EP0225877A1 - Articulation plastique flexible pour cable porteur d'engins de levage - Google Patents

Articulation plastique flexible pour cable porteur d'engins de levage

Info

Publication number
EP0225877A1
EP0225877A1 EP19850904108 EP85904108A EP0225877A1 EP 0225877 A1 EP0225877 A1 EP 0225877A1 EP 19850904108 EP19850904108 EP 19850904108 EP 85904108 A EP85904108 A EP 85904108A EP 0225877 A1 EP0225877 A1 EP 0225877A1
Authority
EP
European Patent Office
Prior art keywords
joint according
hydraulic
gas pressure
load
pressure accumulator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19850904108
Other languages
German (de)
English (en)
Inventor
Norbert Walther
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.)
Phb Weserhuette AG
Original Assignee
Phb Weserhuette 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 Phb Weserhuette AG filed Critical Phb Weserhuette AG
Publication of EP0225877A1 publication Critical patent/EP0225877A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/02—Devices for facilitating retrieval of floating objects, e.g. for recovering crafts from water

Definitions

  • Plastic-elastic sliding joint that can be inserted into the load rope of hoists
  • the invention relates to a plastic-elastic sliding joint that can be placed in the load rope of hoists.
  • Rope grinders for example, are proposed for realizing a passive follow-up system for the main hoist of offshore cranes. There are also suggestions for a springy platform on the ship deck. Other suggestions concern active follow-up systems. With the active footprint sequence, the load on the crane hook should be moved in the vertical direction like the footprint. Small superimposed lifting and lowering speeds should enable bump-free lifting and lowering of loads. Examples include the rope loop of the boom pusher, the hydraulic linear motor on the load hook or the complete additional hoist on the load hook. To achieve the active footprint, lifting speeds must be reached under nominal load, which are in the order of the vertical ship speeds. All proposed solutions based on such high lifting speeds on the main hook cannot be implemented for safety and economic reasons. l
  • the invention has for its object in one
  • the plastic-elastic sliding joint which can be inserted into the load rope of lifting devices for low-impact lifting and lowering of loads without slack rope formation with a relative movement between the hoist boom and the footprint has a plastic-elastic retarding on ⁇ contains direction, which releases a certain length of rope when loaded under limited force, which is overtaken when relieved under yielding force, ie without slack rope formation.
  • the joint is preferably inserted between the lower block and the hook of the load rope of the hoist, but can also be inserted between the jib tip and the upper block of the load rope.
  • the hinge is designed so that it is known, e.g. can be easily inserted and secured by simply attaching it and can therefore be easily dismantled.
  • the elastically decelerating device preferably contains a hydraulic cylinder and a hydraulic piston including piston rod, the one-sided hydraulic medium space of which is connected to an attached gas pressure accumulator via at least one pressure relief valve.
  • This gas pressure spoke can be formed by the annular space existing between the hydraulic cylinder and an outer jacket coaxial therewith, or by a plurality of individual stores arranged predominantly around the hydraulic cylinder.
  • the hydraulic pressure accumulator in the connected gas pressure accumulator is limited while maintaining an overflow of hydraulic medium Force a certain length of rope, i.e. a limited way open.
  • the pressure relief valve has a first bypass line with a check valve which closes in its opening direction.
  • the gas pressure in the accumulator is dimensioned so that the hydraulic piston is reset via the check valve when the load is lowered under a tensioned rope; it is so high that the dead weight, the lifting gear between the joint and the load can be lifted and slack rope formation can be avoided at any time.
  • the extendable Hochstweglos is according to the estimated double amplitude of the vertical footprint movement, e.g. measured on a ship at sea.
  • the maximum speed of the hydraulic piston is determined in compliance with predetermined force limit values according to the relative speed between the bottom block and the surface, e.g. on the ship.
  • a line from the hydraulic medium space to the gas pressure accumulator can be released without a pressure limiting stage. This is done by hydraulically relieving the pressure relief valve via a directional control valve or by hydraulically unlocking the check valve via a directional control valve or via a main flow directional control valve, via which a further bypass line without pressure relief valve is released.
  • follow-up operation ie when following the vertical movement of a load on the floor, hanging on the rope without slack rope formation, a free flow without pressure limitation stage from the hydraulic medium chamber to the gas pressure accumulator and in is achieved via the hydraulic devices mentioned , reverse direction allows.
  • the joint thus acts like a very soft spring, the force of which is determined by the pressure in the gas reservoir. The crane operator always gives the selection signal for limitation or subsequent operation.
  • the switch from follow-up to limit operation takes place when the footprint increases.
  • the switching signal does not have to occur at a precise point in time, but over a certain period of time, since subsequent operation and limiting operation do not differ when the relative path between the bottom block and the load decreases. If the load is lifted, e.g. in rough seas, raised again by a later wave crest, this leads to an impact between the floor space and the load as well as to a relief of the crane, 5 but not to the dangerous impact impact of the crane when the ship's deck subsequently descends, since the load rope is via gas pressure accumulator and check valve is kept under tension and at the high point of the footprint there is again a smooth transfer of the load to the crane.
  • the load rope When the load is lowered, the load rope is switched from limiting operation to subsequent operation after the load rope has been relieved.
  • the signal does not have to be given at an exact point in time, but over the time span of the relief 5 (slack rope).
  • the dangerous blast of speed on the crane which would occur if the load rope suddenly descended when the footprint descends, becomes an uncritical power surge with the small follow-up force determined by the gas storage pressure.
  • Fig. 3 the Aufnähmevorgang and 4 shows the settling process with a joint according to the invention
  • FIG. 5 shows the joint according to the invention in longitudinal section and FIG. 5a in cross section;
  • Fig. 7a, b, c three ways of hydraulic connection of the joint according to the invention.
  • the elastic joint that can be inserted into the load rope of lifting devices consists of a hydraulic cylinder 2, which is connected by a e.g. with the bottom block connected cylinder head 5 and a cylinder base 4 is closed at the end; these parts can be clamped together by anchors, not shown.
  • a hydraulic fluid e.g. Oil-filled space 10 delimited by a hydraulic piston 6, which has a cylindrical extension 7 for end position damping and one that extends through the cylinder base, e.g. piston rod 1 connected to the load hook.
  • the piston On the side opposite the hydraulic fluid space, the piston carries a stop consisting of disc springs 8, which interacts with the end face of the cylinder head.
  • a coaxial outer casing 3a forms, together with the hydraulic cylinder 2, an annular space 11 which serves as a gas pressure accumulator; it is connected to the hydraulic fluid chamber 10 via bores 18 and 19 and pressure relief valves 9.
  • the gas pressure accumulator 11 is formed by a plurality of individual cylinders 3b arranged around the hydraulic cylinder 2. If a closed system is required, a further gas reservoir can be connected on the piston side to ventilate the cylinder.
  • the pressure relief valve 9 has a bypass line 17 with a check valve 12 which closes in its opening device.
  • the pressure relief valve is connected to the hydraulic medium space either directly (FIGS. 7a and 7b) or via a two-way valve 15 (FIG. 7 ⁇ ), which in the position shown opens this way.
  • Switching control flow two-way valves 13, 14 in outputs 20 or 20a or a main flow directional valve 15 in a line 18 in a passage enables in all three cases a free flow of the main flow without pressure limitation from the hydraulic medium space of the Sliding joint to the gas pressure accumulator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
  • Eye Examination Apparatus (AREA)
  • Replacement Of Web Rolls (AREA)
  • Forklifts And Lifting Vehicles (AREA)

Abstract

Une articulation plastique flexible pour câbles porteurs d'engins de levage permet de lever et de poser des charges sans heurts et sans relâchement du câble lors d'un mouvement vertical relatif entre la console de l'engin de levage et la surface de dépôt. L'articulation a la forme d'un dispositif plastique flexible à retardement qui libère une certaine longueur de câble lorsqu'il est soumis à une pression limitée; cette longueur de câble, lorsque la pression diminue, est reprise sans qu'il y ait relâchement du câble. Le dispositif comprend un cylindre hydraulique et un piston hydraulique, comprenant une tige de piston, dont l'espace intermédiaire unilatéral est connecté à un accumulateur annexe de pression de gaz par au moins un limiteur de pression et des alésages.
EP19850904108 1984-08-16 1985-08-13 Articulation plastique flexible pour cable porteur d'engins de levage Withdrawn EP0225877A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3430085 1984-08-16
DE19843430085 DE3430085A1 (de) 1984-08-16 1984-08-16 In das lastseil von hebezeugen einsetzbares plastisch-elastisches verschiebegelenk

Publications (1)

Publication Number Publication Date
EP0225877A1 true EP0225877A1 (fr) 1987-06-24

Family

ID=6243150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850904108 Withdrawn EP0225877A1 (fr) 1984-08-16 1985-08-13 Articulation plastique flexible pour cable porteur d'engins de levage

Country Status (4)

Country Link
EP (1) EP0225877A1 (fr)
DE (1) DE3430085A1 (fr)
NO (1) NO861477L (fr)
WO (1) WO1986001187A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3546277A1 (de) * 1985-12-28 1987-07-02 Bomag Menck Gmbh Kompensatorvorrichtung
GB2501282A (en) * 2012-04-18 2013-10-23 Helix Energy Solutions U K Ltd Emergency auxiliary lifting apparatus for use with winches on ships

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE624057C (de) * 1932-10-18 1936-01-11 Werke Kiel Akt Ges Deutsche Vorrichtung zum Anheben von Flugzeugen aus dem Wasser
US3309065A (en) * 1965-08-24 1967-03-14 Rucker Co Transloader
NL6712911A (fr) * 1967-09-21 1969-03-25
US3512657A (en) * 1967-09-21 1970-05-19 Hydranautics Motion takeup device
US3871527A (en) * 1973-04-04 1975-03-18 Westinghouse Electric Corp Ram tensioning device
US3937163A (en) * 1975-01-31 1976-02-10 Rosenberg Edgar N Launch and recovery vessel
FR2353478A1 (fr) * 1976-06-03 1977-12-30 Bretagne Atel Chantiers Dispositif de manutention de charges, notamment entre supports flottant en pleine mer
FR2401868A1 (fr) * 1977-08-31 1979-03-30 Bretagne Atel Chantiers Procede et dispositif d'enlevement et de depose de charges entre deux supports animes de mouvements relatifs verticaux repetes
US4354608A (en) * 1979-06-08 1982-10-19 Continental Emsco Company Motion compensator and control system for crane

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8601187A1 *

Also Published As

Publication number Publication date
WO1986001187A1 (fr) 1986-02-27
NO861477L (no) 1986-04-16
DE3430085A1 (de) 1986-02-27

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Legal Events

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Inventor name: WALTHER, NORBERT