EP3135625B1 - Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane - Google Patents

Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane Download PDF

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Publication number
EP3135625B1
EP3135625B1 EP15182321.8A EP15182321A EP3135625B1 EP 3135625 B1 EP3135625 B1 EP 3135625B1 EP 15182321 A EP15182321 A EP 15182321A EP 3135625 B1 EP3135625 B1 EP 3135625B1
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EP
European Patent Office
Prior art keywords
hydraulic
line
control device
working
control
Prior art date
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EP15182321.8A
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German (de)
French (fr)
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EP3135625A1 (en
Inventor
Herr. Dr.-Ing. Torsten Verkoyen
Herr Dipl.-Ing.Heinz Henning Hoppmann
Herr Prof.Dr.-Ing.Christian Stammen
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XCMG European Research Center GmbH
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XCMG European Research Center GmbH
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Priority to EP15182321.8A priority Critical patent/EP3135625B1/en
Priority to CN201510635222.5A priority patent/CN106477458B/en
Priority to AU2016312887A priority patent/AU2016312887B2/en
Priority to RU2018110255A priority patent/RU2679942C1/en
Priority to US15/754,421 priority patent/US10974936B2/en
Priority to CA2996374A priority patent/CA2996374C/en
Priority to PCT/EP2016/069399 priority patent/WO2017032641A1/en
Publication of EP3135625A1 publication Critical patent/EP3135625A1/en
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Publication of EP3135625B1 publication Critical patent/EP3135625B1/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
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/54—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes with pneumatic or hydraulic motors, e.g. for actuating jib-cranes on tractors
    • 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
    • B66D1/02—Driving gear
    • B66D1/08—Driving gear incorporating fluid motors
    • 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
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/24—Operating devices
    • B66D5/26—Operating devices pneumatic or hydraulic
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C2700/00—Cranes
    • B66C2700/03—Cranes with arms or jibs; Multiple cranes
    • B66C2700/0321—Travelling cranes
    • B66C2700/0357—Cranes on road or off-road vehicles, on trailers or towed vehicles; Cranes on wheels or crane-trucks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches
    • B66D2700/0133—Fluid actuated

Definitions

  • the invention relates to a hydraulic control system for a hydraulically operated liftable and lowerable hook of a crane, wherein the hydraulic system comprises at least one working machine designed as a hydraulic motor which drives the winch and at least one drive machine, in particular designed as a pump. depending on the operating state of the working machine as feed or return serving, connections via corresponding working lines directly or indirectly connected to at least one of the drive machines, and wherein in a working line a lowering brake valve is provided, which is connected via a control line to the other working line, that the lowering brake valve from its locking position against a restoring force by the prevailing in the other working line and passed over the control line pressure in a flow position for lowering the hook by means of the winch, esp ondere primary winds, is displaced.
  • the US 2012/0285152 A1 discloses such a hydraulic control. From practice such hydraulic controls are known in which determine a hydraulic resistance in the control line and a hydraulic resistance in the drain line, the opening pressure of the lowering brake valve. The disadvantage here is that thus no specific control of the lowering is possible. Either the lowering is safe, but slow, or it there is a risk of vibration and / or cavitation in too fast lowering, depending on the design of the hydraulic resistors.
  • the object of the invention is to avoid the aforementioned disadvantages and to provide a hydraulic control, with which the risk of unstable states is reduced or even avoided.
  • a drain line leading back to a tank branches off from the control line, wherein the drain line is provided with a switching possibility for setting the control pressure acting on the lowering brake valve to different values, with which the effective hydraulic resistance in the drain line is controlled or regulation can be changed to at least two different values.
  • hydraulic resistance for example, diaphragms, throttles or mixed forms in question.
  • the control line may be provided with a changeover between internal and external control.
  • the signal of the external control can be limited such that no complete opening of the lowering brake valve is possible.
  • Part of the pressure is dissipated through the discharge line leading back to the tank, so that the pressure acting on the lowering brake valve is reduced by this part. If the two parallel hydraulic resistances, in particular orifices, are operated simultaneously in the discharge line leading back to the tank, a larger passage results, whereby the pressure acting on the lowering brake valve is reduced and the lowering takes place more slowly.
  • the pressure feedback on the prime mover / pump remains constant and continues to run at its initial state, which may be, for example, around 30 bar.
  • a switch between secured fine control and standard circuit done. It is thus also a fine control possible if no pulley is present and thus the Absenkweg is proportional to the speed of the machine.
  • a working flow controlling volume flow which is variable at least in certain operating conditions via an accelerator pedal and / or a joystick.
  • a control line can connect the operating mode of the working machine as the return serving working line for acting on the switchover by the serving in the prevailing operating state of the machine as a return working line due to the line resistance back pressure with the switchover.
  • a different control or regulation is possible, such.
  • the actuation of the switching possibility can also take place in dependence on the valve travel of the lowering brake valve.
  • the coupling can be arbitrary, z. B. mechanical, hydraulic or otherwise.
  • the switching possibility can also be designed as a combined component and comprise a switchable hydraulic resistance, in particular a diaphragm.
  • the value of the smaller hydraulic resistance may be 0.66 times or 0.85 times the value of the larger hydraulic resistance or the diameter of the smaller aperture may be about 0.66 times or 0.85 times the diameter the larger aperture amount.
  • all ratio values from 0 to 1 are possible in deviation.
  • two parallel provided hydraulic resistances preferably diaphragms with different diameters, be provided, of which the larger hydraulic resistance or the diaphragm with the smaller diameter can be switched over a switchover between activated state and deactivated state, these two hydraulic resistances or Doors open via a shuttle valve in the control line.
  • the value of the smaller hydraulic resistance can be 0.6 times the value of the larger hydraulic resistance diameter or the diameter of the smaller diaphragm can be 0.6 times the diameter of the larger diaphragm.
  • all ratio values from 0 to 1 are possible in deviation.
  • a non-return valve may still be provided which can only be flowed through in the direction of the smaller hydraulic resistance, in particular the larger orifice, to the 3/2-way valve.
  • the external control can be assigned a separate pump, from which it is supplied.
  • the external control may be connected to the drive machine designed as a pump.
  • Fig. 1 shows a hydraulic control 1 for a hydraulically operated by means of a winch raised and lowered, not shown in the drawing hook of a crane.
  • the hydraulic system not shown in detail so far, at least one designed as a hydraulic motor working machine 15 which drives the winch 16 of the crane, and at least one pump designed as a prime mover.
  • the working machine 15 is connected by means of two, depending on the operating state of the working machine 15 as an inlet or return serving, connections via corresponding working lines 2 directly or indirectly connected to at least one of the drive machines.
  • a lowering brake valve 3 is provided, which is connected via a control line 4 with the other working line 2 such that the lowering brake valve 3 from its locking position against a restoring force by the ruling in this other working line 2 and passed over the control line 4 control pressure in a flow position for Lowering of the hook by means of the winch 16, in particular primary winds, is displaced.
  • the control line 4 is provided with a changeover 5 between internal and external control.
  • the diameter of the smaller aperture 9 is approximately 0.66 times the diameter of the larger aperture 8.
  • a portion of the pressure is discharged through the drain line 6 leading back to the tank, so that the pressure acting on the lowering brake valve 3 is reduced by this part.
  • the larger orifice 8 is operated in the drain line 6 leading to the tank, a larger passage results, whereby the control pressure acting on the lowering brake valve 3 is reduced and the lowering takes place more slowly.
  • the changeover 5 between internal and external control is formed by a 3/2-way valve.
  • a check valve 12 is further provided, which can only be flowed through in the direction of the larger aperture 11 to the 3/2-way valve.
  • a control line 17 connects the serving in the prevailing operating state of the working machine 15 as a return line 2 for the actuation of the switch 7 by the serving in the prevailing operating state of the machine 15 as a return working line 2 due to the line resistance back pressure with the switch 7.
  • Fig. 2 illustrated another embodiment, the switching between internal and external control of acting through the control line 4 to the lowering brake valve 3 control pressure via two parallel apertures 10, 11 provided with different diameters, wherein these two apertures 10, 11 via a shuttle valve 14, in a different manner which switches as a function of the applied pressures between the diaphragm 10 and the diaphragm 11, open into the control line 4.
  • the diameter of the smaller aperture 10 is 0.6 times the diameter of the larger aperture 11.
  • the shuttle valve 14 is "actuated" here by the switchover 5 and the pressure acting on the switchover 5 depending on the switching state.
  • FIG. 3 shown third embodiment shows a simplified version of the article after Fig. 1 , where the in Fig. 1 shown switching between internal and external control is omitted and instead only a fixed aperture 10 is provided. In addition, a prime mover 15 and a winch 16 actuated therefrom are shown.
  • FIG. 4 shown fourth embodiment shows an alternative embodiment, wherein provided in the drain line 6 switching option 7 is designed as a 2/2-way valve, with which a diaphragm 9 is activated or deactivated can be, whereby the pressure acting on the lowering brake valve 3 is changeable.
  • the switching option 7 is designed as a "black box", the control line 17 is only indicated and arbitrarily, for. B. electrically, hydraulically, pneumatically or otherwise, can be acted upon.
  • the control of the loading can be done in any way.
  • Fig. 6 variant shown is the embodiment of in Fig. 4 similar embodiment shown, wherein the switching possibility 7 relates to two mutually parallel apertures 8, 9 with different diameters.
  • the aperture 9, which has the smaller diameter are switched over the formed by a 2/2-way valve switching option 7 between activated state and deactivated state, with a faster lowering at the larger aperture 8 (and deactivated smaller aperture 9) and a more stable operation with slower lowering with activated state of the smaller aperture 9 takes place.
  • Fig. 7 shows a modification of the subject Fig. 6
  • the switchover 7 is designed as a combined component and includes a switchable hydraulic resistance in the form of the aperture 9.
  • the switching possibility 7 is mechanically coupled to the valve path of the lowering brake valve 3.
  • the coupling can also z. B. be implemented hydraulically or in any other way.
  • the switchover option 7 is set to "Permeable”
  • the larger aperture 8 acts.
  • the smaller aperture 9 is connected in series with the larger aperture 8 by the switchover 7, only the smaller aperture 9, since it affects the larger hydraulic Has resistance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft eine Hydrauliksteuerung für einen hydraulisch betätigten hebbaren und absenkbaren Haken eines Krans, wobei das Hydrauliksystem zumindest eine als Hydraulikmotor ausgebildete Arbeitsmaschine, welche die Winde antreibt, und zumindest eine, insbesondere als Pumpe ausgebildete, Antriebsmaschine, umfasst, wobei die Arbeitsmaschine mittels zweier, je nach Betriebszustand der Arbeitsmaschine als Zulauf bzw. Rücklauf dienender, Anschlüsse über entsprechende Arbeitsleitungen mittelbar oder unmittelbar mit wenigstens einer der Antriebsmaschinen verbunden ist, und wobei in der einen Arbeitsleitung ein Senkbremsventil vorgesehen ist, welches über eine Steuerleitung mit der anderen Arbeitsleitung derart verbunden ist, dass das Senkbremsventil aus seiner Sperrposition gegen eine Rückstellkraft durch den in der anderen Arbeitsleitung herrschenden und über die Steuerleitung weitergegebenen Druck in eine Durchflussposition zum Absenken des Hakens mittels der Winde, insbesondere Primärwinde, verlagerbar ist. Die US 2012/0285152 A1 offenbart eine solche Hydrauliksteuerung. Aus der Praxis sind derartige Hydrauliksteuerungen bekannt, bei denen ein hydraulischer Widerstand in der Steuerleitung sowie ein hydraulischer Widerstand in der Abflussleitung den Öffnungsdruck des Senkbremsventils bestimmen. Nachteilig hierbei ist, dass damit keine gezielte Steuerung des Absenkens möglich ist. Entweder erfolgt das Absenken sicher, aber langsam, oder es besteht die Gefahr von Schwingungen und/oder Kavitation bei zu schnellem Absenken, je nach Ausgestaltung der hydraulischen Widerstände.The invention relates to a hydraulic control system for a hydraulically operated liftable and lowerable hook of a crane, wherein the hydraulic system comprises at least one working machine designed as a hydraulic motor which drives the winch and at least one drive machine, in particular designed as a pump. depending on the operating state of the working machine as feed or return serving, connections via corresponding working lines directly or indirectly connected to at least one of the drive machines, and wherein in a working line a lowering brake valve is provided, which is connected via a control line to the other working line, that the lowering brake valve from its locking position against a restoring force by the prevailing in the other working line and passed over the control line pressure in a flow position for lowering the hook by means of the winch, esp ondere primary winds, is displaced. The US 2012/0285152 A1 discloses such a hydraulic control. From practice such hydraulic controls are known in which determine a hydraulic resistance in the control line and a hydraulic resistance in the drain line, the opening pressure of the lowering brake valve. The disadvantage here is that thus no specific control of the lowering is possible. Either the lowering is safe, but slow, or it there is a risk of vibration and / or cavitation in too fast lowering, depending on the design of the hydraulic resistors.

Aufgabe der Erfindung ist es, die vorgenannten Nachteile zu vermeiden und eine Hydrauliksteuerung anzugeben, mit der die Gefahr von instabilen Zuständen verringert oder sogar vermieden wird.The object of the invention is to avoid the aforementioned disadvantages and to provide a hydraulic control, with which the risk of unstable states is reduced or even avoided.

Diese Aufgabe wird dadurch gelöst, dass von der Steuerleitung eine zu einem Tank zurückführende Abflussleitung abzweigt, wobei für eine Einstellung des auf das Senkbremsventil wirkenden Steuerdrucks auf verschiedene Werte die Abflussleitung mit einer Umschaltmöglichkeit versehen ist, mit welcher der wirksame hydraulische Widerstand in der Abflussleitung durch Steuerung oder Regelung auf zumindest zwei verschiedene Werte veränderbar ist.This object is achieved in that a drain line leading back to a tank branches off from the control line, wherein the drain line is provided with a switching possibility for setting the control pressure acting on the lowering brake valve to different values, with which the effective hydraulic resistance in the drain line is controlled or regulation can be changed to at least two different values.

Als hydraulischer Widerstand kommen beispielsweise Blenden, Drosseln oder Mischformen in Frage.As a hydraulic resistance, for example, diaphragms, throttles or mixed forms in question.

Für eine Einstellung des auf das Senkbremsventil wirkenden Steuerdrucks auf verschiedene Werte kann die Steuerleitung mit einer Umschaltung zwischen interner und externer Steuerung versehen sein. Dabei kann das Signal der externen Steuerung derart beschränkt sein, dass kein vollständiges Öffnen des Senkbremsventils möglich ist.For setting the control pressure acting on the counterbalance valve to different values, the control line may be provided with a changeover between internal and external control. In this case, the signal of the external control can be limited such that no complete opening of the lowering brake valve is possible.

Durch die zum Tank zurückführende Abflussleitung wird ein Teil des Drucks abgeleitet, so dass der auf das Senkbremsventil wirkende Druck um diesen Teil reduziert ist. Wenn die beiden parallelen hydraulischen Widerstände, insbesondere Blenden, in der zum Tank zurückführenden Abflussleitung gleichzeitig betrieben werden, resultiert ein größerer Durchlass, wodurch der auf das Senkbremsventil wirkende Druck reduziert ist und das Absenken langsamer erfolgt.Part of the pressure is dissipated through the discharge line leading back to the tank, so that the pressure acting on the lowering brake valve is reduced by this part. If the two parallel hydraulic resistances, in particular orifices, are operated simultaneously in the discharge line leading back to the tank, a larger passage results, whereby the pressure acting on the lowering brake valve is reduced and the lowering takes place more slowly.

Bei aktivierter externer Steuerung bleibt die Druckrückmeldung bei der Antriebsmaschine/Pumpe konstant und diese läuft auf ihrem Grundzustand, der beispielsweise bei ca. 30 bar liegen kann, weiter. Insoweit kann ein Umschalten zwischen abgesicherter Feinsteuerung und Standardschaltung erfolgen. Es ist damit auch eine Feinsteuerung möglich, wenn kein Flaschenzug vorhanden ist und somit der Absenkweg proportional zur Drehzahl der Arbeitsmaschine ist.When the external control is activated, the pressure feedback on the prime mover / pump remains constant and continues to run at its initial state, which may be, for example, around 30 bar. In that regard, a switch between secured fine control and standard circuit done. It is thus also a fine control possible if no pulley is present and thus the Absenkweg is proportional to the speed of the machine.

Vorzugsweise kann die beim herrschenden Betriebszustand der Arbeitsmaschine als Zulauf dienende Arbeitsleitung mit einem die Arbeitsgeschwindigkeit steuernden Volumenstrom beaufschlagt sein, welcher zumindest in bestimmten Betriebszuständen über ein Gaspedal und/oder einen Joystick veränderbar ist. Weiterhin kann eine Steuerungsleitung die beim herrschenden Betriebszustand der Arbeitsmaschine als Rücklauf dienende Arbeitsleitung für die Beaufschlagung der Umschaltmöglichkeit durch den in der beim herrschenden Betriebszustand der Arbeitsmaschine als Rücklauf dienenden Arbeitsleitung aufgrund des Leitungswiderstandes resultierenden Staudruck mit der Umschaltmöglichkeit verbinden.Preferably, in the prevailing operating state of the working machine serving as a feed working line can be acted upon by a working flow controlling volume flow, which is variable at least in certain operating conditions via an accelerator pedal and / or a joystick. Furthermore, a control line can connect the operating mode of the working machine as the return serving working line for acting on the switchover by the serving in the prevailing operating state of the machine as a return working line due to the line resistance back pressure with the switchover.

Alternativ ist auch eine abweichende Steuerung oder Regelung möglich, wie z. B. eine aktive, z. B. elektrische, Steuerung. Die Betätigung der Umschaltmöglichkeit kann dabei auch in Abhängigkeit von dem Ventilweg des Senkbremsventils erfolgen. Die Koppelung kann beliebig sein, z. B. mechanisch, hydraulisch oder anderweitig.Alternatively, a different control or regulation is possible, such. B. an active, z. B. electrical, control. The actuation of the switching possibility can also take place in dependence on the valve travel of the lowering brake valve. The coupling can be arbitrary, z. B. mechanical, hydraulic or otherwise.

Auch kann die Umschaltmöglichkeit als kombiniertes Bauteil ausgeführt sein und einen schaltbaren hydraulischen Widerstand, insbesondere eine Blende, umfassen.The switching possibility can also be designed as a combined component and comprise a switchable hydraulic resistance, in particular a diaphragm.

Erfindungsgemäß kann der Wert des kleineren hydraulischen Widerstands das 0,66-fache oder 0,85-fache des Wertes des größeren hydraulischen Widerstands betragen bzw. der Durchmesser der kleineren Blende ca. das 0,66-fache oder 0,85-fache des Durchmessers der größeren Blende betragen. Es sind jedoch abweichend alle Verhältniswerte von 0 bis 1 möglich.According to the invention, the value of the smaller hydraulic resistance may be 0.66 times or 0.85 times the value of the larger hydraulic resistance or the diameter of the smaller aperture may be about 0.66 times or 0.85 times the diameter the larger aperture amount. However, all ratio values from 0 to 1 are possible in deviation.

Weiterhin können für die Umschaltung zwischen interner und externer Steuerung des durch die Steuerleitung auf das Senkbremsventil wirkenden Steuerdrucks zwei parallel zueinander vorgesehene hydraulische Widerstände, vorzugsweise Blenden mit unterschiedlichem Durchmesser, vorgesehen sein, von denen der größere hydraulische Widerstand bzw. die Blende mit dem kleineren Durchmesser über eine Umschaltmöglichkeit zwischen aktiviertem Zustand und deaktiviertem Zustand umgeschaltet werden kann, wobei diese beiden hydraulischen Widerstände bzw. Blenden über ein Wechselventil in die Steuerleitung münden. Hierdurch ist eine feinere Steuerung möglich.Furthermore, for the switching between internal and external control of the control pressure acting on the lowering brake valve by the control line two parallel provided hydraulic resistances, preferably diaphragms with different diameters, be provided, of which the larger hydraulic resistance or the diaphragm with the smaller diameter can be switched over a switchover between activated state and deactivated state, these two hydraulic resistances or Doors open via a shuttle valve in the control line. As a result, a finer control is possible.

Auch kann für die Umschaltung zwischen interner und externer Steuerung des durch die Steuerleitung auf das Senkbremsventil wirkenden Steuerdrucks ein Wechsel zwischen zwei an ein 3/2-Wegeventil angeschlossenen, parallel zueinander vorgesehenen Blenden mit unterschiedlichem Durchmesser vorgesehen sein.Also can be provided for switching between internal and external control of the control line acting on the lowering brake control pressure a change between two connected to a 3/2-way valve, parallel apertures provided with different diameters.

Dabei kann jeweils der Wert des kleineren hydraulischen Widerstands das 0,6-fache des Wertes des größeren hydraulischen Widerstands Durchmessers betragen bzw. der Durchmesser der kleineren Blende das 0,6-fache des Durchmessers der größeren Blende betragen. Es sind jedoch abweichend alle Verhältniswerte von 0 bis 1 möglich.In each case, the value of the smaller hydraulic resistance can be 0.6 times the value of the larger hydraulic resistance diameter or the diameter of the smaller diaphragm can be 0.6 times the diameter of the larger diaphragm. However, all ratio values from 0 to 1 are possible in deviation.

Außerdem kann in dem Leitungsabschnitt mit dem kleineren hydraulischen Widerstand, insbesondere mit der größeren Blende, weiterhin ein Rückschlagventil vorgesehen sein, welches nur in Richtung von dem kleineren hydraulischen Widerstand, insbesondere der größeren Blende, zu dem 3/2-Wegeventil durchströmbar ist.In addition, in the line section with the smaller hydraulic resistance, in particular with the larger orifice, a non-return valve may still be provided which can only be flowed through in the direction of the smaller hydraulic resistance, in particular the larger orifice, to the 3/2-way valve.

Vorzugsweise kann der externen Steuerung eine eigene Pumpe zugeordnet sein, von der sie versorgt wird. Auch kann die externe Steuerung an die als Pumpe ausgebildete Antriebsmaschine angeschlossen sein.Preferably, the external control can be assigned a separate pump, from which it is supplied. Also, the external control may be connected to the drive machine designed as a pump.

Im Folgenden werden in den Zeichnungen dargestellte Ausführungsbeispiele der Erfindung erläutert. Es zeigen:

Fig. 1
ein erstes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung,
Fig. 2
ein zweites Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung,
Fig. 3
ein drittes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung,
Fig. 4
ein viertes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung,
Fig. 5
ein fünftes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung,
Fig. 6
ein sechstes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung und
Fig. 7
ein siebtes Ausführungsbeispiel einer erfindungsgemäßen Hydrauliksteuerung.
Embodiments of the invention illustrated in the drawings are explained below. Show it:
Fig. 1
A first embodiment of a hydraulic control according to the invention,
Fig. 2
A second embodiment of a hydraulic control according to the invention,
Fig. 3
A third embodiment of a hydraulic control according to the invention,
Fig. 4
A fourth embodiment of a hydraulic control according to the invention,
Fig. 5
A fifth embodiment of a hydraulic control according to the invention,
Fig. 6
A sixth embodiment of a hydraulic control according to the invention and
Fig. 7
A seventh embodiment of a hydraulic control according to the invention.

In allen Figuren werden für gleiche bzw. gleichartige Bauteile übereinstimmende Bezugszeichen verwendet.In all figures the same reference numerals are used for identical or similar components.

Fig. 1 zeigt eine Hydrauliksteuerung 1 für einen hydraulisch betätigt mittels einer Winde heb- und absenkbaren, in der Zeichnung nicht dargestellten Haken eines Krans. Dabei weist das insoweit nicht näher dargestellte Hydrauliksystem zumindest eine als Hydraulikmotor ausgebildete Arbeitsmaschine 15, welche die Winde 16 des Krans antreibt, und zumindest eine als Pumpe ausgebildete Antriebsmaschine auf. Die Arbeitsmaschine 15 ist mittels zweier, je nach Betriebszustand der Arbeitsmaschine 15 als Zulauf bzw. Rücklauf dienender, Anschlüsse über entsprechende Arbeitsleitungen 2 mittelbar oder unmittelbar mit wenigstens einer der Antriebsmaschinen verbunden. Fig. 1 shows a hydraulic control 1 for a hydraulically operated by means of a winch raised and lowered, not shown in the drawing hook of a crane. In this case, the hydraulic system not shown in detail so far, at least one designed as a hydraulic motor working machine 15 which drives the winch 16 of the crane, and at least one pump designed as a prime mover. The working machine 15 is connected by means of two, depending on the operating state of the working machine 15 as an inlet or return serving, connections via corresponding working lines 2 directly or indirectly connected to at least one of the drive machines.

In der Arbeitsleitung 2, die beim Absenken als Rücklauf dient, ist - wie in Fig. 1 dargestellt - ein Senkbremsventil 3 vorgesehen, welches über eine Steuerleitung 4 mit der anderen Arbeitsleitung 2 derart verbunden ist, dass das Senkbremsventil 3 aus seiner Sperrposition gegen eine Rückstellkraft durch den in dieser anderen Arbeitsleitung 2 herrschenden und über die Steuerleitung 4 weitergegebenen Steuerdruck in eine Durchflussposition zum Absenken des Hakens mittels der Winde 16, insbesondere Primärwinde, verlagerbar ist.In the working line 2, which serves as a return when lowering, is - as in Fig. 1 shown - a lowering brake valve 3 is provided, which is connected via a control line 4 with the other working line 2 such that the lowering brake valve 3 from its locking position against a restoring force by the ruling in this other working line 2 and passed over the control line 4 control pressure in a flow position for Lowering of the hook by means of the winch 16, in particular primary winds, is displaced.

Für eine Einstellung des auf das Senkbremsventil 3 wirkenden Steuerdrucks auf verschiedene Werte ist die Steuerleitung 4 mit einer Umschaltung 5 zwischen interner und externer Steuerung versehen. Hierzu zweigt von der Steuerleitung 4 zwischen der Umschaltung 5 und dem Senkbremsventil 3 eine zum in der Zeichnung nicht dargestellten Tank zurückführende Abflussleitung 6 ab, in der eine weitere Umschaltmöglichkeit 7 betreffend zwei parallel zueinander vorgesehene Blenden 8, 9 mit unterschiedlichen Durchmessern vorgesehen ist.For setting the control pressure acting on the lowering brake valve 3 to different values, the control line 4 is provided with a changeover 5 between internal and external control. For this purpose, branches off from the control line 4 between the switching 5 and the lowering brake valve 3 to a tank, not shown in the drawing recirculating drain line 6, in which a further switching possibility 7 is provided with respect to two mutually parallel apertures 8, 9 with different diameters.

Dabei kann zwischen der Blende 8 und der Blende 9 über die durch ein 3/2-Wegeventil ausgebildete Umschaltmöglichkeit 7 umgeschaltet werden, wobei ein schnelleres Absenken bei der kleineren Blende 9 und ein stabilerer Betrieb mit langsamerem Absenken bei der größeren Blende 8 erfolgt und wobei weiterhin das Signal der externen Steuerung derart beschränkt ist, dass kein vollständiges Öffnen des Senkbremsventils 3 möglich ist. Dabei beträgt der Durchmesser der kleineren Blende 9 ca. das 0,66-fache des Durchmessers der größeren Blende 8.It can be switched over the formed by a 3/2-way valve switching possibility 7 between the aperture 8 and the aperture 9, with a faster lowering at the smaller aperture 9 and a more stable operation with slower lowering at the larger aperture 8 and continues to be the signal of the external control is limited such that full opening of the lowering brake valve 3 is not possible. The diameter of the smaller aperture 9 is approximately 0.66 times the diameter of the larger aperture 8.

Durch die zum Tank zurückführende Abflussleitung 6 wird ein Teil des Drucks abgeleitet, so dass der auf das Senkbremsventil 3 wirkende Druck um diesen Teil reduziert ist. Wenn die größere Blende 8 in der zum Tank zurückführenden Abflussleitung 6 betrieben wird, resultiert ein größerer Durchlass, wodurch der auf das Senkbremsventil 3 wirkende Steuerdruck reduziert ist und das Absenken langsamer erfolgt.A portion of the pressure is discharged through the drain line 6 leading back to the tank, so that the pressure acting on the lowering brake valve 3 is reduced by this part. When the larger orifice 8 is operated in the drain line 6 leading to the tank, a larger passage results, whereby the control pressure acting on the lowering brake valve 3 is reduced and the lowering takes place more slowly.

Die Umschaltung 5 zwischen interner und externer Steuerung ist durch ein 3/2-Wegeventil gebildet. In einen Leitungsabschnitt 13 mit der größeren Blende 11 ist weiterhin ein Rückschlagventil 12 vorgesehen, welches nur in Richtung von der größeren Blende 11 zu dem 3/2-Wegeventil durchströmbar ist.The changeover 5 between internal and external control is formed by a 3/2-way valve. In a line section 13 with the larger aperture 11, a check valve 12 is further provided, which can only be flowed through in the direction of the larger aperture 11 to the 3/2-way valve.

Eine Steuerungsleitung 17 verbindet die beim herrschenden Betriebszustand der Arbeitsmaschine 15 als Rücklauf dienende Arbeitsleitung 2 für die Beaufschlagung der Umschaltmöglichkeit 7 durch den in der beim herrschenden Betriebszustand der Arbeitsmaschine 15 als Rücklauf dienenden Arbeitsleitung 2 aufgrund des Leitungswiderstandes resultierenden Staudruck mit der Umschaltmöglichkeit 7.A control line 17 connects the serving in the prevailing operating state of the working machine 15 as a return line 2 for the actuation of the switch 7 by the serving in the prevailing operating state of the machine 15 as a return working line 2 due to the line resistance back pressure with the switch 7.

Bei dem in Fig. 2 dargestellten weiteren Ausführungsbeispiel erfolgt in abweichender Weise die Umschaltung zwischen interner und externer Steuerung des durch die Steuerleitung 4 auf das Senkbremsventil 3 wirkenden Steuerdrucks über zwei parallel zueinander vorgesehene Blenden 10, 11 mit unterschiedlichem Durchmesser, wobei diese beiden Blenden 10, 11 über ein Wechselventil 14, welches in Abhängigkeit der anliegenden Drücke zwischen der Blende 10 und der Blende 11 umschaltet, in die Steuerleitung 4 münden. Dabei beträgt der Durchmesser der kleineren Blende 10 das 0,6-fache des Durchmessers der größeren Blende 11.At the in Fig. 2 illustrated another embodiment, the switching between internal and external control of acting through the control line 4 to the lowering brake valve 3 control pressure via two parallel apertures 10, 11 provided with different diameters, wherein these two apertures 10, 11 via a shuttle valve 14, in a different manner which switches as a function of the applied pressures between the diaphragm 10 and the diaphragm 11, open into the control line 4. The diameter of the smaller aperture 10 is 0.6 times the diameter of the larger aperture 11.

Das Wechselventil 14 wird hier durch die Umschaltung 5 und den je nach Schaltzustand der Umschaltung 5 wirkenden Druck "betätigt".The shuttle valve 14 is "actuated" here by the switchover 5 and the pressure acting on the switchover 5 depending on the switching state.

Das in Fig. 3 gezeigte dritte Ausführungsbeispiel zeigt eine vereinfachte Version des Gegenstandes nach Fig. 1, wobei die in Fig. 1 gezeigte Umschaltung zwischen interner und externer Steuerung entfallen ist und stattdessen lediglich eine feste Blende 10 vorgesehen ist. Ergänzend ist eine Antriebsmaschine 15 sowie eine hiervon betätigte Winde 16 gezeigt.This in Fig. 3 shown third embodiment shows a simplified version of the article after Fig. 1 , where the in Fig. 1 shown switching between internal and external control is omitted and instead only a fixed aperture 10 is provided. In addition, a prime mover 15 and a winch 16 actuated therefrom are shown.

Das in Fig. 4 gezeigte vierte Ausführungsbeispiel zeigt eine alternative Ausgestaltung, wobei die in der Abflussleitung 6 vorgesehene Umschaltmöglichkeit 7 als ein 2/2-Wegeventil ausgebildet ist, mit dem eine Blende 9 aktiviert bzw. deaktiviert werden kann, wodurch der auf das Senkbremsventil 3 wirkende Druck veränderbar ist.This in Fig. 4 shown fourth embodiment shows an alternative embodiment, wherein provided in the drain line 6 switching option 7 is designed as a 2/2-way valve, with which a diaphragm 9 is activated or deactivated can be, whereby the pressure acting on the lowering brake valve 3 is changeable.

Bei der in Fig. 5 gezeigten Variante ist die Umschaltmöglichkeit 7 als "Blackbox" ausgebildet, wobei die Steuerungsleitung 17 nur angedeutet ist und beliebig, z. B. elektrisch, hydraulisch, pneumatisch oder anderweitig, beaufschlagt werden kann. Auch die Steuerung der Beaufschlagung kann in beliebiger Weise erfolgen.At the in Fig. 5 variant shown, the switching option 7 is designed as a "black box", the control line 17 is only indicated and arbitrarily, for. B. electrically, hydraulically, pneumatically or otherwise, can be acted upon. The control of the loading can be done in any way.

Die in Fig. 6 gezeigte Variante ist der Ausgestaltung des in Fig. 4 gezeigten Ausführungsbeispiels ähnlich, wobei die Umschaltmöglichkeit 7 zwei parallel zueinander vorgesehene Blenden 8, 9 mit unterschiedlichen Durchmessern betrifft. Dabei kann die Blende 9, welche den kleineren Durchmesser hat, über die durch ein 2/2-Wegeventil ausgebildete Umschaltmöglichkeit 7 zwischen aktiviertem Zustand und deaktiviertem Zustand umgeschaltet werden, wobei ein schnelleres Absenken bei der größeren Blende 8 (und deaktivierter kleinerer Blende 9) und ein stabilerer Betrieb mit langsamerem Absenken bei aktiviertem Zustand der kleineren Blende 9 erfolgt.In the Fig. 6 variant shown is the embodiment of in Fig. 4 similar embodiment shown, wherein the switching possibility 7 relates to two mutually parallel apertures 8, 9 with different diameters. In this case, the aperture 9, which has the smaller diameter, are switched over the formed by a 2/2-way valve switching option 7 between activated state and deactivated state, with a faster lowering at the larger aperture 8 (and deactivated smaller aperture 9) and a more stable operation with slower lowering with activated state of the smaller aperture 9 takes place.

Fig. 7 zeigt eine Abwandlung des Gegenstandes nach Fig. 6, wobei hier die Umschaltmöglichkeit 7 als kombiniertes Bauteil ausgeführt ist und einen schaltbaren hydraulischen Widerstand in Form der Blende 9 umfasst. Die Umschaltmöglichkeit 7 ist dabei mechanisch an den Ventilweg des Senkbremsventils 3 gekoppelt. Die Koppelung kann jedoch auch z. B. hydraulisch oder in beliebiger anderer Weise realisiert sein. Solange die Umschaltmöglichkeit 7 auf "Durchlässig" gestellt ist, wirkt die größere Blende 8. Sobald jedoch durch die Umschaltmöglichkeit 7 die kleinere Blende 9 mit der größeren Blende 8 in Reihe geschaltet ist, wirkt nur noch die kleinere Blende 9, da sie den größeren hydraulischen Widerstand hat. Fig. 7 shows a modification of the subject Fig. 6 , Here, the switchover 7 is designed as a combined component and includes a switchable hydraulic resistance in the form of the aperture 9. The switching possibility 7 is mechanically coupled to the valve path of the lowering brake valve 3. However, the coupling can also z. B. be implemented hydraulically or in any other way. As long as the switchover option 7 is set to "Permeable", the larger aperture 8 acts. However, as soon as the smaller aperture 9 is connected in series with the larger aperture 8 by the switchover 7, only the smaller aperture 9, since it affects the larger hydraulic Has resistance.

Claims (14)

  1. Hydraulic control device (1) of a hydraulic system for a hydraulically actuated raisable and lowerable hook of a crane, wherein the hydraulic system comprises at least one working machine (15), configured as a hydraulic motor, and at least one drive machine, configured in particular as a pump, wherein the working machine (15) is connected to at least one of the drive machines, indirectly or directly, by means of two connections, which, depending on the operational state of the working machine (15), serve as intake or return elements, by way of corresponding working lines (2), and wherein in the one working line (2) a lowering brake valve (3) is provided, which is connected via a control line (4) to the other working line (2) in such a way that the lowering brake valve (3) can be moved, against a resetting force, out of its blocking position by the control pressure prevailing in this other working line (2) and reproduced via the control line (4), into a throughflow position for the lowering of the hook by means of a winch (16), preferably a primary winch, characterised in that an outflow line (6) leading back to a tank branches off from the control line (4), and wherein, for the adjustment of the control pressure taking effect on the lowering brake valve (3) to different values, the outflow line (6) is provided with a switchover capability element (7), with which the effective hydraulic resistance in the outflow line (6) can be changed by controlling or regulating to at least two different values.
  2. Hydraulic control device (1) according to the preceding claim, characterised in that the working line (2) serving as an intake in the prevailing operating state of the working machine (15) is subjected to a volume flow, which controls the working speed and which in at least certain operating states can be changed by means of an accelerator pedal.
  3. Hydraulic control device (1) according to claim 1, characterised in that the working line (2) serving as an intake in the prevailing operating state of the working machine (15) is subjected to a volume flow, which controls the working speed and which in at least certain operating states can be changed by means of a joystick.
  4. Hydraulic control device (1) according to any one of the preceding claims, characterised in that two hydraulic resistors, provided in the outflow line (6), in particular parallel to one another and preferably diaphragms (8,9) with different diameters, wherein the one hydraulic resistor is always active and a further switchover capability element (7) is assigned to the other hydraulic resistor, with which it is possible to switch over between the activated state and the deactivated state of the other hydraulic resistor, in particular for switching between "stable operation" and slower lowering with the activated state of the other hydraulic resistor, and "faster lowering" with the deactivated state of the other hydraulic resistor.
  5. Hydraulic control device (1) according to any one of the preceding claims, characterised in that the switchover capability element 7 is configured as a combined component and comprises a switchable hydraulic resistor, in particular a diaphragm 9.
  6. Hydraulic control device (1) according to any one of the preceding claims, characterised in that the switchover capability element 7 is coupled to the valve path of the lowering brake valve 3.
  7. Hydraulic control device (1) according to any one of the preceding claims, characterised in that a control line (17), which, as a working line (2), serves as a return element with the prevailing operating state of the working machine (15), and connects to the switchover capability element (7), for imposing on the switchover capability element (7) the dynamic pressure resulting in the working line (2), serving a return element in the prevailing operating state of the working machine (15), due to the line resistance.
  8. Hydraulic control device (1) according to any one of the preceding claims, characterised in that the value of the smaller hydraulic resistor amounts to 0.66 times or 0.85 times the value of the larger hydraulic resistor, or, respectively, the diameter of the smaller diaphragm (9) amounts to 0.66 times or 0.85 times the diameter of the larger diaphragm (8).
  9. Hydraulic control device (1) according to any one of the preceding claims, characterised in that for the switching over between internal and external control of the control pressure taking effect by way of the control line (4) on the lowering brake valve (3), two hydraulic resistors are provided, parallel to one another, preferably diaphragms (10, 11) with different diameters, of which the larger hydraulic resistor or the diaphragm (10) with the smaller diameter can be switched over by means of a switchover capability element (5) between an activated state and a deactivated state, wherein these two hydraulic resistors or diaphragms (10, 11) open by way of a changeover valve into the control line (4).
  10. Hydraulic control device (1) according to any one of claims 1 to 8, characterised in that for the switching over between internal and external control of the control pressure taking effect by way of the control line (4) on the lowering brake valve (3), a changeover is provided between two hydraulic resistors, connected to a 3/2-way valve and provided parallel to one another, or diaphragms (10, 11) with different diameters.
  11. Hydraulic control device (1) according to claim 9 or 10, characterised in that the value of the smaller hydraulic resistor amounts to 0.6 times the value of the larger hydraulic resistor, or, respectively, the diameter of the smaller diaphragm (10) amounts to 0.6 times the diameter of the larger diaphragm (11).
  12. Hydraulic control device (1) according to any one of claims 9 to 11, characterised in that a non-return valve 12 is also provided in the line section 13 with the smaller hydraulic resistor, in particular with the larger diaphragm 11, this valve only being capable of being flowed through in the direction from the smaller hydraulic resistor, in particular the larger diaphragm 11, to the 3/2-way valve.
  13. Hydraulic control device (1) according to any one of the preceding claims, characterised in that an individual pump is allocated to the external control, by which the control is supplied.
  14. Hydraulic control device (1) according to any one of the preceding claims, characterised in that the external control is connected to the drive machine, which is configured as a pump.
EP15182321.8A 2015-08-25 2015-08-25 Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane Active EP3135625B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP15182321.8A EP3135625B1 (en) 2015-08-25 2015-08-25 Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane
CN201510635222.5A CN106477458B (en) 2015-08-25 2015-09-30 The hydraulic control device of hydraulic operation lifting suspension hook for crane
RU2018110255A RU2679942C1 (en) 2015-08-25 2016-08-16 Hydraulic controller for hydraulically controlled raised and lowered crane hook
US15/754,421 US10974936B2 (en) 2015-08-25 2016-08-16 Hydraulic controller for hydraulically actuated liftable and lowerable hook of crane
AU2016312887A AU2016312887B2 (en) 2015-08-25 2016-08-16 Hydraulic controller for a hydraulically actuated liftable and lowerable hook of a crane
CA2996374A CA2996374C (en) 2015-08-25 2016-08-16 Hydraulic controller for a hydraulically actuated liftable and lowerable hook of a crane
PCT/EP2016/069399 WO2017032641A1 (en) 2015-08-25 2016-08-16 Hydraulic controller for a hydraulically actuated liftable and lowerable hook of a crane

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15182321.8A EP3135625B1 (en) 2015-08-25 2015-08-25 Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane

Publications (2)

Publication Number Publication Date
EP3135625A1 EP3135625A1 (en) 2017-03-01
EP3135625B1 true EP3135625B1 (en) 2018-05-23

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EP15182321.8A Active EP3135625B1 (en) 2015-08-25 2015-08-25 Hydraulic device for a hydraulically actuated raisable and lowerable hook of a crane

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US (1) US10974936B2 (en)
EP (1) EP3135625B1 (en)
CN (1) CN106477458B (en)
AU (1) AU2016312887B2 (en)
CA (1) CA2996374C (en)
RU (1) RU2679942C1 (en)
WO (1) WO2017032641A1 (en)

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DE102017130485B4 (en) 2017-12-19 2024-05-08 Wessel-Hydraulik Gmbh Hydraulic circuit arrangement for lifting and lowering a load

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Publication number Publication date
US10974936B2 (en) 2021-04-13
WO2017032641A1 (en) 2017-03-02
CA2996374A1 (en) 2017-03-02
CN106477458A (en) 2017-03-08
CN106477458B (en) 2019-02-12
AU2016312887B2 (en) 2018-12-20
CA2996374C (en) 2020-04-07
RU2679942C1 (en) 2019-02-14
US20180257915A1 (en) 2018-09-13
EP3135625A1 (en) 2017-03-01
AU2016312887A1 (en) 2018-03-15

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