter direction in order to carry out a return movement into a base position, wherein each lift cylinder (11) is fitted with a path sensor (79) which emits output signals which can be evaluated in units of the piston lift. Each lift cylinder (11) is fitted with a separate pressure supply unit (12) and a separate electrohydraulic lift control unit (14). The lifting cylinder (11), the pressure supply unit (12) including the storage tank thereof (48), and the electrohydraulic control unit (14) are embodied as a compact lift module (10), whereby it is functionally controlled exclusively by electric control signals. The pressure supply unit (12) which comprises a high pressure pump (13), an electric motor (15) driving said pump, a pressure limiting valve (52) and the storage tank (48) and the electric hydraulic control unit (14) are embodied as a module which an be mounted laterally on the lift cylinder housing (17), whose extension when measured in the direction of the central longitudinal axis (22) f the lift cylinder (F) is less than the minimal height thereof hmin thereof which is measured between the support planes (81 and 82) of the lift cylinder.

Description

Die Erfindung betrifft ein Hubsystem zum Anheben und Absenken und/oder Verschieben großer Lasten, das eine Anzahl von individuell ansteuerbaren, gleichzeitig zu mehreren aktivierbarer Hubmodule hat, die je einen hydraulischen Hubzylinder mit einem Kolben haben, der eine einseitige bewegliche Begrenzung eines Antriebsdruckraumes bildet, durch dessen Druckbeaufschlagung der Kolben zur Ausführung eines Arbeitshubes relativ zum Gehäuse des Zylinders verschiebbar ist, und bei dessen Druckentlastung der Kolben im Sinne der Ausführung einer Rückkehr in eine Grundstellung in der Gegenrichtung verschiebbar ist, wobei jeder Hubzylinder mit einem Weg-Sensor ausgerüstet ist, der Eingangssignale erzeugt, die Einheiten des Kolben-Hubes auswertbar sind.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.

Hubsysteme dieser Art werden z. B. zum Anheben und/oder Absenken von Brückensegmenten, allgemein zum Positionieren von Gebäudeteilen oder Gebäuden verwendet, ggf. zu Positions-Korrekturen, die z. B. erforderlich werden, wenn im Fundamentbereich eines Gebäudes Absenkungen und damit verbundene Neigungen von Gebäudeteilen auftreten, die zu Beschädigungen führen können.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.

Ein derartiges Hubsystem ist auf der Internet-Seite der Firma Enerpac (www.enerpac.com) im Detail erläutert.Such a lifting system is explained in detail on the Internet site of Enerpac (www.enerpac.com) .

Bei den bekannten Hubsystemen ist jeweils einer Gruppe von Hubzylindern, die einer "synchronen" Betriebsweise zugänglich sein sollen, d. h. im wesentlichen gleichzeitig und mit gleichem Hub betreibbar sein sollen, ein gemeinsames Druckversorgungsaggregat zugeordnet, das über einen Steuerventilblock hydraulisch mit den einzelnen Hubzylindern verbunden ist, die mittels flexibler Druckschläuche an die ihnen individuell zugeordneten Steuerventile des Steuerventilblocks angeschlossen sind.In the known lifting systems, 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.

Das insoweit nach Aufbau und Funktion erläuterte, bekannte Hubsystem ist mit zumindest den folgenden Nachteilen behaftet:The extent explained by structure and function, known lifting system is associated with at least the following disadvantages:

Das Installieren eines solchen Hubsystems ist mit einem erheblichen Arbeitsaufwand verbunden, der im wesentlichen durch das Verlegen der Hydraulikleitungen bedingt ist.The installation of such a lifting system is associated with a considerable amount of work, which is essentially due to the laying of the hydraulic lines.

Für den Fall, dass die Last nicht gleichmäßig auf die durch je einen Hubzylinder repräsentieren Abstützpunkte verteilbar ist, d. h. dass die von den Hubzylindern abgestützen Lastanteile dem Betrage nach verschieden sind, ist eine gleichmäßige "synchrone" Lastanhebung an sämtlichen Hubzylindern im Prinzip nicht mehr möglich sondern allenfalls noch angenähert möglich, z. B. derart, dass diejenigen Hubzylinder, die wegen unterschiedlicher Beträge der an Ihnen abgestützten Lastanteile entsprechend verschiedene Hubkräfte entfalten müssen, auch zu verschiedenen Zeiten zur Ausführung einer Teilhub-Bewegungen angesteuert werden. Im Ergebnis wird dadurch sowohl für Vorschub (Hub-)Phasen als auch für Rückkehrphasen mehr Zeit-und Steuerungsaufwand benötigt. Um hierbei einen Aufbau unerwünschter Spannungen im Lastmaterial weitestgehend auszuschließen, ist es im angenommenen Fall erforderlich, den Hub-Vorgang in eine große Anzahl von Teilhüben aufzuteilen, was allerdings wiederum mit einem erheblichen Zeitbedarf verknüpft sein kann.In the event that the load is not evenly distributed to the support points represented by a respective lifting cylinder, d. H. that the load components supported by the lifting cylinders are different in magnitude, a uniform "synchronous" load increase on all lifting cylinders is in principle no longer possible but at best still approximately possible, for. B. such that those lifting cylinders, which must unfold correspondingly different lifting forces due to different amounts of supported on you load shares, are also controlled at different times to perform a Teilhub movements. As a result, more time and control effort is required for both feed (stroke) phases and return phases. In order to exclude a build-up of unwanted stresses in the load material as far as possible, it is necessary in the assumed case to divide the stroke process into a large number of partial strokes, which, however, may in turn be associated with a considerable amount of time.

Aufgabe der Erfindung ist daher ein Hubsystem der Eingangs genannten Art dahingehend zu verbessern, dass sowohl der Zeitbedarf für seine Installation reduziert wird, als auch eine vergleichsweise raschere Positionsänderung der Last mittels des Hubsystems ermöglicht wird.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.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst.This object is achieved by the characterizing features of claim 1.

Dadurch, dass hiernach jeder Hubzylinder mit einem eigenen Druckversorgungsaggregat sowie einer eigenen elektrohydraulischen Hub-Steuereinheit ausgerüstet ist, wobei der Hubzylinder, das Druckversorgungsaggregat einschließlich seines Vorratsbehälters und die elektrohydraulische Steuereinheit konstruktiv ein kompaktes Hubmodul bilden, dessen Funktionssteuerung ausschließlich durch elektrische Steuersignale erfolgt, wobei das Druckversorgungsaggregat eine Hochdruckpumpe, einen diese antreibende Elektromotor, ein Druckbegrenzungsventil und einen Vorratsbehälter umfasst, zusammen mit der elektrohydraulischen Steuereinheit als eine seitlich am Hubzylindergehäuse anmontierte Baugruppe ausgebildet sind, deren in Richtung der zentralen Längsachse des Hubzylinders gemessene Ausdehnung kleiner ist als die zwischen den Stützebenen des Hubzylinders gemessene minimale Höhe desselben. Dabei ist das Hubsystem in eine Anzahl gleichsam autarker Hubmodule unterteilt, die untereinander keiner hydraulischen Verbindung bedürfen, sondern hinsichtlich ihres Zusammenwirkens lediglich einer koordinierten, "simultanen" Funktion lediglich einer geeigneten elektrischen Ansteuerung bedürfen. Dank des - systembedingten - Wegfalls hydraulischer Verbindungen der Hubmodule untereinander ist die Installation des erfindungsgemäßen Hubsystems wesentlich einfacher und auch mit einem wesentlich geringeren Risiko von Installationsmängeln behaftet und daher auch im Betrieb gegen einen Schaden an einem der Hubzylinder weniger anfällig, da keine hydraulische Funktionskopplung zwischen den einzelnen Hubmodulen besteht. Das erfindungsgemäße Hubsystem bietet daher im Vergleich zu dem bekannten System auch eine relativ höhere Funktionssicherheit. Soweit, bedingt durch die der Zahl der Hubmodule entsprechende Zahl von elektrisch angetriebenen Pumpen, gegenüber dem bekannten System ein diesbezüglicher Mehraufwand hinzunehmen ist, wird dieser jedoch durch die durch die kürzeren Installations- und Demontage-Zeiten bedingten Kosteneinsparungen unter wirtschaftlichen Gesichtspunkten weit überkompensiert.The fact that thereafter 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, are formed together with the electro-hydraulic control unit as an assembly laterally mounted on Hubzylindergehäuse 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. In this case, 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. Insofar as, due to the number of lifting modules corresponding number of electrically driven pumps, compared to the known system, a related overhead is acceptable, but this is far overcompensated by the costs incurred by the shorter installation and disassembly times cost savings from an economic point of view.

Ein Hubsystem gemäß den Merkmalen des Anspruchs 2 mit den Hubzylindern einzeln zugeordneten Eilgang-Antrieben, die zweckmäßigerweise so ausgelegt sind, dass die Kolben der Hubzylinder zwar rasch in Anlage mit dem zu bewegenden Objekt gefahren werden können, ihre Antriebskraft jedoch nicht ausreicht, den Last-Hub-Betrieb zu vermitteln, hat den Vorteil, das unabhängig von einer Anfangs-Stellung der Hubzylinderkolben diese sehr schnell in eine "gemeinsame" Ausgangsposition gebracht werden können, ab welcher erst der Last-Hub zu überwachen ist, der zu einer erwünschten Positionierung der Last führen soll. Für eine präzise Hub-Steuerung ist es daher nicht erforderlich, dass die einzelnen Hubzylinder in eine definierte Ausgangsposition gebracht werden; es wird als Ausgangspunkt für die Hub-Messung die Anlageposition des Hubzylinderkolbens an der Last gewählt und der Hub gleichsam von dieser Position ausgewählt.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.

In bevorzugter Ausgestaltung der Hubmodule ist der Eilgang-Antrieb als ein in den jeweiligen Hubzylinder integrierter hydraulischer Eilgang-Zylinder, vorzugsweise als doppelt-wirkender Hydrozylinder ausgebildet, der im Rückzugsbetrieb den Kolben des Hubzylinders gleichsam mitnimmt.In a preferred embodiment of 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.

Durch die Merkmale der Ansprüche 5 und 6 ist eine vorteilhaft einfache Gestaltung eines solchen, in den Hubzylinder integrierten Eilgang-Zylinders angegeben.Due to the features of claims 5 and 6, an advantageous simple design of such, integrated in the lifting cylinder rapid traverse cylinder is specified.

Bei der durch die Merkmale des Anspruchs 7 umrissenen Gestaltung von Hubmodulen eines erfindungsgemäßen Hubsystems können die Hubzylinderkolben gegenüber den Eilgang-Zylindern Kippbewegungen mit kleinen Winkelauslenkungen ausführen. Dadurch können bei jeweils großflächiger Abstützung des Hubzylindergehäuses an einer ebenen Widerlagerfläche bzw. des Hubzylinderkolbens an einer ebenen Stützfläche der Last, geringfügige Abweichungen eines parallelen Verlaufes dieser Flächen im Sinne einer großflächigen Verteilung der Vorschub- und Reaktionskräfte ausgeglichen werden.When outlined by the features of claim 7 design of lifting modules of a lifting system according to the invention, 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 Hubzylindergehäuses 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.

Hierbei ist durch die Merkmale des Anspruchs 8 eine den praktisch auftretenden Bedürfnissen vollauf genügende, einfache Gestaltung des Hubzylinderkolbens angegeben.In this case, by the features of claim 8 a the practical needs occurring fully sufficient, simple design of the Hubzylinderkolbens specified.

Wenn das Druckversorgungsaggregat des jeweiligen Hubmoduls als nullometrisch geführte Hochdruckpumpe ausgebildet ist, zählt insbesondere als Kolbenpumpe, wie gemäß Anspruch 9 vorgesehen, kann diese z. B. durch Steuerung der Drehzahl eines Antriebsmotors der Pumpe auf einfache Weise zur Steuerung der Eil- und Lastgang-Bewegungen des Eilgang-Antriebs bzw. des Hubzylinders des jeweiligen Hubmoduls ausgenutzt werden. Eine diesbezüglich einfache Möglichkeit ist durch die Merkmale des Anspruchs 10 angegeben, die auch zumindest näherungsweise eine Auswertung der Ansteuersignale für den Motor bzw. die Pumpe in Einheiten des ausgeführten bzw. des auszuführenden Hubes ermöglicht.If 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.

Zur Funktionssteuerung des Hubsystems in sinnfälligerweise geeignete Druck-Ist-Wert-Signale, die mittels einer elektronischen Steuereinheit anhand plausibler Verknüpfungen zu Positions-Sollwert-Signalen verarbeitbar sind, können mittels elektronischer oder elektromechanischer Drucksensoren gemäß den Ansprüchen 11 und 12 gewonnen werden.For function control of the lifting system in a manner befittingly suitable pressure actual value signals which can be processed by means of an electronic control unit plausible links to position setpoint signals can be obtained by means of electronic or electro-mechanical pressure sensors according to claims 11 and 12.

Weitere Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung spezieller Ausführungsbeispiele anhand der Zeichnung. Es zeigen:

Fig. 1 -
ein erstes Ausführungsbeispiel eines durch ein Hubmodul reprä- sentierten Hubsystems zum Anheben und Absenken großer Las- ten, mit einem in den Kolben eines Hubzylinders integrierten Eil- gang-Zylinders, einschließlich einer zur Funktionssteuerung vor- gesehene elektrohydraulischen Steuereinheit, in schematisch vereinfachter Blockschaltbild-Darstellung,
Fig. 2
eine schematisch vereinfachte Ansicht des Hubmoduls gemäß Fig. 1 zur Erläuterung eines typischen Einsatzes,
Fig. 3
ein weiteres Ausführungsbeispiel eines Hubmoduls eines erfin- dungsgemäßen Hubsystems in einer der Fig. 1 entsprechenden, schematisch vereinfachten Schnitt- bzw. Blockschaltbilddarstel- lung.
Further details of the invention will become apparent from the following description of specific embodiments with reference to the drawing. Show it:
Fig. 1 -
A first exemplary embodiment of a lifting system represented by a lifting module for lifting and lowering large loads, with a rapid-action cylinder integrated into the piston of a lifting cylinder, including an electro-hydraulic control unit provided for functional control, in a schematically simplified block diagram representation .
Fig. 2
a schematically simplified view of the lifting module according to Fig. 1 to explain a typical use,
Fig. 3
a further embodiment of a lifting module of an inventive Hubsystems in one of Fig. 1 corresponding, schematically simplified sectional or block diagram representation.

Das in der Fig. 1 insgesamt mit 10 bezeichnete Schubmodul ist für ein Hubsystem gedacht, mit dem sehr schwere und auch dem Volumen nach große Lasten, z. B. Teilstücke von Brücken, anhebbar und absenkbar sind, wobei ein solches System eine Vielzahl (N) solcher hydraulischer Hubmodule 10 umfassen kann.That in the Fig. 1 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.

Das Hubmodul 10 umfasst seinerseits einen insgesamt mit 11 bezeichneten linearen Hubzylinder, ein insgesamt mit 12 bezeichnetes Druckversorgungsaggregat mit einer elektrisch antreibbaren Hochdruckpumpe 13 und eine insgesamt mit 14 bezeichnete elektrohydraulische Steuereinheit, mittels derer die verschiedenen Funktionen des Hubmoduls 10 und weiterer, nicht dargestellter Hubmodule des Systems steuerbar sind.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.

Der Hubzylinder 11 ist als einfach wirkender linearer Zylinder ausgebildet, der ein zylindrisch-tropfförmiges Gehäuse 17 hat, in dem ein Kolben 18 druckdicht verschiebbar angeordnet ist, der eine axial bewegliche Abgrenzung eines Antriebsdruckraumes 19 bildet, der axial gehäusefest durch den Boden 21 des topfförmigen Zylindergehäuses 17 gebildet ist. Der Kolben 18 ist rotationssymmetrisch bezüglich der zentralen Längsachse 22 des Hubzylinders 11 ausgebildet.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.

Die Einkopplung von Antriebsdruck in den Antriebsdruckraum 19 erfolgt, in einem nachfolgenden noch näher zu erläuternden Last- Hebe-Betrieb in dem sich der Kolben 18 in Richtung des Pfeils 23 relativ zum Gehäuse 17 "auswärts" bewegt und eine lediglich schematisch angedeutete Last 24, an der der Kolben 18 mit einem Stützfortsatz 26 angreift, gegenüber einem Widerlager 27, an dem der Hubzylinder 11 mit seinem Gehäuseboden 21 abgestützt ist, angehoben werden muß. In den Hubzylinder 11 ist ein insgesamt mit 28 bezeichneter Eilgang-Zylinder baulich integriert, der es ermöglicht, den von der Pumpe 13 bereitgestellten Hydraulikmedien-Volumenstrom für ein rasches Anfahren derjenigen Konfiguration des Hubzylinders 11 zu nutzen, in der dieser gleichsam zwischen dem Widerlager und der Last 24 jeweils abstützend angeordnet - "eingespannt" - ist und der Hebevorgang dadurch eingeleitet werden kann, dass nunmehr der "große" Antriebsdruckraum 19 des Hubzylinders 11 mit Antriebsdruck beaufschlagt wird.The coupling of drive pressure in the drive pressure chamber 19 takes place in a subsequent load-lifting operation to be explained in more detail below the piston 18 moves in the direction of arrow 23 relative to the housing 17 "outward" and an only schematically indicated load 24 to which the piston 18 engages with a support extension 26 against an abutment 27, on which the lifting cylinder 11 with its housing bottom 21st supported, must be raised. In the lifting cylinder 11, 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.

Der Eilgangzylinder 28 ist als ein doppelt - wirkender Linearzylinder mit einseitig aus dem Gehäuse austretender Kolbenstange 29 realisiert, die von einem flach-zylindrischen, flanschförmigen Kolben 31 ausgeht, der innerhalb eines zylindrischen Hohlraumes des Kolbens 18 des Hubzylinders 11 einen zylindrisch topfförmigen Antriebsdruckraum 32 gegen einen Ringraum 33 druckdicht abgrenzt, der von der Kolbenstange 29 axial durchsetzt ist, die im zentralen Bereich des Bodens des Hubzylindergehäusses 17 fest mit dem Zylindergehäuse verbunden ist, so dass bei einer Druckbeaufschlagung des zylindrischen Antriebsdruckraumes 32 des Eilgangzylinders 28 auf den Kolben 18 des Hubzylinders 17 eine den Kolben 18 aus dem Gehäuse 17 heraus drängende Kraft ausgeübt wird, die, für sich gesehen, eine Verschiebung des Kolbens 17 in Richtung des Pfeils 23 bewirkt.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 Hubzylindergehäusses 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.

Der Eilgangzylinder 28 ist so gestaltet und angeordnet, dass seine zentrale Achse mit der zentralen-Längsachse 22 des Hubzylinders 11 zusammenfällt.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.

Zur gleitend verschiebbaren Abdichtung des Kolbens 18 des Hubzylinders 11, der gleichsam das Gehäuse des Eilgangzylinders 28 bildet, gegenüber dessen Kolbenstange 29 ist eine Ringdichtung 34 vorgesehen, die von einer Ringnut eines ringscheibenförmigen Deckelteils 36 aufgenommen ist, mittels dessen der Ringraum 33 des Eilgangzylinders 28 druckdicht gegenüber dem - seinerseits ringförmigen - Antriebsdruckraum 19 des Hubzylinders 11 abgegrenzt ist. Hierfür zusätzlich benötigte Dichtungselemente sind, der Einfachheit der Darstellung halber, nicht eigens dargestellt.For slidingly sliding seal of the piston 18 of the lifting cylinder 11, which forms the same as the housing of the rapid traverse cylinder 28, opposite to the piston rod 29, 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. For this purpose additionally required sealing elements are, for the sake of simplicity of illustration, not specifically shown.

Durch alternative Druckbeaufschlagung und -entlastung des bodenseitigen - größervolumigen - Antriebsdruckraumes 32 des Eilgang-Zylinders 28 sowie seines Ringraumes 33, sind auf die Last 24 hinzu gerichtete sowie von dieser wieder weg gerichtete Eil-Vorschub- und -Rückzugsbewegungen des Kolbens 18 des Hubzylinders 11 steuerbar, die unter der Entfaltung vergleichsweise geringer Kräfte, dafür jedoch mit relativ hoher Bewegungsgeschwindigkeit erfolgen können.By alternative pressurization and relief of the bottom side - larger volume - drive pressure chamber 32 of the rapid traverse cylinder 28 and its annular space 33 are directed to the load 24 and directed away from this again fast forward feed and -rückzugsbewegungen of the piston 18 of the lifting cylinder 11 controllable which can take place under the development of comparatively low forces, but at a relatively high speed of movement.

Zur Anhebung einer schweren Last 24, die größere als mittels des Eilgangzylinders 28 entfaltbare Kräfte erfordert wird, zusätzlich der ringförmige Antriebsdruck 19 des Hubzylinders 11 mit Druck beaufschlagt, wobei Druckmedium mittels der Hochdruckpumpe 13 des Druckversorgungsaggregats 12 über den Hub-Steueranschluß 37in den - großflächig begrenzten - Antriebsdruckraum 19 des Hubzylinders eingeleitet wird.To increase a heavy load 24, which is greater than deployable by the rapid traverse cylinder 28 forces required, in addition, 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.

Zur "langsamen" Absenkung einer Last 24 wird Druckmedium, das, je nach dem Betrag der Last 24 unter einem mehr oder weniger hohen Druck steht, über den Rücklaufanschluß 38 des Hubzylinders 11 aus dessen Antriebsdruckraum 19 ausgeleitet.For "slow" lowering of a load 24 is pressure medium, which, depending on the amount of the load 24 is under a more or less high pressure, discharged via the return port 38 of the lifting cylinder 11 from the drive pressure chamber 19.

Im Eil-Vorschubbetrieb des Eilgangzylinders 28, in dem der Kolben 18 sich auf die Last 24 zu bewegt, bis er an dieser zur Abstützung gelangt, wird Druckmedium mittels der Pumpe 13 in den bodenseitigen Antriebsdruckraum 32 des Eilgangzylinders 28 gefördert, wobei das Druckmedium einen die Kolbenstange 29 in axialer Richtung durchsetzenden Steuerkanal 39 durchströmt, der einen Steuerdruck-Anschluß 41 des Eilgangzylinders 28 mit dem bodenseitigen Antriebsdruckraum 32 verbindet und unmittelbar an den Hochdruck-Ausgang 42 der elektrohydraulischen Steuereinheit 14 angeschlossen ist, die gleichsam zwischen den Eilgangzylinder 28 bzw. den Hubzylinder 11 und das Druckversorgungsaggregat 12 geschaltet ist. Während der bodenseitige Druckraum 32 des Eilgangzylinders 28 Druckmedium aufnimmt, wird solches aus dem Ringraum 33 des Eilgangzylinders 28 verdrängt und über einen weiteren Steuerkanal 43 der Kolbenstange 29, der den Ringraum 33 mit dem Rückzug-Steueranschluß 44 des Eilgangzylinders 28 verbindet, zur elektrohydraulischen Steuereinheit 14 ausgeleitet, in der diester Druckmediumstrom gleichsam wieder dem in den bodenseitigen Druckraum 32 des Eilgang-Zylinders 28 fließenden Druckmediumstrom hinzugefügt wird, entsprechend der in diesem Betriebszustand gegebenen Differenzial-Betriebsphase des Eilgangzylinders 28.In rapid feed operation of the rapid traverse cylinder 28 in which the piston 18 moves toward the load 24 until it comes to this for support, pressure medium is conveyed by means of the pump 13 in the bottom drive pressure space 32 of the rapid traverse cylinder 28, wherein the pressure medium a the Piston rod 29 in the axial direction passing through the control channel 39 flows through, the control pressure connection 41 of the rapid traverse cylinder 28 with the bottom side drive pressure chamber 32 connects and is connected directly to the high-pressure outlet 42 of the electro-hydraulic control unit 14, which is as it were connected between the rapid traverse cylinder 28 and the lifting cylinder 11 and the pressure supply unit 12. While the bottom-side pressure chamber 32 of the rapid traverse cylinder 28 receives pressure medium, such is displaced from the annular space 33 of the rapid traverse cylinder 28 and via a further control channel 43 of the piston rod 29 which connects the annular space 33 with the retreat control terminal 44 of the rapid traverse cylinder 28 to the electro-hydraulic control unit 14th discharged, in the diester pressure medium flow as it were again added to the flowing in the bottom pressure chamber 32 of the rapid traverse cylinder 28 pressure medium flow, according to the given in this operating condition differential operating phase of the rapid traverse cylinder 28th

Die elektrohydraulische Steuereinheit 14 hat einen Hochdruck-Versorgungsanschluß 46, über den der Ausgangsdruck des Druckversorgungsaggregat 12 in die elektrohydraulische Steuereinheit 14 einkoppelbar ist sowie einen Rücklauf-Anschluß 47, der unmittelbar mit dem drucklosen Vorratsbehälter 48 des Druckversorgungsaggregats 12 verbunden ist.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.

Die Hochdruckpumpe 13 des Druckversorgungsaggregats 12 ist in üblicher Weise über ein Eingangs-Rückschlagventil 49 mit dem Vorratsbehälter 48 und über ein Ausgangsrückschlagventil 51 mit dem Hochdruck-Versorgungsanschluß 46 der elektrohydraulischen Steuereinheit 14 verbunden, wobei vorausgesetzt ist, dass diese und das Druckversorgungsaggregat 12 zu einer Bau- und Funktionseinheit zusammengefasst sind, bei der auch das Druckversorgungsaggregat 12 Steuerungsfunktion vermittelt.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.

Das Druckversorgungsaggregat 12 ist mit einem Druckbegrenzungsventil 52 ausgerüstet, das zwischen den Hochdruck-Versorgungs-Anschluß 46 und den Vorratsbehälter 48 geschaltet ist. Der Wert des Druckes, auf den der Ausgangsdruck des Druckversorgungsaggregats begrenzt ist, ist durch Einstellen der Vorspannung einer Ventilfeder 53 des Druckbegrenzungsventils 52 einstellbar. In einer typischen Auslegung des Hubmoduls 10 beträgt der durch Einstellung der Ventilfeder 53 vorgebbare maximale Ausgangsdruck des Druckversorgungsaggregats 12 660 bar.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. In a typical design of the lifting module 10, the presettable by adjusting the valve spring 53 maximum output pressure of the pressure supply unit 12 is 660 bar.

Die elektrohydraulische Steuereinheit 14 umfasst ein elektrisch ansteuerbares Funktionssteuerventil 54, das zwei alternative Funktionsstellungen 0 und I hat, die den alternativen Richtungen der Relativbewegungen zugeordnet sind, die der Kolben 18 des Hubzylinders 11 relativ zu dessen Gehäuse 17 ausführen kann.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.

Das Funktionssteuerventil 54 ist als 3/2-Wegemagnetventil ausgebildet, das als Umschaltventil arbeitet, in dessen alternativen Funktionsstellungen 0 und I definierte Öffnungsquerschnitte der jeweils geöffneten Strömungspfade gegeben sind.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.

Das Funktionssteuerventil 54 wird - im stromlosen Zustands seines Steuermagneten 56 - durch die Wirkung einer vorgespannten Ventilfeder 57 in seine Grundstellung 0 gedrängt, in welcher der mit dem Hochdruck-Versorgungsanschluß des Druckversorgungsaggregats 12 verbundene P-Versorgungsanschluß 58 über einen in dieser Funktionsstellung 0 freigegebenen Strömungspfad 59 kommunizierend mit dem A-Steueranschluß 61 des Funktionssteuerventils 54 verbunden ist, der über ein AusgangsRückschlagventil 62 mit dem Hochdruck-Ausgang 42 der elektrohydraulischen Steuereinheit 14 verbunden ist, wobei dieses AusgangsRückschlagventil 62 durch relativ höheren Druck am A-Steuerausgang des Funktionssteuerventils 54 als am Hochdruck-Ausgang 42 bzw. dem Steuerdruck-Anschluß 41 des Eilgangzylinders 28 in Öffnungsrichtung angesteuert und sonst sperrend ist.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.

In dieser Grundstellung 0 über das Funktionssteuerventil zu 54 ist ein versorgungsseitiger T-Rücklaufanschluss 63 des Funktionssteuerventils 54, der mit Rücklaufanschluss 47 der elektrohydraulischen Steuereinheit 14 bzw. des Druckversorgungsaggregats 12 verbunden ist, gegen den A-Steueranschluß 61 des Funktionssteuerventils 54 abgesperrt.In this basic position 0 via the function control valve to 54 is a supply side T-return port 63 of the function control valve 54, the is connected to return port 47 of the electro-hydraulic control unit 14 and the pressure supply unit 12, shut off against the A-control port 61 of the function control valve 54.

In der Grundstellung 0 des Funktionssteuerventils 54 ist es somit der Hochdruck-Versorgungsanschluß 46 des Druckversorgungsaggregats 12 bzw. der elektrohydraulischen Steuereinehit 14 über das Ausgangs-Rückschlagventils 62 mit dem Steuerdruckanschluß 41 des Eilgangzylinders 28 verbunden und somit der Pumpen-Ausgangsdruck in den Antriebsdruckraum 32 des Eilgangzylinders 28 einkoppelbar.In the initial position 0 of the function control valve 54, it is thus the high-pressure supply port 46 of the pressure supply unit 12 and the electro-hydraulic Steuerereinehit 14 connected via the output check valve 62 to the control pressure port 41 of the rapid traverse cylinder 28 and thus the pump output pressure in the drive pressure chamber 32 of the rapid traverse cylinder 28 can be coupled.

Der Hochdruckausgang 42 der elektrohydraulischen Steuereinheit 14 ist des weiteren über ein Anschluß-Rückschlagventil 63 an den Rückzug-Steueranschluß 44 des Eilgangzylinders 28 des Hubzyliners 11 angeschlossen, wobei dieses Anschluß- Rückschlagventil 63 durch relativ höheren Druck am Hochdruck-Ausgang 42 der elektgangzylinders 28 in seine OffenStellung gesteuert und ansonsten sperrend ist. Insbesondere wird das Anschluß-Rückschlagventil 63 durch den hohen Ausgangsdruck der Pumpe 13 in Öffnungsrichtung beaufschlagt.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. In particular, the connection check valve 63 is acted upon by the high outlet pressure of the pump 13 in the opening direction.

Desweiteren ist der Hochdruck-Ausgang der elektrohydraulischen Steuereinheit 14 über ein als Rückschlagventil dargestelltes Druckminderventil 64 mit dem Hub-Steueranschluß 37 des "großen" Ringraums 19 des Hubzylinders 11 angeschlossen, über das diesen Ringraum 19 ein Druck einkoppelbar ist, der um einen definierten Betrag Δρ niedriger ist als der über den Hochdruck-Ausgang 42 in den großflächig begrenzten "bodenseitigen" Antriebsdruckraum 32 des Eilgangzylinders 28 einkoppelbare Druck, der im wesentlichen dem Ausgangsdruck des Druckversorgungsaggregats 12 entspricht.Furthermore, 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 Δρ 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.

Zwischen den Rücklaufanschluß 38 des Hubzylinders 11 und den Rücklaufanschluß 47 der elektrohydraulischen Steuereinheit 14 ist ein als Rückschlagventil dargestelltes Füllventil 66 geschaltet, über das, wenn der Kolben 18 des Hubzylinders 11 durch Aktivieren des Eilgangzylinders 28 im Sinne einer Vergrößerung des Ringraumes 19 des Hubzylinders 11 verschoben wird, Druckmedium aus dem Vorratsbehälter 48 des Druckversorgungsaggregats 12 in diesen Ringraum 19 nachströmen - und diesen gefüllt halten - kann.Between the return port 38 of the lifting cylinder 11 and the return port 47 of the electro-hydraulic control unit 14 is 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.

Die Grundstellung 0 des Funktions- Steuerventils 54 ist denjenigen Betriebsphasen des Hubzylinders 11 zugeordnet, in denen der Kolben 18 im Eilgang auf die Last 24 zu bewegt wird oder diese im Last- Hubbetrieb anhebt bzw. verschiebt.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.

Bei Erregung des Steuermagneten 26 des Funktions- Steuerventils 54 mit einem Steuer- Ausgangssignal der elektronischen Steuereinheit 16 gelangt das Funktions-Steuerventil 54 in seine Funktionsstellung 1, in welcher der P-Versorgungsanschluß 58 gegen den A-Steuerausgang 61 des FunktionsSteuerventils 54 abgesperrt, dieser jedoch über einen nunmehr freigegebenen Auslaß-Strömungspfad 67 mit dem T-Rücklaufanschluß 65 des Funktions-Steuerventils 54 verbunden ist - die Funktionsstellung 1 des FunktionsSteuerventils ist dem Rückzugsbetrieb - Absenkung der Last und/oder Eil-Rückzugsbewegung des Kolbens 18 - des Hubzylinders 11 zugeordnet.Upon energization of the control solenoid 26 of the function control valve 54 with a control output of the electronic control unit 16 enters the function control valve 54 in its functional position 1, in which the P-supply port 58 is shut off against the A-control output 61 of the function control valve 54, but this is connected via a now released outlet flow path 67 to the T-return port 65 of the function control valve 54 - the functional position 1 of the function control valve is the retraction operation - lowering the load and / or rapid return movement of the piston 18 - the lifting cylinder 11 assigned.

Zwischen den Rücklaufanschluß des Hubzylinders 11 und den Rücklaufanschluß 47 des Druckversorgungsaggregats 12 ist - in hydraulischer Parallelschaltung zu dem Füllventil 66 eine einstellbare Drossel 67 und ein - erstes - Ablassventil 68 umfassende hydraulische Reihenschaltung geschaltet, über die im Falle der Absenkung der Last 24 Druckmedium aus dem Ringraum 19 des Hubzylinders 11 kontrolliert abströmen kann.Between the return port of the lifting cylinder 11 and the return port 47 of the pressure supply unit 12 is - connected in hydraulic parallel to the filling valve 66, an adjustable throttle 67 and a - first - drain valve 68 comprehensive hydraulic series circuit, via which in the case of lowering the load 24 pressure medium from the Annular space 19 of the lifting cylinder 11 can flow controlled.

Ebenfalls in hydraulischer Parallelschaltung zu dem Füllventil 66 bzw. dem die Drossel 67 und das erste Ablassventil 68 umfassend Ablasszweig der elektrohydraulischen Steuereinheit 14 ist ein Eilgang-Ablassventil 69 vorgesehen, über das im Eil-Rückzugsbetrieb des Hubzylinders 11 Druckmedium aus seinem Ringraum 19 zum Druckversorgungsaggregat hin abströmen kann.Also in hydraulic parallel connection to the filling valve 66 or the throttle 67 and the first discharge valve 68 comprising discharge branch of the electro-hydraulic control unit 14, 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.

Das "Last"-Ablassventil 68 ist als druck-gesteuertes 2/2-Wege-Umschaltventil mit sperrender Grundstellung und offener Schaltstellung ausgebildet. Der - bewegliche - Ventilkörper des Last- Ablassventils 68 wird zum einen durch die Vorspannung einer Ventilfeder 71 und zum anderen durch Beaufschlagung einer Steuerfläche 72 mit dem am A-Steuerausgang 61 des Funktionssteuerventils 54 herrschenden Druck pA in die sperrende Grundstellung 0 gedrängt; durch Beaufschlagung einer kleinen px-Steuerfläche des Ventilkörpers des Last-Ablassventils 68 mit dem Ausgangsdruck des Druckversorgungs-Aggregats 12 wird eine zu der Kraft der Ventilfeder 71 entgegengesetzt gerichtete Schaltkraft erzielt, die den Ventilkörper in die offene - Stellung 1 des Last-Ablassventils 68 drängt. Diejenige Steuerfläche 72, durch deren Beaufschlagung mit dem Steuerdruck pA eine das Ventil in seine Grundstellung drängende "Schließ"-Kraft erzeugt wird, ist dem Betrag nach größer als die Steuerfläche 73, die dem Ausgangsdruck px des Druckversorgungsaggregats 12 aussetzbar ist.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.

Das Eilgang-Ablaßventil 69 ist ebenfalls als druckgesteuertes 2/2-Wege-Umschaltventil mit sperrender Grundstellung 0 und durchgängiger Schaltstellung 1 ausgebildet. Der widerum durch das 2/2-Wege-Ventilsymbol repräsentierte Ventilkörper des Eilgang-Ablaßventils 69 wird zum einen durch die Vorspannung einer Ventilfeder 74 und zum anderen durch Druck-Beaufschlagung einer Steuerfläche 76 mit dem im "großen" Ringraum 19 des Hubzylinders 11 herrschenden Druck in die sperrende Grundstellung des Ventils und durch Druckbeaufschlagung einer Gegen-Fläche 77 mit dem Ausgangsdruck px des Druckversorgungsaggregats in seine Durchlass-Stellung 1 gedrängt, wobei analog zum Last-Ablassventil 68, der Betrag der mit dem Ausgangsdruck des Druckversorgungsaggregats beaufschlagbarenThe 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

Gegenfläche 77 signifikant kleiner ist als der Betrag der mit dem Druck im Ringraum 19 beaufschlagten Steuerfläche 76.Counter surface 77 is significantly smaller than the amount of the acted upon by the pressure in the annular space 19 control surface 76th

Das Hubmodul 10 ist mit einem elektromagnetischen oder elektronischen Drucksensor 78 ausgerüstet, der ein mittels der elektronischen Steuereinheit 16 auswertbares und mittelbar zur Steuerung des Hubmoduls 10 nutzbares elektrisches Ausgangssignal erzeugt, das ein Mass für den im Ringraum 19 des Hubzylinders 11 herrschenden Druck ist.
Das Hubmodul 10 ist des weiteren mit einem lediglich schematisch angedeuteten, insgesamt mit 79 bezeichneten Weg-Mess-System ausgerüstet, das für die Position des Kolbens 18 im Hubzylinder 11 charakteristische elektrische Ausgangssignale generiert, aus deren Verarbeitung die Information über den Hub gewinnbar ist, den die Last 24 im Verlauf eines Arbeitszyklus erfährt. Hierbei ist es zweckmäßig, wenn das Weg-Mess-System 79 als Absolut-Mess-System ausgebildet ist, dessen Ausgangssignale ein Maß für die Auslenkung des Kolbens 18 aus einer z. B. minimalem Volumen des Ringraumes 19 entsprechenden Grundstellung sind.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.

Abweichend von der schematisierten "Schaltbild"-Darstellung der Fig. 1 sind bei dem Hubmodul 10, wie schematisch vereinfacht in der Fig. 2 dargestellt, der Hubzylinder 11, die elektrohydraulische Steuereinheit 14 und auch das Druckversorgungsaggregat 12 zu einer kompakten Baueinheit zusammengefasst, derart, dass die elektrohydraulische Steuereinheit 14 und das Druckversorgungsaggregat 12 seitlich vom Hubzylinder 11 angeordnet sind, insbesondere derart, dass die elektrohydraulische Steuereinheit 14 und das Druckversorgungsaggregat 12 in einem an das Gehäuse 17 des Hubzylinders 11 fest anmontierten gemeinsamen Gehäuse untergebracht sind. Hierbei sind Anschlusskanäle 172 und 173, welche die als Steuerblock ausgeführte elektrohydraulische Steuereinheit 14 mit dem Hubzylinder 11 verbinden, in Richtung der zentralen Achse 22 des Hubzylinders 11 gesehen, in einem Abstand von der Außenfläche 129 des Zylinderbodens 21 angeordnet, mit der das Hubmodul 10 z. B. auf einem tragenden Fundament abstützbar ist, und es sind die die elektrohydraulische Steuereinheit 14 sowie das Druckversorgungsaggregat 12 aufnehmenden Gehäuseteile zwischen den - parallelen - Ebenen 81 und 82 geordnet, deren Abstand hmin minimaler Höhe des Hubzylinders 11 entspricht, wobei die Höhe der seitlich geordneten Gehäuseteile geringer ist als diese minimale Höhe hmin des Hubzylinders 11.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. Here are 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.

Zur Erläuterung einer typischen Art der Benutzung des Hubmoduls 10 sei davon ausgegangen, dass eine Last 24 zunächst um einen Hub Ha angehoben werden soll, z. B. zu dem Zweck, diese Last temporär tragende Stützen anordnen zu können, danach die Last 24 nocheinmal anzuheben, um die Stützen wieder entfernen zu können und sodann die Last wieder um einen definierten Betrag Hs in eine Endposition abzusenken, in der sie verbleiben kann und sodann den Kolben 18 des Hubzylinders 11 soweit abzusenken, dass das Hubmodul 10 aus dem Bereich unterhalb der abgestützen Last 24 bequem entfernt werden kann.To explain a typical way of using the Hubmoduls 10 is assumed that 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.

Solange der elektrische Antriebsmotor 15 des Druckversorgungsaggregat 12 nicht bestromt ist und demgemäß die Pumpe 13 nicht fördert und das Funktionssteuerventil 54 in seiner Grundstellung 0 gehalten ist, ist der Kolben 18 des Hubyzylinders 11 in seiner Position gleichsam hydraulisch fixiert; da die Ablassventile 68 und 69 ihre sperrende Grundstellung einnehmen und auch das Füllventil 66 sowie das Druckminderventil 64 und das Ausgangsrückschlagventil 62 der elektrohydraulischen Steuereinheit 14 durch einen etwaigen Druck im Ringraum 19 und/oder im Antriebsdruckraum 32 des Eilgangzylinders 28 in Sperr-Richtung beaufschlagte sind, kann weder aus dem Ringraum 19 noch aus diesem Antriebsdruckraum 22 Hydraulikmedium abfließen, mit der Folge, dass der Kolben 18 des Hubzylinders 11 gegen eine "Abwärts"-Bewegung im Sinne einer Verringerung des Volumens des Ringraumes 19 gesichert ist.As long as the electric drive motor 15 of the pressure supply unit 12 is not energized and accordingly does not promote the pump 13 and the function control valve 54 is held in its normal position 0, the piston 18 of the Hubyzylinders 11 is fixed in position as it were hydraulically; since the drain valves 68 and 69 occupy their locking basic position and also the filling valve 66 and the pressure reducing valve 64 and the output check valve 62 of the electro-hydraulic control unit 14 are acted upon by any pressure in the annular space 19 and / or in the drive pressure chamber 32 of the rapid traverse cylinder 28 in the blocking direction, can drain neither from the annular space 19 nor from this drive pressure chamber 22 hydraulic medium, with the result that the piston 18 of the lifting cylinder 11 is secured against a "downward" movement in the sense of reducing the volume of the annular space 19.

Wird, von diesem "Ruhe"-Zustand ausgehend, die Pumpe 13 aktiviert, so wird - in der Grundstellung des Funktionssteuerventils 54-Druckmedium in den Druckraum 32 des Eingangzylinders 28 gefördert, und Druckmedium aus dem Ringraum 33 des Eingangzylinders 28 verdrängt, mit der Folge, dass sich der Kolben 18 des Hubzylinders 11 in Richtung des Pfeils 23 bewegt. Das aus dem Ringraum 33 verdrängte Druckmedium strömt gleichsam zum Hochdruck-Versorgungsanschluß 46 der elektrohydraulischen Steuereinheit 14 zurück und wird zu dem von der Pumpe 13 zum Antriebsdruckraum 32 des Eilzylinders fließenden Druckmedium Strom hinzuaddiert. Durch die hieraus resultierende auf die Last 24 zugerichtete "Aufwärts"-Bewegung des Hubzylinderkolbens 18 vergrößert sich dessen Ringraum 19, mit der Folge, dass über das Füllventil 66 Druckmedium aus dem Vorratsbehälter 48 in diesen Ringraum 19 nachströmt. Der Kolben 18 bewegt sich, angetrieben durch den Eilgangzylinder 28 mit relativ großer Geschwindigkeit bei mäßigem Druck im Antriebsdruckraum 32 auf die Last 24 zu.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, as it were, 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. As a result of the resultant "upwards" movement of the lifting cylinder piston 18 on the load 24, its annular space 19 increases, with the result that pressure medium from the reservoir 48 flows into the annular space 19 via the filling valve 66. The piston 18, driven by the rapid traverse cylinder 28, moves toward the load 24 at a relatively high speed under moderate pressure in the driving pressure space 32.

Davon ausgehend, dass die Gewichtskraft der Last 24 signifikant größer ist als die durch Druckbeaufschlagung des Antriebsdruckraumes 32 des Eilgangzylinders 28 erzeugbare, zur Eilgang-Bewegung des Zylinderkolbens 18 erforderliche Kraft bleibt der Kolben 18, sobald er auf die Last 24 auftrifft, zunächst stehen, bis sich der Ausgangsdruck des Druckversorgungsaggregats 12 soweit erhöht hat, dass das Druckminderventil 64 anspricht und über dieses Ventil vom Hochdruckausgang 42 der elektrohydraulischen Steuereinheit 14 aus Druckmedium über den Hub-Starranschluß 37 des Hubzylinders 11 in dessen Ringraum 19 eintreten kann, in dem sich in der Folge ein Druck einstellt, der um die Druckdifferenz Δp z. B. 30 bar niedriger ist, als der im bodenseitigen Antriebsdruckraum 32 des Eilgangzylinders 28 bzw. am Hochdruckausgang 42 der elektrohydraulischen Steuereinheit 14 herrschende Druck.Assuming that the weight of the load 24 is significantly greater than the force that can be generated by pressurizing the drive pressure chamber 32 of the rapid traverse cylinder 28 for rapid traverse movement of the cylinder piston 18, the piston 18, as soon as it hits the load 24, initially stops until the output pressure of the pressure supply unit 12 has increased so far that the pressure reducing valve 64 responds and can enter via this valve from the high pressure outlet 42 of the electrohydraulic control unit 14 of pressure medium via the hub star connection 37 of the lifting cylinder 11 in the annular space 19, in which in the sequence adjusts a pressure which is the pressure difference .DELTA.p z. B. 30 bar is lower than the prevailing pressure in the bottom drive pressure chamber 32 of the rapid traverse cylinder 28 and the high pressure outlet 42 of the electro-hydraulic control unit 14.

Dieser Betriebszustand des Hubmoduls 10 ist dadurch erkennbar, dass das Druck-charakteristische Ausgangssignal des Drucksensors 78 einen stetig wachsenden Druck signalisiert, wogegen das Hub-charakteristische Ausgangssignal Weg-Messystems 79 sich nicht ändert.This operating state of the lifting module 10 can be seen that the pressure-characteristic output signal of the pressure sensor 78 is a steady Growing pressure signals, whereas the stroke-characteristic output signal path measuring system 79 does not change.

Damit in diesem "Last"-Hub-Betrieb das Eilgang-Abwärtsventil 69 nicht in seine Durchfluss-Stellung gelangen kann, ist dessen Ventilfeder 74 soweit vorgespannt, dass Sie der in Öffnungs-wirkenden Kraft, die durch die Druckbeaufschlagung der "kleinen" Steuerfläche 77 mit dem Ausgangsdruck der Pumpe 13 resultiert, überkompensiert und dadurch das Ventil 69 in seiner Sperrstellung 0 halten kann, solange der Pumpen-Ausgangsdruck auf die "kleine" Steuerfläche 77 wirkt. Mit zunehmendem Druck im Ringraum 19 bleibt das Eilgang-Ablassventil 69 zuverlässig geschlossen, da dieser Druck durch seine Wirkung auf die größere Steuerfläche 76 eine zusätzliche "Schließ"-Kraft entfaltet, die das Eilgang-Ablassventil 69 in dessen Sperrstelllung 0 hält.Thus, in this "load" stroke operation, 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. 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.

Das "Last"-Ablassventil 68 bleibt in der genannten Betriebsphase schon allein deswegen in seiner Sperr-Stellung, weil der Ausgangsdruck pA auf beide Steuerflächen 72 und 73 des Ventils wirkt und die durch die Druckbeaufschlagung der größeren Steuerfläche 72 resultierende, größere Steuerkraft das Last-Ablassventil 68 zuverlässig in dessen Sperrstellung hält, unabhängig davon, welche "Schließ"-Kraft durch seine Steuerfeder 71 entfaltet, die demgemäß auf eine dem Betrage nach kleinere Schließkraft ausgelegt sein kann als die Ventilfeder 74 des Eilgang-Ablassventils 69.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

Zur Beendigung des Last-Hub-Betriebes genügt es, die Pumpe 13 abzuschalten worauf der Kolben 18 des Hubzylinders gehen bleibt.To complete the load-stroke operation, it is sufficient to turn off the pump 13 whereupon the piston 18 of the lifting cylinder remains.

Soll nunmehr die Last 24, z. B. um einen Bruchteil des zuvor ausgeführten Last-Hubes abgesenkt werden, so wird das Funktionssteuerventil 24 durch Ansteuerung seines Steuermagneten 56 mit einem Ausgangssignal der elektronischen Steuereinheit 16 in seine Funktionsstellung I umgeschaltet, in der nunmehr der P-Versorgungsanschluß 56 gegen den Steueranschluß 61 des Funktionssteuerventils 54 abgesperrt und dieser jedoch mit dem Tank-Rücklaufanschluß 65 über den Strömungspfad 70 verbunden ist, was zur Folge hat, dass die "größere" Steuerfläche 72 des Last-Ablass-Ventils 68 druckentlastet ist und - wegen der als gering vorausgesetzten Rückstellkraft seiner Ventilfeder 71 - ein entsprechend niedriger Steuerdruck px, mit dem die Gegenfläche 73 beaufschlagt wird, genügt, um das Last-Ablass-Ventil 68 in seine Durchflussstellung I umzuschalten. Diese Umschaltung erfolgt mit dem Wiedereinschalten der Pumpe 13, so dass deren Ausgangsdruck auf die x-Steuerfläche 73 des Last-Ablassventils 64 wirkt und dieses gegen die Rückstellkraft der Ventilfeder 71 in die Durchfluss-Stellung 1 gelangt. In dieser Betriebssituation strömt Druckmedium von der Pumpe 13 über den Hochdruck-Versorgungsanschluß 46 der elektrohydraulischen Steuereinheit 14 zu dem Rückzug-Steueranschluß 44 des Eilgang-Zylinders 28 in dessen Ringraum 33, wodurch auf den Kolben 18 eine Kraft entgegen der Richtung des Pfeils 23 ausgeübt wird. Zusätzlich wirkt - entgegen der Richtung des Pfeils 23 - die Last 24 auf dem Kolben 8, wobei Druckmedium aus dem Ringraum 19 über die Drossel 67 und das in seine Offenstellung 1 gelangte Last-Ablass-Ventil 68 zum Vorratsbehälter 48 des Druckversorgungsaggregats hin abströmen kann, wobei der Volumenstrom durch die Wirkung der Drossel 67 begrenzt wird. Druckmedium, das aus dem bodenseitigen Antriebsdruckraum 32 des Eilgangzylinders 28 zum Hochdruck-Ausgang 42 der elektrohydraulischen Steuereinheit 14 hin verdrängt wird, strömt über das Druckminderventil 64 "zurück" in den Ringraum 19 des Hubzylinders 11 und von diesem über den Rücklaufanschluss 38, die Drossel 67 und das Last - Ablassventil 68 zum Vorwärtsbehälter 48.If now the load 24, z. Example, be lowered by a fraction of the previously performed load stroke, 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. This switching takes place with the pump 13 being switched on again, so that its output pressure acts on the x-control surface 73 of the load-release valve 64, and the latter comes against the restoring force of the valve spring 71 into the flow-through position 1. In this operating situation, pressure medium flows from the pump 13 via the high-pressure supply port 46 of the electro-hydraulic control unit 14 to the retraction control port 44 of the rapid traverse cylinder 28 in the annular space 33, whereby a force against the direction of the arrow 23 is exerted on the piston 18 , In addition acts - contrary to the direction of the arrow 23 - the load 24 on the piston 8, wherein pressure medium from the annular space 19 via the throttle 67 and the arrived in its open position 1 load-discharge valve 68 can flow to the reservoir 48 of the pressure supply unit out, wherein the volume flow is limited by the action of the throttle 67. 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.

Das Eilgang-Ablassventil 69 bleibt, solange die Last auf den Kolben 18 des Hubzylinders 11 wirkt und wegen der Drosselung des Ausgangsstromes ein nennenswerter Druck im Ringraum 19 des Hubzylinders 17 herrscht, gesperrt und dies solange, wie dieser Druck ausreicht, um den Kolben des Ablassventils 69 mit Unterstützung der Ventilfeder 74 gegen die Kraft, die aus der Beaufschlagung der Gegenfläche 77 mit dem Ausgangsdruck der Pumpe 13 entfaltet wird, in der Sperrstellung zu halten, was durch geeignete Auslegung des Eilgang-Ablassventils 69 aufgrund gängiger fachmännischer Maßnahmen möglich ist.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.

Hat die Last 24 ihre tiefste vorgesehene Position erreicht, z. B. durch Auflage auf einer Stützkonstruktion, so dass ein weiteres Absenken des Kolbens 18 des Hubzylinders 11 zu einem Abheben des Kolbens von der Last 24 führt, so tritt als Folge hiervon im Ringraum 19 des Hubzylinders 11 eine drastische Druckerniedrigung ein, die nunmehr dazu führt, dass das Eilgang-Ablassventil 69 in seine Durchflussstellung 1 gesteuert wird, weil der Ausgangsdruck der Pumpe jetzt bei weitem ausreicht, die zuvor durch Druckbeaufschlagung der Steuerfläche 76 generierte, gleichsinnig mit der Ventilfederkraft 74 gerichtete Schließkraft zu überwinden und das Eilgang-Ablassventil 69 in seine Offen-Stellung zu steuern, in der Druckmedium aus dem Ringraum 19 des Hubzylinders 11 gleichsam ungehindert zum Vorratsbehälter 48 hin abströmen kann; desgleichen kann aus dem bodenseitigen Antriebsdruckraum 32 des Eilgangzylinders ausströmendes Hydraulikmedium über das Rückschlagventil 63 dem Hydraulikmedium-Strom zugeführt werden, der zur Steuerung des Eil-Ablassbetriebes mittels der Pumpe 13 in den Ringraum 33 des Eilgang-Zylinders 28 geleitet wird.Has the load 24 reached its lowest intended position, z. B. by resting on a support structure, so that a further lowering of the piston 18 of the lifting cylinder 11 leads to a lifting of the piston from the load 24, so occurs as a result thereof in the annular space 19 of the lifting cylinder 11 a drastic reduction in pressure, which now leads to it in that the rapid traverse discharge valve 69 is controlled into its flow position 1 because the output pressure of the pump is now far enough to overcome the closing force previously generated by pressurizing the control surface 76 in the same direction as the valve spring force 74 and the rapid traverse discharge valve 69 into its To control the open position, in the pressure medium from the annular space 19 of the lifting cylinder 11 can flow as it were unhindered to the reservoir 48 out; Likewise, hydraulic fluid flowing out of the bottom-side drive pressure chamber 32 of the rapid traverse cylinder can be supplied via the check valve 63 to the hydraulic medium flow, which is directed by the pump 13 into the annulus 33 of the rapid traverse cylinder 28 to control the rapid purge operation.

Der in der Fig. 3, auf deren Einzelheiten nunmehr Bezug gekommen sei, dargestellte, insgesamt mit 111 bezeichnete Hubzylinder ist nach Aufbau und Funktion dem anhand der Fig. 1 erläuterten Hubzylinder 11 weitgehend analog und kann auch mit der anhand der Fig. 1 geschilderten, elektrohydraulischen Peripherie, nämlich dem Druckversorgungsaggregat 12 und der elektrohydraulischen Steuereinheit 14 zweckentsprechend betrieben werden.The Indian Fig. 3 , to the details of which reference has now been made, shown, generally designated 111 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.

Auch bei dem Hubzylinder 111 ist ein zylindrisch-topfförmiges, insgesamt mit 117 bezeichnetes, Gehäuse vorgesehen, innerhalb dessen ein dem Lastantrieb zugeordneter Kolben 118 druckdicht verschiebbar angeordnet ist und die axial bewegliche Begrenzung eines Last-Antriebsdruckraumes 119 bildet, der gehäusefest durch den Gehäuseboden 112 begrenzt ist.Also in the lifting cylinder 111 is 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.

Für den Hubzylinder 111 sei vorausgesetzt, dass der Kolben 118 auch dann, wenn er in eine "Grund"-Stellung zurückgeschoben ist, die einem minimalen Volumen des Last-Antriebsdruckraumes 119 entspricht, mit einem dem Gehäuseboden 112 abgewandten "äußeren" Stützabschnitt 118/1 über die freie, kreisringförmige Stirnfläche 121 des rohrförmigen Mantels 117/1 des Zylindergehäuses hinausragt, oder in dieser Position seine äußere freie Stirnfläche 122 allenfalls in der Ebene der freien Ringstirnfläche 121 des Gehäusemantels 117/1 verläuft.It is assumed for the lifting cylinder 111 that even when the piston 118 is pushed back into a "basic" position, which corresponds to a minimum volume of the load drive pressure chamber 119, an "outer" support section 118/1 facing away from the housing bottom 112 extends beyond the free, annular end face 121 of the tubular shell 117/1 of the cylinder housing, or in this position its outer free end face 122 at most in the plane of the free annular end face 121 of the housing shell 117/1 runs.

Der Kolben 118 hat äußerlich die Form eines Kegelstumpfes; wobei der Kegelwinkel, den eine Mantellinie der Kegelmantelfläche 123 mit der zentralen Längsachse 22/1 einschließt, vergleichsweise klein ist und einen typischen Wert zwischen 2 und 3°, z. B. einen Wert von 2,5° hat; in unmittelbarer Nähe der dem Durchmesser nach größeren "inneren" ebenen Begrenzungsfläche 124 des Kolbens 118 hat dieser eine periphere Ringnut 126 die eine insgesamt mit 127 bezeichnete Ringdichtung aufnimmt, mittels derer der Antriebskolben 118 gleitend verschiebbar in dem Gehäusemantel 117/1 abgedichtet ist.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.

Die Ringdichtungsanordnung 127 ist so gestaltet, dass sie, wenn sie in die Nut 126 eingesetzt ist, unter einer Dehnungsvorspannung steht und, wenn der Kolben 118 in das Gehäuse 117 eingesetzt ist, in radialer Richtung soweit zusammengedrückt wird, dass sowohl zwischen dem Gehäusemantel 117/1 und dem äußeren Dichtungsring 127/1 als auch zwischen dem äußeren Dichtungsring 127/1 und dem inneren Dichtungsring 127/2 und auch zwischen diesem und dem Grund 126/1 der Ringnut 126 eine gute Dichtwirkung erzielt wird und dass diese Dichtung auch erhalten bleibt, wenn der Kolben in dem Gehäuse 117 innerhalb eines durch den Kegelwinkel vorgegebenen und begrenzten Bereiches etwas gekippt wird.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.

Dieser Kipp-Freiheitsgrad ermöglicht ist, dass der Kolben 118 sich mit seiner freien Stirnfläche 122 großflächig an eine ebenflächig begrenzte Last 24 anlegen kann, wenn der Hubzylinder großflächig mit der unteren Begrenzungsfläche 129 des Gehäusebodens 112 an einem ebenflächig begrenzten Fundament als Widerlager abstützen kann, auch wenn dessen Abstützfläche nicht exakt parallel zur ebenflächigen Unterseite der Last 24 verläuft.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.

Für den in der Fig. 3 insgesamt mit 128 bezeichnete Eilgang-Zylinder, sei wieder eine Ausbildung als doppelt-wirkender-Linearzylinder vorausgesetzt, mit einseitig aus dem Gehäuse 131 austretender Kolbenstange 132, die fest mit dem Gehäuse 117 des Last-Hubzylinders 111 verbunden ist und mit einem flanschförmigen Kolben 133, der innerhalb des Eilgang-Zylindergehäuses 131 einen von der Kolbenstange 132 axial durchsetzten, stangenseitigen Ringraum 134 gegen einen topfförmig-zylindrischen Antriebsdruckraum 136 druckdicht und axial beweglich abgrenzt, der radial durch ein zylindrisch-rohrförmiges Gehäuseteil 137 und axial durch einen in das rohrförmige Gehäuseteil 137 dicht eingesetztes Bodenteil 138 abgeschlossen ist.For in the Fig. 3 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.

Der flanschförmige Kolben 133 des Eilgangzylinders 128 ist durch einen Gewindering 133/1 gebildet, der auf einen Gewindefortsatz 133/2 der Kolbenstange 132 aufgeschraubt ist, wobei durch die Verschraubung eine hinreichend dichte Verbindung zwischen dem Kolben-Gewindering 133/1 und der Kolbenstange 132 erzielt wird.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.

Gehäuseseitig ist der Kolben 133 mittels einer äußeren, kolbenfesten Ringdichtungsanordnung 139 gegen die zentrale, jeweils die gehäusefeste radiale Begrenzung der Druckräume 134 und 136 des Eilgangzylinders 128 bildende Gehäusebohrung 141 des Eilgangzylindergehäuses 131 abgedichtet.On the housing side, 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.

Zur Abdichtung des relativ zur Kolbenstange 122 gleitend verschiebbaren Zylindergehäuses 131 des Eilgang-Zylinders 128 gegenüber der Kolbenstange 132 ist eine gehäusefeste "innere" Ringdichtungsanordnung 142 vorgesehen, die innerhalb des kurzen Bohrungsabschnittes 143 der dem Bodenteil 138 gegenüber liegend angeordneten Endstirnwand 144 des Gehäuses 131 angeordnet ist, durch die die Kolbenstange 132 des Eilgang-Zylinderkolbens hindurchtritt.For sealing the relative to the piston rod 122 slidingly displaceable cylinder housing 131 of the rapid traverse cylinder 128 relative to the piston rod 132 is 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.

Das Gehäuse 131 des Eilgang-Zylinders 128 ist innerhalb des Kolbens 118 des Last-Hubzylinders 111 in einem insgesamt topfförmigen Hohlraum 146 angeordnet, der durch eine den Kolben 118 in axialer Richtung durchsetzende, insgesamt mit 147 bezeichnete Stufenbohrung und einen diese einseitig - an der der Last zugewandten Seite - verschließenden insgesamt mit 148 bezeichneten Abschlussflansch berandet ist, an dessen Innenseite 149 das Gehäuse 131 des Eilgang-Zylinders 128 mit der flach-kalottenförmig gestalteten Außenfläche des in der Art einer Plan-Konvexlinse ausgebildeten Bodenteils 138 einseitig axial abgestützt ist.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.

Desweiteren ist das Gehäuse 131 des Eilgang-Zylinders 128 - gleichsam in der Gegenrichtung - an einer inneren radialen Ringschulter 151 der den Hohlraum 146 des Antriebskolbens 118 begrenzenden Bohrungswand axial abgestützt, an der das Gehäuse 131 des Eilgangzylinders 128 mit einer radial äußeren Gehäusestufe 152 abstützbar ist.Furthermore, the housing 131 of the rapid traverse cylinder 128 - as it were in the opposite direction - axially supported on an inner radial annular shoulder 151 of the cavity 146 of the drive piston 118 limiting bore wall to which the housing 131 of the rapid traverse cylinder 128 with a radially outer housing stage 152 can be supported ,

Das Bodenteil 138 ist über einen elastischen Dichtring 153, vorzugsweise einen O-Ring, an einer schmalen, inneren Ringschulter 154 des Gehäuses 131 des Eilgangzylinders 128 abgestützt, die zwischen der Gehäusebohrung 141 und einer kurzen, inneren Bohrungs-Endstufe 156 des Zylindergehäuses 131 vermittelt, die den kurzen Endabschnitt 157 des insgesamt rohrförmigen Eilgang-Zylindergehäuses 131 durchsetzt, der das plan-konvexe Bodenteil 138 umgibt, dessen Durchmesser d/1 geringfügig kleiner ist als der Durchmesser d/2 der kurzen Bohrungsendstufe 156, so dass zwischen dieser und dem Bodenteil 138 ein kleines radiales Spiel vorhanden ist, dessen Betrag jedoch nur einen kleinen Bruchteil der radialen Breite der inneren Ringschulter 154 des Gehäuses 131 beträgt, z. B. 1/20 bis 1/10 derselben.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. which passes through the short end portion 157 of the generally tubular rapid traverse cylinder housing 131, which surrounds the plano-convex bottom portion 138, 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.

Auch der Durchmesser d/3 eines in axialer Richtung nur kurzen "scheibenförmigen" Zentriereinsatzes 158 des außenseitig gewölbten Bodenteils 138 ist um einen vergleichbare Betrag kleiner als der leichte Durchmesser d/4 der zentralen Bohrung 141 des Eilgang-Zylindergehäuses 131, so dass ein Spiel vorhanden ist, das dank der Elastizität des Dichtungsringes 153 kleine Relativbewegungen des Bodenteils 138 gegenüber dem Mantelteil 137 des Eilgangzylindergehäuses 131 ermöglicht.Also, 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.

Der Eilgang-Zylinder 128 ist in einem insgesamt topfförmigen, in radialer Richtung durch die Stufenbohrung 147 und in axialer Richtung einseitig - lastseitig - durch den Abschlussflansch 148 begrenzten Aufnahmeraum 159 angeordnet. In diesem Hohlraum ist das das gewölbte Bodenteil 138 und das rohrförmige Gehäuseteil 137 umfassende Gehäuse 131 des Eilgangzylinders 128 zwischen dem Abschlussflansch 148 des Kolbens 118 und der Ringschulter 151 der Stufenbohrung 137 gleichsam elastisch eingespannt, wobei diese Einspannung durch die elastische Kompression des Dichtungsringes 153 zustande kommt, der bei der Montage des Hubzylinders 111 in axialer Richtung etwas zusammengedrückt wird.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. In this cavity, 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.

Der Abschlussflansch 148 ist seinerseits der Grundform nach topfförmig gestaltet, derart, dass ein einseitig von einer kreisrunden Flanschplatte 148/1 aufragender, rohrförmiger Mantelabschnitt 148/2 vorgesehen ist, der radial außen von einem kreisringförmigen Fixierungsbereich 148/3 des Abschlussflansches 148 umschlossen ist, der auf einer Ringschulter 161 der Stufenbohrung 147 abstützbar ist, die zwischen der - lastseitigen - äußersten Bohrungsstufe 147/1 des - größten - Durchmessers D/1 der Stufenbohrung 147 und deren Bohrungsstufe 147/2 etwas kleineren Durchmessers D/2 vermittelt, gegenüber welcher der Abschlussflansch 148 mittels einer in eine Außennut 162 seines rohrförmigen Mantelabschnitts 148/2 eingesetzten Ringdichtung 163 abgedichtet ist.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 - lastseitigen - 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.

Zwischen dieser - zweitgrößten - Bohrungsstufe 147/2 und einer dritten, "mittleren" Bohrungsstufe 147/3 der Stufenbohrung 147 des Hubzylinderkolbens 118 vermittelt eine "mittlere" Ringschulter 164, deren radiale Breite der Wanddicke des Mantelabschnitts 148/2 des Abschlussflansches 148 entspricht, so dass, abgesehen von einem in axialer Richtung schmalen Schlitz zwischen der ringförmigen Stirnfläche des rohrförmigen Mantelabschnitts 148/2 und der dieser gegenüberliegenden Ringschulter 164 der Aufnahmeraum 159 zwischen der Innenseite 149 des Abschlussflansches 148 und der Ringschulter 151 der Stufenbohrung 141 praktisch überall denselben lichten Durchmesser D/3 hat.Between this-second largest -bore stage 147/2 and a third, "middle" bore stage 147/3 of the stepped bore 147 of the Hubzylinderkolbens 118 mediates a "middle" annular shoulder 164, whose radial width corresponds to the wall thickness of the skirt portion 148/2 of the end flange 148, so that, apart from an axially narrow slot between the annular end face of the tubular skirt portion 148/2 and the opposite annular shoulder 164 of the receiving space 159 between the inner side 149 of the Abschlussflansches 148 and the annular shoulder 151 of the stepped bore 141 practically everywhere the same clear diameter D / 3 has.

Zwischen der mittleren Bohrungsstufe 147/3 des Durchmessers D/3 und der dem Durchmesser nach kleinsten Bohrungsstufe 147/4 des Hubzylinderkolbens 118 vermittelt die radiale Ringstufe 152, an der das Zylindergehäuse 131 des Eilgangzylinders 128 in der dargestellten Konfiguration des Hubzylinders 111 axial abgestützt ist.Between the central bore 147/3 of the diameter D / 3 and the diameter of the smallest hole level 147/4 of the Hubzylinderkolbens 118 mediates the radial annular step 152 to which the cylinder housing 131 of the rapid traverse cylinder 128 is axially supported in the illustrated configuration of the lift cylinder 111.

Der Außendurchmesser D/a des durch die kleinste Bohrungsstufe 147/4 hindurchtretenden Endstirnwand - Bereiches 144 des zylindrisch rohrförmigen Gehäuseteils 137 des Eilgangzylinders 128, sowie der Außendurchmesser D/m des rohrförmigen Gehäuseteils 137 des Eilgangzylinders 128 sind, verglichen mit den Durchmessern D/4 und D/2 der sie umgebenden Bohrungswände um so viel kleiner als deren lichte Durchmesser gewählt, dass die Kippbewegungen des Hubzylinderkolbens 118 durch die Gestaltung des Eilgangzylinders 128 nicht eingeschränkt sind.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.

Der Hubzylinder 111 gemäß Fig. 3 ist wie folgt montierbar:

  • Als erstes wird die Kolbenstange 132 am Gehäuseboden 112 des Hubzylindergehäuses 117 montiert. Die Abdichtung des Antriebsdruckraumes 119 gegen die Umgebung kann hierbei durch eine außenseitig angeordnete Dichtung 166 erfolgen, an der die Köpfe 167 von Ankerschrauben 168, die relativ langgestreckte, gewindefreie, dehnfähige Spannabschnitte 169 haben, abstützbar sind.
The lifting cylinder 111 according to Fig. 3 can be mounted as follows:
  • First, the piston rod 132 is mounted on the housing bottom 112 of the Hubzylindergehäuses 117. The sealing of the drive pressure chamber 119 against the environment can in this case be effected by a seal 166 arranged on the outside, on which the heads 167 of anchor bolts 168, which have relatively elongated, unthreaded, elastic clamping sections 169, can be supported.

Hiernach wird der Kolben 118 in das Zylindergehäuse 117, bezüglich der zentralen Längsachse 22 exakt zentriert, eingesetzt. Eine geeignete Position des Kolbens 118 hierfür ist seine Abstützung an der Innenseite des Bodens 112 des Zylindergehäuses 117.After this, 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

Hiernach wird der zylindrisch-rohrförmige Gehäusemantel 137 des Eilgangzylindergehäuses 131 in den durch die Stufenbohrung 147 berandeten Innenbereich des Hubzylinders 111 eingeschoben. Sodann wird der Gewindering 133/1 auf den Gewindefortsatz 133/2 der Kolbenstange 132 aufgeschraubt, wobei der Gewindeeingriff zwischen Gewindering 133/1 und dem Gewinde des Gewindefortsatzes 133/2 eine hinreichende Dichtwirkung "innenseitig" vermittelt, während die Ringdichtung 139 den Gewindering radial außen gegen den rohrförmigen Gehäuseabschnitt 137 des Eilgangzylindergehäuses 131 abdichtet. Zum Anschrauben des Gewinderinges ist ein gabelförmiges Spezialwerkzeug erforderlich, das mit nicht dargestellten axialen Sackbohrungen des Gewinderinges in Eingriff bringbar ist.Thereafter, 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. Then, 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. For screwing the threaded ring a fork-shaped special tool is required, which can be brought into engagement with axial blind bores, not shown, of the threaded ring.

Nachdem der Gewindering 133/1 auf die Kolbenstange 132 aufgeschraubt ist, wird der Dichtring 153 auf die innere Ringschulter 154 des Eilgangzylindergehäuses 131 aufgelegt und das Bodenteil 138 in die Bohrungsendstufe 156 des zylindrisch-rohrförmigen Mantelteils 137 eingesteckt. Hiernach wird der lastseitig angeordnete Abschlussflansch 148 in die Bohrungsstufen 147/1 und 147/2 eingesetzt und mittels der axialsymmetrisch gruppierten Befestigungsschrauben 171, die sich lastseitig an dem Abschlussflansch 148 abstützen und in Ankergewinde eingreifen, die im Bereich der lastseitigen Ringschulter 161 angeordnet sind, fixiert; hierbei drängt der Abschlussflansch 148 das Bodenteil 138 des Eilgangzylindergehäuses 131 in dessen rohrförmigen Mantel 137 etwas hinein, wodurch die Ringdichtung 143 in ihre dichtende, etwas zusammengedrückte Konfiguration gelangt, in der sie unter einer Vorspannung steht, die das Bodenteil 138 und das Mantelteil 137 des Eilgang-Zylindergehäuses am Abschlussflansch 148, einerseits, und an der Ringschulter 151 des Hubzylinderkolbens 118, andererseits, mit einer Mindestkraft in Anlage hält.After the threaded ring 133/1 is screwed onto the piston rod 132, 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. Thereafter, 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; In this case, 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.

Den Steuerkanälen 39 und 43 gemäß Fig. 1 entsprechende Steuerkanäle 39/2 und 43/2, über die Druckmedium in die Druckräume 136 bzw. 134 des Eilgangzylinders 128 gemäß Fig. 3 einströmen oder aus diesen austreten kann, sind beim Ausführungsbeispiel gemäß Figur 3 an Anschlusskanäle 172 bzw. 173 dicht angeschlossen, die im Gehäuseboden 112 verlaufen und zu dem jeweiligen Steuerdruckanschluss 41 und dem Rücklaufsteueranschluss 44 der elektrohydraulischen Steuereinheit 14 führen.The 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.

Diese Steueranschlüsse 44 und 41 sind oberhalb der Unterseite 129 des Gehäusebodens 112 "seitlich" vom Hubzylindergehäuse 117 angeordnet. Auf analoge Weise ist auch ein dem Hub-Steueranschluss 37 und dem Rücklaufsteueranschluß 38 entsprechender Steueranschluss "seitlich angeordnet und ggf. mit einem - nicht dargestellten - ebenfalls im Gehäuseboden 112 verlaufenden Anschlusskanal mit dem Antriebsdruckraum 119 des Hubzylinders 111 kommunizierend verbunden.These control terminals 44 and 41 are above the bottom 129 of the housing bottom 112 "laterally" arranged by Hubzylindergehäuse 117. In an analogous manner, 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.

Claims (12)

  1. Lifting system for the raising and lowering and/or displacement of large loads, with a number of individually activatable hydraulic lifting cylinders (11), of which a plurality can be activated simultaneously and which each have a piston (18) which forms a one-sided movable boundary of a drive-pressure space (19), by the action of pressure upon which the piston (18) can be displaced in relation to the housing (17) and the cylinder (11) in order to execute a working stroke, and upon the relief of pressure of which the piston (18) can be displaced into a basic position in the opposite direction with the effect of executing a return movement, each lifting cylinder (11) being equipped with a path sensor (79) which generates output signals which can be evaluated in units of the piston stroke, characterized by the following features:
    a) each lifting cylinder (11) is equipped with a specific pressure supply assembly (12) and with a specific electrohydraulic lift control unit (14);
    b) the lifting cylinder (11), the pressure supply assembly (12), including its reservoir (48), and the electrohydraulic control unit (14) are constructed as a compact lifting module (10), the functional control of which takes place solely by means of electrical control signals;
    c) the pressure supply assembly (12), which comprises a high-pressure pump (13), an electric motor (15) driving the latter, a pressure-limiting valve (52) and the reservoir (48), and the electrohydraulic control unit (14) are designed as a subassembly which is mounted laterally on the lifting-cylinder housing (17) and of which the extent, measured in the direction of the central longitudinal axis (22) of the lifting cylinder (f), is smaller than the minimum height (hmin), measured between the supporting planes (81 and 82) of the lifting cylinder, of said lifting cylinder.
  2. Lifting system according to Claim 1, characterized in that the lifting cylinder (11; 111) of the respective lifting module (10) is equipped with a hydraulic rapid-motoring drive (17, 18; 117, 118), by means of which the piston (18; 118) of the lifting cylinder can be moved with low advancing force, but relatively quickly, into the initial position which is required for triggering the load stroke and from which the implementation of the load-stroke pressure of the lifting cylinder commences, in which the advance drive by the lifting cylinder (11; 111) takes place by the action of pressure upon its drive-pressure space (19; 119), the speed of advance in load-advancing operation being reduced significantly, as compared with the rapid-motion speed, with the advancing force being increased correspondingly.
  3. Lifting system according to Claim 2, characterized in that the rapid-motion drive is designed as a hydraulic rapid-motion cylinder integrated into the lifting cylinder (11) (Fig. 1).
  4. Lifting system according to Claim 3, characterized in that the rapid-motion cylinder (28) is designed as a double-acting hydraulic cylinder.
  5. Lifting system according to Claim 4, characterized in that the rapid-motion cylinder (28) has a flange-shaped piston (31) which is firmly connected by means of a piston rod (29) to the bottom (21) of a pot-shaped housing (17) of the lifting cylinder (11) and, within a cylindrical inner space of the piston (18) of the lifting cylinder (11), delimits a cylindrical drive-pressure space (31) such that the latter is sealed off, pressure-tight, with respect to an annular space (33) through which the piston rod (29) passes axially and which is itself sealed off slidably with respect to the drive-pressure space (19) of the lifting cylinder (11) by means of a directional seal arranged fixedly in terms of displacement on the drive piston (18) and surrounding the piston rod.
  6. Lifting system according to Claim 4, characterized in that the rapid-motion cylinder (128) has a piston (133), firmly connected to the housing of the lifting cylinder, and a housing element (137) which is movable in relation to said piston and which is anchored, resistant to tensile and shearing strength, between stop elements (148 and 152) of the piston (118) of the lifting cylinder (111).
  7. Lifting system according to Claim 6, characterized in that
    a) the rapid-motion cylinder (128) has a cylindrically tubular housing casing, the outside diameter D/1 of which is smaller than the diameter D/2 of a central bore step (147/3), radially delimiting a cylindrically pot-shaped inner space (146) of the lifting cylinder (111), of the lifting-cylinder piston (118), that is however larger than the diameter D/4 of a bore end step (147/4) which adjoins the central bore portion (147/3) of diameter D/2 via a radial annular step (152) on which the housing part (137) can be supported axially, in that
    b) the stepped bore of the lifting-cylinder piston is closed off on the load side by means of a closing-off flange (148), on the inside of which the movable housing part (137) of the rapid-motion cylinder is supported, essentially in a punctiform manner, by means of a bottom part which is configured on the outside in the form of a spherical cap and which forms the load-side boundary of the control-pressure space (136) of the rapid-motion cylinder (128), and in that
    c) the piston of the lifting-cylinder is arranged movably in its housing in such a way that its central axis can assume, within a small range of variation, an orientation which deviates from the central longitudinal axis (22) of the housing (117) of the lifting cylinder.
  8. Lifting system according to Claim 7, characterized in that the piston (118) of the lifting cylinder (111) is in the form of a cone frustum with a small cone angle (amounting to between 2° and 3°), this piston having, in the immediate vicinity of the planar base surface (124) of larger diameter, a peripheral annular groove (126) into which is inserted an annular seal (127), by means of which the drive piston is sealed off, within its tilting range possible with respect to the central longitudinal axis (22) of the housing, in a slidably displaceable manner with respect to the housing (117).
  9. Lifting system according to one of Claims 1 to 8, characterized in that the high-pressure pump (13) of the pressure supply assembly (12) is designed as a piston pump, of which the feed volume per revolution of the drive motor (15) has a defined value.
  10. Lifting system according to one of Claims 1 to 9, characterized in that the pump (13) and/or the electric drive motor (15) of the respective pressure supply assembly (12) is equipped with a cycle counter which generates an electric output signal evaluatable only in an electronic control unit (16) of the lifting system and characteristic of the number of executed motor revolutions or feed strokes of the pump (13).
  11. Lifting system according to one of Claims 1 to 10, characterized in that an electronic or electromechanical pressure sensor (78) is provided, which generates an electrical output signal which is characteristic of the pressure in the drive-pressure space (19) of the lifting cylinder (11) and which is delivered to the electronic control unit (16) of the lifting system (10) as an information input signal.
  12. Lifting system according to one of Claims 1 to 11, characterized in that a pressure sensor is provided, which generates an electrical output signal which is characteristic of the outlet pressure pA of the pump (13) of the respective pressure supply assembly (12) and which is delivered to the electronic control unit (16) of the lifting system (10) as an information input signal.
EP04803767A 2003-12-30 2004-12-11 Lift system used to lift and lower and/or displace heavy loads Not-in-force EP1699727B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10361807A DE10361807A1 (en) 2003-12-30 2003-12-30 Lifting system for lifting and lowering and / or moving large loads
PCT/EP2004/014126 WO2005066062A1 (en) 2003-12-30 2004-12-11 Lift system used to lift and lower and/or displace heavy loads

Publications (2)

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

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ID=34706710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04803767A Not-in-force EP1699727B1 (en) 2003-12-30 2004-12-11 Lift system used to lift and lower and/or displace heavy loads

Country Status (4)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069384A1 (en) * 2022-09-27 2024-04-04 Automa By Magic S.R.L. Device for moving moulds and associated method

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Publication number Priority date Publication date Assignee Title
DE202009004608U1 (en) * 2009-04-03 2010-08-12 Khd Humboldt Wedag Gmbh Hydraulic flat cylinder with swiveling piston and return device
DE102010015115A1 (en) * 2010-04-16 2011-10-20 Georg Kramp Gmbh & Co. Kg Mobile lifter with electro-hydraulic drive
CN103318799A (en) * 2012-03-23 2013-09-25 程曼华 Short mechanical interlocking type hydraulic jack
DE102013103458A1 (en) * 2013-04-08 2014-10-09 Peri Gmbh Formwork system for the production of a concrete floor
CN103925257B (en) * 2014-04-08 2017-01-04 奇瑞汽车股份有限公司 Jacking system
CN104879344B (en) * 2015-05-21 2017-02-01 黄杰 Dustproof jacking device
CN114319382B (en) * 2022-01-07 2023-09-05 上海巨鲲科技有限公司 Foundation Pit Steel Support Hydraulic Axial Force Box
CN114920162B (en) * 2022-05-24 2023-06-13 柳州欧维姆机械股份有限公司 Jack nest-preventing cylinder protection method

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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 (en) * 2001-11-02 2003-05-02 Roberto Maggiori SELF-LEVELING INTEGRATED LIFTING DEVICE.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024069384A1 (en) * 2022-09-27 2024-04-04 Automa By Magic S.R.L. Device for moving moulds and associated method

Also Published As

Publication number Publication date
DE10361807A1 (en) 2005-07-28
WO2005066062A1 (en) 2005-07-21
DE502004009163D1 (en) 2009-04-23
EP1699727A1 (en) 2006-09-13
ATE425117T1 (en) 2009-03-15

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