EP2636633B1 - Hydraulic system and crane - Google Patents

Hydraulic system and crane Download PDF

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Publication number
EP2636633B1
EP2636633B1 EP12008080.9A EP12008080A EP2636633B1 EP 2636633 B1 EP2636633 B1 EP 2636633B1 EP 12008080 A EP12008080 A EP 12008080A EP 2636633 B1 EP2636633 B1 EP 2636633B1
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EP
European Patent Office
Prior art keywords
hydraulic
pressure
hydraulic circuit
crane
crane according
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.)
Active
Application number
EP12008080.9A
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German (de)
French (fr)
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EP2636633A1 (en
Inventor
Christof Gassner
Markus Schwarzhans
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Liebherr Werk Nenzing GmbH
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Liebherr Werk Nenzing GmbH
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Publication of EP2636633A1 publication Critical patent/EP2636633A1/en
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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
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B66C13/10—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack for preventing cable slack
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B27/00—Arrangement of ship-based loading or unloading equipment for cargo or passengers
    • B63B27/08—Arrangement of ship-based loading or unloading equipment for cargo or passengers of winches
    • 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
    • B66D1/52—Control devices automatic for varying rope or cable tension, e.g. when recovering craft from water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/008—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors with rotary output
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20569—Type of pump capable of working as pump and 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/763—Control of torque of the output member by means of a variable capacity motor, i.e. by a secondary control on the 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a hydraulic system for a crane with at least one hydraulic circuit comprising at least one hydraulic consumer, and a constant pressure network.
  • a corresponding feed pressure is required.
  • a hydraulic pump generates the appropriate feed pressure by sucking hydraulic fluid from the tank and provides at its output the feed pressure for operation of the hydraulic consumer.
  • Such an application is in the operation of a Seegangs say adopted, also referred to as Active Heave Compensation before.
  • the load should be held steady during the lifting work, despite the swell of the deep-sea hoist.
  • the compensation device is intervened for this purpose in the control of the hoist winch.
  • US 2005/179021 A discloses a crane according to the preamble of claim 1.
  • Such a pressure reducer expediently comprises at least one input and at least one output, it being possible to vary the pressure and / or volumetric flow present at the respective connection points by means of the pressure reducer.
  • a low volume flow at high pressure within the constant pressure network can be converted into a high volume flow at low pressure within the hydraulic circuit.
  • the use of a feed pump can be dispensed with, since the required high volume flow in the hydraulic circuit is only available through the pressure reducer.
  • the pressure reducer comprises at least two interconnected pistons with a suitable ratio of the piston surfaces.
  • the piston with a small piston surface is coupled to the constant pressure network, whereas the large piston surface of the second piston is in communication with the hydraulic circuit.
  • a power output to the constant pressure network is made possible. For example, if a volume flow is generated at the input of the pressure reducer on the side of the hydraulic circuit, the piston unit shifts in the direction of the constant pressure network and generates on this side a low volume flow with a high pressure level.
  • a reversal of the volume flow in the hydraulic circuit is made possible, for example, by storing part of the volume flow or pressure during normal operation.
  • at least one pressure accumulator can be arranged in the hydraulic circuit. If the memory stores the stored pressure energy, then the volume flow in the hydraulic circuit is reversed so that this pressure energy is released back to the constant pressure network via the pressure reducer.
  • At least one pressure storage medium may preferably be a fluid storage medium, gas storage medium or a storage medium for other media. If the storage form does not correspond to the hydraulic fluid used, a pressure medium converter can preferably be integrated in front of the storage.
  • the storage means is designed as an air pressure accumulator and the pressure energy of the hydraulic fluid can be converted by means of the pressure medium converter in the corresponding air pressure level.
  • a hydraulic consumer is suitably a hydraulic motor in question, which is preferably operable in both flow directions. This can be the Operating the hydraulic motor in a first direction of rotation by the volume flow generated via the pressure reducer and in an opposite direction of rotation via the stored energy of the storage means.
  • the present invention can be by means of at least one hydraulic circuit or the hydraulic motor, a crane winch, in particular a Tiefseehubseilwinde drive.
  • the hydraulic motor is operated to implement an Active Heave Compensation, which has the compensation of the sea state to the task.
  • the hydraulic fluid can be pushed back and forth between it and, if appropriate, an arranged memory, which is used in particular in the active-heave compensation mode or similar cyclic operating modes.
  • the tank circulation can be significantly reduced.
  • the system is characterized by a particularly efficient energy recovery.
  • the crane can have a Weghubseilwinde, which is supplied by a hydraulic drive.
  • a closed hydraulic circuit with at least one hydraulic motor serves to set the hoist winch in rotation for carrying out a take-off or winding-up movement.
  • the crane may comprise a constant pressure network which can be supplied by a central hydraulic pump and is used to supply one or more hydraulic consumers, in particular various crane components.
  • the integrated hydraulic motor may preferably be part of a Seegangs merge Kunststoff.
  • the winch is here driven separately by the hydraulic motor to compensate for the sea state during the actual lifting work can.
  • FIGS. 1 . 2 show an embodiment of the hydraulic system according to the invention for operating an offshore crane.
  • the crane or hydraulic system is designed especially for deep-sea lifting.
  • a Seegangs merge reinforce is installed.
  • the construction of the in the FIGS. 1 . 2 shown hydraulic system comprises a constant pressure network 2 with a relatively high pressure level.
  • the hydraulic pump 1 is provided which sucks hydraulic oil from the tank and brings it to the corresponding pressure level of the constant pressure network 2.
  • FIG. 2 additionally drawn two hydraulic consumers 13 in the form of a hydraulic motor and a hydraulic cylinder, which are each fed via the hydraulic pump 1 with the pressure level of the constant pressure network 2.
  • Both consumers 13 should only be representative of a possible construction of the constant pressure network 2.
  • any number of identical or different hydraulic components can be arranged in the constant pressure network 2 or be in connection therewith.
  • the crane further comprises a drive motor 11 with euinem gear 12.
  • a drive motor 11 with euinem gear 12 In addition to the hydraulic pump 1 for feeding the constant pressure network 2 also sits the pump motor unit 9 of the closed circuit on the drive shaft 12th
  • the winch 7 is mainly by the closed circuit, d. H. the hydraulic motor 8 driven both in the up and in the unwinding to perform the required lifting work.
  • a sea-gear sequencing device which is known in principle is provided, which is intended to compensate for the swell of the sea via additional control of the winch 7.
  • the hydraulic circuit 4 To implement the Seegangs Grande Surprise, which is also referred to as Active Heave Compensation, is the hydraulic circuit 4. This includes a operable in both directions of flow hydraulic motor 5, whose torque also drives the winch 7 in both directions. At the same time the engine 5 is designed as an adjustment.
  • the pressure reducer 3 consists of two pistons, which have a common piston rod with deviating piston surfaces on the rod end faces.
  • the smaller area of the piston is connected to the constant pressure network 2, whereas the relatively large piston area of the second cylinder communicates with the hydraulic circuit 4.
  • the selected area ratio of the two piston surfaces causes the small volume flow of high pressure from the constant pressure network 2 is converted into a high volume flow at low pressure within the hydraulic circuit 4.
  • the pressure reducer 3 takes over the hydraulic oil feed, which prevents dry running of the system.
  • the pressure reducer 3 is in communication with an input of the hydraulic motor 5.
  • a storage means 15 is connected via a directional control valve 10 and a pressure medium converter 6, via which the lifting work is done.
  • a pressure limiting valve 17 is additionally arranged, which releases excess hydraulic oil to the tank when a certain limit pressure level is reached.
  • an additional hydraulic pump 18 may be provided in the hydraulic circuit 4 in order to ensure a certain pressure level or a certain flow.
  • the hydraulic pump 18 is seated on a common drive shaft with the adjustable motor 12 of the constant pressure network 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control And Safety Of Cranes (AREA)

Description

Die Erfindung betrifft ein Hydrauliksystem für einen Kran mit wenigstens einem Hydraulikkreislauf, der wenigstens einen hydraulischen Verbraucher umfasst, und einem Konstantdrucknetz.The invention relates to a hydraulic system for a crane with at least one hydraulic circuit comprising at least one hydraulic consumer, and a constant pressure network.

Zum Betrieb des Hydraulikkreislaufs bzw. des hydraulischen Verbrauchers ist ein entsprechender Einspeisedruck erforderlich. In der Regel erzeugt eine Hydraulikpumpe den passenden Einspeisdruck, indem sie Hydraulikfluid aus dem Tank ansaugt und an ihrem Ausgang den Speisedruck zum Betrieb des hydraulischen Verbrauchers bereitstellt.To operate the hydraulic circuit or the hydraulic consumer, a corresponding feed pressure is required. In general, a hydraulic pump generates the appropriate feed pressure by sucking hydraulic fluid from the tank and provides at its output the feed pressure for operation of the hydraulic consumer.

Je nach Anwendungsfall ist für den Betrieb des hydraulischen Verbrauchers ein bestimmtes Druckniveau bzw. ein definierter Volumenstrom erforderlich.Depending on the application, a certain pressure level or a defined volume flow is required for the operation of the hydraulic consumer.

Ein solcher Anwendungsfall liegt beim Betrieb einer Seegangsfolgeeinrichtung, auch als Active Heave Compensation bezeichnet, vor. Hier soll die Last während der Hubarbeit trotz Seegangs beim Tiefseehub ruhig gehalten wertden. Mittels der Kompensationseinrichtung wird hierzu in die Ansteuerung der Hubwinde eingegriffen.Such an application is in the operation of a Seegangsfolgeeinrichtung, also referred to as Active Heave Compensation before. Here, the load should be held steady during the lifting work, despite the swell of the deep-sea hoist. By means of the compensation device is intervened for this purpose in the control of the hoist winch.

US 2005/179021 A offenbart einen Kran gemäß dem Oberbegriff des Anspruchs 1. US 2005/179021 A discloses a crane according to the preamble of claim 1.

Die Aufgabe der vorliegenden Erfindung setzt sich zum Ziel, ein derartiges Kran mit einem Hydrauliksystem weiterzuentwickeln, um die Energiebilanz des Systems durch gezielte Maßnahmen zu optimieren.The object of the present invention is to further develop such a crane with a hydraulic system to optimize the energy balance of the system through targeted measures.

Diese Aufgabe wird durch ein Kran mit einem Hydrauliksystem gemäß den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Ausführungen des Krans sind Gegenstand der abhängigen Ansprüche 2 bis 7.This object is achieved by a crane with a hydraulic system according to the features of claim 1. Advantageous embodiments of the crane are the subject of the dependent claims 2 to 7.

Gemäß Anspruch 1 wird ein Kran mit einem Hydrauliksystem mit wenigstens einem Hydraulikkreislauf und einem Konstantdrucknetz vorgeschlagen. Wenigstens ein Hydraulikkreislauf weist einen hydraulischen Verbraucher auf. Zur Optimierung der Energiebilanz des gesamten Systems ist erfindungsgemäß vorgesehen, dass der erforderliche Einspeisedruck für den hydraulischen Verbraucher nicht durch eine Einspeispumpe erzeugt wird, sondern statt dessen der wenigstens eine Hydraulikkreislauf über wenigstens einen Druckuntersetzer mit dem Konstantdrucknetz gekoppelt ist.According to claim 1, a crane is proposed with a hydraulic system with at least one hydraulic circuit and a constant pressure network. At least one hydraulic circuit has a hydraulic consumer. To optimize the energy balance of the entire system is provided according to the invention that the required feed pressure for the hydraulic consumer is not generated by a feed pump, but instead is coupled at least one hydraulic circuit via at least one pressure reducer to the constant pressure network.

Ein derartiger Druckuntersetzer umfasst zweckmäßig wenigstens einen Eingang sowie wenigstens einen Ausgang, wobei mittels des Druckuntersetzers der an den jeweiligen Anschlussstellen anliegende Druck und/oder Volumenstrom variierbar ist.Such a pressure reducer expediently comprises at least one input and at least one output, it being possible to vary the pressure and / or volumetric flow present at the respective connection points by means of the pressure reducer.

Mittels des Druckuntersetzers kann ein geringer Volumenstrom mit hohem Druck innerhalb des Konstantdrucknetzes in einen hohen Volumenstrom mit niederem Druck innerhalb des Hydraulikkreislaufs wandelbar sein. Damit kann auf den Einsatz einer Einspeisepumpe verzichtet werden, da der erforderliche hohe Volumenstrom im Hydraulikkreislauf ausschließlich durch den Druckuntersetzer lieferbar ist. Diese erfindungsgemäße Maßnahme ist insbesondere dort von Vorteil, wo ein Konstantdrucknetz ohnehin installiert ist und der Einsatz des Druckuntersetzers die Integration einer zusätzlichen Pumpe überflüssig macht.By means of the pressure reducer, a low volume flow at high pressure within the constant pressure network can be converted into a high volume flow at low pressure within the hydraulic circuit. Thus, the use of a feed pump can be dispensed with, since the required high volume flow in the hydraulic circuit is only available through the pressure reducer. This measure according to the invention is particularly advantageous where a Konstantdrucknetz is installed anyway and the use of the pressure reducer makes the integration of an additional pump superfluous.

In einer vorteilhaften Ausführung umfasst der Druckuntersetzer wenigstens zwei zusammengeschaltete Kolben mit einem geeigneten Verhältnis der Kolbenflächen. Insbesondere ist der Kolben mit kleiner Kolbenfläche an das Konstantdrucknetz gekoppelt, wohingegen die große Kolbenfläche des zweiten Kolbens mit dem Hydraulikkreislauf in Verbindung steht. Durch geeignete Wahl des Flächenverhältnisses kann gezielt auf das Umwandlungsverhältnis und den zu erzielenden Volumenstrom eingegangen werden.In an advantageous embodiment, the pressure reducer comprises at least two interconnected pistons with a suitable ratio of the piston surfaces. In particular, the piston with a small piston surface is coupled to the constant pressure network, whereas the large piston surface of the second piston is in communication with the hydraulic circuit. By suitable choice of the area ratio can be addressed specifically to the conversion ratio and the volume flow to be achieved.

Weiterhin kann vorgesehen sein, dass bei Umkehrung der Strömungsrichtung im Hydraulikkreislauf mittels des Druckuntersetzers eine Leistungsabgabe an das Konstantdrucknetz ermöglicht wird. Wird beispielsweise am Eingang des Druckuntersetzers auf der Seite des Hydraulikkreislauf ein Volumenstrom erzeugt, so verschiebt sich die Kolbeneinheit in Richtung des Konstantdrucknetzes und erzeugt auf dieser Seite einen niedrigen Volumenstrom mit hohem Druckniveau.Furthermore, it can be provided that upon reversal of the flow direction in the hydraulic circuit by means of the pressure reducer, a power output to the constant pressure network is made possible. For example, if a volume flow is generated at the input of the pressure reducer on the side of the hydraulic circuit, the piston unit shifts in the direction of the constant pressure network and generates on this side a low volume flow with a high pressure level.

Eine Umkehrung des Volumenstroms im Hydraulikkreislauf wird beispielsweise dadurch ermöglicht, dass ein Teil des Volumenstroms bzw. Drucks im Normalbetrieb gespeichert wird. Hierzu kann wenigstens ein Druckspeicher im Hydraulikkreislauf angeordnet sein. Gibt der Speicher die gespeicherte Druckenergie ab, so kehrt sich der Volumenstrom im Hydraulikkreislauf um, so dass diese Druckenergie über den Druckuntersetzer zurück an das Konstantdrucknetz abgebar ist.A reversal of the volume flow in the hydraulic circuit is made possible, for example, by storing part of the volume flow or pressure during normal operation. For this purpose, at least one pressure accumulator can be arranged in the hydraulic circuit. If the memory stores the stored pressure energy, then the volume flow in the hydraulic circuit is reversed so that this pressure energy is released back to the constant pressure network via the pressure reducer.

Wenigstens ein Druckspeichermittel kann vorzugsweise ein Fluidspeichermittel, Gasspeichermittel oder ein Speichermittel für sonstige Medien sein. Entspricht die Speicherform nicht dem verwendeten Hydraulikfluid, so kann vorzugsweise vor dem Speicher ein Druckmittelwandler eingebunden sein. Beispielsweise ist das Speichermittel als Luftdruckspeicher ausgeführt und die Druckenergie des Hydraulikfluids ist mittels des Druckmittelwandlers in das entsprechende Luftdruckniveau wandelbar.At least one pressure storage medium may preferably be a fluid storage medium, gas storage medium or a storage medium for other media. If the storage form does not correspond to the hydraulic fluid used, a pressure medium converter can preferably be integrated in front of the storage. For example, the storage means is designed as an air pressure accumulator and the pressure energy of the hydraulic fluid can be converted by means of the pressure medium converter in the corresponding air pressure level.

Als hydraulischer Verbraucher kommt zweckmäßig ein Hydromotor in Frage, der vorzugsweise in beiden Strömungsrichtungen betreibbar ist. Damit lässt sich der Hydromotor in einer ersten Drehrichtung durch den über dem Druckuntersetzer erzeugten Volumenstrom betreiben und in einer entgegengesetzten Drehrichtung über die gespeicherte Energie des Speichermittels.As a hydraulic consumer is suitably a hydraulic motor in question, which is preferably operable in both flow directions. This can be the Operating the hydraulic motor in a first direction of rotation by the volume flow generated via the pressure reducer and in an opposite direction of rotation via the stored energy of the storage means.

In einer besonders bevorzugten Ausführung der vorliegenden Erfindung lässt sich mittels des wenigstens einen Hydraulikkreislaufs bzw. des Hydromotors eine Kranseilwinde, insbesondere eine Tiefseehubseilwinde, antreiben. Vorzugsweise wird der Hydromotor zur Umsetzung einer Active Heave Compensation betrieben, die die Kompensation des Seegangs zur Aufgabe hat.In a particularly preferred embodiment of the present invention can be by means of at least one hydraulic circuit or the hydraulic motor, a crane winch, in particular a Tiefseehubseilwinde drive. Preferably, the hydraulic motor is operated to implement an Active Heave Compensation, which has the compensation of the sea state to the task.

Durch die Verwendung eines Druckuntersetzers kann das Hydraulikfluid zwischen diesem und gegebenenfalls einem angeordneten Speicher hin -und hergeschoben werden, was insbesondere in der Betriebsart Active Heave Compensation oder ähnlicher zyklischer Betriebsarten zur Anwendung kommt. Durch das erfindungsgemäße Hydrauliksystem lässt sich die Tankumwälzmenge merklich reduzieren. Zudem zeichnet sich das System durch eine besonders effiziente Energierückgewinnung aus.By using a pressure reducer, the hydraulic fluid can be pushed back and forth between it and, if appropriate, an arranged memory, which is used in particular in the active-heave compensation mode or similar cyclic operating modes. By the hydraulic system according to the invention, the tank circulation can be significantly reduced. In addition, the system is characterized by a particularly efficient energy recovery.

Der Kran kann eine Tiefseehubseilwinde aufweisen, die durch einen hydraulischen Antrieb versorgt wird. Insbesondere dient ein geschlossener Hydraulikkreislauf mit wenigstens einem Hydraulikmotor dazu, die Hubseilwinde zur Ausführung einer Ab- bzw. Aufwickelbewegung in Rotation zu versetzen. Zudem kann der Kran ein Konstantdrucknetz umfassen, das von einer zentralen Hydraulikpumpe versorgbar ist und zur Speisung ein oder mehrerer hydraulischer Verbraucher, insbesondere diverser Krankomponenten, verwendet wird.The crane can have a Tiefseehubseilwinde, which is supplied by a hydraulic drive. In particular, a closed hydraulic circuit with at least one hydraulic motor serves to set the hoist winch in rotation for carrying out a take-off or winding-up movement. In addition, the crane may comprise a constant pressure network which can be supplied by a central hydraulic pump and is used to supply one or more hydraulic consumers, in particular various crane components.

Der integrierte Hydromotor kann vorzugsweise Bestandteil einer Seegangsfolgeeinrichtung sein. Die Winde wird hier durch den Hydromotor gesondert angetrieben, um den Seegang während der eigentlichen Hubarbeit kompensieren zu können.The integrated hydraulic motor may preferably be part of a Seegangsfolgeeinrichtung. The winch is here driven separately by the hydraulic motor to compensate for the sea state during the actual lifting work can.

Weitere Vorteile und Einzelheiten der Erfindung werden anhand von zwei Zeichnungen näher beschrieben.Further advantages and details of the invention will be described in more detail with reference to two drawings.

Die beiden Figuren 1, 2 zeigen eine Ausführungsform des erfindungsgemäßen Hydrauliksystems zum Betrieb eines Offshore-Krans. Der Kran bzw. das Hydrauliksystem ist insbesondere für den Tiefseehub konstruiert. Neben dem eigentlichen hydraulischen Antrieb der Tiefseehubwinde ist eine Seegangsfolgeeinrichtung installiert.The two FIGS. 1 . 2 show an embodiment of the hydraulic system according to the invention for operating an offshore crane. The crane or hydraulic system is designed especially for deep-sea lifting. In addition to the actual hydraulic drive of Tiefseehubwinde a Seegangsfolgeeinrichtung is installed.

Der Aufbau des in den Figuren 1, 2 gezeigten Hydrauliksystems umfasst ein Konstantdrucknetz 2 mit einem verhältnismäßig hohen Druckniveau. Zur Erzeugung des Konstantdruckes ist die Hydraulikpumpe 1 vorgesehen, die Hydrauliköl aus dem Tank ansaugt und auf das entsprechende Druckniveau des Konstantdrucknetzes 2 bringt.The construction of the in the FIGS. 1 . 2 shown hydraulic system comprises a constant pressure network 2 with a relatively high pressure level. To generate the constant pressure, the hydraulic pump 1 is provided which sucks hydraulic oil from the tank and brings it to the corresponding pressure level of the constant pressure network 2.

Zudem sind in der Figur 2 zusätzlich zwei hydraulische Verbraucher 13 in Form eines Hydraulikmotors und eines Hydraulikzylinders eingezeichnet, die jeweils über die Hydraulikpumpe 1 mit dem Druckniveau des Konstantdrucknetzes 2 gespeist werden. Beide Verbraucher 13 sollen jedoch nur stellvertretend für einen möglichen Aufbau des Konstantdrucknetzes 2 stehen. Grundsätzlich können beliebig viele gleichartige oder verschiedene Hydraulikkomponenten im Konstantdrucknetz 2 angeordnet sein bzw. mit diesem in Verbindung stehen.In addition, in the FIG. 2 additionally drawn two hydraulic consumers 13 in the form of a hydraulic motor and a hydraulic cylinder, which are each fed via the hydraulic pump 1 with the pressure level of the constant pressure network 2. Both consumers 13 should only be representative of a possible construction of the constant pressure network 2. In principle, any number of identical or different hydraulic components can be arranged in the constant pressure network 2 or be in connection therewith.

Für den Antrieb der Tiefseehubseilwinde 7 steht ein geschlossener Hydraulikkreislauf zur Verfügung, bestehend aus der Pumpen-Motoreinheit 9 sowie dem in beide Strömungsrichtungen betreibbaren Hydraulikmotor 8.For driving the Tiefseehubseilwinde 7 is a closed hydraulic circuit available, consisting of the pump motor unit 9 and the operable in both flow directions hydraulic motor. 8

Der Kran umfasst weiterhin einen Antriebsmotor 11 mit euinem Getriebe 12. Neben der Hydraulikpumpe 1 zur Speisung des Konstantdrucknetzes 2 sitzt zudem die Pumpen-Motoreinheit 9 des geschlossenen Kreislaufs auf der Antriebswelle 12.The crane further comprises a drive motor 11 with euinem gear 12. In addition to the hydraulic pump 1 for feeding the constant pressure network 2 also sits the pump motor unit 9 of the closed circuit on the drive shaft 12th

Die Seilwinde 7 wird hauptsächlich durch den geschlossenen Kreislauf, d. h. den Hydraulikmotor 8 sowohl in Auf- als auch in Abwickelrichtung angetrieben, um die erforderliche Hubarbeit auszuführen.The winch 7 is mainly by the closed circuit, d. H. the hydraulic motor 8 driven both in the up and in the unwinding to perform the required lifting work.

Da der Kran während des Tiefseehubs den äußeren Einflüssen des Seegangs unterliegt, ist eine prinzipiell bekannte Seegangsfolgeeinrichtung vorgesehen, die den Seegang über eine zusätzliche Ansteuerung der Seilwinde 7 kompensieren soll.Since the crane is subject to the external influences of the sea state during the deep-sea stroke, a sea-gear sequencing device which is known in principle is provided, which is intended to compensate for the swell of the sea via additional control of the winch 7.

Zur Umsetzung der Seegangsfolgeeinrichtung, die auch als Active Heave Compensation bezeichnet wird, dient der Hydraulikkreislauf 4. Dieser umfasst einen in beide Strömungsrichtungen betreibbaren Hydraulikmotor 5, dessen Drehmoment ebenfalls die Seilwinde 7 in beide Richtungen antreibt. Gleichzeitig ist der Motor 5 als Verstelleinheit ausgeführt.To implement the Seegangsfolgeeinrichtung, which is also referred to as Active Heave Compensation, is the hydraulic circuit 4. This includes a operable in both directions of flow hydraulic motor 5, whose torque also drives the winch 7 in both directions. At the same time the engine 5 is designed as an adjustment.

Zur Speisung des Hydromotors 5 wird ein besonders hoher Volumenstrom verlangt, der oftmals in Bereiche bis mehrere tausend I/Minute vorstößt. Dieser hohe Volumenstrom wird erfindungsgemäß nicht über eine eigene Einspeispumpe, wie aus dem Stand der Technik bekannt, realisiert, sondern erfolgt durch die Kopplung des Konstantdrucknetzes 2 an den Kreislauf 4 mit Hilfe des Druckuntersetzers 3.To supply the hydraulic motor 5, a particularly high volume flow is required, which often penetrates into areas up to several thousand I / minute. This high volume flow is inventively not via its own feed pump, as known from the prior art, realized, but is done by the coupling of the constant pressure network 2 to the circuit 4 by means of the pressure reducer. 3

Der Druckuntersetzer 3 besteht aus zwei Kolben, die eine gemeinsame Kolbenstange mit abweichenden Kolbenflächen an den Stangenstirnseiten aufweisen. Die Kolbenfläche mit geringerem Umfang ist mit dem Konstantdrucknetz 2 verbunden, wohingegen die verhältnismäßig große Kolbenfläche des zweiten Zylinders mit dem Hydraulikreislauf 4 in Verbindung steht.The pressure reducer 3 consists of two pistons, which have a common piston rod with deviating piston surfaces on the rod end faces. The smaller area of the piston is connected to the constant pressure network 2, whereas the relatively large piston area of the second cylinder communicates with the hydraulic circuit 4.

Das gewählte Flächenverhältnis der beiden Kolbenflächen bewirkt, dass der kleine Volumenstrom mit hohem Druck aus dem Konstantdrucknetz 2 in einen hohen Volumenstrom mit niederem Druck innerhalb des Hydraulikkreislaufs 4 gewandelt wird.The selected area ratio of the two piston surfaces causes the small volume flow of high pressure from the constant pressure network 2 is converted into a high volume flow at low pressure within the hydraulic circuit 4.

Der Druckuntersetzer 3 übernimmt die Hydrauliköleinspeisung, die ein Trockenlaufen des Systems verhindert. Hierzu steht der Druckuntersetzers 3 mit einem Eingang des Hydraulikmotors 5 in Verbindung. Am Ausgang des Hydraulikmotors 5 ist über ein Wegeventil 10 sowie einen Druckmittelwandler 6 ein Speichermittel 15 angeschlossen, über welches die Hubarbeit geleistet wird.The pressure reducer 3 takes over the hydraulic oil feed, which prevents dry running of the system. For this purpose, the pressure reducer 3 is in communication with an input of the hydraulic motor 5. At the output of the hydraulic motor 5, a storage means 15 is connected via a directional control valve 10 and a pressure medium converter 6, via which the lifting work is done.

Um Drucküberlastungen im Hydraulikkreis 4 zu vermeiden, ist zusätzlich ein Druckbegrenzungsventil 17 angeordnet, das bei Erreichen eines bestimmten Grenzdruckniveaus überschüssiges Hydrauliköl an den Tank freigibt.In order to avoid pressure overloads in the hydraulic circuit 4, a pressure limiting valve 17 is additionally arranged, which releases excess hydraulic oil to the tank when a certain limit pressure level is reached.

Wie der Figur 1 zu entnehmen ist, kann hilfsweise eine zusätzliche Hydraulikpumpe 18 im Hydraulikkreislauf 4 vorgesehen sein, um ein bestimmtes Druckniveau bzw. einen bestimmten Volumenstrom gewährleisten zu können. Die Hydraulikpumpe 18 sitzt auf einer gemeinsamen Antriebswelle mit dem verstellbaren Motor 12 des Konstantdrucknetzes 2.Again FIG. 1 can be seen, in the alternative, an additional hydraulic pump 18 may be provided in the hydraulic circuit 4 in order to ensure a certain pressure level or a certain flow. The hydraulic pump 18 is seated on a common drive shaft with the adjustable motor 12 of the constant pressure network 2.

Claims (10)

  1. A crane with a hydraulic system with at least one hydraulic circuit (4), which comprises at least one hydraulic consumer (13), and a constant pressure network (2),
    characterized in
    that the at least one hydraulic circuit (4) is coupled with the constant pressure network via at least one pressure reducer (3), whereby a higher volume flow with low pressure as compared to the constant pressure network can be generated in the hydraulic circuit.
  2. The crane according to claim 1, characterized in that the pressure reducer includes at least two pistons with a corresponding piston surface ratio.
  3. The crane according to any of the preceding claims, characterized in that upon reversal of the flow direction of the at least one hydraulic circuit pressure energy can be released to the constant pressure network.
  4. The crane according to any of the preceding claims, characterized in that at least one pressure accumulator (15) is provided in the hydraulic circuit, wherein in the at least one accumulator pressure energy can be stored, which upon flow reversal can be released to the constant pressure network.
  5. The crane according to any of the preceding claims, characterized in that the at least one pressure accumulator is incorporated via at least one air-oil actuator.
  6. The crane according to any of the preceding claims, characterized in that at least one hydraulic consumer of the at least one hydraulic circuit is a hydraulic motor (5) which is operable in two flow directions.
  7. The crane according to claim 6, characterized in that the hydraulic motor is operable in a first direction of rotation by means of the volume flow generated by the pressure reducer and is operable in a second direction of rotation by means of the pressure energy stored in at least one pressure accumulator.
  8. The crane according to claim 6 or 7, characterized in that by means of the at least one hydraulic circuit or the hydraulic motor a crane cable winch (7), in particular a deep-sea hoisting cable winch, can be driven, preferably for compensating the heave.
  9. The crane according to any of the preceding claims, characterized in that it is an offshore crane.
  10. The crane according to any of the preceding claims with a deep-sea hoisting cable winch, wherein the winch can be driven via a closed hydraulic circuit and the deep-sea hoisting winch in addition can be driven by means of the hydraulic motor in the hydraulic circuit, in order to compensate the heave.
EP12008080.9A 2012-03-08 2012-12-03 Hydraulic system and crane Active EP2636633B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012004737A DE102012004737A1 (en) 2012-03-08 2012-03-08 Hydraulic system and crane

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EP2636633A1 EP2636633A1 (en) 2013-09-11
EP2636633B1 true EP2636633B1 (en) 2015-07-22

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012004802A1 (en) * 2012-03-09 2013-09-12 Liebherr-Werk Nenzing Gmbh Crane control with distribution of a kinematically limited size of the hoist
CN108679040A (en) * 2018-08-01 2018-10-19 江苏恒立液压股份有限公司 Depressurize oil cylinder
NO344544B1 (en) 2018-11-22 2020-01-27 Kongsberg Maritime CM AS Multi ratio accumulator system.
DE102021207464A1 (en) 2021-07-14 2023-01-19 Robert Bosch Gesellschaft mit beschränkter Haftung Method of operating a hydraulic winch

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1144900B (en) * 1960-05-14 1963-03-07 Krupp Ardelt Gmbh Hydraulically driven winch with a sea state follower
DE1528583A1 (en) * 1965-05-20 1970-01-29 Stahl U Appbau Hans Leffer Gmb Hydraulically or pneumatically continuously operated piston drive with reciprocating movement, especially double-acting pressure intensifier
US3381939A (en) * 1966-01-24 1968-05-07 Brown Oil Tools Hydraulic draw works with automatic power output control
US3828683A (en) * 1972-12-04 1974-08-13 A Lehrer Marine load transfer system
NO770299L (en) * 1977-01-28 1978-07-31 Stroemmen Staal A S SYSTEM FOR ACTIVE COMPENSATION OF UNDESIRED RELATIVE MOVEMENTS, PREFERREDLY DURING TRANSFER OF LOAD
DD137088A1 (en) * 1978-06-14 1979-08-15 Gerd Marschall CONTROL SYSTEM WITH PNEUMO-HYDRAULIC PRESSURE TRANSLATOR
DE3418026C2 (en) * 1984-05-15 1987-04-02 Mannesmann Rexroth GmbH, 8770 Lohr Winch for lifting floating loads in rough seas
DE3643114C2 (en) * 1986-01-13 1995-06-01 Rexroth Mannesmann Gmbh Winch control with swell tracking device
DE8806159U1 (en) * 1988-05-09 1988-09-15 H.M.B Hydraulik & Maschinenbau Buxtehude GmbH, 21614 Buxtehude Crane winch
US5209302A (en) * 1991-10-04 1993-05-11 Retsco, Inc. Semi-active heave compensation system for marine vessels
EP1025922B1 (en) * 1999-02-05 2002-06-26 Strömsholmen AB Hydraulic arrangement for performing a secondary operation in a pressing tool for sheet metal forming
US6932325B1 (en) * 2004-02-18 2005-08-23 Dynacon, Inc. Active-over-passive coordinated motion winch
US20080169131A1 (en) * 2005-03-15 2008-07-17 Shu Takeda Device And Method For Measuring Load Weight On Working Machine
DE102007046696A1 (en) * 2007-09-28 2009-04-09 Liebherr-Werk Nenzing Gmbh Hydraulic drive system
WO2009120062A2 (en) * 2008-03-26 2009-10-01 Itrec B.V. Heave compensation system and method
US8181460B2 (en) * 2009-02-20 2012-05-22 e Nova, Inc. Thermoacoustic driven compressor
DE102009029840A1 (en) * 2009-06-22 2011-01-27 Liebherr-Werk Nenzing Gmbh hydraulic system
CN201925250U (en) * 2010-12-15 2011-08-10 浙江浦大液压机械有限公司 Ultrahigh pressure flow amplifier

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US9248997B2 (en) 2016-02-02
DE102012004737A1 (en) 2013-09-12
US20130236272A1 (en) 2013-09-12
EP2636633A1 (en) 2013-09-11
CN103307045A (en) 2013-09-18

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