EP0241023B1 - Procédé de commande pour grues à câble automatiques et commande hydraulique - Google Patents

Procédé de commande pour grues à câble automatiques et commande hydraulique Download PDF

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Publication number
EP0241023B1
EP0241023B1 EP87105231A EP87105231A EP0241023B1 EP 0241023 B1 EP0241023 B1 EP 0241023B1 EP 87105231 A EP87105231 A EP 87105231A EP 87105231 A EP87105231 A EP 87105231A EP 0241023 B1 EP0241023 B1 EP 0241023B1
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EP
European Patent Office
Prior art keywords
valve
pressure
switch lever
automatic cable
working cylinders
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87105231A
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German (de)
English (en)
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EP0241023A3 (en
EP0241023A2 (fr
Inventor
Jakob Mairhofer
Josef Werlberger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WERLBERGER, JOSEF
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Individual
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Publication of EP0241023A3 publication Critical patent/EP0241023A3/de
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Publication of EP0241023B1 publication Critical patent/EP0241023B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C21/00—Cable cranes, i.e. comprising hoisting devices running on aerial cable-ways

Definitions

  • the invention relates to a method for controlling a cable crane machine according to the preamble of claim 1 and a hydraulic control according to the preamble of claim 2.
  • Such a generic method or the corresponding hydraulic control is known from AT-PS 328 505.
  • This known automatic control of a crane cable car or crane cable machine for load transport in which a clamping device for locking the cable crane machine and a load pendulum or a load hook connectable with it are provided, has the disadvantage that when the operating position is reached , that is, the position in which the cable crane automat should abseil or lift the load, for safety reasons only a delay time until the actual switching position in which the working cylinders are actuated is provided.
  • This delay time is essential since, when the cable crane machine is at a standstill, at least a certain decay of the vibrations of the suspension cable must first be waited for before the clamping jaw device for clamping the cable crane machine on the suspension cable can be pivoted in and fixed.
  • Hydraulic controls with a different design for automatic cable cranes are known, for example, from AT-PSn 378 943 and 379 994.
  • the invention is based on the object of improving the safety-related aspects of the cable crane machine in such a way that even swinging movements on the load hook do not activate of the cable crane machine can bring about with sufficient security and that also with regard to reaching the switching position for loading the working cylinder from the "zero" position, this can be carried out with a high degree of certainty, the structural design permitting a largely controllable, gradual control process , where leakage losses can be largely prevented.
  • the first delay time is advantageously realized by the components of a delay path between the tappet actuating the pressure valve and the corresponding pretensioning of a control piston 18.
  • the second delay time which is also considered proportional can be viewed to a second deceleration distance is determined by the distance or time that a control lever needs or has to cover in order to reach the effective range of a control pin that can be actuated by the load pendulum.
  • the control lever itself can, depending on its "zero" position, be designed as a straight-line control rod or with a part-circular recess.
  • the use of separate ball seat valves and their control ensures that leakage losses do not occur even in the case of long idle times in the operating position in which, for example, the working cylinders are pressurized.
  • control lever with a pivoting movement in the manner of clock hands around its axis or with a slight oblique deflection against the axis allows the control lever to be movable from an operative connection with the shifting gate when the load pendulum is retracted reliably and a corresponding release mechanism for the clamping jaws is actuated can gradually return to its zero position under the pre-tensioned control piston of the valves.
  • the working cylinders for pivoting the clamping jaws or actuating the clamping jaws themselves are expediently coupled to one another in such a way that an overflow to the working cylinder of the clamping basin is only released after the reliable engagement and pivoting-in, so that the fixing process only then begins.
  • This ensures that oscillating movements of the suspension cable have at least largely subsided and the clamping jaws can thus be reliably fixed on the suspension cable.
  • the cable crane automat according to the invention can alternatively be equipped for single-cable operation, two-cable operation or three-cable operation.
  • the second delay time which is essential to the invention can therefore be defined as the time which the control lever requires, to get from the switch position to a control pin that is operatively connected to the load pendulum. During this time, an uncontrolled activation of the cable crane machine is not possible for safety reasons.
  • the invention therefore has the advantages that the shift lever can act on a switching piston of the valves by the control via a shift gate so that the pressure relief valve is always closed and the pressure valve subsequently opens in order to enable the working cylinder to be acted upon safely via the opened valve .
  • This process does not start suddenly, as with conventional control valves, but takes place gradually, so that pressure losses are avoided.
  • the release of the shift lever from its locked position on the shift gate by a lateral movement at an angle to its axis is effected via inclined surfaces of a linkage and the control bolt, so that the shift lever is pressed from its position on or in the shift gate and both due to the pressure of the pressure fluid and a compression spring is returned to its initial position (zero position).
  • the shift lever can therefore only be taken from the shift gate when the operating position of the cable crane machine, which is understood to mean the place at which the load is to be picked up or roped, is only taken back when the shift gate is back in its right due to the movement of the timer piston Has reached the end position. In this end position, the shift lever is pressed by a spring in front of the front face of the shift gate.
  • a major advantage of the hydraulic control is that the entire control is housed in a closed, compact block, which also includes the mechanical components. This makes it easier to repair reached. An additional rope break protection can also be easily retrofitted. It is also achieved that the switching operations can only take place when the pressure accumulator is charged and without further control of a pressure switch.
  • the time between the unlocking of the load hook or the clamping on the supporting cable and between the earliest possible relocking or releasing the clamping on the supporting cable is carried out via at least one adjustable throttle, so that an automatic setting of the switching time is realized.
  • the invention therefore makes it possible to provide an optimal hydraulic control for a cable crane machine which has to be clamped on the supporting cable for lowering or lifting a load hook, during which time the load hook lock is opened.
  • the hydraulic control 1 serves to clamp an automatic cable crane for lowering or lifting a load hook, which is not shown in the drawings, on the supporting cable and to open the lock of the load hook during this time.
  • an oil pump 2 continuously pumps the hydraulic fluid, which in the example is a pressure oil, from the tank 3 into the compactly designed control block.
  • the control block essentially comprises all lines, time cylinders and valves as well as the mechanical control mechanisms in order to ensure the full function of the automatic cable crane.
  • the pressure oil from the pump 2 reaches a pressure accumulator via a high pressure filter 4 and a check valve 5.
  • the pressure oil delivered into the pressure accumulator 6 has the primary function of applying the appropriate pressure oil to the working cylinders 22 to 24 when the operating position is reached.
  • the pressure accumulator 6 is connected to a pressure valve 7.
  • This pressure valve 7 is designed as a check valve and has a valve ball 8 which, in the position shown in FIG. 1, bears against the valve seat 29, so that the valve is closed.
  • the pressure oil pumped into the time cylinder 10 pushes its piston 9 to the right and thus moves the piston rod 11 and the shifting link 16 articulated thereon against the force of a spring 12 to the right.
  • 1 shows the "zero" position of the piston 9 or of a shift lever or shift finger 15 which can be controlled via the shift link 16.
  • the pressure relief valve 20 for returning the pressure oil from the working cylinders 22 to 24 into the tank 3 is open in this position, or is closed again after relieving the pressure on the working cylinders.
  • the delay distance V1 must first be covered.
  • the valve tappet 30 which is decisive for this is connected to the control piston 18, through which the switching lever 15 can be guided, for example, so that a force-fitting actuation of both elements is possible.
  • the control piston 18 is also biased toward the right by a spring 19. As a result, this spring force 19 acts against a force acting through the switching link 16 on the control lever 15 and directed to the left.
  • the control lever 15 is moved from its "zero" position into the position of the shift lever 15 shown in solid line in FIG. 2 through the shift gate.
  • the shift lever 15 performs a clockwise movement about its axis 48, so to speak.
  • the pressure relief valve 20 is closed. This is most suitably done with a minimal movement out of the "zero" position, so that almost the entire deceleration distance or the first deceleration time resulting therefrom taking into account the spring characteristic 19 is available in terms of safety.
  • This first delay can vary depending on the design of the individual components between approx. 2 to 30 seconds.
  • the first delay time can therefore be defined as the period of time that the control lever 15 needs to get from its "zero" position to the "switching position". From a safety point of view, this first delay time primarily serves to calm the suspension cable after the operating position of the cable crane machine has been reached. Only when the pressure valve 7 is open, after the first delay time has elapsed, for example, the working piston 22 of the pivoting cylinder is pressurized with pressure oil, the clamping jaw cylinder itself being actuated only after an overflow 26 has been reached.
  • pressure oil therefore flows from the pressure accumulator 6 via the valve 7 to the working cylinders 22 to 24 and there causes the automatic cable crane to be clamped to the supporting cable and the load hook to be unlocked.
  • this pressure oil reaches the second valve 20, which is still blocked, however, since it only has the function of depressurizing the working cylinders when the load hook is retracted.
  • the time that should elapse between reaching the operating position of the cable crane machine and releasing the clamping can therefore be regulated by means of the adjustable throttle valve 14.
  • the load hook triggers the control pin 40 or trigger via a shift linkage 41 and a slope 43 (FIG. 3, FIG. 4). That is, by shifting the shift linkage 41 upward against a spring 42 (FIG. 3), the slope 43 comes into sliding engagement with a slope 44 on the control piston 40 and pushes it against a spring 45 to the right.
  • the shift lever 15 guided according to FIG. 3 on the front edge 17 of the shifting link 16 is pressed over the ring surface 52 of the control bolt 40 to the right into a certain oblique position against the spring force 46.
  • the guide opening 49 within the control piston is held so that the slight inclination from the vertical to the axis 48 can still be realized without the control lever 15 jamming in the shifting link or the control piston 18.
  • the control pin 40 By moving the control pin 40, which is slidably movable in a guide 51, for example of the housing, the lower end 50 of the control lever 15 is brought out of engagement with the front edge 17 of the switching link 16 and is inserted into a groove 47 of the switching link.
  • the spring force 19 causes the control piston to shift to the right, so that the valve 7 is first closed and the pressure relief valve 20 is gradually opened so that the working piston 22 up to 24 can be relieved of pressure.
  • the cable crane machine is now ready to drive again. While driving on the oil pump 2, the partially emptied pressure accumulator 6 is filled again and then the timer cylinder 10, so that the shift lever 15 returns to a standby position in which its "zero" position according to FIG. 1 with system the front edge 17 of the shift gate 16 is reached.
  • a second delay time or a second delay line V2 is structurally provided in order to get a handle on vibration-like inward and outward movements of the load hook or load pendulum cylinder when the rope crane machine reaches the operating position.
  • This delay section is necessary from a safety point of view, since, for example, in the starting phase of lowering a load of the load hook via the shift linkage 41, it could cause a shift movement, as shown in FIG. 4. This would lead to the locking of the valve 7 and the opening of the valve 20 and thus the release of the jaw cylinder 23, which could have catastrophic consequences. In order to avoid this, the return of the shift lever 15 (FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Control And Safety Of Cranes (AREA)
  • Jib Cranes (AREA)
  • Load-Engaging Elements For Cranes (AREA)

Claims (8)

  1. Procédé de commande d'un mécanisme automatique de blondin, dans lequel, lors de l'atteinte de la position de fonctionnement, après écoulement d'un temps de retard, l'alimentation en vue du travail des vérins (22, 23, 24) d'un dispositif de serrage est libérée avec un fluide sous pression, puis, par mise en place du crochet de chargement, le retour du fluide sous pression hors des vérins (22, 23, 24) alimentés s'effectue dans le réservoir à fluide sous pression (3), caractérisé en ce que la libération du retour du fluide sous pression hors des vérins (22, 23, 24) alimentés est effectuée avec un premier temps de retard (V1) après blocage de l'alimentation des vérins (22, 23, 24) et en ce que le déclenchement de la libération du retour, par une charge ou une oscillation du crochet de chargement, est prévue après écoulement d'un deuxième temps de retard (V2).
  2. Commande hydraulique pour mécanisme automatique de blondin, qui, en position de fonctionnement du mécanisme, après écoulement d'un premier temps de retard réglable (V1), alimente les vérins (22, 23, 24), par l'intermédiaire d'une soupape de pression (7), en fluide sous pression venant d'un accumulateur à pression (6), avec une soupape de détente (20), pour refouler le fluide sous pression des vérins (22, 23, 24) dans un réservoir (3) et avec un levier de manoeuvre (15) pour l'actionnement d'au moins la soupape de pression (7), le levier de manoeuvre (15) étant relié fonctionnellement à un vérin de manoeuvre temporisé (10), caractérisée en ce que les soupapes de pression (7) et de détente (20) sont réalisées sous forme de soupapes à une voie séparées et sont déplaçables, par l'intermédiaire d'un piston de manoeuvre (18) précontraint, en tenant compte du premier temps de retard (V1), respectivement dans une position d'ouverture complémentaire de l'une et une position de fermeture complémentaire de l'autre soupape, en ce qu'est prévue une coulisse de manoeuvre (16), couplée au vérin de manoeuvre temporisé (10), en vue d'assurer la commande du levier de manoeuvre (15), le levier de manoeuvre (15) pouvant être amené, par une tige de commande (40), hors de liaison fonctionnelle avec la coulisse de manoeuvre (16), et en ce qu'entre une tringlerie de manoeuvre (41, 43) actionnable par le pendule de charge et la tige de manoeuvre (40) s'effectue seulement après écoulement d'un deuxième temps de retard réglable (V2) une liaison fonctionnelle, pour la "manoeuvre de libération" d'au moins un vérin de travail (22, 23, 24).
  3. Commande hydraulique selon la revendication 2, caractérisée en ce que, par une remise en place, ou oscillation du crochet de chargement, le levier de manoeuvre (15) est écarté par la tige de commande (40) latéralement de la coulisse de manoeuvre (16), de sorte que le levier de manoeuvre (15) revient à sa position initiale, au moyen du piston de manoeuvre (18) précontraint par un ressort, la soupape de pression (7) se fermant et la soupape de détente (20) s'ouvrant, de sorte que le fluide sous pression peut revenir des vérins (22 à 24), dans le réservoir (3).
  4. Commande hydraulique selon la revendication 2 ou 3, caractérisée en ce que le piston de manoeuvre (18), précontraint en direction de la soupape de détente (20), est réalisé, du côté de la soupape de pression (7), de telle façon que le fluide sous pression assiste un ressort (19) du piston de manoeuvre (18), en direction de la pression, jusqu'à ce que la soupape de détente (20) soit ouverte.
  5. Commande hydraulique selon l'une des revendications 2 à 4, caractérisée en ce que le levier de manoeuvre (15) est monté de façon qu'il peut effectuer tant un mouvement de pivotement autour de son axe (48) qu'également un mouvement d'articulation radial par rapport à celui-ci.
  6. Commande hydraulique selon l'une des revendications 2 à 5, caractérisée en ce que le levier de manoeuvre (15) est amené, dans sa position "zéro", malgré la précontrainte d'un ressort (46), lors d'un déplacement de la coulisse de manoeuvre (16), en coulissant dans un évidement (47) de la coulisse de manoeuvre (16)
  7. Commande hydraulique selon l'une des revendications 2 à 6, caractérisée en ce que lors de l'atteinte de la position de fonctionnement du mécanisme automatique du blondin, le vérin de manoeuvre temporisé (10) a déplacé la coulisse de manoeuvre (16) de telle façon que le levier de manoeuvre (15) appuie, avec transmission d'effort, du fait de la force élastique (46), contre une surface d'entraînement (17) de la coulisse de manoeuvre.
  8. Commande hydraulique selon l'une des revendications 2 à 7, caractérisée en ce que le premier et le deuxième temps de retard sont réglables par, respectivement, l'intermédiaire d'une soupape d'étranglement commune (14) et de deux soupapes d'étranglement séparées.
EP87105231A 1986-04-08 1987-04-08 Procédé de commande pour grues à câble automatiques et commande hydraulique Expired - Lifetime EP0241023B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT913/86 1986-04-08
AT0091386A AT389863B (de) 1986-04-08 1986-04-08 Hydraulische steuerung fuer seilkran-automaten

Publications (3)

Publication Number Publication Date
EP0241023A2 EP0241023A2 (fr) 1987-10-14
EP0241023A3 EP0241023A3 (en) 1990-05-30
EP0241023B1 true EP0241023B1 (fr) 1993-09-22

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EP87105231A Expired - Lifetime EP0241023B1 (fr) 1986-04-08 1987-04-08 Procédé de commande pour grues à câble automatiques et commande hydraulique

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EP (1) EP0241023B1 (fr)
AT (2) AT389863B (fr)
DE (1) DE3787486D1 (fr)

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* Cited by examiner, † Cited by third party
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CN112897356B (zh) * 2021-01-21 2022-06-17 赣州建工集团有限公司 一种装配式建筑住宅施工用起吊装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2025575A (en) * 1934-04-11 1935-12-24 Gen Electric Control system
AT177159B (de) * 1950-06-21 1954-01-11 Jakob Wyssen Transporteinrichtung zum Senkrechtbewegen von Lasten und Verfahren derselben längs eines Tragseiles
US3058601A (en) * 1960-03-09 1962-10-16 Wyssen Jakob Transportation system
CH379086A (de) * 1960-03-09 1964-06-30 Wyssen Jakob Transporteinrichtung zum Senkrechtbewegen von Lasten und Verfahren derselben längs eines Drahtseils
US3776390A (en) * 1971-06-17 1973-12-04 N Junes Skyline logging carriage
AT328505B (de) * 1972-05-23 1976-03-25 Koller Josef Automatische steuerung von kranseilbahnwagen
AT378943B (de) * 1983-03-09 1985-10-25 Nesler Johann Selbsttaetige steuerung von kranseilbahnwagen zur lastbefoerderung
AT379994B (de) * 1983-03-09 1986-03-25 Nesler Johann Einrichtung zur betaetigung eines hydraulischen steuerventiles

Also Published As

Publication number Publication date
DE3787486D1 (de) 1993-10-28
ATA91386A (de) 1989-07-15
ATE94851T1 (de) 1993-10-15
AT389863B (de) 1990-02-12
EP0241023A3 (en) 1990-05-30
EP0241023A2 (fr) 1987-10-14

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