EP1514832A1 - Lifting device - Google Patents

Lifting device Download PDF

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Publication number
EP1514832A1
EP1514832A1 EP03405677A EP03405677A EP1514832A1 EP 1514832 A1 EP1514832 A1 EP 1514832A1 EP 03405677 A EP03405677 A EP 03405677A EP 03405677 A EP03405677 A EP 03405677A EP 1514832 A1 EP1514832 A1 EP 1514832A1
Authority
EP
European Patent Office
Prior art keywords
boom
arrow
dart
foot
counterweight
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.)
Withdrawn
Application number
EP03405677A
Other languages
German (de)
French (fr)
Inventor
Jean-Marc Yerly
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.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP03405677A priority Critical patent/EP1514832A1/en
Priority to AU2004272136A priority patent/AU2004272136A1/en
Priority to AT04761917T priority patent/ATE446275T1/en
Priority to DE602004023738T priority patent/DE602004023738D1/en
Priority to CA002539014A priority patent/CA2539014A1/en
Priority to US10/571,982 priority patent/US7331476B2/en
Priority to PCT/CH2004/000577 priority patent/WO2005026036A1/en
Priority to EP04761917A priority patent/EP1667931B1/en
Publication of EP1514832A1 publication Critical patent/EP1514832A1/en
Withdrawn legal-status Critical Current

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    • 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
    • B66C23/62—Constructional features or details
    • B66C23/64—Jibs
    • B66C23/68—Jibs foldable or otherwise adjustable in configuration
    • 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
    • B66C23/62—Constructional features or details
    • B66C23/72—Counterweights or supports for balancing lifting couples
    • B66C23/74—Counterweights or supports for balancing lifting couples separate from jib
    • B66C23/76—Counterweights or supports for balancing lifting couples separate from jib and movable to take account of variations of load or of variations of length of jib

Definitions

  • the present invention relates to a hoist and load handling with directional distributor arrow, comprising a pylon with a rotating pivot, a mounted boom in articulation at the top of the pylon by an axis of rotation horizontal arranged at the first end of the said arrow, an arrow lifting device and a restraint assembly arrow comprising a punch, at least one sling of boom retainer and a mobile counterweight connected to the boom by said restraining sling.
  • cranes are usually used horizontal directional distributor arrow, on which slides a trolley serving as a guide to ways of suspension of charges.
  • the lift cranes have the advantage, for example compared to horizontal boom cranes, to be able to bring loads at greater heights, at tower heights comparable.
  • the effort of the dead weight of an arrow operating in workable mode of work varies considerably between arrow positions close to the horizontal and position raised close to the vertical. That's why this type of crane is sometimes equipped with a mobile counterweight, whose position varies depending on the angle that the arrow with the horizontal.
  • DE 3438937 discloses a boom crane lift-able, with a platform at the top of the pylon, carrying a counterweight disposed at one end of an oscillating arm.
  • the position of the arm is slaved to the angular position of the boom, attached to the other end of the swingarm, such so that the counterweight is close to the axis of rotation of the pylon when the arrow is raised, and spreads in a pendulum motion when the arrow tilts horizontally.
  • This device assists the operation of lifting for important lifting angles.
  • This kind of crane always requires a lifting device to high torque.
  • EP 379448 discloses a luffing jib crane comprising a rotating pivot, on which is mounted the boom, a platform carrying the boom lift mechanisms and lifting loads and a mobile counterweight, fixed at the back of the pivot, opposite the arrow.
  • the counterweight is mounted rolling on straight spars of the platform, which have a slight slope directed towards the axis of pylon.
  • the counterweight is connected by a tie rod to the boom, via a pulley, so that deviate from the pylon when the arrow falls towards horizontally and to get closer to the pylon when the arrow is raised.
  • This device makes it possible to compensate the moment of the dead weight of the boom on the pylon structure but the lifting requires a mechanism providing a very important.
  • Port-type cranes can also be used. with articulated horizontal directional distributor arrow, moving the load, moving away respectively bringing it closer to the pivot axis of the crane by deployment, respectively refolding the arrow.
  • the moment of the own weight of an arrow of this type varies considerably between the extended position of the arrow and the folded position towards the pylon. He is difficult to balance these variations of effort by a single counterweight mobile.
  • Document DE 1 260 733 describes a crane of this type and proposes to reduce or even eliminate the counterweight and use a distribution reminder cable, attached to the end of the dart tip, cooperating with a cable arrow retainer acting on the end of the counter-dart, via punches and return pulleys, these two cables being operated by winches.
  • the implementation of these winches require engines with very high torque.
  • Patent FR 2605619 discloses a collapsible lifting device that combines the effects of a bailing crane articulated with those of a crane with a distributing boom liftable, giving it a certain versatility.
  • this crane because of the design of the joints of the dispenser boom, this crane always has a reach minimal importance.
  • the hook height gain when the point of the arrow is raised remains relatively weak, can not exceed an angular amplitude equivalent to 30 ° to the horizontal.
  • Applicant's patent application EP 1057776 describes a folding lifting machine with directional distributing boom able to work in articulated mode or in lift mode.
  • the arrow consists of an arrow foot, the first of which end is mounted in rotation at the top of the pylon, and a dart mounted in articulation on the second end of the foot of arrow, this dart being delimited by this articulation in two parts, namely a counter-dart and a dart tip.
  • the counter-dart and the part of foot of arrow near this joint are consistent so that the foot of the arrow and the dart can come into alignment in a work-up mode, which increases both the horizontal reach and the height maximum under hook of the machine.
  • This device uses a distribution cable not held by guides on a great length when the arrow is almost completely deployed, resulting in stability problems in rotation and in distribution under load and headwind.
  • Applicant's patent application WO 02/04336 describes collapsible lifting gear and tower cranes, with arrows adjustable, articulated, liftable and tilting darts.
  • the part of the neighboring arrow foot the dart and counter-dart have shapes conjugates allowing the dart tip to come into aligned with the boom foot in working mode lift.
  • a system of jacks is arranged at the level of the articulation between the foot of the arrow and the dart for Deploy and reposition the arrow working horizontal or reclining articulated.
  • These cranes may include a mobile counterweight system for balance the crane in all working positions.
  • the system may comprise in combination a fixed counterweight, example at the end of the platform mechanisms, a main counterbalance counterweight and a second counterweight oscillating corrector.
  • a fixed counterweight example at the end of the platform mechanisms
  • a main counterbalance counterweight example at the end of the platform mechanisms
  • a second counterweight oscillating corrector The adjustment of masses and positions of the three counterweights helps balance these cranes optimally in the different work modes liftable, tilting and articulated.
  • the object of the present invention is to propose a machine lifting of the defined type of entry that does not show the disadvantages mentioned above.
  • the object of the present invention is in particular to propose a hoist with the same character of versatility of use as that described in the WO document 02/04336 while lowering the cost of manufacturing, in simplifying implementation and, in addition, reducing the clutter below the platform.
  • the boom restraint system of the hoist according to the invention may comprise only one sling of detention. However, it is best to use a set two slings and two punches with their return pulleys respective slings being arranged and attached to and other of the arrow, symmetrically with respect to the plane of symmetry of it.
  • the following description describes, for the sake of didactic simplification, a hoist equipped with a restraining sling. It applies mutatis mutandis to a craft equipped with two slings.
  • the guideway according to the invention is arranged in the opposite of the arrow, that is to say that projection view vertically on a horizontal plane, it extends into the opposite direction of the projection of the arrow with respect to the axis of rotation of the pylon.
  • lateral view it presents the profile of a curve, the slope variations being chosen by the manufacturer according to the efforts requested by the arrow.
  • the curvilinear guideway has in its 1 st portion, the closest to the pylon, a weak slope, lower than the slope of a second portion of the track, further from the pylon.
  • the guideway can thus have two portions of constant but different slopes, connected by a rounded.
  • the guideway may have a more complex profile, in particular a sigmoidal profile.
  • the mobile counterweight is provided with rolling means, and the guideway is a rolling track on which roll said rolling means.
  • Such a running track can be achieved by means of a pair of curved rails parallel to each other, and the counterweight may consist of a carriage movable on these rails, and ballast elements carried by the said carriage.
  • F and C correspond to the components of the vector P respectively parallel and perpendicular to the guideway
  • ⁇ varies according to x, the function ⁇ (x) being determined by the choice of the profile curvilinear guideway made by the manufacturer of the crane.
  • the distance x of the counterweight to the axis of the pylon itself being a decreasing function of the angle what does the foot of arrow with the horizontal, because of the sling, the choice of the profile of the curvilinear bearing according to the invention makes it possible to modulate a component of the foot of the arrow, so that it automatically assists the lifting mechanism of the arrow, and / or the mechanism (s) operating the deployment and the folding of the boom, such as cylinders, motors, winches.
  • variable recall component in lift-up, hinged or tilting working mode the use of mechanical lifting devices offering a maximum torque and lower maximum power.
  • variable recall component of the counterweight also allows the use of less devices powerful and lighter than cylinders to operate the arrow in articulated work mode for distribution horizontal loads.
  • the counterweight system according to the invention can be applied to lifting gear with articulated dispensing boom, or with machines luffing jib, or gear with articulated and liftable boom, or with articulated boom, lift and tilting dart.
  • the counterweight system can in particular be used for gear whose boom includes a foot of articulated arrow at the top of the pylon by its first end, a dart articulated in rotation at the second end of the foot of arrow, the said dart comprising of else from its axis of articulation to the foot of arrow respectively a dart tip and a counter-dart, the said second end of the arrow foot and the counter-dart having conjugate forms allowing the dart tip coming into position aligned with the boom foot in the upright work position, the end the boom retaining sling being attached to the dart.
  • the counter-dart and the second end of the arrow foot can present profiles prismatic conjugates and come into contact one against the other when the foot of the arrow and the dart are aligned.
  • the second end of the foot of arrow can present the form of a fork to two branches and the counter-dart comes to lodge in the space between the two branches.
  • the boom foot consists of two parallel beams and the counter-dart is housed in the gap between two beams.
  • the boom can have an arrow / dart lock as those described in WO 02/04336.
  • the rotation of the jib around the 2nd end of the jib foot is performed by means of a system of opposing cables wound and unwound by means of electric winches.
  • these winches, a portion of the cables and their return pulleys can be housed in the foot of the arrow.
  • the rotation of the dart around the end of the arrow foot is realized by means of a gear system comprising a motor, a pinion and a toothed segment.
  • the engine is fixed on the foot of arrow and drives, via a pinion, a circular toothed segment in solidarity with the dart.
  • FIG. 2 is a schematic view, in profile, of a mode of the guideway 1 of the counterweight 100.
  • a illustrative title she was represented with a ballast 110 in two different positions and with support arms 108, 109 which carry it, the other elements of the crane having deleted for the sake of simplification.
  • the path of bearing may consist of two rails 2, 3 curvilinear and parallel, which are visible both, in section, on the Figure 5. However, in all schematic views side showing the crane, only one rail is shown.
  • the rolling track 1 can have a length of the order of 5 to 20 meters.
  • Zone A the closest to the pylon, has a slight slope, making an angle ⁇ A with the horizontal of 2 ° to 25 °. Moving away from the crane, the slope increases.
  • the raceway can form an angle ⁇ B of the order of 15 ° to 85 ° with the horizontal.
  • the slope decreases again, the path forming an angle ⁇ c of 2 ° to 45 °.
  • the ballast mass is twenty tons and the slope of ⁇ A is 5 °, the restoring force F A is of the order of 17 kN.
  • the ballast essentially exerts a torque on the structure of the crane, which torque, at a distance x A , is about Px A.
  • the slope is maximum and, in the embodiment shown in FIG. 2, of the order of 50 °.
  • the restoring force that the ballast exerts on the boom retaining sling becomes much larger.
  • this restoring force corresponds approximately to the component of the weight P parallel to this guideway, ie F b .
  • zone C slightly sloping, this force of reminder decreases again.
  • the skilled person will observe without only if in Area C the slope remained constant and equal to the maximum value reached in zone B, the force recall in zone C the maximum value reached in zone B.
  • Figure 3 shows the restoring force as a function of the distance between counterweight and pylon for three systems of different counterweights. In all three systems, the mass total counterweight is 20 tons.
  • Curve (b) represents the restoring force of a pendular counterweight, attached to the end of a swing arm 12 meters long, cumbersome.
  • Curve (c) represents the return force obtained at means of a raceway according to the invention similar to that of Figure 2, for which the slope is 3 ° to near the pylon, then increases to a maximum of 53 ° at a distance of 9 meters, to reduce thereafter, the slope being of the order of 30 ° at the end of the track.
  • the profile of the curve (c) is determined by the choice of the profile of the guide way that is to say by the variations of slope between the zones A, B and C shown in FIG. 2.
  • FIGS 4 and 5 show, respectively in profile and front, an embodiment of the counterweight according to the invention.
  • the cart is usually designated by 101.
  • the chassis of the trolley consists of four longitudinal beams, two external beams 102 and two internal beams 103 connected by four beams transverse 104.
  • Each beam 102, 103 carries two roller bearing devices 105 which roll on both curvilinear rails 2 and 3 constituting the raceway.
  • the outer longitudinal beams 102 each carry three substantially vertical support beams, namely a upper beam 106 and two lower beams 107, constituting three points of support.
  • Each longitudinal beam 102 also carries two support arms 108, 109.
  • These support arms are preferably mounted inclined to remove the games between ballast elements, which come to support one another against others, and against points of support.
  • the support arms, and the corresponding fixing means of the elements ballast are arranged so that the level of the center of gravity of the counterweight is close to, and preferably substantially coincides with the level of the track at where the cart is, to avoid swaying during the movements of the crane.
  • Support arms can be mounted on articulations allowing them to fold, in order to reduce the size of the trolley during transportation.
  • Each pair of unfolded arms 108, 109 receives one or more ballast mass (s).
  • FIGS. 2 and 5 these ballast masses may consist of concrete slabs with two holes allowing them to be hang on support arms 108 and 109.
  • Holes 111 can be made in the form of two turned squares angularly 90 ° relative to each other and spaced from each other so that the support arms 108 and 109 are placed in the corners as shown in the figure 2. Those skilled in the art will readily understand that this provision allows both easy placement of the weights on the support arms, the dimensions of the holes 111 being clearly greater than the diameter of the support arms 108 and 109, and on the other hand avoids a tilting of masses and shocks corresponding when the moving carriage moves between the zone A and the zones B and C of the raceway. Setting in place of the weights on the cart is completed by putting in place of a set of bars 113 and security cables 112 between the support arm and the support beams of the carriage.
  • FIGs 1a and 1b show an arrow crane articulated, maximum jib foot and dart folded against the foot of the arrow.
  • the ballast masses come very close to the pylon, framing it on both sides, as shown in Figure 1b.
  • the masses of ballast on the one hand and the mass of the arrow on the other hand relatively low stresses on the tower and the chassis rolling the crane, so that moving the crane standing is possible on the site, by means of a chase, without the need to dismantle the crane to move it.
  • Jacks 33 can lift and adjust the level of the crane during such a displacement.
  • Figures 6a and 6b show the operation of the counterweight on a hoist whose boom is working in working mode.
  • Figure 6a shows the machine, the arrow 10 being almost horizontal, in the range position Max.
  • the counterweight 100 represented so simplified in Figure 6a by a square ballast and a set of pebbles, is in the distal zone of lane 1 by relative to the axis of the tower.
  • the arrow 10 is raised in the minimum range position.
  • the sling 11 of boom retainer is attached at its first end to counterweight 100. It passes on a pulley 9 arranged at the distal end of the track and on a second deflection pulley 8 arranged at the top of the punch 7.
  • the other end 12 of the restraining sling is attached to the arrow, at the same level as the easel 13.
  • the easel 13 serves as a point of attachment to the lifting device.
  • the lifting device may consist of several parts, namely a lifting tie 14, connecting the lifting bridge to a pulley or muffle 16, and a cable lift 15, which can make several strands of muffle.
  • the lifting cable 15 is connected to a lifting winch 17 of which the reel is arranged on the solidarity platform of the track rolling.
  • the boom retainer 11 cooperates with the lifting motor device for raising the boom.
  • FIGS. 6b can be a rigid boom or articulated boom as that of Figure 7c.
  • Figures 7a, 7b and 7c illustrate the operation an articulated boom operating in distribution mode articulated horizontal.
  • Figure 7a similar to the figure 1a, shows the arrow in position of minimum range, dart 18 folded against the foot of arrow 19.
  • Figure 7c shows the arrow 10 in a position similar to that of FIG. 6a, in the maximum range position, the boom foot and the dart being aligned.
  • Figure 7b shows the arrow in one position Intermediate deployment.
  • the counterweight 100 is about halfway and that the pull component on the retaining sling 11 of the arrow is important.
  • Arrow lift 14 attached to the bridge 13 passes on the end 21 of the counter-dart 20 who returns it.
  • the hinge 32 formed by a horizontal axis of rotation between the boom foot 19 and the dart 18 delimits the latter between dart 22 and counter-dart 20. It is at this level that is attached in 12 the sling retaining 11.
  • the rotation of the dart around the hinge axis 32 is carried out using two opposing cables 23 and 24.
  • the winding coils 25, 26 of the cables 24 and 23 can be arranged in the foot of arrow, for example near the joint 27 of the first end of the arrow foot at the top of the pylon.
  • a pulley 29 of the cables 23, 24 is arranged in the foot of arrow, in an area near the articulation 32 between foot of arrow and dart as shown in the figure.
  • Figure 7a shows the area of the arrow surrounding the 32 foot joint arrow / arrow in the position of Figure 7a.
  • 1 '(the) arrow retainer (s) pass (s) a little below and to the right of the 32 foot joint of / jib; the lifting cable 15 and the tie rod 14 boom lift pass on the end 21 of the counter-dart and lie a little to the left of the joint 32 between foot of arrow and dart.
  • Cables 23 and 24 have antagonistic effects. From this position, the cable upper 23 is controlled by the crane operator and the lower cable 24 unfolds. The upper cable 23 is deflected by the cane superior 30.
  • the upper cable 23 always draws on the counter-dart, in order to continue the deployment movement but the upper cane 30 does not deviate plus the upper cable 23.
  • the lower cable 24 is always drive through the top cable.
  • the upper cable 23 always draws on the counter-dart, in order to continue to deploy the arrow, and the lower cable 24 is always done drive through the upper cable. It will be noted that the cable lower 24 comes into contact with lower cane 31 and that the holding sling 11 has passed the hinge 32 between foot of arrow and dart.
  • the tie rod lift 14 is no longer in contact with the end 21 of the against jib.
  • the lower cane 31 increases the angle of traction of the lower cable 24 to reduce the efforts of this one and to ensure the stability of the elements around the articulation 32.
  • the contribution restoring force of the boom retaining sling 11 decreases. This is why it is preferable that the distal zone of the Guideway 1 indicated as zone C in FIG. 2 has a slope lower than the slope of zone B.
  • Figures 9a and 9b illustrate the way of working at tilting dart of the previously articulated boom described in relation to the groups of Figures 7 and 8.
  • the jib foot 19 does not move, it is in support against a device of stop 33.
  • stop devices are known in the state of the art.
  • the mobile counterweight 100 is located in both positions in a low slope area of the track, near the pylon.
  • this attachment point 12 describes a arc around the articulation 32 of the arrow, driving the counterweight in a limited displacement.
  • the set of antagonistic cables 24 and 23 with their winches winding and unwinding 25, 26 arranged in the foot of arrow is replaced by a gear system 200, composed a motor 201, a pinion 202 and a toothed segment 203, arranged at the level of the articulation 232 between the foot of arrow 204 and the dart 205.
  • the electric motor 201 is fixed on the foot of arrow, it drives a pinion 202 which itself meshes with a circular toothed segment 203 integral with the dart, to ensure the rotation of the dart around articulation 232 between the foot of the arrow and the dart.
  • the arrangement and function of the restraining slings 11 of boom and lift tie 14 are the same as those of the modes of execution described above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
  • Valve Device For Special Equipments (AREA)
  • Magnetic Heads (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Earth Drilling (AREA)

Abstract

The machinery has counter-weights (100) moving in a curvilinear guiding path (1) arranged opposite a boom. Slope variation of the path is chosen such that the counter-weights exert a variable traction on the boom through a hold back (11). The traction assists deployment/folding movement of the boom in articulated or inclinable working mode and/or change of conformation of the boom associated to a change of working mode.

Description

La présente invention concerne un engin de levage et de manutention de charges à flèche distributrice orientable, comprenant un pylône avec un pivot tournant, une flèche montée en articulation au sommet du pylône par un axe de rotation horizontal agencé à la première extrémité de la dite flèche, un dispositif de relevage de flèche et un ensemble de retenue de flèche comprenant un poinçon, au moins une élingue de retenue de flèche et un contrepoids mobile relié à la flèche par la dite élingue de retenue.The present invention relates to a hoist and load handling with directional distributor arrow, comprising a pylon with a rotating pivot, a mounted boom in articulation at the top of the pylon by an axis of rotation horizontal arranged at the first end of the said arrow, an arrow lifting device and a restraint assembly arrow comprising a punch, at least one sling of boom retainer and a mobile counterweight connected to the boom by said restraining sling.

Pour permettre la manutention de charges sur des chantiers de construction, on utilise habituellement des grues à flèche distributrice horizontale orientable, sur laquelle coulisse un chariot servant de guide à des moyens de suspension des charges.To allow the handling of loads on construction sites, cranes are usually used horizontal directional distributor arrow, on which slides a trolley serving as a guide to ways of suspension of charges.

Dans certaines circonstances, par exemple lorsque les chantiers sont encombrés ou lorsque la législation interdit le survol de parcelles jouxtant le chantier, on leur préfère des grues à flèche distributrice relevable et orientable. Les grues à flèche distributrice relevable ont l'avantage, par rapport aux grues à flèche horizontale, de pouvoir amener des charges à de plus grandes hauteurs, à hauteurs de pylônes comparables. L'effort du poids mort d'une flèche opérant en mode de travail relevable varie considérablement entre les positions de la flèche proches de l'horizontale et la position relevée proche de la verticale. C'est pourquoi ce type de grue est quelquefois muni d'un contrepoids mobile, dont la position varie en fonction de l'angle que fait la flèche avec l'horizontale.In certain circumstances, for example when construction sites are congested or where legislation prohibits overflight of parcels adjacent to the site, they are preferred cranes with lifting and tilting distributor boom. The lift cranes have the advantage, for example compared to horizontal boom cranes, to be able to bring loads at greater heights, at tower heights comparable. The effort of the dead weight of an arrow operating in workable mode of work varies considerably between arrow positions close to the horizontal and position raised close to the vertical. That's why this type of crane is sometimes equipped with a mobile counterweight, whose position varies depending on the angle that the arrow with the horizontal.

Le document DE 3438937 décrit une grue à flèche relevable, avec une plate-forme au sommet du pylône, portant un contrepoids disposé à une extrémité d'un bras oscillant. La position du bras est asservie à la position angulaire de la flèche, fixée à l'autre extrémité du bras oscillant, de telle sorte que le contrepoids se trouve à proximité de l'axe de rotation du pylône lorsque la flèche est relevée, et s'en écarte en un mouvement pendulaire lorsque la flèche s'incline vers l'horizontale. Ce dispositif assiste peu l'opération de relevage pour des angles de relevages importants. Ce type de grue nécessite toujours un dispositif moteur de relevage à couple élevé.DE 3438937 discloses a boom crane lift-able, with a platform at the top of the pylon, carrying a counterweight disposed at one end of an oscillating arm. The position of the arm is slaved to the angular position of the boom, attached to the other end of the swingarm, such so that the counterweight is close to the axis of rotation of the pylon when the arrow is raised, and spreads in a pendulum motion when the arrow tilts horizontally. This device assists the operation of lifting for important lifting angles. This kind of crane always requires a lifting device to high torque.

Le document EP 379448 décrit une grue à flèche relevable comprenant un pivot tournant, sur lequel est montée la flèche, une plate-forme portant les mécanismes de relevage de flèche et de levage des charges ainsi qu'un contrepoids mobile, fixée à l'arrière du pivot, à l'opposé de la flèche. Le contrepoids est monté roulant sur des longerons rectilignes de la plate-forme, qui présentent une légère pente dirigée vers l'axe du pylône. Le contrepoids est relié par un tirant de retenue à la flèche, via une poulie de renvoi, de telle sorte à s'écarter du pylône lorsque la flèche s'abaisse vers l'horizontale et à se rapprocher du pylône lorsque la flèche est relevée. Ce dispositif permet de compenser le moment du poids mort de la flèche sur la structure du pylône, mais le relevage nécessite un mécanisme fournissant un couple très important.EP 379448 discloses a luffing jib crane comprising a rotating pivot, on which is mounted the boom, a platform carrying the boom lift mechanisms and lifting loads and a mobile counterweight, fixed at the back of the pivot, opposite the arrow. The counterweight is mounted rolling on straight spars of the platform, which have a slight slope directed towards the axis of pylon. The counterweight is connected by a tie rod to the boom, via a pulley, so that deviate from the pylon when the arrow falls towards horizontally and to get closer to the pylon when the arrow is raised. This device makes it possible to compensate the moment of the dead weight of the boom on the pylon structure but the lifting requires a mechanism providing a very important.

On peut également recourir à des grues de type portuaire, à flèche distributrice horizontale orientable articulée, effectuant un déplacement de la charge, éloignant respectivement rapprochant celle-ci de l'axe de pivotement de la grue par déploiement, respectivement reploiement de la flèche. Le moment du poids propre d'une flèche de ce type varie considérablement entre la position déployée de la flèche et la position repliée vers le pylône. Il est difficile d'équilibrer ces variations d'effort par un seul contrepoids mobile.Port-type cranes can also be used. with articulated horizontal directional distributor arrow, moving the load, moving away respectively bringing it closer to the pivot axis of the crane by deployment, respectively refolding the arrow. The moment of the own weight of an arrow of this type varies considerably between the extended position of the arrow and the folded position towards the pylon. He is difficult to balance these variations of effort by a single counterweight mobile.

Le document DE 1 260 733 décrit une grue de ce type et propose de réduire, voire de supprimer le contrepoids et de recourir à un câble de rappel de distribution, fixé à l'extrémité de la pointe de fléchette, coopérant avec un câble de retenue de flèche agissant sur l'extrémité de la contre-fléchette, via des poinçons et des poulies de renvoi, ces deux câbles étant actionnés par des treuils. La mise en oeuvre de ces treuils nécessite des moteurs à très fort couple.Document DE 1 260 733 describes a crane of this type and proposes to reduce or even eliminate the counterweight and use a distribution reminder cable, attached to the end of the dart tip, cooperating with a cable arrow retainer acting on the end of the counter-dart, via punches and return pulleys, these two cables being operated by winches. The implementation of these winches require engines with very high torque.

Le brevet FR 2605619 décrit un engin de levage repliable qui combine les effets d'une grue à flèche distributrice articulée avec ceux d'une grue à flèche distributrice relevable, lui conférant ainsi une certaine polyvalence. Toutefois, du fait de la conception des articulations de la flèche distributrice, cette grue possède toujours une portée minimale importante. De plus, le gain de hauteur sous crochet lorsque la pointe de la flèche est relevée reste relativement faible, ne pouvant dépasser une amplitude angulaire équivalente à 30° par rapport à l'horizontale.Patent FR 2605619 discloses a collapsible lifting device that combines the effects of a bailing crane articulated with those of a crane with a distributing boom liftable, giving it a certain versatility. However, because of the design of the joints of the dispenser boom, this crane always has a reach minimal importance. In addition, the hook height gain when the point of the arrow is raised remains relatively weak, can not exceed an angular amplitude equivalent to 30 ° to the horizontal.

La demande de brevet EP 1057776 du déposant décrit un engin de levage repliable à flèche distributrice orientable capable de travailler en mode articulé ou en mode relevable. La flèche est constituée d'un pied de flèche dont la première extrémité est montée en rotation au sommet du pylône, et d'une fléchette montée en articulation sur la deuxième extrémité du pied de flèche, cette fléchette étant délimitée par cette articulation en deux parties, à savoir une contre-fléchette et une pointe de fléchette. La contre-fléchette et la partie du pied de flèche proche de cette articulation sont conformées de telle sorte que le pied de flèche et la fléchette puissent venir en alignement en mode de travail relevable, ce qui augmente à la fois la portée horizontale et la hauteur maximale sous crochet de l'engin. Ce dispositif fait appel à un câble de distribution non maintenu par des guides sur une grande longueur lorsque la flèche est presque entièrement déployée, d'où des problèmes de stabilité en rotation et en distribution sous charge et vent de face. Applicant's patent application EP 1057776 describes a folding lifting machine with directional distributing boom able to work in articulated mode or in lift mode. The arrow consists of an arrow foot, the first of which end is mounted in rotation at the top of the pylon, and a dart mounted in articulation on the second end of the foot of arrow, this dart being delimited by this articulation in two parts, namely a counter-dart and a dart tip. The counter-dart and the part of foot of arrow near this joint are consistent so that the foot of the arrow and the dart can come into alignment in a work-up mode, which increases both the horizontal reach and the height maximum under hook of the machine. This device uses a distribution cable not held by guides on a great length when the arrow is almost completely deployed, resulting in stability problems in rotation and in distribution under load and headwind.

La demande de brevet WO 02/04336 du déposant décrit des engins de levage repliables et des grues sur tour, à flèches distributrices orientables, articulées, relevables et à fléchettes inclinables. La partie du pied de flèche voisine de la fléchette et la contre-fléchette présentent des formes conjuguées permettant à la pointe de fléchette de venir en position alignée avec le pied de flèche en mode de travail relevable. Un système de vérins est agencé au niveau de l'articulation entre le pied de flèche et la fléchette pour assurer le déploiement et le reploiement de la flèche en mode de travail articulé horizontal ou inclinable. Ces grues peuvent comporter un système de contrepoids mobile pour équilibrer la grue dans toutes les positions de travail. Ce système peut comporter en combinaison un contrepoids fixe, par exemple à l'extrémité de la plate-forme des mécanismes, un contrepoids pendulaire principal et un deuxième contrepoids oscillant correcteur. L'ajustement des masses et des positions des trois contrepoids permet d'équilibrer ces grues de façon optimale dans les différents modes de travail relevable, inclinable et articulé.Applicant's patent application WO 02/04336 describes collapsible lifting gear and tower cranes, with arrows adjustable, articulated, liftable and tilting darts. The part of the neighboring arrow foot the dart and counter-dart have shapes conjugates allowing the dart tip to come into aligned with the boom foot in working mode lift. A system of jacks is arranged at the level of the articulation between the foot of the arrow and the dart for Deploy and reposition the arrow working horizontal or reclining articulated. These cranes may include a mobile counterweight system for balance the crane in all working positions. This The system may comprise in combination a fixed counterweight, example at the end of the platform mechanisms, a main counterbalance counterweight and a second counterweight oscillating corrector. The adjustment of masses and positions of the three counterweights helps balance these cranes optimally in the different work modes liftable, tilting and articulated.

Toutefois, le fonctionnement d'un tel système de contrepoids peut se révéler délicat à régler. Par ailleurs, l'articulation de la flèche, constituée de vérins, est relativement onéreuse, sa commande manque de précision et son poids contribue à alourdir l'ensemble de la flèche.However, the operation of such a system of counterweight can be tricky to adjust. Otherwise, the articulation of the boom, consisting of jacks, is relatively expensive, his order lacks precision and his weight helps to weigh down the entire boom.

Le but de la présente invention est de proposer un engin de levage du type défini d'entrée qui ne présente pas les inconvénients mentionnés ci-dessus.The object of the present invention is to propose a machine lifting of the defined type of entry that does not show the disadvantages mentioned above.

Le but de la présente invention est en particulier de proposer un engin de levage présentant le même caractère de polyvalence d'utilisation que celui décrit dans le document WO 02/04336 tout en abaissant le coût de fabrication, en simplifiant la mise en oeuvre et, de plus, en réduisant l'encombrement en-dessous de la plate-forme. The object of the present invention is in particular to propose a hoist with the same character of versatility of use as that described in the WO document 02/04336 while lowering the cost of manufacturing, in simplifying implementation and, in addition, reducing the clutter below the platform.

Ces buts sont atteints grâce à un contrepoids asservi à suivre une voie de guidage curviligne agencée à l'opposé de la flèche, dont les variations de pente sont choisies de telle sorte que le contrepoids exerce, via la ou les élingue(s) de retenue de flèche, une traction variable sur cette flèche, assistant le dispositif de relevage et/ou le mouvement de déploiement/reploiement de la flèche en mode articulé, et/ou les changements de conformation de la flèche associés à un changement de mode de travail.These goals are achieved through a counterweight to follow a curvilinear guideway arranged opposite the arrow, whose slope variations are chosen from so that the counterweight exerts, via the sling (s) of arrow restraint, a variable traction on this arrow, assist the lifting device and / or the movement of deployment / folding of the boom in articulated mode, and / or the conformation changes of the arrow associated with a change of work mode.

L'ensemble de retenue de flèche de l'engin de levage selon l'invention peut ne comporter qu'une seule élingue de retenue. Il est cependant préférable d'employer un ensemble de deux élingues et deux poinçons avec leurs poulies de renvoi respectives, les élingues étant agencées et attachées de part et d'autre de la flèche, symétriquement par rapport au plan de symétrie de celle-ci. L'exposé ci-dessous décrit, par souci de simplification didactique, un engin de levage équipé d'une élingue de retenue. Il s'applique mutatis mutandis à un engin équipé de deux élingues.The boom restraint system of the hoist according to the invention may comprise only one sling of detention. However, it is best to use a set two slings and two punches with their return pulleys respective slings being arranged and attached to and other of the arrow, symmetrically with respect to the plane of symmetry of it. The following description describes, for the sake of didactic simplification, a hoist equipped with a restraining sling. It applies mutatis mutandis to a craft equipped with two slings.

La voie de guidage selon l'invention est agencée à l'opposé de la flèche, c'est-à-dire que vue en projection verticale sur un plan horizontal, elle s'étend dans la direction opposée de la projection de la flèche par rapport à l'axe de rotation du pylône. D'autre part, en vue latérale, elle présente le profil d'une courbe, les variations de pente étant choisies par le constructeur en fonction des efforts demandés par la flèche.The guideway according to the invention is arranged in the opposite of the arrow, that is to say that projection view vertically on a horizontal plane, it extends into the opposite direction of the projection of the arrow with respect to the axis of rotation of the pylon. On the other hand, in lateral view, it presents the profile of a curve, the slope variations being chosen by the manufacturer according to the efforts requested by the arrow.

De préférence, la voie de guidage curviligne présente dans sa 1ère portion, la plus proche du pylône, une pente faible, plus faible que la pente d'une deuxième portion de la voie, plus éloignée du pylône. La voie de guidage peut ainsi présenter deux portions de pentes constantes mais différentes, reliées par un arrondi. La voie de guidage peut présenter un profil plus complexe, en particulier un profil sigmoïdal. Preferably, the curvilinear guideway has in its 1 st portion, the closest to the pylon, a weak slope, lower than the slope of a second portion of the track, further from the pylon. The guideway can thus have two portions of constant but different slopes, connected by a rounded. The guideway may have a more complex profile, in particular a sigmoidal profile.

De préférence, pour minimiser les forces de frottement, le contrepoids mobile est muni de moyens de roulement, et la voie de guidage est une voie de roulement sur laquelle roulent les dits moyens de roulement.Preferably, to minimize frictional forces, the mobile counterweight is provided with rolling means, and the guideway is a rolling track on which roll said rolling means.

Une telle voie de roulement peut être réalisée au moyen d'une paire de rails courbes parallèles entre eux, et le contrepoids peut être constitué d'un chariot, mobile sur ces rails, et d'éléments de lest portés par le dit chariot.Such a running track can be achieved by means of a pair of curved rails parallel to each other, and the counterweight may consist of a carriage movable on these rails, and ballast elements carried by the said carriage.

Un contrepoids de poids P placé sur la voie de roulement, lorsqu'il est situé à une distance x de l'axe du pylône, en une zone où la voie de guidage présente un angle α avec l'horizontale, exerce d'une part une force de rappel F sur la flèche via l'élingue de retenue et les poulies de renvoi, et d'autre part un couple C sur les structures de la grue, s'opposant au couple exercé par le poids propre de la flèche sur le pylône. En première approximation, F et C correspondent aux composantes du vecteur P respectivement parallèle et perpendiculaire à la voie de guidage, et F ≅ P.sinα C ≅ P.x A counterweight of weight P placed on the track, when it is located at a distance x from the axis of the pylon, in an area where the guideway has an angle α with the horizontal, on the one hand a restoring force F on the boom via the holding sling and the return pulleys, and secondly a torque C on the structures of the crane, opposing the torque exerted by the own weight of the boom on the pylon. In a first approximation, F and C correspond to the components of the vector P respectively parallel and perpendicular to the guideway, and F ≅ P.sinα C ≅ Px

Or selon l'invention, α varie en fonction de x, la fonction α(x) étant déterminée par le choix du profil curviligne de la voie de guidage fait par le constructeur de la grue. La distance x du contrepoids par rapport à l'axe du pylône étant elle-même une fonction décroissante de l'angle que fait le pied de flèche avec l'horizontale, du fait de l'élingue de retenue, le choix du profil de la voie de roulement curviligne selon l'invention permet de moduler une composante de rappel du pied de flèche, de telle sorte que celle-ci assiste automatiquement le mécanisme de relevage de la flèche, et/ou le ou les mécanisme(s) opérant le déploiement et le reploiement de la flèche, tels que vérins, moteurs, treuils. According to the invention, α varies according to x, the function α (x) being determined by the choice of the profile curvilinear guideway made by the manufacturer of the crane. The distance x of the counterweight to the axis of the pylon itself being a decreasing function of the angle what does the foot of arrow with the horizontal, because of the sling, the choice of the profile of the curvilinear bearing according to the invention makes it possible to modulate a component of the foot of the arrow, so that it automatically assists the lifting mechanism of the arrow, and / or the mechanism (s) operating the deployment and the folding of the boom, such as cylinders, motors, winches.

Les relations (I) et (II) ne sont données qu'à titre illustratif du principe de l'invention. Elles ne tiennent pas compte de facteurs correctifs liés aux positions en élévation du centre de gravité du contrepoids, des points d'attache de la/des élingue(s) de retenue et des poulies de renvoi. Ces équations ne sauraient donc définir des limitations de l'étendue de la protection recherchée.Relations (I) and (II) are given only as illustrative of the principle of the invention. They do not hold corrective factors related to elevation positions the center of gravity of the counterweight, the attachment points of the sling (s) and the return pulleys. These equations can not therefore define the extent of protection sought.

L'utilisation de cette composante de rappel variable en mode de travail relevable, articulé ou inclinable permet l'emploi de dispositifs mécaniques de relevage offrant un couple maximal et une puissance maximale moins élevés.The use of this variable recall component in lift-up, hinged or tilting working mode the use of mechanical lifting devices offering a maximum torque and lower maximum power.

L'utilisation de cette composante de rappel variable du contrepoids permet également l'emploi de dispositifs moins puissants et plus légers que des vérins pour faire opérer la flèche en mode de travail articulé pour la distribution horizontale des charges.The use of this variable recall component of the counterweight also allows the use of less devices powerful and lighter than cylinders to operate the arrow in articulated work mode for distribution horizontal loads.

Le système de contrepoids selon l'invention peut s'appliquer à des engins de levage
à flèche distributrice articulée, ou à des engins
à flèche relevable, ou à des engins
à flèche articulée et relevable, ou encore
à flèche articulée, relevable et fléchette inclinable.The counterweight system according to the invention can be applied to lifting gear
with articulated dispensing boom, or with machines
luffing jib, or gear
with articulated and liftable boom, or
with articulated boom, lift and tilting dart.

Le système de contrepoids peut en particulier être utilisé pour des engins dont la flèche comprend un pied de flèche articulé au sommet du pylône par sa première extrémité, une fléchette articulée en rotation à la deuxième extrémité du pied de flèche, la dite fléchette comportant de part et d'autre de son axe d'articulation au pied de flèche respectivement une pointe de fléchette et une contre-fléchette, la dite deuxième extrémité du pied de flèche et la contre-fléchette présentant des formes conjuguées permettant à la pointe de fléchette de venir en position alignée avec le pied de flèche en position de travail relevable, l'extrémité de l'élingue de retenue de flèche étant fixée à la fléchette.The counterweight system can in particular be used for gear whose boom includes a foot of articulated arrow at the top of the pylon by its first end, a dart articulated in rotation at the second end of the foot of arrow, the said dart comprising of else from its axis of articulation to the foot of arrow respectively a dart tip and a counter-dart, the said second end of the arrow foot and the counter-dart having conjugate forms allowing the dart tip coming into position aligned with the boom foot in the upright work position, the end the boom retaining sling being attached to the dart.

L'architecture générale de tels engins de levage, et notamment des structures et formes avantageuses de pieds de flèche et de fléchettes sont décrites dans le document WO 02/04336 dont le contenu est incorporé à la présente demande par référence. La contre-fléchette et la deuxième extrémité du pied de flèche peuvent présenter des profils prismatiques conjugués et viennent en contact l'une contre l'autre lorsque pied de flèche et fléchette sont alignés. Selon d'autres formes d'exécution, la deuxième extrémité du pied de flèche peut présenter la forme d'une fourche à deux branches et la contre-fléchette vient se loger dans l'espace entre les deux branches. Selon d'autres formes encore, le pied de flèche est constitué de deux poutres parallèles et la contre-fléchette vient se loger dans l'écartement entre les deux poutres. Lorsque le pied de flèche est réalisé sous forme de fourche ou sous forme de deux poutres, la flèche peut comporter un dispositif de blocage pied de flèche/fléchette tel que ceux décrits dans le document WO 02/04336.The general architecture of such lifting gear, and particular structures and advantageous forms of feet of arrow and darts are described in the document WO 02/04336 whose content is incorporated herein. request by reference. The counter-dart and the second end of the arrow foot can present profiles prismatic conjugates and come into contact one against the other when the foot of the arrow and the dart are aligned. According to other embodiments, the second end of the foot of arrow can present the form of a fork to two branches and the counter-dart comes to lodge in the space between the two branches. In still other forms, the boom foot consists of two parallel beams and the counter-dart is housed in the gap between two beams. When the arrow foot is made under fork shape or in the form of two beams, the boom can have an arrow / dart lock as those described in WO 02/04336.

Selon un mode de réalisation préféré, la rotation de la fléchette autour de la 2ème extrémité du pied de flèche est effectuée au moyen d'un système de câbles antagonistes enroulés et déroulés au moyen de treuils électriques. Selon un mode d'exécution particulier, ces treuils, une partie des câbles et leurs poulies de renvoi peuvent être logés dans le pied de flèche.According to a preferred embodiment, the rotation of the jib around the 2nd end of the jib foot is performed by means of a system of opposing cables wound and unwound by means of electric winches. According to a particular embodiment, these winches, a portion of the cables and their return pulleys can be housed in the foot of the arrow.

Selon un autre mode de réalisation préféré, la rotation de la fléchette autour de l'extrémité du pied de flèche est réalisée au moyen d'un système d'engrenage comprenant un moteur, un pignon et un segment denté. Selon un mode d'exécution particulier, le moteur est fixé sur le pied de flèche et entraíne, via un pignon, un segment denté circulaire solidaire de la fléchette. According to another preferred embodiment, the rotation of the dart around the end of the arrow foot is realized by means of a gear system comprising a motor, a pinion and a toothed segment. According to a mode of particular execution, the engine is fixed on the foot of arrow and drives, via a pinion, a circular toothed segment in solidarity with the dart.

D'autres caractéristiques et avantages de l'invention apparaítront à l'homme du métier de la description ci-dessous de modes d'exécution particuliers en relation avec le dessin, dans lequel:

  • La figure 1 présente deux vues schématiques, de profil en 1a et de face en 1b, d'une grue de chantier selon l'invention, montée sur un chenillard, flèche repliée et relevée, la fléchette étant rabattue contre le pied de flèche.
  • La figure 2 est une vue schématique de profil, d'une voie de roulement de contrepoids.
  • La figure 3 compare les variations de la force de rappel d'un contrepoids selon l'invention avec celles de contrepoids de l'art antérieur.
  • La figure 4 est une vue de profil d'un contrepoids.
  • La figure 5 est une vue de face d'un contrepoids.
  • Les figures 6a et 6b sont deux vues schématiques, de profil, d'une grue à flèche relevable.
  • Les figures 7a, 7b et 7c sont trois vues schématiques, de profil, d'une grue à flèche articulée.
  • Le groupe de figures 8, c'est-à-dire 8a, 8b, 8c, 8d et 8e, sont des vues de détail illustrant le fonctionnement de la grue des figures 7a, 7b et 7c.
  • Les figures 9a, 9b sont deux vues schématiques de profil d'une grue opérant en mode de travail à fléchette inclinable.
  • Les figures 10a 10b et 10c sont trois vues schématiques illustrant un autre mode d'exécution de grue à flèche articulée.
Other features and advantages of the invention will become apparent to those skilled in the art from the following description of particular embodiments in connection with the drawing, in which:
  • Figure 1 shows two schematic views, in profile 1a and front 1b, of a construction crane according to the invention, mounted on a chase, folded arrow and raised, the dart being folded against the foot of arrow.
  • Figure 2 is a schematic side view of a counterweight rolling track.
  • FIG. 3 compares the variations of the restoring force of a counterweight according to the invention with those of the counterweight of the prior art.
  • Figure 4 is a side view of a counterweight.
  • Figure 5 is a front view of a counterweight.
  • Figures 6a and 6b are two schematic views, in profile, of a luffing jib crane.
  • Figures 7a, 7b and 7c are three schematic views, in profile, of an articulated boom crane.
  • Figures 8, 8a, 8b, 8c, 8d and 8e are detail views illustrating the operation of the crane of Figures 7a, 7b and 7c.
  • Figures 9a, 9b are two schematic profile views of a crane operating in tilting jib work mode.
  • Figures 10a 10b and 10c are three schematic views illustrating another embodiment of articulated boom crane.

La figure 2 est une vue schématique, de profil, d'un mode d'exécution de la voie de guidage 1 du contrepoids 100. A titre illustratif, elle a été représentée avec un lest 110 dans deux positions différentes et avec les bras de support 108, 109 qui le portent, les autres éléments de la grue ayant été supprimés par souci de simplification. La voie de roulement peut être constituée de deux rails 2, 3 curvilignes et parallèles, qui sont visibles tous deux, en coupe, sur la figure 5. Toutefois, dans toutes les vues schématiques latérales montrant la grue, un seul rail est représenté.FIG. 2 is a schematic view, in profile, of a mode of the guideway 1 of the counterweight 100. A illustrative title, she was represented with a ballast 110 in two different positions and with support arms 108, 109 which carry it, the other elements of the crane having deleted for the sake of simplification. The path of bearing may consist of two rails 2, 3 curvilinear and parallel, which are visible both, in section, on the Figure 5. However, in all schematic views side showing the crane, only one rail is shown.

Selon le gabarit d'ensemble de la grue la voie de roulement 1 peut avoir une longueur de l'ordre de 5 à 20 mètres. La zone A, la plus proche du pylône, présente une pente faible, faisant un angle αA avec l'horizontale de 2° à 25°. En s'éloignant de la grue, la pente augmente. Dans la zone indiquée par B sur la figure 2, la voie de roulement peut former un angle αB de l'ordre de 15° à 85° avec l'horizontale. Enfin, dans la zone indiquée par C, proche de l'extrémité distale de la voie de roulement par rapport à l'axe du pylône, la pente diminue à nouveau, la voie formant un angle αc de 2° à 45°.According to the overall jig of the crane the rolling track 1 can have a length of the order of 5 to 20 meters. Zone A, the closest to the pylon, has a slight slope, making an angle α A with the horizontal of 2 ° to 25 °. Moving away from the crane, the slope increases. In the zone indicated by B in FIG. 2, the raceway can form an angle α B of the order of 15 ° to 85 ° with the horizontal. Finally, in the area indicated by C, close to the distal end of the track relative to the axis of the tower, the slope decreases again, the path forming an angle α c of 2 ° to 45 °.

Sur la figure 2, on a schématisé les composantes des forces qu'une masse de lest exerce sur les autres parties de la grue.In Figure 2, we have schematized the components of the forces that a mass of ballast exerts on the other parts of the the crane.

Si on décompose le vecteur poids P en ses composantes respectivement perpendiculaire et parallèle à l'axe de la voie, on constate que dans la zone A, la composante parallèle à la voie FA est très petite. La force de rappel du lest sur l'élingue de retenue est faible, mais suffit à maintenir cette élingue tendue, le chariot tendant à revenir vers le pylône. A titre d'exemple, si la masse de lest est de vingt tonnes et si la pente de αA est de 5°, la force de rappel FA est de l'ordre de 17 kN. Le lest exerce essentiellement un couple sur la structure de la grue, couple qui, à une distance xA, vaut environ P.xA. If one decomposes the weight vector P in its components respectively perpendicular and parallel to the axis of the way, one finds that in zone A, the component parallel to the way F A is very small. The restoring force of the ballast on the restraining sling is weak, but it is sufficient to keep the sling stretched, the carriage tending to return to the pylon. By way of example, if the ballast mass is twenty tons and the slope of α A is 5 °, the restoring force F A is of the order of 17 kN. The ballast essentially exerts a torque on the structure of the crane, which torque, at a distance x A , is about Px A.

Dans la zone indiquée par B, la pente est maximale et, dans le mode d'exécution représenté sur la figure 2, de l'ordre de 50°. La force de rappel que le lest exerce sur l'élingue de retenue de flèche devient beaucoup plus importante. Sous réserve de la position du point d'attache de l'élingue de retenue au contrepoids et de la position de la poulie de renvoi, qui est située à proximité de l'extrémité distale de la voie de roulement, mais qui peut être agencée sur cette dernière, ou au-dessus, ou au-dessous, cette force de rappel correspond approximativement à la composante du poids P parallèle à cette voie de guidage, soit Fb.In the zone indicated by B, the slope is maximum and, in the embodiment shown in FIG. 2, of the order of 50 °. The restoring force that the ballast exerts on the boom retaining sling becomes much larger. Subject to the position of the point of attachment of the restraining sling to the counterweight and the position of the return pulley, which is located near the distal end of the track, but which may be arranged on the latter, or above, or below, this restoring force corresponds approximately to the component of the weight P parallel to this guideway, ie F b .

Dans la zone C, légèrement moins pentue, cette force de rappel diminue à nouveau. L'homme du métier observera sans peine que si dans la zone C, la pente restait constante et égale à la valeur maximale atteinte dans la zone B, la force de rappel conserverait dans la zone C la valeur maximale atteinte dans la zone B.In zone C, slightly sloping, this force of reminder decreases again. The skilled person will observe without only if in Area C the slope remained constant and equal to the maximum value reached in zone B, the force recall in zone C the maximum value reached in zone B.

La figure 3 représente la force de rappel en fonction de la distance entre contrepoids et pylône pour trois systèmes de contrepoids différents. Dans les trois systèmes, la masse totale du contrepoids est de 20 tonnes. La courbe (a) représente la force de rappel pour une voie de roulement à profil rectiligne, correspondant par exemple à celui décrit dans EP 379448, avec α = 5°. La courbe (b) représente la force de rappel d'un contrepoids pendulaire, accroché à l'extrémité d'un bras oscillant de 12 mètres de long, encombrant.Figure 3 shows the restoring force as a function of the distance between counterweight and pylon for three systems of different counterweights. In all three systems, the mass total counterweight is 20 tons. The curve (a) represents the restoring force for a raceway to rectilinear profile, corresponding for example to that described in EP 379448, with α = 5 °. Curve (b) represents the restoring force of a pendular counterweight, attached to the end of a swing arm 12 meters long, cumbersome.

La courbe (c) représente la force de rappel obtenue au moyen d'une voie de roulement selon l'invention similaire à celle de la figure 2, pour laquelle la pente vaut 3° à proximité du pylône, augmente ensuite jusqu'à un maximum de 53° à une distance de 9 mètres, pour rediminuer ensuite, la pente étant de l'ordre de 30° à l'extrémité de la voie. Le profil de la courbe (c) est déterminé par le choix du profil de la voie de guidage c'est-à-dire par les variations de pente entre les zones A, B et C représentées sur la figure 2.Curve (c) represents the return force obtained at means of a raceway according to the invention similar to that of Figure 2, for which the slope is 3 ° to near the pylon, then increases to a maximum of 53 ° at a distance of 9 meters, to reduce thereafter, the slope being of the order of 30 ° at the end of the track. The profile of the curve (c) is determined by the choice of the profile of the guide way that is to say by the variations of slope between the zones A, B and C shown in FIG. 2.

Les figures 4 et 5 représentent, respectivement de profil et de face, un mode d'exécution du contrepoids selon l'invention. Dans ces figures, le chariot est généralement désigné par 101. Le châssis du chariot est constitué de quatre poutres longitudinales, deux poutres extérieures 102 et deux poutres intérieures 103, reliées par quatre poutres transversales 104. Chaque poutre 102, 103 porte deux dispositifs de roulement à galets 105 qui roulent sur les deux rails curvilignes 2 et 3 constituant la voie de roulement. Les poutres longitudinales extérieures 102 portent chacune trois poutres d'appui sensiblement verticales, à savoir une poutre supérieure 106 et deux poutres inférieures 107, constituant trois points d'appui. Chaque poutre longitudinale 102 porte également deux bras-support 108, 109. Ces bras-support sont de préférence montés inclinés pour supprimer les jeux entre éléments de lest, qui viennent s'appuyer les uns contre les autres, et contre les points d'appui. Les bras-support, et les moyens de fixation correspondants des éléments de lest sont agencés de telle sorte que le niveau du centre de gravité du contrepoids soit proche du, et de préférence coïncide sensiblement avec le niveau de la voie de roulement à l'endroit où se trouve le chariot, pour éviter des balancements lors des mouvements de la grue. Les bras-support peuvent être montés sur des articulations permettant de les replier, en vue de diminuer l'encombrement du chariot pendant le transport. Chaque paire de bras dépliés 108, 109 reçoit une ou plusieurs masse(s) de lest 110. Comme le montrent les figures 2 et 5, ces masses de lest peuvent être constituées de dalles de béton munies de deux trous permettant de les accrocher sur les bras-support 108 et 109. Les trous 111 peuvent être réalisés sous forme de deux carrés tournés angulairement de 90° l'un par rapport à l'autre et espacés l'un de l'autre de telle sorte que les bras-support 108 et 109 viennent se placer dans les angles comme le montre la figure 2. L'homme du métier comprendra aisément que cette disposition permet à la fois un placement facile des lests sur les bras-support, les dimensions des trous 111 étant nettement supérieures au diamètre des bras-support 108 et 109, et d'autre part évite un basculement des masses et les chocs correspondants lorsque le chariot mobile se déplace entre la zone A et les zones B et C de la voie de roulement. La mise en place des lests sur le chariot est parachevée par la mise en place d'un ensemble de barres 113 et câbles de sécurité 112 entre bras-support et poutres d'appui du chariot.Figures 4 and 5 show, respectively in profile and front, an embodiment of the counterweight according to the invention. In these figures, the cart is usually designated by 101. The chassis of the trolley consists of four longitudinal beams, two external beams 102 and two internal beams 103 connected by four beams transverse 104. Each beam 102, 103 carries two roller bearing devices 105 which roll on both curvilinear rails 2 and 3 constituting the raceway. The outer longitudinal beams 102 each carry three substantially vertical support beams, namely a upper beam 106 and two lower beams 107, constituting three points of support. Each longitudinal beam 102 also carries two support arms 108, 109. These support arms are preferably mounted inclined to remove the games between ballast elements, which come to support one another against others, and against points of support. The support arms, and the corresponding fixing means of the elements ballast are arranged so that the level of the center of gravity of the counterweight is close to, and preferably substantially coincides with the level of the track at where the cart is, to avoid swaying during the movements of the crane. Support arms can be mounted on articulations allowing them to fold, in order to reduce the size of the trolley during transportation. Each pair of unfolded arms 108, 109 receives one or more ballast mass (s). FIGS. 2 and 5, these ballast masses may consist of concrete slabs with two holes allowing them to be hang on support arms 108 and 109. Holes 111 can be made in the form of two turned squares angularly 90 ° relative to each other and spaced from each other so that the support arms 108 and 109 are placed in the corners as shown in the figure 2. Those skilled in the art will readily understand that this provision allows both easy placement of the weights on the support arms, the dimensions of the holes 111 being clearly greater than the diameter of the support arms 108 and 109, and on the other hand avoids a tilting of masses and shocks corresponding when the moving carriage moves between the zone A and the zones B and C of the raceway. Setting in place of the weights on the cart is completed by putting in place of a set of bars 113 and security cables 112 between the support arm and the support beams of the carriage.

L'homme du métier constatera également sur la figure 5 que les deux rails curvilignes 2 et 3 sont reliés par un ensemble de poutres transversales 4 constituant ainsi une sorte de plate-forme qui peut recevoir un ou plusieurs treuils 5, poinçons ou tirants de poinçons 6.The skilled person will also note in Figure 5 that the two curvilinear rails 2 and 3 are connected by a set of transverse beams 4 thus constituting a sort of platform that can receive one or more winches 5, punches or tie rods 6.

Les figures 1a et 1b montrent une grue à flèche articulée, pied de flèche relevé au maximum et fléchette repliée contre le pied de flèche. Dans la position où le pied de flèche est entièrement relevé, les masses de lest viennent très près du pylône, en l'encadrant de part et d'autre, comme le montre la figure 1b. Dans cette position, les masses de lest d'une part et la masse de la flèche d'autre part exercent des contraintes relativement faibles sur la tour et le châssis roulant de la grue, de sorte que le déplacement de la grue debout est possible sur le chantier, au moyen d'un chenillard, sans qu'il y ait besoin de démonter la grue pour la déplacer. Des vérins 33 peuvent permettre de soulever et de régler le niveau de la grue lors d'un tel déplacement.Figures 1a and 1b show an arrow crane articulated, maximum jib foot and dart folded against the foot of the arrow. In the position where the foot boom is fully raised, the ballast masses come very close to the pylon, framing it on both sides, as shown in Figure 1b. In this position, the masses of ballast on the one hand and the mass of the arrow on the other hand relatively low stresses on the tower and the chassis rolling the crane, so that moving the crane standing is possible on the site, by means of a chase, without the need to dismantle the crane to move it. Jacks 33 can lift and adjust the level of the crane during such a displacement.

Les figures 6a et 6b montrent le fonctionnement du contrepoids sur un engin de levage dont la flèche fonctionne en mode de travail relevable. La figure 6a montre l'engin, la flèche 10 étant presque à l'horizontale, en position de portée maximale. Le contrepoids 100, représenté de manière simplifiée sur la figure 6a par un lest carré et un jeu de galets, se trouve dans la zone distale de la voie 1 par rapport à l'axe de la tour. Sur la figure 6b, la flèche 10 est relevée en position de portée minimum. L'élingue 11 de retenue de flèche est fixée à sa première extrémité au contrepoids 100. Elle passe sur une poulie de renvoi 9 agencée à l'extrémité distale de la voie de roulement et sur une deuxième poulie de renvoi 8 agencée au sommet du poinçon 7. L'autre extrémité 12 de l'élingue de retenue est fixée à la flèche, au même niveau que le chevalet 13. Le chevalet 13 sert de point d'attache au dispositif de relevage. Le dispositif de relevage peut être constitué de plusieurs parties, à savoir un tirant de relevage 14, reliant le chevalet de relevage à une poulie ou un moufle 16, et un câble de relevage 15, qui peut faire plusieurs brins de moufle. Le câble de relevage 15 est relié à un treuil de relevage 17 dont la bobine est agencée sur la plate-forme solidaire de la voie de roulement.Figures 6a and 6b show the operation of the counterweight on a hoist whose boom is working in working mode. Figure 6a shows the machine, the arrow 10 being almost horizontal, in the range position Max. The counterweight 100, represented so simplified in Figure 6a by a square ballast and a set of pebbles, is in the distal zone of lane 1 by relative to the axis of the tower. In Figure 6b, the arrow 10 is raised in the minimum range position. The sling 11 of boom retainer is attached at its first end to counterweight 100. It passes on a pulley 9 arranged at the distal end of the track and on a second deflection pulley 8 arranged at the top of the punch 7. The other end 12 of the restraining sling is attached to the arrow, at the same level as the easel 13. The easel 13 serves as a point of attachment to the lifting device. The lifting device may consist of several parts, namely a lifting tie 14, connecting the lifting bridge to a pulley or muffle 16, and a cable lift 15, which can make several strands of muffle. The lifting cable 15 is connected to a lifting winch 17 of which the reel is arranged on the solidarity platform of the track rolling.

L'élingue de retenue 11 de flèche coopère avec le dispositif moteur de relevage pour relever la flèche. En se référant à la figure 3, on constatera que sa contribution est importante dans les positions proches de celle montrée par la figure 6a, c'est-à-dire lorsqu'un couple de relevage important est nécessaire, et faible dans les positions proches de celle de la figure 6b, c'est-à-dire lorsque le dispositif moteur de relevage n'a besoin que d'un couple faible. Le système de contrepoids selon l'invention permet donc de diminuer le couple nominal maximal du dispositif de relevage.The boom retainer 11 cooperates with the lifting motor device for raising the boom. By getting Referring to Figure 3, it will be seen that his contribution is important in positions close to that shown by the Figure 6a, that is to say, when a large lifting torque is necessary, and weak in positions close to that of FIG. 6b, that is to say when the driving device of lifting only needs a low torque. The system of counterweight according to the invention thus makes it possible to reduce maximum rated torque of the lifting device.

On notera que la flèche 10 montrée sur les figures 6a et 6b peut être une flèche rigide ou une flèche articulée comme celle de la figure 7c.It will be noted that the arrow 10 shown in FIGS. 6b can be a rigid boom or articulated boom as that of Figure 7c.

Les figures 7a, 7b et 7c illustrent le fonctionnement d'une flèche articulée fonctionnant en mode de distribution articulée horizontale. La figure 7a, similaire à la figure 1a, montre la flèche en position de portée minimale, fléchette 18 repliée contre pied de flèche 19. La figure 7c montre la flèche 10 dans une position similaire à celle de la figure 6a, en position de portée maximale, le pied de flèche et la fléchette étant alignés.Figures 7a, 7b and 7c illustrate the operation an articulated boom operating in distribution mode articulated horizontal. Figure 7a, similar to the figure 1a, shows the arrow in position of minimum range, dart 18 folded against the foot of arrow 19. Figure 7c shows the arrow 10 in a position similar to that of FIG. 6a, in the maximum range position, the boom foot and the dart being aligned.

La figure 7b montre la flèche dans une position intermédiaire de déploiement. L'homme du métier constatera en particulier que dans la position illustrée par la figure 7b, le contrepoids 100 est environ à mi-course et que la composante de traction sur l'élingue de retenue 11 de la flèche est importante. Le tirant de relevage 14 de flèche attaché au chevalet 13 passe sur l'extrémité 21 de la contre-fléchette 20 qui le renvoie. L'articulation 32 formée par un axe de rotation horizontal entre le pied de flèche 19 et la fléchette 18 délimite cette dernière entre pointe de fléchette 22 et contre-fléchette 20. C'est à ce niveau qu'est attaché en 12 l'élingue de retenue 11. La rotation de la fléchette autour de l'axe d'articulation 32 est réalisée à l'aide de deux câbles antagonistes 23 et 24. Les bobines d'enroulement 25, 26 des câbles 24 et 23 peuvent être agencées dans le pied de flèche, par exemple à proximité de l'articulation 27 de la première extrémité du pied de flèche au sommet du pylône. Une poulie de renvoi 29 des câbles 23, 24 est agencée dans le pied de flèche, dans une zone proche de l'articulation 32 entre pied de flèche et fléchette, comme l'illustre la figure.Figure 7b shows the arrow in one position Intermediate deployment. The skilled person will see in particular in the position illustrated in Figure 7b, the counterweight 100 is about halfway and that the pull component on the retaining sling 11 of the arrow is important. Arrow lift 14 attached to the bridge 13 passes on the end 21 of the counter-dart 20 who returns it. The hinge 32 formed by a horizontal axis of rotation between the boom foot 19 and the dart 18 delimits the latter between dart 22 and counter-dart 20. It is at this level that is attached in 12 the sling retaining 11. The rotation of the dart around the hinge axis 32 is carried out using two opposing cables 23 and 24. The winding coils 25, 26 of the cables 24 and 23 can be arranged in the foot of arrow, for example near the joint 27 of the first end of the arrow foot at the top of the pylon. A pulley 29 of the cables 23, 24 is arranged in the foot of arrow, in an area near the articulation 32 between foot of arrow and dart as shown in the figure.

Le fonctionnement de la distribution horizontale depuis la portée minimale (figure 7a) jusqu'à la portée maximale, figure 7c, en mode de travail articulé est illustré plus en détails par les figures 8a, 8b, 8c, 8d et 8e. La figure 8a montre la zone de la flèche entourant l'articulation 32 pied de flèche/fléchette dans la position de la figure 7a. On notera que 1' (les) élingues(s) de retenue de flèche passe(nt) un peu en-dessous et à droite de l'articulation 32 pied de flèche/fléchette; le câble de relevage 15 et le tirant de relevage 14 de flèche passent sur l'extrémité 21 de la contre-fléchette et se trouvent un peu à gauche de l'articulation 32 entre pied de flèche et fléchette. Les câbles 23 et 24 ont des effets antagonistes. A partir de cette position, le câble supérieur 23 est commandé par le grutier et le câble inférieur 24 se déroule. Le câble supérieur 23 est dévié par la canne supérieure 30.The operation of the horizontal distribution since the minimum range (Figure 7a) to the maximum range, Figure 7c, in articulated work mode is shown more in details in FIGS. 8a, 8b, 8c, 8d and 8e. Figure 8a shows the area of the arrow surrounding the 32 foot joint arrow / arrow in the position of Figure 7a. We note that 1 '(the) arrow retainer (s) pass (s) a little below and to the right of the 32 foot joint of / jib; the lifting cable 15 and the tie rod 14 boom lift pass on the end 21 of the counter-dart and lie a little to the left of the joint 32 between foot of arrow and dart. Cables 23 and 24 have antagonistic effects. From this position, the cable upper 23 is controlled by the crane operator and the lower cable 24 unfolds. The upper cable 23 is deflected by the cane superior 30.

Dans la position montrée par la figure 8b, le câble supérieur 23 tire sur la contre-fléchette, afin de continuer l'opération de déploiement, la canne supérieure 30 déviant toujours le câble supérieur 23. Le câble inférieur 24 se fait alors entraíner par le câble supérieur 23, la vitesse étant pilotée par le grutier.In the position shown in Figure 8b, the cable superior 23 pulls the counter-dart, in order to continue the deployment operation, the upper cane deviant always the upper cable 23. The lower cable 24 is then lead by the upper cable 23, the speed being driven by the crane operator.

Au stade montré par la figure 8c, le câble supérieur 23 tire toujours sur la contre-fléchette, afin de continuer le mouvement de déploiement, mais la canne supérieure 30 ne dévie plus le câble supérieur 23. Le câble inférieur 24 se fait toujours entraíner par le câble supérieur.At the stage shown in FIG. 8c, the upper cable 23 always draws on the counter-dart, in order to continue the deployment movement but the upper cane 30 does not deviate plus the upper cable 23. The lower cable 24 is always drive through the top cable.

Au stade montré par la figure 8d, le câble supérieur 23 tire toujours sur la contre-fléchette, afin de continuer à déployer la flèche, et le câble inférieur 24 se fait toujours entraíner par le câble supérieur. On notera que le câble inférieur 24 entre en contact avec la canne inférieure 31 et que l'élingue de retenue 11 a dépassé l'articulation 32 entre pied de flèche et fléchette.At the stage shown in FIG. 8d, the upper cable 23 always draws on the counter-dart, in order to continue to deploy the arrow, and the lower cable 24 is always done drive through the upper cable. It will be noted that the cable lower 24 comes into contact with lower cane 31 and that the holding sling 11 has passed the hinge 32 between foot of arrow and dart.

Dans la position illustrée par la figure 8e, le tirant de relevage 14 n'est plus en contact avec l'extrémité 21 de la contre-fléchette. La canne inférieure 31 augmente l'angle de traction du câble inférieur 24 afin de diminuer les efforts de celui-ci et d'assurer la stabilité des éléments autour de l'articulation 32.In the position illustrated in Figure 8e, the tie rod lift 14 is no longer in contact with the end 21 of the against jib. The lower cane 31 increases the angle of traction of the lower cable 24 to reduce the efforts of this one and to ensure the stability of the elements around the articulation 32.

Pour la fraction du déploiement qui se situe entre les figures 8d et 8e, il est préférable que la contribution en force de rappel de l'élingue de retenue de flèche 11 diminue. C'est pourquoi il est préférable que la zone distale de la voie de guidage 1 indiquée comme zone C sur la figure 2 présente une pente inférieure à la pente de la zone B.For the fraction of the deployment that lies between figures 8d and 8e, it is preferable that the contribution restoring force of the boom retaining sling 11 decreases. This is why it is preferable that the distal zone of the Guideway 1 indicated as zone C in FIG. 2 has a slope lower than the slope of zone B.

Les figures 9a et 9b illustrent le mode de travail à fléchette inclinable de la flèche articulée précédemment décrite en relation avec les groupes de figures 7 et 8. Entre les deux positions des figures 9a et 9b, le pied de flèche 19 ne se déplace pas, il est en appui contre un dispositif de butée 33. De tels dispositifs de butée sont connus dans l'état de la technique. Le contrepoids mobile 100 est situé dans les deux positions dans une zone de pente faible de la voie de roulement, à proximité du pylône. Toutefois, du fait de la distance non nulle entre le point d'attache 12 de l'élingue de retenue de flèche et de l'articulation 32 entre pied de flèche et fléchette, ce point d'attache 12 décrit un arc de cercle autour de l'articulation 32 de la flèche, entraínant le contrepoids dans un déplacement limité. Les variations de moment du contrepoids vis-à-vis du pylône qui en résultent équilibrent les variations du moment du poids de la flèche dues à la rotation de la fléchette. La rotation de la fléchette autour de l'articulation 32 avec le pied de flèche est assurée par les systèmes de câbles antagonistes 24 et 23 de la même manière qu'exposé plus haut en relation avec le groupe de figures 8.Figures 9a and 9b illustrate the way of working at tilting dart of the previously articulated boom described in relation to the groups of Figures 7 and 8. Between the two positions of FIGS. 9a and 9b, the jib foot 19 does not move, it is in support against a device of stop 33. Such stop devices are known in the state of the art. The mobile counterweight 100 is located in both positions in a low slope area of the track, near the pylon. However, because the non-zero distance between the point of attachment 12 of the boom retaining sling and articulation 32 between foot of arrow and dart, this attachment point 12 describes a arc around the articulation 32 of the arrow, driving the counterweight in a limited displacement. The variations of moment of the counterweight with respect to the pylon which in result balance the moment variations of the weight of the arrow due to the rotation of the dart. The rotation of the dart around the hinge 32 with the arrow foot is provided by the opposing cable systems 24 and 23 in the same way as explained above in relation to the group of figures 8.

Dans un autre mode d'exécution de l'engin de levage selon l'invention, illustré par les figures 10a, 10b et 10c, l'ensemble de câbles antagonistes 24 et 23 avec leurs treuils d'enroulement et de déroulement 25, 26 agencés dans le pied de flèche est remplacé par un système d'engrenage 200, composé d'un moteur 201, d'un pignon 202 et d'un segment denté 203, agencés au niveau de l'articulation 232 entre le pied de flèche 204 et la fléchette 205. Le moteur électrique 201 est fixé sur le pied de flèche, il entraíne un pignon 202 qui lui-même engrène avec un segment denté circulaire 203 solidaire de la fléchette, pour assurer la rotation de la fléchette autour de l'articulation 232 entre pied de flèche et fléchette. L'agencement et la fonction des élingues de retenue 11 de flèche et du tirant de relevage 14 sont les mêmes que ceux des modes d'exécution décrits plus haut.In another embodiment of the hoist according to the invention, illustrated by FIGS. 10a, 10b and 10c, the set of antagonistic cables 24 and 23 with their winches winding and unwinding 25, 26 arranged in the foot of arrow is replaced by a gear system 200, composed a motor 201, a pinion 202 and a toothed segment 203, arranged at the level of the articulation 232 between the foot of arrow 204 and the dart 205. The electric motor 201 is fixed on the foot of arrow, it drives a pinion 202 which itself meshes with a circular toothed segment 203 integral with the dart, to ensure the rotation of the dart around articulation 232 between the foot of the arrow and the dart. The arrangement and function of the restraining slings 11 of boom and lift tie 14 are the same as those of the modes of execution described above.

Dans toutes les positions de la portée définie par le grutier, la stabilité de l'extrémité de la flèche est assurée par un frein électro-mécanique à manque de courant installé sur les moteurs des câbles 23 et 24.In all positions of the scope defined by the crane operator, the stability of the end of the boom is ensured by an electromechanical brake with no current installed on the motors of the cables 23 and 24.

Claims (14)

Engin de levage et de manutention de charges à flèche distributrice orientable comprenant un pylône avec un pivot tournant, une flèche (10) montée en articulation au sommet du pylône par un axe de rotation horizontal (27) agencé à la première extrémité de ladite flèche, un dispositif de relevage de flèche (14, 15, 17) et un ensemble de retenue de flèche comprenant un poinçon (7), au moins une élingue de retenue (11) de flèche et un contrepoids mobile relié à la flèche par ladite élingue de retenue, caractérisé en ce que le contrepoids (100) est asservi à suivre une voie de guidage curviligne (1) agencée à l'opposé de la flèche, dont les variations de pente (α) sont choisies de sorte que le contrepoids exerce, via ladite élingue de retenue (11) de flèche, une traction variable sur ladite flèche, assistant le dit dispositif de relevage et/ou le mouvement de déploiement/reploiement de la flèche en mode de travail articulé ou inclinable et/ou les changements de conformation de la flèche associés à un changement de mode de travail.Loader lifting and handling machine with directional distributing boom comprising a pylon with a rotating pivot, an arrow (10) mounted in articulation at the top of the pylon by a horizontal axis of rotation (27) arranged at the first end of said boom, an arrow lifting device (14, 15, 17) and an arrow holding assembly comprising a punch (7), at least one boom holding sling (11) and a movable counterweight connected to the boom by said sling of retainer, characterized in that the counterweight (100) is slaved to follow a curvilinear guideway (1) arranged opposite the arrow, whose slope variations (α) are chosen so that the counterweight exerts, via said deflection retaining sling (11), variable traction on said boom, assisting said lifting device and / or boom deployment / folding movement in articulated or tilting working mode and / or changing Boom conformation nts associated with a change of work mode. Engin de levage selon la revendication 1, caractérisé en ce que la voie de guidage curviligne (1) présente dans sa portion (A) la plus proche du pylône une pente (αA) plus faible que la pente (αB) dans au moins une portion (B) plus éloignée du pylône.Lifting machine according to claim 1, characterized in that the curvilinear guideway (1) has in its portion (A) closest to the pylon a slope (α A ) lower than the slope (α B ) in at least a portion (B) farther from the pylon. Engin de levage selon l'une des revendications 1 ou 2 caractérisé en ce que la voie de guidage curviligne (1) présente un profil sygmoïdal.Lifting machine according to one of claims 1 or 2 characterized in that the curvilinear guideway (1) has a sygmoidal profile. Engin de levage selon l'une des revendications précédentes, caractérisé en ce que le contrepoids mobile (1) est muni de moyens de roulement (105) et que la voie de guidage constitue une voie de roulement pour les dits moyens de roulement. Lifting vehicle according to one of the preceding claims, characterized in that the movable counterweight (1) is provided with rolling means (105) and that the guide track constitutes a raceway for said rolling means. Engin de levage selon la revendication 4, caractérisé en ce que la voie de roulement (1) est constituée d'une paire de rails curvilignes (2, 3) parallèles et que le contrepoids comprend un chariot mobile (101) sur lesdits rails et des éléments de lest (110) portés par ledit chariot.Lifting machine according to claim 4, characterized in that the rolling path (1) consists of a pair of parallel curvilinear rails (2, 3) and that the counterweight comprises a movable carriage (101) on said rails and ballast elements (110) carried by said carriage. Engin de levage selon la revendication 5, caractérisé en ce que le chariot (101) comprend un châssis (102, 103, 104) et sur chacun des côtés latéraux du châssis, deux bras de support (108, 109) agencés en position inclinée pour recevoir et porter lesdits éléments de lest (110) de part et d'autre des rails de telle sorte que le niveau du centre de gravité du contrepoids soit proche du niveau de la voie de roulement, et en ce que lesdits bras de support sont repliables.Lifting machine according to claim 5, characterized in that the carriage (101) comprises a frame (102, 103, 104) and on each of the lateral sides of the frame, two support arms (108, 109) arranged in an inclined position for receiving and carrying said ballast elements (110) on either side of the rails so that the level of the center of gravity of the counterweight is close to the level of the raceway, and in that said support arms are collapsible . Engin de levage selon l'une des revendications 5 ou 6, caractérisé en ce que lesdits éléments de lest (110) sont constitués de plaques présentant chacune des trous (111) de surface supérieure à la section des bras de support (108, 109) et configurés de façon à ce qu'un élément de lest suspendu à une paire de bras-support associés soit maintenu en position immobile par rapport au dit chariot (101) quelle que soit la position du chariot sur la voie de roulement (1).Lifting machine according to one of claims 5 or 6, characterized in that said ballast elements (110) consist of plates each having holes (111) with a surface greater than the section of the support arms (108, 109). and configured so that a weight member suspended from a pair of associated support arms is held stationary relative to said carriage (101) regardless of the position of the carriage on the raceway (1). Engin de levage selon l'une quelconque des revendications précédentes, capable de travailler en mode articulé et en mode relevable, dont la flèche (10) comprend un pied de flèche (19) articulé au sommet du pylône par sa première extrémité (27), une fléchette (18) articulée en rotation à la deuxième extrémité du pied de flèche, ladite fléchette comportant de part et d'autre de son axe d'articulation (32) au pied de flèche respectivement une pointe de fléchette (22) et une contre-fléchette (20), ladite deuxième extrémité du pied de flèche et la contre-fléchette présentant des formes conjuguées permettant à la pointe de fléchette de venir en position alignée avec le pied de flèche en position de travail relevable et en ce que l'extrémité de ladite élingue de retenue (11) de flèche est fixée à la fléchette.Lifting apparatus according to one of the claims previous, able to work in articulated mode and in lift-up mode, whose boom (10) comprises a foot of arrow (19) articulated at the top of the pylon by its first end (27), a dart (18) articulated in rotation to the second end of the arrow foot, said dart having on both sides of its axis of articulation (32) at the foot of arrow respectively a point of dart (22) and a counter-dart (20), said second end of the foot of the arrow and the counter-dart having conjugate forms allowing the tip of dart to come in aligned with the foot of boom in a work-up position and in that the end of said boom retaining sling (11) is attached to the dart. Engin de levage selon la revendication 8, caractérisé en ce que le point d'attache (12) de l'extrémité de l'élingue de retenue (11) de flèche est agencé entre la pointe de fléchette (22) et la contre-fléchette (20).Lifting machine according to claim 8, characterized in that the point of attachment (12) of the end of the boom retaining sling (11) is arranged between the dart tip (22) and the counter-dart (20). Engin de levage selon la revendication 9, caractérisé en ce que ledit point d'attache (12) est agencé à distance de l'articulation (32) entre pied de flèche et fléchette de sorte que ladite élingue de retenue (11) de flèche croise l'axe d'articulation (32) pied de flèche/fléchette au cours du déploiement de la flèche en mode de travail articulé, entre la position de portée minimale et la position de portée maximale.Lifting machine according to claim 9, characterized in that said attachment point (12) is arranged at a distance from the articulation (32) between the jib and the jib so that said boom retaining sling (11) intersects the hinge axis (32) of the boom / jib during deployment of the boom in hinged work mode, between the minimum reach position and the maximum reach position. Engin de levage selon l'une des revendications 8 à 10, caractérisé en ce que la rotation de la fléchette (18) autour de l'articulation (32) pied de flèche/fléchette est commandée au moyen d'un système de câbles antagonistes (23, 24).Lifting machine according to one of claims 8 to 10, characterized in that the rotation of the dart (18) around the articulation (32) of the boom / jib is controlled by means of a system of opposing cables ( 23, 24). Engin de levage selon la revendication 11, caractérisé en ce que ledit système de câbles antagonistes (23, 24) comprend des treuils électriques (25, 26) et des poulies de renvoi (29) logées dans le pied de flèche (19).Lifting machine according to claim 11, characterized in that said system of opposing cables (23, 24) comprises electric winches (25, 26) and return pulleys (29) housed in the jib foot (19). Engin de levage selon l'une des revendications 8 à 10, caractérisé en ce que la rotation de la fléchette (205) autour de l'extrémité du pied de flèche (204) est effectuée au moyen d'un système à engrenage (200) comprenant un moteur électrique (201), un pignon (202) et un segment denté (203). Lifting machine according to one of claims 8 to 10, characterized in that the rotation of the dart (205) around the end of the jib foot (204) is effected by means of a gear system (200) comprising an electric motor (201), a pinion (202) and a toothed segment (203). Engin de levage selon la revendication 13, caractérisé en ce que ledit moteur électrique (201) est fixé sur le pied de flèche (204) et entraíne, via ledit pignon (202), un segment denté circulaire (203) solidaire de la fléchette (205).Lifting machine according to claim 13, characterized in that said electric motor (201) is fixed on the jib foot (204) and drives, via said pinion (202), a circular toothed segment (203) integral with the jib ( 205).
EP03405677A 2003-09-15 2003-09-15 Lifting device Withdrawn EP1514832A1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP03405677A EP1514832A1 (en) 2003-09-15 2003-09-15 Lifting device
AU2004272136A AU2004272136A1 (en) 2003-09-15 2004-09-14 Lifting appliance
AT04761917T ATE446275T1 (en) 2003-09-15 2004-09-14 LIFTING DEVICE
DE602004023738T DE602004023738D1 (en) 2003-09-15 2004-09-14 LIFT
CA002539014A CA2539014A1 (en) 2003-09-15 2004-09-14 Lifting appliance
US10/571,982 US7331476B2 (en) 2003-09-15 2004-09-14 Lifting appliance
PCT/CH2004/000577 WO2005026036A1 (en) 2003-09-15 2004-09-14 Lifting appliance
EP04761917A EP1667931B1 (en) 2003-09-15 2004-09-14 Lifting device

Applications Claiming Priority (1)

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EP03405677A EP1514832A1 (en) 2003-09-15 2003-09-15 Lifting device

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EP1514832A1 true EP1514832A1 (en) 2005-03-16

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EP03405677A Withdrawn EP1514832A1 (en) 2003-09-15 2003-09-15 Lifting device
EP04761917A Not-in-force EP1667931B1 (en) 2003-09-15 2004-09-14 Lifting device

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EP04761917A Not-in-force EP1667931B1 (en) 2003-09-15 2004-09-14 Lifting device

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US (1) US7331476B2 (en)
EP (2) EP1514832A1 (en)
AT (1) ATE446275T1 (en)
AU (1) AU2004272136A1 (en)
CA (1) CA2539014A1 (en)
DE (1) DE602004023738D1 (en)
WO (1) WO2005026036A1 (en)

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CN102756978A (en) * 2012-07-20 2012-10-31 辽宁抚挖重工机械股份有限公司 Foldable arm of crawler crane
CN107717949A (en) * 2017-11-23 2018-02-23 苏州夏木自动化科技有限公司 Ground moving boosting manipulator
JP2018199555A (en) * 2017-05-26 2018-12-20 コベルコ建機株式会社 Jib retracting device and jib retracting method

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Also Published As

Publication number Publication date
DE602004023738D1 (en) 2009-12-03
EP1667931B1 (en) 2009-10-21
CA2539014A1 (en) 2005-03-24
ATE446275T1 (en) 2009-11-15
AU2004272136A1 (en) 2005-03-24
WO2005026036A1 (en) 2005-03-24
EP1667931A1 (en) 2006-06-14
US20060283826A1 (en) 2006-12-21
US7331476B2 (en) 2008-02-19

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