EP0448021B1 - Load-lifting system comprising two parallel drums rotating in synchronism - Google Patents

Load-lifting system comprising two parallel drums rotating in synchronism Download PDF

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Publication number
EP0448021B1
EP0448021B1 EP91104174A EP91104174A EP0448021B1 EP 0448021 B1 EP0448021 B1 EP 0448021B1 EP 91104174 A EP91104174 A EP 91104174A EP 91104174 A EP91104174 A EP 91104174A EP 0448021 B1 EP0448021 B1 EP 0448021B1
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EP
European Patent Office
Prior art keywords
load
drum
plate
hoisting device
disk
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Expired - Lifetime
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EP91104174A
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German (de)
French (fr)
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EP0448021A1 (en
Inventor
Gérard Freneix
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ACB
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ACB
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    • 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
    • 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
    • B66D1/54—Safety gear
    • 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
    • B66D1/26—Rope, cable, or chain winding mechanisms; Capstans having several drums or barrels

Definitions

  • the present invention relates to a load lifting system comprising a geared motor group with two parallel output pinions in which each output pinion respectively drives a lifting device, each lifting device comprising a toothed ring meshing with the corresponding output pinion and driving a winch drum whose rotation in the direction corresponding to the descent of the load ensures the coupling of a clutch.
  • GB-A-2 179 618 describes such a system.
  • the load 30 is suspended from the lifting device by a single double-pass cable 31, 32 ensuring a reduction.
  • the two drums 15 and 16 are mounted on a single shaft, therefore very long.
  • the clutch system is such that it requires brakes 29 and emergency brakes 28 because the load tends to cause the motor 23 to rotate in the direction of descent and it must therefore be able to brake it.
  • the object of the invention is to propose a lifting system ensuring anti-fall security by redundancy of the lifting members situated between the load and the lifting gearmotor. In addition, it offers a clutch system requiring no brakes.
  • each lifting device is individually connected to the load by a cable attached to the corresponding drum and wound therein, in that said gear ring of each lifting device drives its drum by said clutch which is a friction clutch comprising an intermediate clutch disc comprising retaining pawls preventing its rotation in the direction corresponding to the descent of the load, the drum of each device of lifting being integral with a central shaft, and in that the central shaft of one of the lifting devices is synchronized in rotation with the central shaft of the other lifting device by means of a plate coupling and coupling disc provided with orthogonal pins, or orthogonal grooves, the two shafts central being supported by a fixed frame.
  • said clutch which is a friction clutch comprising an intermediate clutch disc comprising retaining pawls preventing its rotation in the direction corresponding to the descent of the load
  • the drum of each device of lifting being integral with a central shaft
  • the central shaft of one of the lifting devices is synchronized in rotation with the central shaft of the other lifting device by means of a plate coupling and coupling disc provided with ortho
  • said intermediate clutch disc of each lifting device is sandwiched between a hub ensuring the connection between said drum and said central shaft and comprising a bearing surface against said disc and a nut plate mounted on a threaded seat of said central shaft, said nut plate being driven in rotation by a centralizer integral with said toothed ring, said connection in rotation of the centralizer and said nut plate being effected by means allowing a slight axial displacement of said nut plate with respect to said centralizer, the rotation of said ring gear in the direction corresponding to the rise of said load causing the axial displacement of said plate-nut in the direction ensuring its application against said intermediate clutch disc.
  • the cable of each lifting device is attached to the load and then passes over a front idler pulley to be wound on the drum, the two deflection pulleys being mounted at the two ends of a lifter articulated horizontally in the middle to a fixed part secured to said frame, vertical to said load, the movement of said lifter being limited between two stops each provided with a detector.
  • said load is mounted to slide along a vertical column.
  • FIG. 1 showing the principle of the system for lifting a load according to the invention, there is seen a geared motor 1 comprising at each of its ends an output pinion: pinion 2 to the right and pinion 3 to left. These pinions are arranged in parallel and are strictly integral in rotation.
  • the pinion 2 drives a first lifting device which is connected to a load 4 by a first cable 5.
  • This first lifting device on the right in the figure, comprises a toothed crown 6 which drives, by means of a friction clutch 7, a first winch drum 8 on which the first cable 5 is wound and unwound. and to which it is attached.
  • the left pinion 3 also drives a second lifting device which is connected to the load 4 by a second cable 9.
  • This second lifting device located on the left in the figure, is identical to the first and comprises a ring gear 6A, a friction clutch 7A and a winch drum 8A.
  • the friction clutch 7 (or 7A) comprises an intermediate clutch disc which includes retaining pawls preventing its rotation in the direction which corresponds to the descent of the charge 4.
  • This lifting system is thus redundant and ensures the maintenance of the load 4 whatever the failure of any one or more members of one of the two lifting devices, including the output pinion of the gear motor and the cable, on condition that this failure, or these failures, only occur on one of the two lifting devices, right or left.
  • the clutch for each side, is ensured automatically by the rotation of the output pinion in the direction ensuring the rise of the load 4.
  • the rotation of the drum 8 in the direction corresponding to the Descent of the load 4 also has the automatic effect of ensuring the clutch of the friction clutch 7, the intermediate disc of which is retained by its pawls in the direction of rotation corresponding precisely to this descent of the load.
  • the descent of the load is carried out by an alternative succession of disengaging and clutching the friction clutch by controlling the gear motor in the opposite direction of the ascent: the disengagement being caused by this rotation and the clutch by the rotation of the drum under the weight of the load.
  • each drum is integral with a central shaft: 10 for the right-hand device and 11 for the left-hand device which are synchronized in rotation by a coupling with plates 12 and 13 and coupling disc 14 provided with pins, or of grooves, orthogonal.
  • a coupling is known per se and bears the name of "joint of oldham ".
  • This synchronization device is particularly advantageous because it avoids a single long shaft, it allows the uncoupling of the two shafts for focusing and in particular to make up for the play resulting from a permanent and not identical, inevitable elongation of the two cables.
  • the "oldham joint" comprises a plurality of tenons, and orthogonal grooves so as to allow making a 1/8 or 1/4 turn, for example, to one of the two shafts.
  • this coupling allows a non-alignment of the two shafts, allowing a certain distance d between axes.
  • the general lifting system of the invention is thus redundant, synchronized and entirely mechanical, leading to no particular requirement on the electrical part.
  • pulleys 15 and 16 are mounted at the ends of a lifting beam 17 which is articulated in its middle 18 to a fixed part, integral with the frame of the assembly (described below).
  • the horizontal articulation 18 is vertical to the load 4 which, in this case, is slidably mounted along a vertical column 19.
  • the load 4 can in reality be a support for an organ, for a tool or any charge.
  • the movement of the spreader 17 is limited between two stops 20 and 21 each provided with a detector 22 and 23. This system makes it possible to detect a differential elongation of the two cables 5 and 9 and therefore to carry out the adjustment said above.
  • Figure 2 shows the practical embodiment of the framed part A of Figure 1 comprising the gear motor 1 and the two lifting devices with synchronization.
  • the output pinion 2 meshes with the ring gear 6 which is integral with a centering device 24 which comprises several drive fingers 25 which penetrate into recesses 26 of a nut plate 27 mounted on a threaded seat 28 of the central shaft 10.
  • the recess 26 is deep enough to allow a slight axial movement of the nut plate 27 relative to the centralizer 24 , by screwing and unscrewing the nut plate 27 on the threaded surface 28.
  • the central shaft 10 and the centralizer 24 are rotatably supported by a fixed frame 29 in several parts, by means of ball bearings 30, 31, 32, 33.
  • the bearing 33 is mounted in a bearing 34 fixed to the frame 29.
  • the central shaft 10 is integral with a hub 35 to which the drum 8 is fixed by means of a plate 36.
  • the drum 8 rotates around portions of the fixed frame 29 by rubbing on seals 37, 38 sealing the interior of the mechanism.
  • the hub 35 has a flat surface 39, in the form of a circular crown which sandwiches, with the nut plate 27, an intermediate clutch disc 40 provided with crowns 41, 42 made of a material ensuring good friction.
  • This intermediate clutch disc has pawls 43 with spring 44. These pawls pivot about an axis 45.
  • a fixed toothed ring 46 is linked to the frame 29 by screws 47.
  • the intermediate clutch disc can thus only rotate in the direction of arrow F (FIG. 4) which corresponds to the rotation of the geared motor group 1 in the direction ensuring the rise of the load 4.
  • the central shaft carries the plate 12 which is in abutment on the right against a collar 48 in two parts.
  • the plate 12 carries grooves 49, at least two grooves located at 90 ° from one another, and in practice several pairs of grooves at 90 °, each pair of grooves being offset from the following by a certain angle for example 15 ° or 30 ° so as to allow the length of the cables 5 and 9 to be adjusted.
  • the operation is as follows: To raise the load, the gearmotor is rotated in the direction that causes the nut-plate 27 to be screwed to the right. When, taking into account the weight of the load 4, the tightening of the disc 40 between the plate- nut 27 and the hub 35 is sufficient, the rotation of the nut plate 27 then also rotates the hub 35 and therefore the drum 8 and the central shaft 10 linked to this hub. The rotation of the drum in the opposite direction being, in this engaged position, absolutely impossible because of the ratchet disc 40.
  • the clutch To lower the load, the clutch must be released. To do this, the gear motor 1 is rotated in the opposite direction, which causes the nut plate 27 to move to the left, thus freeing the hub 35 and therefore the drum 8 which rotates under the weight of the load in the direction of the descent (by turning relative to the intermediate disc 40 retained by its pawls 43). However, this rotation of the hub 35 also causes the rotation of the central shaft 10, which immediately causes the nut plate 27 to tighten against the disc 40 and the hub 35, stopping the descent of the load, unless the gear motor keeps spinning. The descent is therefore carried out by an alternative succession of clutch and disengage, the descent speed being in practice perfectly controlled by the speed of rotation of the gear motor 1 and smoothly by a slight sliding of the hub 35 against the intermediate clutch disc 40.

Description

La présente invention concerne un système de levage d'une charge comprenant un groupe motoréducteur à deux pignons de sortie parallèles dans lequel chaque pignon de sortie entraîne respectivement un dispositif de levage, chaque dispositif de levage comprenant une couronne dentée engrenant avec le pignon de sortie correspondant et entraînant un tambour de treuil dont la rotation dans le sens correspondant à la descente de la charge assure l'accouplement d'un embrayage.The present invention relates to a load lifting system comprising a geared motor group with two parallel output pinions in which each output pinion respectively drives a lifting device, each lifting device comprising a toothed ring meshing with the corresponding output pinion and driving a winch drum whose rotation in the direction corresponding to the descent of the load ensures the coupling of a clutch.

Le document GB-A-2 179 618 décrit un tel système. Dans ce document, la charge 30 est suspendue au dispositif de levage par un câble unique à double passage 31, 32 assurant une démultiplication. Par ailleurs, les deux tambours 15 et 16 sont montés sur un arbre unique donc très long. Enfin, le système d'embrayage est tel qu'il nécessite des freins 29 et des freins de secours 28 car la charge a tendance à entraîner le moteur 23 en rotation dans le sens de la descente et il faut donc pouvoir la freiner.GB-A-2 179 618 describes such a system. In this document, the load 30 is suspended from the lifting device by a single double-pass cable 31, 32 ensuring a reduction. Furthermore, the two drums 15 and 16 are mounted on a single shaft, therefore very long. Finally, the clutch system is such that it requires brakes 29 and emergency brakes 28 because the load tends to cause the motor 23 to rotate in the direction of descent and it must therefore be able to brake it.

L'invention a pour but de proposer un système de levage assurant une sécurité anti-chute par redondance des organes de levage situés entre la charge et le motoréducteur de levage. En outre, elle propose un système d'embrayage ne nécessitant aucun frein.The object of the invention is to propose a lifting system ensuring anti-fall security by redundancy of the lifting members situated between the load and the lifting gearmotor. In addition, it offers a clutch system requiring no brakes.

L'invention a ainsi pour objet un système de levage d'une charge tel que ci-dessus, caractérisé en ce que chaque dispositif de levage est relié individuellement à la charge par un câble attaché au tambour correspondant et y enroulé, en ce que ladite couronne dentée de chaque dispositif de levage entraîne son tambour par ledit embrayage qui est un embrayage à friction comprenant un disque intermédiaire d'embrayage comportant des cliquets de retenue interdisant sa rotation dans le sens correspondant à la descente de la charge, le tambour de chaque dispositif de levage étant solidaire d'un arbre central, et en ce que l'arbre central de l'un des dispositifs de levage est synchronisé en rotation avec l'arbre central de l'autre dispositif de levage au moyen d'un accouplement à plateaux et disque d'accouplement muni de tenons orthogonaux, ou de rainures orthogonales, les deux arbres centraux étant supportés par un bâti fixe.The invention thus relates to a load lifting system as above, characterized in that each lifting device is individually connected to the load by a cable attached to the corresponding drum and wound therein, in that said gear ring of each lifting device drives its drum by said clutch which is a friction clutch comprising an intermediate clutch disc comprising retaining pawls preventing its rotation in the direction corresponding to the descent of the load, the drum of each device of lifting being integral with a central shaft, and in that the central shaft of one of the lifting devices is synchronized in rotation with the central shaft of the other lifting device by means of a plate coupling and coupling disc provided with orthogonal pins, or orthogonal grooves, the two shafts central being supported by a fixed frame.

Selon une réalisation particulière, ledit disque intermédiaire d'embrayage de chaque dispositif de levage est pris en sandwich entre un moyeu assurant la liaison entre ledit tambour et ledit arbre central et comportant une surface d'appui contre ledit disque et un plateau-écrou monté sur une portée filetée dudit arbre central, ledit plateau-écrou étant entraîné en rotation par un centreur solidaire de ladite couronne dentée, ladite liaison en rotation du centreur et dudit plateau-écrou s'effectuant par un moyen permettant un léger déplacement axial dudit plateau-écrou par rapport audit centreur, la rotation de ladite couronne dentée dans le sens correspondant à la montée de ladite charge provoquant le déplacement axial dudit plateau-écrou dans le sens assurant son application contre ledit disque intermédiaire d'embrayage.According to a particular embodiment, said intermediate clutch disc of each lifting device is sandwiched between a hub ensuring the connection between said drum and said central shaft and comprising a bearing surface against said disc and a nut plate mounted on a threaded seat of said central shaft, said nut plate being driven in rotation by a centralizer integral with said toothed ring, said connection in rotation of the centralizer and said nut plate being effected by means allowing a slight axial displacement of said nut plate with respect to said centralizer, the rotation of said ring gear in the direction corresponding to the rise of said load causing the axial displacement of said plate-nut in the direction ensuring its application against said intermediate clutch disc.

Selon une autre caractéristique, le câble de chaque dispositif de levage est attaché à la charge puis passe sur une poulie de renvoi avant de s'enrouler sur le tambour, les deux poulies de renvoi étant montées aux deux extrémités d'un palonnier articulé horizontalement en son milieu à une partie fixe solidaire dudit bâti, à la verticale de ladite charge, le mouvement dudit palonnier étant limité entre deux butées munies chacune d'un détecteur.According to another characteristic, the cable of each lifting device is attached to the load and then passes over a front idler pulley to be wound on the drum, the two deflection pulleys being mounted at the two ends of a lifter articulated horizontally in the middle to a fixed part secured to said frame, vertical to said load, the movement of said lifter being limited between two stops each provided with a detector.

Selon une autre caractéristique, ladite charge est montée coulissante le long d'une colonne verticale.According to another characteristic, said load is mounted to slide along a vertical column.

On va maintenant donner la description d'un exemple de mise en oeuvre de l'invention en se reportant au dessin annexé dans lequel :

  • La figure 1 est une vue générale schématique d'un système de levage d'une charge selon l'invention.
  • La figure 2 est une réalisation pratique de l'ensemble A de la figure 1 montrant le moto-réducteur, les deux dispositifs de levage et le dispositif de synchronisation en rotation des deux arbres centraux.
  • La figure 3 est une vue partielle agrandie de la figure 2 en coupe axiale montrant la moitié du moto-réducteur, la moitié du dispositif de levage de droite et le dispositif de synchronisation en rotation des deux arbres centraux.
  • La figure 4 est une vue partielle selon la flèche IV de la figure 3 montrant le dispositif de retenue par cliquets du disque intermédiaire d'embrayage.
We will now give the description of an exemplary implementation of the invention with reference to the appended drawing in which:
  • Figure 1 is a schematic general view of a load lifting system according to the invention.
  • Figure 2 is a practical embodiment of the assembly A of Figure 1 showing the gear motor, the two lifting devices and the synchronization device in rotation of the two central shafts.
  • Figure 3 is an enlarged partial view of Figure 2 in axial section showing half of the gear motor, half of the right lifting device and the device for synchronizing the rotation of the two central shafts.
  • Figure 4 is a partial view along arrow IV of Figure 3 showing the pawl retainer of the intermediate clutch disc.

En se référant maintenant à la figure 1 montrant le principe du système de levage d'une charge selon l'invention, on voit un moto-réducteur 1 comprenant à chacune de ses extrémités un pignon de sortie : pignon 2 à droite et pignon 3 à gauche. Ces pignons sont disposés parallèlement et sont strictement solidaires en rotation. Le pignon 2 entraîne un premier dispositif de levage qui est relié à une charge 4 par un premier câble 5.Referring now to FIG. 1 showing the principle of the system for lifting a load according to the invention, there is seen a geared motor 1 comprising at each of its ends an output pinion: pinion 2 to the right and pinion 3 to left. These pinions are arranged in parallel and are strictly integral in rotation. The pinion 2 drives a first lifting device which is connected to a load 4 by a first cable 5.

Ce premier dispositif de levage, à droite sur la figure, comprend une couronne dentée 6 qui entraîne, par l'intermédiaire d'un embrayage à friction 7, un premier tambour de treuil 8 sur lequel s'enroule et se déroule le premier câble 5 et auquel il est fixé.This first lifting device, on the right in the figure, comprises a toothed crown 6 which drives, by means of a friction clutch 7, a first winch drum 8 on which the first cable 5 is wound and unwound. and to which it is attached.

Le pignon de gauche 3 entraîne également un deuxième dispositif de levage qui est relié à la charge 4 par un second câble 9. Ce deuxième dispositif de levage, situé à gauche sur la figure, est identique au premier et comprend une couronne dentée 6A, un embrayage à friction 7A et un tambour de treuil 8A.The left pinion 3 also drives a second lifting device which is connected to the load 4 by a second cable 9. This second lifting device, located on the left in the figure, is identical to the first and comprises a ring gear 6A, a friction clutch 7A and a winch drum 8A.

Comme il sera décrit en détail en référence aux figures 3 et 4, l'embrayage à friction 7 (ou 7A) comprend un disque intermédiaire d'embrayage qui comporte des cliquets de retenue interdisant sa rotation dans le sens qui correspond à la descente de la charge 4.As will be described in detail with reference to FIGS. 3 and 4, the friction clutch 7 (or 7A) comprises an intermediate clutch disc which includes retaining pawls preventing its rotation in the direction which corresponds to the descent of the charge 4.

Ce système de levage est ainsi redondant et assure le maintien de la charge 4 quelle que soit la défaillance d'un quelconque ou de plusieurs organes de l'un des deux dispositifs de levage, y compris le pignon de sortie du moto-réducteur et le câble, à la condition que cette défaillance, ou ces défaillances, ne surviennent que sur l'un seulement des deux dispositifs, droite ou gauche, de levage.This lifting system is thus redundant and ensures the maintenance of the load 4 whatever the failure of any one or more members of one of the two lifting devices, including the output pinion of the gear motor and the cable, on condition that this failure, or these failures, only occur on one of the two lifting devices, right or left.

Comme on le verra plus loin, l'embrayage, pour chaque côté, est assuré automatiquement par la rotation du pignon de sortie dans le sens assurant la montée de la charge 4. En outre, la rotation du tambour 8 dans le sens correspondant à la descente de la charge 4 a également pour effet automatique d'assurer l'embrayage de l'embrayage à friction 7 dont le disque intermédiaire est retenu par ses cliquets dans le sens de rotation correspondant précisément à cette descente de la charge.As will be seen later, the clutch, for each side, is ensured automatically by the rotation of the output pinion in the direction ensuring the rise of the load 4. In addition, the rotation of the drum 8 in the direction corresponding to the Descent of the load 4 also has the automatic effect of ensuring the clutch of the friction clutch 7, the intermediate disc of which is retained by its pawls in the direction of rotation corresponding precisely to this descent of the load.

Ainsi, la descente de la charge est effectuée par une succession alternative de débrayage et d'embrayage de l'embrayage à friction en commandant le moto-réducteur dans le sens inverse de la montée : le débrayage étant provoqué par cette rotation et l'embrayage par la rotation du tambour sous le poids de la charge.Thus, the descent of the load is carried out by an alternative succession of disengaging and clutching the friction clutch by controlling the gear motor in the opposite direction of the ascent: the disengagement being caused by this rotation and the clutch by the rotation of the drum under the weight of the load.

Inévitablement, un tel système de descente par frictions successives ne peut pas être identique des deux côtés à cause des coefficients de frottement non absolument identiques de chaque côté, de l'usure non égale etc... Aussi, pour que les deux câbles 5 et 9 soient en permanence tendus tous les deux, il est nécessaire d'assurer la synchronisation en rotation des deux tambours 8 et 8A.Inevitably, such a system of descent by successive frictions cannot be identical on the two sides because of the coefficients of friction not absolutely identical on each side, of the unequal wear etc ... Also, so that the two cables 5 and 9 are permanently tensioned both, it is necessary to ensure the synchronization in rotation of the two drums 8 and 8A.

Pour cela, chaque tambour est solidaire d'un arbre central : 10 pour le dispositif de droite et 11 pour le dispositif de gauche qui sont synchronisés en rotation par un accouplement à plateaux 12 et 13 et disque d'accouplement 14 muni de tenons, ou de rainures, orthogonales. Un tel accouplement est connu en soi et porte le nom de "joint d'oldham".For this, each drum is integral with a central shaft: 10 for the right-hand device and 11 for the left-hand device which are synchronized in rotation by a coupling with plates 12 and 13 and coupling disc 14 provided with pins, or of grooves, orthogonal. Such a coupling is known per se and bears the name of "joint of oldham ".

Ce dispositif de synchronisation est particulièrement avantageux car il évite un arbre unique long, il permet le désaccouplage des deux arbres pour les mises au point et en particulier pour rattraper le jeu résultant d'une élongation permanente et non identique, inévitable, des deux câbles. A cet effet, le "joint d'oldham" comporte une pluralité de tenons, et rainures orthogonales de manière à permettre d'effectuer un 1/8 ou un 1/4 de tour, par exemple, à l'un des deux arbres. Enfin, cet accouplement permet un non alignement des deux arbres, autorisant une certaine distance d entre axes.This synchronization device is particularly advantageous because it avoids a single long shaft, it allows the uncoupling of the two shafts for focusing and in particular to make up for the play resulting from a permanent and not identical, inevitable elongation of the two cables. For this purpose, the "oldham joint" comprises a plurality of tenons, and orthogonal grooves so as to allow making a 1/8 or 1/4 turn, for example, to one of the two shafts. Finally, this coupling allows a non-alignment of the two shafts, allowing a certain distance d between axes.

Le système général de levage de l'invention est ainsi redondant, synchronisé et entièrement mécanique ne conduisant à aucune exigence particulière sur la partie électrique.The general lifting system of the invention is thus redundant, synchronized and entirely mechanical, leading to no particular requirement on the electrical part.

Sur cette figure 1, on voit que les câbles 5 et 9, attachés à la charge 4 passent sur des poulies de renvoi 15 et 16 avant de s'enrouler sur les tambours 8 et 8A.In this FIG. 1, it can be seen that the cables 5 and 9, attached to the load 4 pass over return pulleys 15 and 16 before being wound up on the drums 8 and 8A.

Ces poulies 15 et 16 sont montées aux extrémités d'un palonnier 17 qui est articulé en son milieu 18 à une partie fixe, solidaire du bâti de l'ensemble (décrit plus loin). L'articulation horizontale 18 est à la verticale de la charge 4 qui, en l'occurence, est montée coulissante le long d'une colonne verticale 19. La charge 4 peut en réalité être un support d'un organe, d'un outil ou d'une charge quelconque. Le mouvement du palonnier 17 est limité entre deux butées 20 et 21 munies chacune d'un détecteur 22 et 23. Ce système permet de détecter une élongation différentielle des deux câbles 5 et 9 et donc d'effectuer le réglage dit ci-dessus.These pulleys 15 and 16 are mounted at the ends of a lifting beam 17 which is articulated in its middle 18 to a fixed part, integral with the frame of the assembly (described below). The horizontal articulation 18 is vertical to the load 4 which, in this case, is slidably mounted along a vertical column 19. The load 4 can in reality be a support for an organ, for a tool or any charge. The movement of the spreader 17 is limited between two stops 20 and 21 each provided with a detector 22 and 23. This system makes it possible to detect a differential elongation of the two cables 5 and 9 and therefore to carry out the adjustment said above.

La figure 2 montre la réalisation pratique de la partie encadrée A de la figure 1 comprenant le moto-réducteur 1 et les deux dispositifs de levage avec la synchronisation.Figure 2 shows the practical embodiment of the framed part A of Figure 1 comprising the gear motor 1 and the two lifting devices with synchronization.

On va maintenant décrire en détail, en se référant aux figures 3 et 4, un dispositif de levage, celui de droite, et le dispositif de synchronisation, étant entendu que le dispositif de levage de gauche est absolument identique.We will now describe in detail, with reference to FIGS. 3 and 4, a lifting device, the one on the right, and the synchronization device, it being understood that the lifting device on the left is absolutely identical.

Le pignon de sortie 2 engrène sur la couronne dentée 6 qui est solidaire d'un centreur 24 qui comporte plusieurs doigts d'entraînement 25 qui pénètrent dans des évidements 26 d'un plateau-écrou 27 monté sur une portée filetée 28 de l'arbre central 10. L'évidement 26 est suffisamment profond pour permettre un léger déplacement axial du plateau-écrou 27 par rapport au centreur 24, par vissage et dévissage du plateau-écrou 27 sur la portée filetée 28. L'arbre central 10 et le centreur 24 sont supportés en rotation par un bâti fixe 29 en plusieurs parties, par l'intermédiaire de roulement à billes 30, 31, 32, 33. Le roulement 33 est monté dans un palier 34 fixé au bâti 29. L'arbre central 10 est solidaire d'un moyeu 35 auquel est fixé le tambour 8 par l'intermédiaire d'un plateau 36. Le tambour 8 tourne autour de portions du bâti fixe 29 en frottant sur des joints 37, 38 assurant l'étanchéité de l'intérieur du mécanisme. Le moyeu 35 comporte une surface plane 39, en forme de couronne circulaire qui prend en sandwich, avec le plateau-écrou 27, un disque intermédiaire d'embrayage 40 muni de couronnes 41, 42 en matériau assurant une bonne friction.The output pinion 2 meshes with the ring gear 6 which is integral with a centering device 24 which comprises several drive fingers 25 which penetrate into recesses 26 of a nut plate 27 mounted on a threaded seat 28 of the central shaft 10. The recess 26 is deep enough to allow a slight axial movement of the nut plate 27 relative to the centralizer 24 , by screwing and unscrewing the nut plate 27 on the threaded surface 28. The central shaft 10 and the centralizer 24 are rotatably supported by a fixed frame 29 in several parts, by means of ball bearings 30, 31, 32, 33. The bearing 33 is mounted in a bearing 34 fixed to the frame 29. The central shaft 10 is integral with a hub 35 to which the drum 8 is fixed by means of a plate 36. The drum 8 rotates around portions of the fixed frame 29 by rubbing on seals 37, 38 sealing the interior of the mechanism. The hub 35 has a flat surface 39, in the form of a circular crown which sandwiches, with the nut plate 27, an intermediate clutch disc 40 provided with crowns 41, 42 made of a material ensuring good friction.

Ce disque intermédiaire d'embrayage possède des cliquets 43 à ressort 44. Ces cliquets pivotent autour d'un axe 45. Autour du disque 40 portant ses cliquets 43 se trouve une couronne crantée 46 fixe, liée au bâti 29 par des vis 47.This intermediate clutch disc has pawls 43 with spring 44. These pawls pivot about an axis 45. Around the disc 40 carrying its pawls 43 is a fixed toothed ring 46, linked to the frame 29 by screws 47.

Le disque intermédiaire d'embrayage ne peut ainsi tourner que dans le sens de la flèche F (figure 4) qui correspond à la rotation du groupe moto-réducteur 1 dans le sens assurant la montée de la charge 4.The intermediate clutch disc can thus only rotate in the direction of arrow F (FIG. 4) which corresponds to the rotation of the geared motor group 1 in the direction ensuring the rise of the load 4.

A son extrémité, l'arbre central porte le plateau 12 qui est en butée à droite contre un collier 48 en deux parties. Le plateau 12 porte des rainures 49, au moins deux rainures situées à 90° l'une de l'autre, et en pratique plusieurs couples de rainures à 90°, chaque couple de rainure étant décalé du suivant d'un certain angle par exemple 15° ou 30° de manière à permettre le réglage de la longueur des câbles 5 et 9. Pour cela, il suffit de démonter le collier 48, de reculer le plateau 12, claveté sur l'arbre 10 et de tourner l'ensemble pour placer le couple de tenons perpendiculaires 50 du disque d'accouplement 14 dans un couple voisin de rainures 49 du plateau 12 puis de replacer le collier 48 (à noter que les tenons pourraient être portés par les plateaux 12, 13 et les rainures par le disque 14).At its end, the central shaft carries the plate 12 which is in abutment on the right against a collar 48 in two parts. The plate 12 carries grooves 49, at least two grooves located at 90 ° from one another, and in practice several pairs of grooves at 90 °, each pair of grooves being offset from the following by a certain angle for example 15 ° or 30 ° so as to allow the length of the cables 5 and 9 to be adjusted. For this, it suffices to dismantle the collar 48, move the plate 12 back, keyed onto the shaft 10 and turn the assembly to place the pair of perpendicular pins 50 of the coupling disc 14 in an adjacent pair of grooves 49 on the plate 12 and then replace the collar 48 (note that the pins could be carried by the plates 12, 13 and the grooves by the disk 14).

Le fonctionnement est le suivant :
   Pour la montée de la charge, on fait tourner le moto-réducteur dans le sens qui provoque le vissage vers la droite du plateau-écrou 27. Lorsque, compte tenu du poids de la charge 4, le serrage du disque 40 entre le plateau-écrou 27 et le moyeu 35 est suffisant, la rotation du plateau-écrou 27 entraîne alors également en rotation le moyeu 35 et donc le tambour 8 et l'arbre central 10 liés à ce moyeu. La rotation du tambour en sens inverse étant, dans cette position embrayée, absolument impossible à cause du disque 40 à cliquets.The operation is as follows:
To raise the load, the gearmotor is rotated in the direction that causes the nut-plate 27 to be screwed to the right. When, taking into account the weight of the load 4, the tightening of the disc 40 between the plate- nut 27 and the hub 35 is sufficient, the rotation of the nut plate 27 then also rotates the hub 35 and therefore the drum 8 and the central shaft 10 linked to this hub. The rotation of the drum in the opposite direction being, in this engaged position, absolutely impossible because of the ratchet disc 40.

Pour la descente de la charge, il faut desserrer l'embrayage. Pour ce faire, on fait tourner le moto-réducteur 1 en sens inverse, ce qui provoque le déplacement vers la gauche du plateau-écrou 27 libérant ainsi le moyeu 35 et donc le tambour 8 qui tourne sous le poids de la charge dans le sens de la descente (en tournant par rapport au disque intermédiaire 40 retenu par ses cliquets 43). Cependant cette rotation du moyeu 35 entraîne également la rotation de l'arbre central 10, ce qui provoque immédiatement le resserrage du plateau-écrou 27 contre le disque 40 et le moyeu 35, stoppant la descente de la charge, sauf si le moto-réducteur continue à tourner. La descente s'effectue donc par une succession alternative d'embrayage et de débrayage, la vitesse de descente étant en pratique parfaitement commandée par la vitesse de rotation du moto-réducteur 1 et sans à-coup par un léger glissement du moyeu 35 contre le disque intermédiaire d'embrayage 40.To lower the load, the clutch must be released. To do this, the gear motor 1 is rotated in the opposite direction, which causes the nut plate 27 to move to the left, thus freeing the hub 35 and therefore the drum 8 which rotates under the weight of the load in the direction of the descent (by turning relative to the intermediate disc 40 retained by its pawls 43). However, this rotation of the hub 35 also causes the rotation of the central shaft 10, which immediately causes the nut plate 27 to tighten against the disc 40 and the hub 35, stopping the descent of the load, unless the gear motor keeps spinning. The descent is therefore carried out by an alternative succession of clutch and disengage, the descent speed being in practice perfectly controlled by the speed of rotation of the gear motor 1 and smoothly by a slight sliding of the hub 35 against the intermediate clutch disc 40.

Grâce à l'accouplement homocinétique des deux arbres centraux 10 et 11, la rotation est parfaitement synchronisée et le seul réglage nécessaire provient des élongations nécessairement non identiques des deux câbles 5 et 9 au bout d'un certain temps de fonctionnement.Thanks to the constant velocity coupling of the two central shafts 10 and 11, the rotation is perfectly synchronized and the only necessary adjustment comes from the necessarily non-identical elongations of the two cables 5 and 9 after a certain operating time.

Claims (4)

  1. A load-hoisting system (4) comprising a motor and gear box unit (1) having two parallel outlet gears (2, 3) in which each outlet gear drives a respective hoisting device, each hoisting device comprising a toothed disk (6, 6A) meshing with the corresponding outlet gear (2, 3), and driving a winch drum (8, 8A) whose rotation in the direction corresponding to lowering the load ensures that a clutch is engaged, characterized in that each hoisting device is individually linked to the load by a cable (4, 5) attached to the corresponding drum and would thereon, and in that said toothed disk (6, 6A) of each hoisting device drives its drum (8, 8A) by said clutch which is a friction clutch comprising an intermediate clutch disk (40) including retaining catches (43) preventing it from rotating in a direction corresponding to lowering the load (4), the drum of each hoisting device being fixed to a central shaft (10, 11) , and in that said central shaft of one of the hoisting devices is synchronized in rotation with the central shaft of the other hoisting device by means of a plate coupling (12, 13) and a coupling disk (14) provided with orthogonal tenons (50) or orthogonal grooves, the two central shafts being supported by a fixed frame (29).
  2. A hoisting system according to claim 1, characterized in that said intermediate clutch disk (40) of each hoisting device is sandwiched between a hub (35) providing a connection between said drum (8) and said central shaft (10) and including a thrust surface (29) against which said disk (40) bears, and a nut-plate (27) mounted on a threaded bearing surface (28) of said central shaft (10), said nut-plate (27) being rotated by a centralizer (24) which is fixed to said toothed disk (6), said rotary connection of the centralized (24) and of said nut-plate (27) taking place via means (25, 26) enabling said nut-plate to move slightly axially relative to said centralizer, rotation of said toothed disk (6) in the direction corresponding to raising said load (5) causing said nut-plate (27) to move axially in the direction that presses it against said intermediate clutch disk (40).
  3. A hoisting system according to claim 1 or 2, characterized in that the cable (5, 9) of each hoisting device is attached to the load (4) and then passes over a return sheave (15, 16) prior to being wound onto the winch drum (8, 8A), the two return sheaves (15, 16) being mounted at the two ends of a spreader bar (17) horizontally hinged in its middle (18) to a fixed portion which is fixed to said frame (29) vertically above said load (4), movement of said spreader bar (17) being limited between two abutments (20, 21) each provided with a detector (22, 23).
  4. A hoisting system according to any preceding claim, characterized in that said load is mounted to slide along a vertical column.
EP91104174A 1990-03-21 1991-03-18 Load-lifting system comprising two parallel drums rotating in synchronism Expired - Lifetime EP0448021B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9003625A FR2659951B1 (en) 1990-03-21 1990-03-21 SYSTEM FOR LIFTING A TWO-DRUM LOAD WORKING IN PARALLEL, SYNCHRONIZED IN ROTATION.
FR9003625 1990-03-21

Publications (2)

Publication Number Publication Date
EP0448021A1 EP0448021A1 (en) 1991-09-25
EP0448021B1 true EP0448021B1 (en) 1994-09-14

Family

ID=9394964

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Application Number Title Priority Date Filing Date
EP91104174A Expired - Lifetime EP0448021B1 (en) 1990-03-21 1991-03-18 Load-lifting system comprising two parallel drums rotating in synchronism

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US (1) US5324007A (en)
EP (1) EP0448021B1 (en)
JP (1) JPH04223997A (en)
KR (1) KR910016614A (en)
BG (1) BG60028A3 (en)
CA (1) CA2038711C (en)
CS (1) CS76691A2 (en)
DE (1) DE69103937T2 (en)
ES (1) ES2062586T3 (en)
FI (1) FI93202C (en)
FR (1) FR2659951B1 (en)
HU (1) HU208286B (en)
RO (1) RO107397B1 (en)
YU (1) YU47960B (en)
ZA (1) ZA912071B (en)

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GB2324278A (en) * 1997-02-20 1998-10-21 J & A Promotions Ltd Vehicle with vertically movable deck
JP2000344449A (en) 1999-06-02 2000-12-12 Teijin Seiki Co Ltd Elevator drive
US6598859B1 (en) 2001-05-31 2003-07-29 Magnetek, Inc. Multiple hoist synchronization apparatus and method
CA2389957C (en) 2002-06-10 2009-08-04 Brent's Grading Ltd. Blade installation tool
FR2892785B1 (en) * 2005-11-03 2008-01-18 Unicum Transmission De Puissan DEVICE FOR SAFETY DEVICE FOR MECHANICAL TRANSMISSION BY IRREVERSIBLE GEAR TO STOP
FI118729B (en) * 2006-04-04 2008-02-29 Kone Corp Arrangement to stop a lift basket in an emergency and lift
EP1955976A1 (en) * 2007-02-08 2008-08-13 BAUER Maschinen GmbH Winching device
US9624076B2 (en) * 2014-04-04 2017-04-18 David R. Hall Synchronized motorized lifting devices for lifting shared loads
CN104085809B (en) * 2014-06-30 2016-05-04 东北大学 A kind of self-adapting load hoisting mechanism
KR102642682B1 (en) * 2023-11-02 2024-03-04 주식회사 에스디호이스트 Rewinding device for correcting rope twist and drum rope winding method using the device

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GB655450A (en) * 1949-06-08 1951-07-18 Austin Hopkinson Improvements in or relating to hoisting or haulage gear
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Also Published As

Publication number Publication date
ZA912071B (en) 1991-12-24
FI93202B (en) 1994-11-30
FR2659951A1 (en) 1991-09-27
BG60028A3 (en) 1993-07-15
RO107397B1 (en) 1993-11-30
DE69103937T2 (en) 1995-02-09
HU910932D0 (en) 1991-10-28
YU47960B (en) 1996-07-24
FI911314A (en) 1991-09-22
YU47291A (en) 1994-09-09
HU208286B (en) 1993-09-28
CS76691A2 (en) 1991-09-15
HUT60695A (en) 1992-10-28
ES2062586T3 (en) 1994-12-16
JPH04223997A (en) 1992-08-13
DE69103937D1 (en) 1994-10-20
FI911314A0 (en) 1991-03-18
FR2659951B1 (en) 1992-05-29
CA2038711C (en) 1993-12-21
EP0448021A1 (en) 1991-09-25
KR910016614A (en) 1991-11-05
CA2038711A1 (en) 1991-09-22
US5324007A (en) 1994-06-28
FI93202C (en) 1995-03-10

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