EP3135625B1 - Commande hydraulique d'un crochet de grue abaissable et relevable hydrauliquement - Google Patents

Commande hydraulique d'un crochet de grue abaissable et relevable hydrauliquement 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
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EP15182321.8A
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German (de)
English (en)
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EP3135625A1 (fr
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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Publication date
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Priority to EP15182321.8A priority Critical patent/EP3135625B1/fr
Priority to CN201510635222.5A priority patent/CN106477458B/zh
Priority to US15/754,421 priority patent/US10974936B2/en
Priority to CA2996374A priority patent/CA2996374C/fr
Priority to AU2016312887A priority patent/AU2016312887B2/en
Priority to PCT/EP2016/069399 priority patent/WO2017032641A1/fr
Priority to RU2018110255A priority patent/RU2679942C1/ru
Publication of EP3135625A1 publication Critical patent/EP3135625A1/fr
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Publication of EP3135625B1 publication Critical patent/EP3135625B1/fr
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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)

Claims (14)

  1. Commande hydraulique (1) d'un système hydraulique pour un crochet de grue abaissable et relevable hydrauliquement, où le système hydraulique comprend au moins une unité de travail réalisée sous la forme d'un moteur hydraulique (15) et au moins une unité d'entraînement, en particulier conçue sous la forme d'une pompe, où l'unité de travail (15) est reliée directement ou indirectement à au moins l'une des unités d'entraînement au moyen de deux branchements servant d'alimentation ou de retour, selon l'état de fonctionnement de l'unité de travail (15), sur des lignes de travail respectives (2), et où dans la première ligne de travail (2) est prévue une soupape de frein d'abaissement (3), laquelle est reliée via une ligne de commande (4) à l'autre ligne de travail (2) de telle sorte que la soupape de frein d'abaissement (3) peut être déplacée grâce à la pression de commande régnant dans ladite autre ligne de travail (2) et transmise via la ligne de commande (4) de sa position fermée en allant à l'encontre d'une force de rappel à une position d'écoulement pour l'abaissement du crochet au moyen d'un treuil (16), de préférence un treuil primaire, caractérisée en ce qu'une ligne d'évacuation (6) retournant vers un réservoir part de la ligne de commande (4), où pour un réglage de la pression de commande de la soupape de frein d'abaissement (3) à des valeurs différentes, la ligne d'évacuation (6) est dotée d'un dispositif de commutation (7) avec lequel la résistance hydraulique efficace dans la ligne d'évacuation (6) peut être modifiée par commande ou régulation entre au moins deux valeurs différentes.
  2. Commande hydraulique (1) selon la revendication précédente, caractérisée en ce que la ligne de travail (2) servant d'alimentation selon l'état de fonctionnement en vigueur de l'unité de travail (15) se voit appliquer un débit volumique contrôlant la vitesse de travail, lequel peut être modifié au moins dans certains états de fonctionnement par l'intermédiaire d'une pédale d'accélérateur.
  3. Commande hydraulique (1) selon la revendication 1, caractérisée en ce que la ligne de travail (2) servant d'alimentation selon l'état de fonctionnement en vigueur de l'unité de travail (15) se voit appliquer un débit volumique contrôlant la vitesse de travail, lequel peut être modifié au moins dans certains états de fonctionnement par l'intermédiaire d'un levier ou d'une manette de commande.
  4. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que dans la ligne d'évacuation (6) sont prévus deux dispositifs de résistance hydraulique, en particulier prévus parallèlement l'un à l'autre, de préférence des diaphragmes (8, 9) de diamètres différents, où un premier dispositif de résistance hydraulique est toujours actif et un autre dispositif de commutation (7) est associé à l'autre dispositif de résistance hydraulique, grâce auquel l'autre dispositif de résistance hydraulique peut être commuté entre un état activé et un état désactivé, en particulier pour la commutation entre un « fonctionnement stable » et un abaissement plus lent dans l'état activé de l'autre dispositif de résistance hydraulique et un « abaissement plus rapide » dans l'état désactivé de l'autre dispositif de résistance hydraulique.
  5. Commande hydraulique (1) selon la revendication précédente, caractérisée en ce que le dispositif de commutation (7) est réalisé sous la forme d'un composant combiné et comprend un dispositif de résistance hydraulique commutable, en particulier un diaphragme (9).
  6. Commande hydraulique (1) selon la revendication 4 ou 5, caractérisée en ce que le dispositif de commutation (7) est couplé à la course de soupape de la soupape de frein d'abaissement (3).
  7. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une ligne de commande (17) de la ligne de travail (2) servant de retour selon l'état de fonctionnement en vigueur de l'unité de travail (15) pour l'actionnement du dispositif de commutation (7) via la ligne de travail (2) servant de retour selon l'état de fonctionnement en vigueur de l'unité de travail (15) sur la base de la pression dynamique résultant de la résistance de ligne est reliée avec le dispositif de commutation (7).
  8. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la valeur de la plus petite résistance hydraulique est égale à 0,66 fois ou 0,85 fois la valeur de la plus grande résistance hydraulique ou le diamètre du plus petit diaphragme (9) est égal à 0,66 fois ou 0,85 fois le diamètre du plus grand diaphragme (8).
  9. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que pour la commutation entre la commande interne et externe de la pression de commande exercée par la ligne de commande (4) sur la soupape de frein d'abaissement (3), sont prévus deux dispositifs de résistance hydraulique parallèles, de préférence des diaphragmes (10, 11) de diamètres différents, où le plus grand de ces dispositifs de résistance hydraulique ou le diaphragme (10) de plus petit diamètre peut être commuté via un dispositif de commutation (5) entre l'état activé et l'état désactivé, où lesdits deux dispositifs de résistance hydraulique ou diaphragmes (10, 11) débouchent sur une vanne à deux voies dans la ligne de commande (4).
  10. Commande hydraulique (1) selon l'une quelconque des revendications 1 à 8, caractérisée en ce que pour la commutation entre la commande interne et externe de la pression de commande exercée par la ligne de commande (4) sur la soupape de frein d'abaissement (3), un changement entre deux dispositifs de résistance hydraulique ou diaphragmes (10, 11) de différents diamètres, parallèles, raccordés par un distributeur à 3/2 voies est prévu.
  11. Commande hydraulique (1) selon la revendication 9 ou 10, caractérisée en ce que la valeur de la plus petite résistance hydraulique est égale à 0,6 fois la valeur de la plus grande résistance hydraulique ou le diamètre du plus petit diaphragme (10) est égal à 0,6 fois le diamètre du plus grand diaphragme (11).
  12. Commande hydraulique (1) selon l'une quelconque des revendications 9 à 11, caractérisée en ce que dans la section de ligne (13) avec la plus petite valeur de résistance hydraulique, en particulier avec le plus grand diaphragme (11) est en outre prévu un clapet anti-retour (12), lequel ne peut être traversé que dans le sens de la plus petite valeur de résistance hydraulique, en particulier le plus grand diaphragme (11), vers le distributeur à 3/2 voies.
  13. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la commande externe est associée à une pompe dédiée, à partir de laquelle elle est alimentée.
  14. Commande hydraulique (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la commande externe est raccordée à l'unité d'entraînement réalisée sous la forme d'une pompe.
EP15182321.8A 2015-08-25 2015-08-25 Commande hydraulique d'un crochet de grue abaissable et relevable hydrauliquement Active EP3135625B1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP15182321.8A EP3135625B1 (fr) 2015-08-25 2015-08-25 Commande hydraulique d'un crochet de grue abaissable et relevable hydrauliquement
CN201510635222.5A CN106477458B (zh) 2015-08-25 2015-09-30 用于起重机的液压操作升降吊钩的液压控制装置
CA2996374A CA2996374C (fr) 2015-08-25 2016-08-16 Commande hydraulique pour un crochet de grue, actionne hydrauliquement et pouvant etre souleve et abaisse
AU2016312887A AU2016312887B2 (en) 2015-08-25 2016-08-16 Hydraulic controller for a hydraulically actuated liftable and lowerable hook of a crane
US15/754,421 US10974936B2 (en) 2015-08-25 2016-08-16 Hydraulic controller for hydraulically actuated liftable and lowerable hook of crane
PCT/EP2016/069399 WO2017032641A1 (fr) 2015-08-25 2016-08-16 Commande hydraulique pour un crochet de grue, actionné hydrauliquement et pouvant être soulevé et abaissé
RU2018110255A RU2679942C1 (ru) 2015-08-25 2016-08-16 Гидравлический контроллер для гидравлически управляемого поднимаемого и опускаемого крюка крана

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Application Number Priority Date Filing Date Title
EP15182321.8A EP3135625B1 (fr) 2015-08-25 2015-08-25 Commande hydraulique d'un crochet de grue abaissable et relevable hydrauliquement

Publications (2)

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

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

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DE102017130485B4 (de) 2017-12-19 2024-05-08 Wessel-Hydraulik Gmbh Hydraulische Schaltungsanordnung zum Heben und Senken einer Last

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

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