EP1272420B1 - Commande de treuil hydraulique - Google Patents

Commande de treuil hydraulique Download PDF

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Publication number
EP1272420B1
EP1272420B1 EP01913517A EP01913517A EP1272420B1 EP 1272420 B1 EP1272420 B1 EP 1272420B1 EP 01913517 A EP01913517 A EP 01913517A EP 01913517 A EP01913517 A EP 01913517A EP 1272420 B1 EP1272420 B1 EP 1272420B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
winch
connection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01913517A
Other languages
German (de)
English (en)
Other versions
EP1272420A1 (fr
Inventor
Karlheinz Hunschede
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1272420A1 publication Critical patent/EP1272420A1/fr
Application granted granted Critical
Publication of EP1272420B1 publication Critical patent/EP1272420B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/48—Control devices automatic
    • B66D1/50—Control devices automatic for maintaining predetermined rope, cable, or chain tension, e.g. in ropes or cables for towing craft, in chains for anchors; Warping or mooring winch-cable tension 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3138—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/329—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—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
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/50—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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a hydraulic winch control according to the preamble of claim 1.
  • winch controls are used to use a winch, hoist, and mooring winch.
  • a winch control is known from data sheet RD 65/050 / 03.96 from the applicant, in which the winch is driven by an adjustable hydraulic motor.
  • the winch is preferably driven by an adjustable hydraulic motor.
  • the flow paths of a pressure medium between a pressure medium source, the hydraulic motor and a pressure medium reservoir are controlled with a pilot-controlled, proportionally adjustable and spring-centered directional control valve in a central position.
  • a pilot control device with an arbitrarily actuable control lever is used, which can be deflected from a neutral position for differently fasting over a certain fiering angle range in one direction and for differently fast heaving over a certain hoisting angle range in the opposite direction.
  • the directional control valve is opened further and further when the control lever is deflected, so that the amount of pressure medium flowing to the hydraulic motor increases further and further.
  • the swallowing volume of the hydraulic motor is reduced. It is conceivable the opening cross-section of the directional valve and the absorption volume of the hydraulic motor to change in parallel.
  • the prior art provides that only the hydraulically piloted directional control valve is adjusted up to a pilot pressure of, for example, 18 bar and only the adjustable hydraulic motor in the range of a pilot pressure of, for example, 20 to 30 bar.
  • the hawser In the mooring operation, the hawser should be kept under a predefinable tension. This tension can be adjusted by the absorption volume of the hydraulic motor.
  • the control lever of the pilot control device In the prior art, the control lever of the pilot control device is deflected from a neutral position against the force of a return spring for hoisting operation of the winch in one direction and for hoisting operation of the winch in the other direction.
  • a parking brake is provided in the known hydraulic control arrangement for the control lever, which brakes the control lever within the range of the angular angle against the Holds force of the return spring in a position corresponding to a certain absorption volume of the hydraulic motor.
  • the quantity to be set namely the speed of the hawser
  • the size to be set is the torque exerted by the hydraulic motor. This becomes smaller with increasing deflection angle of the control lever, a behavior that contradicts the usual ideas of setting a size via a control lever and can therefore lead to incorrect settings.
  • Another disadvantage of the known hydraulic control is that heave operation and mooring operation do not differentiate based on the position of the control lever.
  • the speed at which the hawser is brought in is limited to a small value.
  • this is done by a nozzle arranged in a bypass line to the directional control valve and a control valve which can be switched to a mooring position when the control lever changes from the heave angle range to the mooring angle range, in which the nozzle in order to limit the speed of the hydraulic motor to small values in via the hydraulic motor leading flow path of the pressure medium.
  • Such a limitation of the speed of the hydraulic motor is particularly advantageous for the direction of rotation in which the hawser is wound up.
  • the winding takes place only at a limited speed, so that the loose rope does not get wild in the area and endangers people.
  • the directional control valve is brought into its neutral position in the mooring operating state and bypassed via the bypass line, the nozzle limiting the pressure medium flow to the hydraulic motor.
  • the speed is set up to about 50% of the maximum adjustable control pressure via the directional control valve, while in the range from 50% to the maximum adjustable control pressure, the speed setting of the adjustment motor is carried out by changing the swivel angle.
  • the invention has for its object to provide a winch control in which a simple Setting the torque in the mooring operating state with minimal circuitry effort is required.
  • the hydraulic winch control is carried out in such a way that the directional control valve for controlling the pressure medium flow between the pressure medium source and the adjusting motor can be subjected to a predetermined pressure difference in the mooring operating state, via which the directional control valve is only partially deflected.
  • the pressure medium flow to the servomotor is limited by partial deflection of the directional control valve, the control pressure being selected so that the torque can be adjusted by changing the pivoting angle of the servomotor.
  • the pressure medium flow is therefore limited solely by suitable control of the directional control valve, so that the bypass line with a nozzle for limiting the pressure medium flow can be dispensed with.
  • the winch control can thus be carried out much more easily than in the described prior art.
  • the directional valve is hydraulically adjusted to its intermediate position.
  • the directional control valve is designed with two control rooms, which can be acted upon with a predetermined control pressure difference. This control pressure difference is chosen so that the directional valve is brought into the predetermined intermediate position.
  • the construction of the winch control is particularly simple if the control pressures are tapped from a control channel that carries the control pressure that is used to adjust the swivel angle.
  • a control line then branches off from this control channel to each control chamber, a valve arrangement being provided in a control line in order to set the predetermined control pressure difference.
  • This valve arrangement can be, for example, a pressure reducing valve or a hydraulic potentiometer circuit.
  • a hydraulic potentiometer circuit an inlet nozzle and a flow valve are connected in series in a control line, the second control line branching off between the two elements.
  • the flow valve can be designed, for example, as a discharge nozzle, the opening of which is preferably designed with a larger diameter than that of the supply nozzle.
  • a disadvantage of using a drain nozzle is that the control pressure difference changes with the pressure medium stream flowing out via the drain nozzle. This deficiency can be remedied by using a flow regulator instead of the drain nozzle. Such a flow controller keeps the pressure medium volume flow flowing out to the tank constant, so that the control pressure difference in the two control rooms of the directional control valve is also constant.
  • pilot control device Similar to the solution described in DE 199 13 275.5, the control valve and the valve device interacting with the control lever are combined in one pilot control device.
  • This pilot control device also has an adjustable pilot valve with a pilot pressure connection which is connected to the various control valves via the control valve actuated by the deflection of the control lever Pilot chambers of the directional valve can be connected.
  • a pilot control device with a pilot valve, the pilot pressure connection of which can be connected via a control valve to one or the other pilot chamber of a proportionally adjustable directional valve has the advantage that the behavior of the pilot control regardless of the direction in which the control lever is deflected from its neutral position, is not influenced in different ways by tolerances in the pilot valve.
  • the pilot valve is actuated in the same way when the control lever is deflected from the neutral position regardless of the direction depending on the angle, the pilot pressures are the same even with the same deflection angle.
  • the pilot valve is set, the pilot pressures in both deflection directions are influenced in the same way.
  • a metering orifice of the proportionally adjustable directional control valve is assigned a pressure compensator, which maintains a fixed pressure difference across the metering orifice.
  • a check valve which opens in the direction of the inflow of pressure medium from the pressure medium source to the hydraulic motor.
  • a pressure relief valve which is arranged between the two connections of the hydraulic motor and by means of which the pressure at the connection of the hydraulic motor which is pressurized in mooring operation is limited to a maximum value.
  • a hydraulically ventilable mechanical brake which can be supplied with pressure medium from the directional control valve or from the control valve via a shuttle valve.
  • FIG. 1 shows a winch 10 which can be driven in opposite directions via a gear 11 by an adjustable hydraulic motor 12.
  • a brake 13 is arranged between the output shaft of the hydraulic motor and the transmission and can be actuated via a single-acting hydraulic cylinder 14.
  • the hydraulic cylinder 14 is constructed in the manner of a differential cylinder, the piston and piston rod of which can be displaced by a spring in the sense of an engagement of the brake. By applying pressure medium to the annular space 15 of the hydraulic cylinder 14, the piston and the piston rod are moved back against the force of the spring and the brake 13 is thereby released.
  • the absorption volume of the hydraulic motor 12 can be adjusted continuously as a function of a control pressure applied to the control input 16 and is smaller the greater the control pressure.
  • a positioning cylinder 17 designed as a differential cylinder and a pump control valve 18 are provided for the adjustment.
  • This has a tank connection, which is connected to a leak oil line 19, a pressure connection, which is connected via two check valves 20 to the motor connection 21 or 22, and a cylinder connection connected to the piston rod-side pressure chamber of the actuating cylinder 17.
  • the pressure chamber of the actuating cylinder 17 on the piston rod side is connected to the pressure connection of the pump control valve 18.
  • the piston valve of the pump control valve 18 is acted upon by the control pressure in the sense of a connection of the cylinder connection to the pressure connection and by a first compression spring set to a fixed value and a second compression spring in the sense of a connection of the cylinder connection, the pretensioning of which depends on the position of the piston and the piston rod of the actuating cylinder 17 changes.
  • Piston and piston rod of the actuating cylinder 17 each take such a position that the force generated by the applied control pressure and the force generated by the springs is balanced on the piston of the pump control valve 18. In this way, a certain absorption volume of the hydraulic motor 12 can be set by the control pressure.
  • the source of the pressure medium that is supplied to the hydraulic motor 12 is a variable displacement pump 25, which sucks in hydraulic oil from a tank 26 and delivers it into an inlet line 27.
  • the variable displacement pump 25 is provided with a pressure regulator 28, that is, when the pressure set on the pressure regulator 28 is reached in the inlet line 27, swings back to a stroke volume which is sufficient to maintain the set pressure in the inlet line 27.
  • a pressure relief valve 29 is connected to the inlet line 27.
  • the maximum stroke volume of the variable displacement pump is designed so that it has not yet been swung out to the stop, even if, taking into account the simultaneous actuation of several hydraulic consumers, the maximum amount of pressure medium is requested.
  • the speed at which the hydraulic motor 12 rotates and the direction of rotation can be controlled with a proportionally adjustable directional valve 35.
  • This is spring centered in a central position and can be operated hydraulically. It has a total of six connections, namely an inlet connection 36 to which pressure medium can flow from the inlet line 27 via a pressure compensator 37, an outlet connection 38 which is connected directly to a tank line 39, and a second outlet connection 40 which is connected to the tank line via a brake valve 41 39 is connected, a first consumer connection 42, which is connected to the motor connection 21 via a consumer line 43, a second consumer connection 44, which is connected to the motor connection 22 via a consumer line 45 is and a brake port 46 through which the annular space 15 of the hydraulic cylinder 14 can be acted upon with pressure medium.
  • the directional control valve 35 In the spring-centered central position of the directional control valve 35, its connections 36, 40 and 44 are shut off.
  • the connections 42 and 46 are connected to the connection 38 and thus to the tank 26.
  • the consumer connection 42 and the brake connection 46 are connected to the inlet connection 36 via a metering orifice 48, the opening cross-section of which depends on the degree of displacement of the valve piston.
  • the consumer connection 44 is connected to the discharge connection 40 via an outlet throttle 49.
  • valve piston of the directional control valve 35 moves from the central position to a different extent into a second working position, in which the consumer connection 42 is connected to the drain connection 38 without restriction.
  • the brake connection and the other consumer connection 44 are connected together via the metering orifice 48 to the inlet connection 36.
  • the drain port 40 is shut off.
  • the maximum displacement of the valve piston in the two opposite directions is limited by adjustable stops 51.
  • the pressure compensator 37 is arranged according to the connections described between the various connections of the directional control valve 35 in its two working positions upstream of the metering orifice 48.
  • the control piston of the pressure compensator 37 is in the direction of closing of the pressure upstream of the metering orifice and in the direction of opening one Compression spring 52 and acted upon by a pressure which is applied via a control line 53 which is connected to the brake connection of the directional control valve and thus in each case to the consumer connection 42 or 44 of the directional control valve 35 lying in the flow to the hydraulic motor 12.
  • the pressure is therefore in each case equal to the pressure downstream of the metering orifice 48.
  • the pressure compensator 37 regulates a specific pressure difference, which is equivalent to the force of the spring 52, via the metering orifice 48.
  • the amount of pressure medium flowing through the metering orifice 48 thus only depends on the opening cross section of the metering orifice and is independent of the load pressure and the pump pressure.
  • the regulating piston of the brake valve 41 is acted upon in the opening direction by the pressure present at the consumer connection 42 of the directional control valve 35 and thus also in the consumer line 43 and at the motor connection 21, and in the closing direction by the force of a compression spring 54 and by a pilot pressure applied via a control line 55 which is constant in the range of eg 40 bar.
  • the two pressures act on surfaces of the same size, so that the brake valve 41 throttles the flow of pressure medium from the hydraulic motor 12 via the consumer line 45 when the load is being pulled together with the throttle 49 in such a way that a pressure is built up in the consumer line 43
  • Control piston of the brake valve generates a force that maintains the balance of the force of the compression spring 54 and the force generated by the pilot pressure.
  • the speed of the hydraulic motor 12 is thus determined even by a pulling load through the opening cross section of the metering orifice 48.
  • the pressure at the brake port 46 of the directional control valve 35 is so high, even with a pulling load, that the brake 13 remains released.
  • a pressure relief valve 60 is arranged, which on a Pressure is set which is 10-20 bar above the pressure regulated by the variable pump 25, but below the set pressure of the pressure relief valve 29.
  • the directional control valve 35, the pressure compensator 37, the brake valve 41 and the pressure relief valve 60 are accommodated in a valve plate 61.
  • a pilot control device 65 is built onto this, into which a shut-off pressure line 66 leads, which flows upstream of the pressure compensator 37 from the feed line 27.
  • the pilot control device 65 contains two pressure reducing valves 68 and 69, a control valve 70, a check valve 71, various shuttle valves 67, 72, 73, 74 and 75, two damping nozzles 76, two relief nozzles 77 and different channels for connecting the valves to one another.
  • the check valve 71 is located in the bypass line 66 and blocks the supply line 27. Downstream of the check valve 71, the pressure reducing valve 68 is connected with its pressure connection to the pressure line 66. A relief connection of the pressure reducing valve 68 is connected to a leakage channel 78.
  • the pressure reducing valve 68 is set to a fixed value and regulates, for example, the already mentioned pressure of 40 bar at its control output and in a pilot pressure supply channel 79, to which the control line 55 leading to the brake valve 41 is also connected.
  • the second pressure reducing valve 69 which is connected with its pressure connection to the channel 79, with its relief connection to the channel 78 and with its control output to a pilot pressure channel 80, can be adjusted from a neutral position by pivoting a control lever 81.
  • the pivot axis of the control lever 81 is designated 82.
  • a control disk 83 is fastened to the control lever with a control cam, against which an actuating tappet 84 of the pressure reducing valve 69 rests.
  • the control curve is like this designed that when the control lever is pivoted from the neutral position, the pressure reducing valve 69 is initially adjusted in the same way regardless of the pivoting direction. Namely, the pilot pressure in channel 80 increases continuously, if not necessarily everywhere with the same slope, from a swivel angle of approximately 8 degrees to a swivel angle of 45 degrees.
  • the pivot angle of the control lever 81 is limited to approximately 50 degrees. In this direction, the control lever for pivoting, that is, for unrolling the hawser from the winch 10, is pivoted.
  • the control lever is pivoted in the other direction for lifting purposes, that is when the hawser is to be rolled up onto the winch 10.
  • the control lever 81 returns to its neutral position both when pivoting in the direction of Fieren and when pivoting in the direction of Hieven due to a reset device acting on it when it is released. In the direction of heaving, the control lever can, however, be pivoted up to a pivoting angle of approximately 100 degrees, whereby when pivoting beyond approximately 54 degrees it remains in the position it then assumed, even when it is released. In this area the winch 10 is operated in the mooring.
  • the three angular ranges fiering, heaving and mooring are indicated by hatching in FIG. 1 and provided with the reference numbers 85 for fiering, 86 for heaving and 87 for mooring.
  • the control disk 83 is designed such that the pressure in the channel 80 in the mooring angle region 87 decreases with increasing pivoting angle of the control lever 81.
  • the control valve 70 is mechanically operated by the control lever 81. Its movable valve element is shown schematically in FIG. 2 and is preferably designed as a rotary slide whose axis of rotation coincides with the axis 82 of the control lever 81. There can be a total of four assume functionally distinguishable switching positions and has 6 connections, of which a connection 89 is connected downstream of the check valve 71 to the pressure line.
  • the pilot pressure channel 80 leads to a connection 90.
  • a connection 91 is connected to the leakage channel 78.
  • the three remaining connections 92, 93 and 94 each lead to a first input of a shuttle valve 72 or 73 or 74.
  • the second input of the shuttle valve 74 is connected to the brake port 46 of the directional control valve 35.
  • a line 95 leads from the outlet of this shuttle valve to the annular space 15 of the hydraulic cylinder 14.
  • the second input of each of the two shuttle valves 72 and 73 is each connected to an external connection 99, which in the present case is closed, but offers the possibility of using a second pilot control device for the winch to control, which is remote from the block consisting of the plate 61 and the pilot device 65.
  • the line between the connection 46 of the directional control valve 35 and the shuttle valve 74 is necessary since the annular space 15 of the hydraulic cylinder 14 can then be pressurized via this line.
  • a control line 96 leads to the control chamber 50 via a damping nozzle 76, and from the outlet of the shuttle valve 73 also via a damping nozzle 76 to the control chamber 47 of the directional control valve 35.
  • the shuttle valve 75 is located at the outlet of the shuttle valve 72 and with its other input at the outlet of the shuttle valve 73. Its outlet is connected via a line 100 to an inlet of the shuttle valve 67. Its other input is connected via a connecting line 102 to the control output of the pressure reducing valve 68.
  • a further pressure reducing valve 103 is provided in the connecting line 102, via which the pressure is reduced to approximately 18-20 bar.
  • the output port of the shuttle valve 67 is connected to the pressure port P of a switching valve 104, which in the spring-biased basic position is connected via a working port A to a control line 98, which is led to the control input 16 of the hydraulic motor 12.
  • a second working connection B is connected in the basic position via a tank connection T to a return line 105 which opens into the leakage channel 78.
  • the switching valve 104 can be brought into its second switching position, in which the control line 98 is connected to the tank connection, so that the control input 16 is relieved and the adjusting motor 12 is pivoted back into its basic position with a maximum pivoting angle.
  • control valve 70 In the neutral position of the control lever 81, the control valve 70 assumes a position in which the connections 89 and 90 are shut off and the other connections are connected to the tank channel 78. Control lines 95, 96, 97 and 98 are relieved of pressure to channel 78. The directional control valve 35 is thus in its central position.
  • the hydraulic motor 12 has a maximum absorption volume.
  • the brake 13 has gripped.
  • the control lever for gearing is now adjusted in the angular range 85.
  • the control valve 70 reaches a switch position (a) in which the connections 89 and 94, the connections 90 and 93 and the connections 91 and 92 are each connected to one another.
  • the control chamber 47 of the directional control valve 35 is acted upon by a control pressure via the connections 90 and 93 as well as the shuttle valve 73 and the control line 97.
  • This control pressure is also at the control input via the shuttle valve 75, the line 100, the shuttle valve 67 and the switching valve 104 16 of the hydraulic motor 12.
  • the control chamber 50 of the directional control valve 35 is relieved of pressure via the control line 96, the shuttle valve 72 and the connections 91 and 92 of the control valve 70 or via a relief nozzle 77.
  • the directional control valve 35 is thus brought into a position in which the inlet connection 36 is connected to the consumer connection 42 and to the brake connection 46 via the metering orifice 48.
  • a pressure builds up in the consumer line 43 and in the feed line 27, which is also present in the annular space 15 of the hydraulic cylinder 14 via the shuttle valve 74 and is finally sufficient to release the brake.
  • Pressure medium conveyed by the hydraulic pump 25 can now flow via the feed line 27, the pressure compensator 37, the directional control valve 35 and the consumer line 43 to the hydraulic motor 12 and from there via the consumer line 45 the throttle opening 49 of the directional control valve 35 and via the brake valve 41 to the tank 26.
  • the hawser is unwound from the winch 10.
  • the brake valve 41 ensures that the outflow of pressure medium from the hydraulic motor 12 to the tank can only be throttled, so that a certain pressure is maintained in the consumer line 43. This is sufficient to keep the brake 13 released.
  • the speed at which the hawser is unwound is determined solely by the control pressure dependent on the deflection of the control lever 81.
  • the speed of the winch 10 is influenced in two ways. Only the directional control valve 35 is adjusted up to a deflection angle of 25 degrees, but not the hydraulic motor 12. This remains at maximum swallowing volume and maximum torque.
  • the torque is indicated in Figure 1 by the radial expansion of the fields 85, 86 and 87.
  • the directional control valve 35 is fully open. With a further deflection of the control lever 81, the absorption volume of the hydraulic motor 12 becomes reduced, which increases its speed, but reduces its torque. This is indicated by the decreasing radial extension of the field 85 in FIG. 1.
  • control lever 81 If, starting from the neutral position shown, the control lever 81 is pivoted into the auxiliary angle range 86, the control valve 70 reaches a position (b) in which the connections 89 and 94 are in turn connected to one another. However, terminal 90 is now connected to terminal 92 and terminal 91 to terminal 93. Thus, the control chamber 47 is relieved of pressure and the control chamber 50 of the directional control valve 35 is acted upon by a pilot pressure dependent on the deflection angle of the control lever 81. This is also available at the control input 16 of the hydraulic motor 12.
  • the directional control valve 35 reaches its second working position, in which pressure medium delivered by the variable displacement pump 25 can flow to the hydraulic motor 12 via the feed line 27, the pressure compensator 37, the connections 36 and 44 with the metering orifice 48 in between and the consumer line 45.
  • the discharge of the pressure medium from the hydraulic motor 12 takes place via the consumer line 43 and the connections 42 and 38 of the directional control valve 35 to the tank 26.
  • a load-dependent pressure builds up, which is sufficient to release the brake 13 , The hawser is now wound onto the winch 10.
  • control lever 81 If the control lever 81 is pivoted further into the mooring angle region 87, the control valve 70 reaches a switching position (c) in which the connection 94 is connected to the connection 89.
  • valve member of the control valve 70 can be designed, for example, as a rotary slide valve or in some other suitable manner.
  • the switching symbol of the control valve 70 is shown enlarged in Figure 2.
  • the connection 89 is connected to the connection 94, so that pressure medium is supplied via the pressure line 66, the shuttle valve 74 and the line 95 in the annular space 15 of the hydraulic cylinder 14 is guided and the brake intervention is released.
  • the control curve 83 of the control lever 81 is selected such that a control pressure is set in the mooring swivel position of the control lever 81 which corresponds to more than 50% of the maximum adjustable control pressure. That is, the control pressure is in a range in which the swivel angle of the hydraulic motor 12 is reduced to increase the speed.
  • the directional control valve 35 is acted upon with a control pressure difference via a hydraulic potentiometer circuit implemented by the control valve 70, by means of which the valve slide of the directional control valve 35 is displaced into an intermediate position.
  • the pressure medium is brought to the desired control pressure by means of the pivoting of the control lever 81 via the two pressure reducing valves 68, 69 and is present via the pilot pressure channel 80 at the connection 90 of the directional control valve 70 indicated in FIGS. 2 and 3.
  • the pilot pressure channel 80 branches into a first control line 106 and a second control line 107, which lead to the connections 92 and 93, which are only indicated, and from there to the control spaces 47 and 50 of the directional control valve 35.
  • In the first control line 106 an inlet nozzle 108 is provided in the first control line 106 .
  • a tank duct 109 branches off downstream of the inlet nozzle 108 and leads to the connection 92.
  • the control pressure in the control chamber 47 can be reduced by a predetermined pressure difference compared to the control pressure in the control chamber 50, so that the valve spool of the directional control valve 35 is partially deflected in the mooring area.
  • the two nozzles 108 and 110 are selected such that the pressure medium flow to the motor input 22 is limited to a comparatively low value.
  • the diameter of the outlet nozzle 110 is preferably larger than that of the inlet nozzle 108, a size ratio of 0.8 to 0.6, for example, having proven successful.
  • the higher control pressure present at port 92 is conducted via the shuttle valves 72, 75, 74 and the switching valve 104 to the control input 16 of the hydraulic motor 12, so that the swivel angle is changed accordingly.
  • the structure described above makes it possible to control a small amount of pressure medium via the directional control valve 35 with very little circuitry, so that reliable control of the adjusting motor 12 is ensured.
  • a hydraulic winch control in which an adjusting motor for driving the winch is supplied with pressure medium via a directional valve.
  • the directional control valve is activated via a control valve that is operatively connected to a control lever.
  • the directional control valve can be subjected to a predetermined control pressure difference, so that the pressure medium flow to the adjustment motor is reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Jib Cranes (AREA)

Abstract

La présente invention concerne une commande de treuil hydraulique qui comprend un moteur (12) à cylindrée variable permettant d"entraîner ledit treuil (10) au moyen d"un agent de pression, par l"intermédiaire d"un distributeur (35). Ledit distributeur est commandé par l"intermédiaire d"une soupape de commande (70) qui est en liaison active avec un levier de réglage (81). Dans un état de fonctionnement d"amarrage, ledit distributeur peut être soumis à une différence de pression de commande prédéfinie, de façon à réduire le flux de pression circulant jusqu"au moteur à cylindrée variable.

Claims (14)

  1. Commande de treuil hydraulique comportant une soupape de distribution (35) à réglage proportionnel pour commander la liaison hydraulique entre un moteur hydraulique réglable (12) et une source de fluide sous pression (25) ou un réservoir (26), la soupape de distribution (35) pouvant être chargée par l'intermédiaire d'une soupape de commande (70) avec une pression de commande, qui est réglable par l'intermédiaire d'un levier de réglage (80) servant à régler un état de fonctionnement de halage, de filage d'amarre ou d'amarrage, caractérisée en ce que dans l'état de fonctionnement d'amarrage, la soupape de distribution (35) peut être partiellement déviée dans une position intermédiaire.
  2. Commande de treuil selon la revendication 1, dans laquelle la soupape de distribution (35) comporte deux chambres de commande (47,50), qui, dans l'état de fonctionnement d'amarrage, peuvent être chargées par une différence de pression de commande prédéterminée.
  3. Commande de treuil selon la revendication 2, comportant deux canalisations de commande (106,107) aboutissant aux chambres de commande (47,50), un dispositif à soupape (108,110;112) servant à régler la différence de pression de commande étant prévu dans une canalisation de commande (106).
  4. Commande de treuil selon la revendication 3, dans laquelle le dispositif à soupape est une soupape de détente de pression.
  5. Commande de treuil selon la revendication 3, dans laquelle le dispositif à soupape est un circuit potentiométrique hydraulique comportant une buse d'admission (108) et une soupape de régulation d'écoulement (110,112), et que la seconde canalisation de commande (107) se ramifie entre la buse d'amenée (108) et la soupape d'écoulement (110,112).
  6. Commande de treuil selon la revendication 5, dans laquelle la soupape de régulation d'écoulement est une buse d'évacuation (110).
  7. Commande de treuil selon la revendication 5, dans laquelle la soupape de régulation d'écoulement est un régulateur de quantité (112).
  8. Commande de treuil selon l'une des revendications 5 à 7, selon laquelle le dispositif à soupape est intégré dans la soupape de commande (110).
  9. Commande de treuil selon l'une des revendications 3 à 8, dans laquelle le levier de commande (80) et la soupape de commande (110) font partie d'un appareil de commande pilote (65), qui comprend par ailleurs une soupape pilote réglable (69) comportant un raccord de pression de commande pilote (80), qui peut être relié à au moins l'une des chambres de commande pilotes (47,50) au moyen de l'actionnement du levier de commande (81).
  10. Commande de treuil selon la revendication 9, dans laquelle en série avec un diaphragme de mesure (48) ouvert proportionnellement lors d'un réglage de la soupape de distribution (35) à partir de la position médiane, est disposée une balance de pression (35), qui maintient la différence de pression fixe par l'intermédiaire du diaphragme de mesure (48).
  11. Commande de treuil selon la revendication 9 ou 10, comportant une soupape antiretour (71), qui est disposée dans la canalisation de pression (66) et s'ouvre dans la direction du flux arrivant de fluide sous pression provenant de la source de fluide sous pression (25) d'un moteur hydraulique (12), et comportant une soupape de limitation de pression (60), au moyen de laquelle la pression au niveau du raccord (22), chargé par une pression lors du fonctionnement au démarrage, du moteur hydraulique (12) est limitée à une valeur maximale.
  12. Commande de treuil selon la revendication 8, dans laquelle le raccord de pression d'une soupape de détente de la pression (68) est raccordé, sur le côté amont de le dispositif à soupape (108, 110; 112), à la canalisation de pression (66), et la soupape antiretour (71) est disposée entre le raccord de pression et la source (25) de fluide sous pression.
  13. Commande de treuil selon la revendication 12, dans laquelle la sortie de régulation de la soupape de réduction de pression (68) est reliée à une entrée d'une soupape à deux voies (67), dont l'autre entrée est chargée par la pression de commande réglée au moyen de la soupape de commande (70), et dont la sortie est reliée à l'entrée de commande (16) du moteur hydraulique (12) par l'intermédiaire d'une soupape de commutation actionnée manuellement (104).
  14. Commande de treuil selon l'une des revendications précédentes, dans laquelle un frein mécanique, pouvant être aéré par voie hydraulique, est associé au treuil (10).
EP01913517A 2000-03-27 2001-01-18 Commande de treuil hydraulique Expired - Lifetime EP1272420B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10014811A DE10014811A1 (de) 2000-03-27 2000-03-27 Hydraulische Windensteuerung
DE10014811 2000-03-27
PCT/DE2001/000207 WO2001072625A1 (fr) 2000-03-27 2001-01-18 Commande de treuil hydraulique

Publications (2)

Publication Number Publication Date
EP1272420A1 EP1272420A1 (fr) 2003-01-08
EP1272420B1 true EP1272420B1 (fr) 2004-03-31

Family

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EP01913517A Expired - Lifetime EP1272420B1 (fr) 2000-03-27 2001-01-18 Commande de treuil hydraulique

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Country Link
EP (1) EP1272420B1 (fr)
DE (2) DE10014811A1 (fr)
NO (1) NO20024556L (fr)
WO (1) WO2001072625A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3067309A1 (fr) * 2015-03-10 2016-09-14 HAWE Hydraulik SE Soupape de commande de groupe hydraulique et système hydraulique doté d'une soupape de commande correspondante

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6676921B2 (en) 2001-05-11 2004-01-13 Rohm And Haas Company Method for preparation of lithium aluminum hydride from sodium aluminum hydride

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Publication number Priority date Publication date Assignee Title
JPH01226697A (ja) * 1988-03-03 1989-09-11 Kobe Steel Ltd 建設機械における操作レバーの操作反力制御装置
DE19913275A1 (de) * 1999-03-24 2000-09-28 Mannesmann Rexroth Ag Hydraulische Steueranordnung zum Betreiben einer Winde im Fieren-, Hieven- und Mooring-Betrieb

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3067309A1 (fr) * 2015-03-10 2016-09-14 HAWE Hydraulik SE Soupape de commande de groupe hydraulique et système hydraulique doté d'une soupape de commande correspondante

Also Published As

Publication number Publication date
EP1272420A1 (fr) 2003-01-08
NO20024556D0 (no) 2002-09-23
WO2001072625A1 (fr) 2001-10-04
DE10014811A1 (de) 2001-10-11
NO20024556L (no) 2002-09-23
DE50101851D1 (de) 2004-05-06

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