EP3816091B1 - Turmkran mit automatisch ein- und ausklappbarem gegenausleger - Google Patents

Turmkran mit automatisch ein- und ausklappbarem gegenausleger Download PDF

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Publication number
EP3816091B1
EP3816091B1 EP20204539.9A EP20204539A EP3816091B1 EP 3816091 B1 EP3816091 B1 EP 3816091B1 EP 20204539 A EP20204539 A EP 20204539A EP 3816091 B1 EP3816091 B1 EP 3816091B1
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EP
European Patent Office
Prior art keywords
tower crane
punch
stanchion
folding
tension force
Prior art date
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EP20204539.9A
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English (en)
French (fr)
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EP3816091A1 (de
Inventor
Olivier Gevaudant
Yves ALLOIN
Vincent VEILLEROT
Simon GRIMAUD
Sylvain CUILLERIER
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Manitowoc Crane Group France SAS
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Manitowoc Crane Group France SAS
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Publication of EP3816091A1 publication Critical patent/EP3816091A1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • 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
    • B66C23/18—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 specially adapted for use in particular purposes
    • B66C23/26—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 specially adapted for use in particular purposes for use on building sites; constructed, e.g. with separable parts, to facilitate rapid assembly or dismantling, for operation at successively higher levels, for transport by road or rail
    • B66C23/34—Self-erecting cranes, i.e. with hoisting gear adapted for crane erection purposes
    • B66C23/344—Self-erecting cranes, i.e. with hoisting gear adapted for crane erection purposes adapted for transport purposes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • 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
    • B66C23/16—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes with jibs supported by columns, e.g. towers having their lower end mounted for slewing movements
    • 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
    • B66C23/18—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 specially adapted for use in particular purposes
    • B66C23/26—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 specially adapted for use in particular purposes for use on building sites; constructed, e.g. with separable parts, to facilitate rapid assembly or dismantling, for operation at successively higher levels, for transport by road or rail
    • B66C23/34—Self-erecting cranes, i.e. with hoisting gear adapted for crane erection purposes
    • B66C23/348—Self-erecting cranes, i.e. with hoisting gear adapted for crane erection purposes the erection being operated by jacks
    • 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

Definitions

  • the present invention relates to an automatic folding and unfolding tower crane, comprising at least one punch whose folding and unfolding are also automatic.
  • said mast and said boom can comprise several sections articulated together and adapted to be folded on top of each other, so as to make such a tower crane even more compact in its transport configuration.
  • Such tower cranes also include a lifting cable, extending along the mast and along the jib, connected to a block to which a load to be lifted is attached: by winding or unwinding this lifting cable, for example at by means of a lifting winch secured to the chassis or a lower end of the mast, it is thus possible to move said load in the vertical direction.
  • the arrow usually has a punch (also sometimes called “counter-arrow”) arranged at one of its ends, so that the arrow is extended, when it is in its working position, by said punch towards the rear of its point of connection with the top of the mast.
  • a punch also sometimes called "counter-arrow”
  • This punch is also connected to a rear retainer, which can consist of several articulated tie rods or cables, extending substantially parallel to the mast and connecting said punch to the frame: this rear retainer thus makes it possible, in the working configuration of the tower crane, to stabilize the position of the boom at the top of the mast and in certain cases to adjust its inclination relative to the vertical.
  • this rear retainer makes possible the automatic folding and unfolding of such a tower crane, the unfolding of the mast (under the effect of a dedicated actuator) exerting a tension force in the rear retainer causing deployment of the boom in relation to the mast, via the punch.
  • the punch is also foldable and unfoldable between a working position, in which it extends in the extension of the boom, and a position of transport, in which it is folded in the direction of this same arrow.
  • the document FR2834505 describes a tower crane whose punch extends, when said tower crane is in its working configuration, obliquely to and above the boom.
  • this method of folding the punch is only applicable to such tower cranes in which the punch extends significantly above the boom in working configuration, and also has the disadvantage of requiring a preliminary partial unfolding step of the boom when unfolding these tower cranes in order to allow unfolding of the punch: the unfolding process is therefore made more complex, thus increasing the risk of errors which could damage such tower cranes.
  • the document EP3184481 describes a tower crane whose punch has (in the working configuration of the tower crane) a slight inclination relative to the boom and a reduced length, so that said punch can be folded into a transport position vertical, against an end portion of the arrow.
  • This crane also includes a telescopic mast, having two mast sections which can slide one in the other in the vertical direction: when folding this crane, the boom is caused to be inclined vertically and towards the ground when de- telescoping of the mast, causing an automatic folding of the punch on an end portion of the boom, under the effect of its own weight.
  • this method of folding the punch has the disadvantage of being limited to tower cranes comprising a telescopic mast.
  • the document EP1364906 describes the use of a system comprising gas cylinders arranged in the boom allowing the punch to be folded against it, in its transport position.
  • this principle requires a larger footprint inside the boom, in order to allow greater travel of the crankshaft controlled by the gas cylinders and thus reduce the forces required to move the punch. If the space available in the boom is smaller, it is then necessary to increase the number of gas cylinders, thus making the system more complex and more expensive.
  • this solution does not guarantee reliable unfolding or folding of the punch over time, thus potentially causing a risk of damage to the crane. in turn, for example in the event of failure to unfold the punch when unfolding the tower crane.
  • the present invention therefore aims to resolve all or part of the aforementioned drawbacks, by proposing a tower crane whose folding and unfolding of the punch are carried out automatically, in a simple and reliable manner.
  • Another objective of the invention is to provide a tower crane making it possible to precisely control the speed of folding or unfolding of the punch.
  • Yet another objective of the invention is to propose a suitable tower crane which may be of variable type and/or capacity, in particular a tower crane which may be of high or low capacity and may or may not include a telescopic mast.
  • yet another objective of the invention is to propose a tower crane whose method of folding or unfolding the punch involves elements already present in widespread tower cranes of the state of the art and requiring only a modest modification of their architecture.
  • a tower crane of the foldable and unfoldable type between a working configuration and a transport configuration, having a boom articulated in rotation relative to a mast around a main axis of rotation, said crane with tower comprising a rear retainer fixed to a frame supporting said mast and to a punch, said punch being provided to extend said boom to the rear of said main axis of rotation and designed to be movable relative to said boom between a working position and a transport position, said tower crane being characterized in that it comprises a lifting cable connected to a winding device designed to exert a tension force on said lifting cable, said tension force being applied to said punch by means of a system of return designed to cooperate with said lifting cable, so as to cause a movement of said punch from its working position to its transport position.
  • the invention proposes a tower crane in which the folding movement of the punch, from its working position to its transport position, and carried out using the lifting cable: the tension force exerted on it -this by the winding device is transmitted to the punch via the return system, so as to move the punch.
  • the lifting cable usually comprises a first portion, extending along the mast, connected to a second portion extending along the boom: by means of force tension applied by the furling device (which may for example consist of a winch secured to the mast) on this lifting cable, it is possible to vary a length of the latter to lift and vertically move a load fixed to a block, itself connected to said lifting cable.
  • the furling device which may for example consist of a winch secured to the mast
  • the invention therefore proposes to exploit this tension force in another way, by applying it, by means of the return system, to an area of the punch in order to cause it to fold.
  • the lifting cable retains its load lifting function: the use of the lifting cable for folding the punch during the passage of the tower crane from its configuration of work to its transport configuration is thus an additional characteristic not modifying the normal operation of the tower crane when it is in its work configuration.
  • the unfolding of the punch can be carried out by means of a rear retainer, composed of articulated rods or a cable extending along the mast and connecting the punch to the chassis supporting this same mast: when the tower crane according to the invention passes from its transport configuration to its working configuration, the rear retainer exerts a force on the punch causing the automatic movement of the latter from its transport position to its working position.
  • the invention envisages combining simultaneous actions on the punch of the tension force of the lifting cable and the rear restraint during the unfolding of the tower crane, so as to control the unfolding speed of the punch.
  • the return system comprises at least one main return element in which the lifting cable is engaged, said main return element being fixed on the punch.
  • the lifting cable of a tower crane thus comprises an intermediate portion connecting the first portion and the second portion of the latter, this intermediate portion cooperating with the return system near the punch and the main axis of rotation articulating the boom and the mast.
  • the lifting cable is engaged in a main return element integral with the punch: the tension force, exerted on the lifting cable by the winding device is thus transmitted to this main return element, which in turn transmits to the minus part of this tension force at the punch.
  • the main return element is a pulley comprising a wheel cooperating with the lifting cable and a yoke, carrying said wheel and fixed on the punch.
  • the punch is connected in rotation, around a secondary axis of rotation, to a first arrow section extending in an arrow direction, said punch being movable, between its working position and its transport position, by a rotational movement relative to the first boom section around said secondary axis of rotation.
  • the secondary axis of rotation is parallel to the main axis of rotation.
  • the punch has a punch body extending in a punch direction between a first end, connected to the first arrow section, and a second opposite end, the main return element of the return system being arranged at proximity to said second end.
  • the tension force of the lifting cable is thus applied to the punch at a maximum distance from the secondary axis of rotation, so as to increase as much as possible the lever arm exerted on the punch by the folding force transmitted by the main reference element.
  • the folding movement of the punch can be carried out without the tension force having to present too high an intensity.
  • the punch direction is parallel to the arrow direction when said punch is in its working position, and the punch direction is orthogonal to the arrow direction when said punch is in its transport position.
  • the punch extends in a punch direction substantially parallel to the arrow direction in its working position, and substantially orthogonal to this same arrow direction in its transport position. .
  • the invention envisages embodiments in which the punch direction forms with the arrow direction an angle whose measurement is between -20° and 20° when the punch is in its working position, and an angle whose measurement is between 70° and 110° when the punch is in its working position.
  • the folding movement of the punch consists of making the latter perform a rotational movement of approximately 90° around the secondary axis of rotation.
  • the punch can be formed by two ribs, joined at one of their ends and forming with the secondary axis of rotation an isosceles triangle, substantially parallel to the direction of arrow when the punch is in its working configuration.
  • the main return element can then be placed at this junction point between the two members.
  • this junction point can also be connected to an upper chord of the first boom section by a line of upper tie rods making it possible to transmit to said first boom section the forces exerted on the punch by the rear retainer so as to cause a movement rotation of said first boom section relative to the mast: this line of upper tie rods thus forms with the two frames and the secondary axis of rotation a general trihedron shape.
  • the first boom section has at least one upper chord and one lower chord defining respectively, in a direction perpendicular to the direction of arrow, an upper limit and a lower limit of said first boom section, where the axis of secondary rotation is positioned at said lower limit, and in which the return system comprises at least one return element secondary positioned near said upper limit, the lifting cable being engaged successively in said secondary return element then in the main return element, so that the tension force generates on said main return element a directed folding force in the direction of said secondary return element and allowing movement of said punch from its working position to its transport position.
  • This particular configuration of the return system guarantees that the tension force exerted by the lifting cable on the main return element (integral to the punch) has a direction allowing the punch to be moved towards its transport position. Indeed, by positioning a secondary return element at the upper limit of the first boom section while the secondary axis of rotation is arranged near the lower limit thereof, the tension force exerted by the cable lifting on the main return element is directed in the direction of this upper limit and therefore tends to bring the main return element closer to this same upper limit.
  • the tension force transmitted to the punch via the main return element has an oblique direction, directed "upwards", relative to the arrow direction and makes it possible to put this punch into position. rotation around the secondary axis of rotation.
  • the main axis of rotation is for its part between the upper limit and the lower limit of the first boom section.
  • the secondary return element is fixed on the mast and connected to the winding device by a first portion of the lifting cable intended to extend along said mast, where said secondary return element and the main return element are positioned, according to the direction of the arrow, on either side of the secondary axis of rotation when the punch is in its working position.
  • the first portion of the lifting cable, extending along the mast, is directly engaged in the secondary return element secured to the mast, then this same lifting cable is engaged in the main return element secured to the punch.
  • the tracking system therefore does not include, in this embodiment, any other return element in which the lifting cable is engaged between the main return element and the secondary return element.
  • the return system comprises one or more tertiary return elements fixed on the mast, the punch or the first boom section, the lifting cable being engaged in said tertiary return elements, so as to transmit the force of tension of the main return element to a second portion of the lifting cable, said second portion being designed to extend along the first boom section.
  • the lifting cable is therefore successively engaged in the secondary return element, then in the main return element, then in the tertiary return element(s).
  • the main, secondary and tertiary return elements are positioned so as to transmit the tension force from the first portion of the lifting cable to the second portion of the lifting cable without applying deformation forces to this same lifting cable in torsion.
  • this can be achieved by aligning the return directions of two successive return elements in pairs.
  • the tower crane according to the invention comprises a boom offset relative to the mast, that is to say in the case where the first boom section is offset relative to the mast. to the mast in a transverse direction, orthogonal to both the boom direction and a direction of extension of the mast.
  • the return system must be configured to transmit the tension force along the lifting cable also in this transverse direction, potentially causing the appearance of significant torsional forces in the lifting cable and leading to his breakup.
  • the winding device comprises an actuator adapted to vary an intensity of the tension force exerted on the lifting cable by said winding device.
  • the lifting cable extends between a first end fixed to the boom and a second end connected to the winding device, said winding device being integral with the mast, and wherein the actuator of the winding device is adapted to vary a cable length of said lifting cable measured between said first end and said winding device, so as to vary the intensity of the tension force.
  • the winding device therefore makes it possible to increase the intensity of the tension force exerted on the lifting cable by shortening the cable length, or to reduce this intensity by increasing this cable length.
  • the characteristic quantity can correspond to an intensity of the supply current of this motor, or even a value of a resistive torque exerted on the motor shaft of this one.
  • Such a control system thus makes it possible to maintain approximately constant, permanently and automatically, the value of the intensity of the tension force, throughout the folding or unfolding of the tower crane according to the invention, and especially throughout the folding or unfolding of the punch.
  • the length traveled by the lifting cable between its first end (fixed on the boom) and its second end (connected to the winding device, secured to the mast) is made to vary.
  • the winding device (controlled by the control system) unwinds a predefined length of lifting cable, in order to slightly lower this value (and therefore, equivalently, to lower the intensity of the tension force in the lifting cable).
  • this same value of the characteristic quantity reaches the threshold value and the winding device unwinds the lifting cable again, etc.
  • control system operates in a similar manner during tower crane folding (and in particular during punch folding), with the reel device winding the lifting cable in stages.
  • the control system therefore makes it possible to automatically control the kinetics of the folding and unfolding movements of the tower crane or the punch, by indirect (or direct depending on the embodiment) control of the value of the force intensity Of voltage.
  • the tension force exerted in the lifting cable 5 must be sufficiently significant at all times to hold the block against the boom, in order to avoid damage to the tower crane during the folding or unfolding processes.
  • the folding movement of the punch consisting for example of an “upward” rotational movement around the secondary axis of rotation, tends to oppose the weight of said punch: it is thus necessary that the force of tension is applied to the punch so as to generate a folding force directed opposite to earth's gravity and making it possible to compensate in particular for the weight of the punch and the rear retainer, in order to be able to "raise” it and move it to its transport position.
  • the tower crane is as previously described, the folding phase comprising a step of controlling the actuator of the winding device by the control system so as to reduce the cable length so as to cause the punch to move towards its transport configuration.
  • This step of reducing the cable length results in an increase in the tension force in the lifting cable, then by an increase in the folding force exerted on the punch, and finally by a movement of the punch towards its position of transport under the effect of this folding force.
  • the unfolding phase comprises at least one step during which the control system compares the value of the characteristic quantity representative of the intensity of the tension force to an unfolding threshold value
  • the folding phase comprises at least one step during which the control system compares the value of the characteristic quantity representative of the intensity of the tension force to a folding threshold value, said folding threshold value being greater than said unfolding threshold value
  • the tension force exerted in the lifting cable results in the application of a folding force on the punch tending to oppose the weight of said punch and the rear retainer.
  • the punch is moved towards its working position under the effect of its own weight, and the folding force then has the role of partially compensating this weight to slow down the kinetics of the folding movement and control the speed unfolding of the punch: the folding force should therefore not be as significant as during a folding movement.
  • the tension force must have a lower intensity during unfolding movements than during folding movements of the punch: this characteristic then results in a choice of a folding threshold value greater than a threshold value unfolding.
  • the folding threshold value is at least 20% greater than the unfolding threshold value.
  • folding and/or unfolding processes can be carried out, at least partially, by a human operator, said operator being able in particular to control the winding device so as to vary the intensity of the tension force in the lifting cable.
  • the operator can choose to carry out this unfolding of the punch at a moment in the unfolding process of the tower crane where the punch is as far away as possible from said building or external element.
  • FIG. 1 represents a tower crane 1 according to the invention, in working configuration.
  • This tower crane 1 comprises a boom 2 having a first boom section 21, a second boom section 22 and a third boom section 23, articulated two by two in rotation around a first boom rotation axis 221 and a second axis of arrow rotation 231.
  • the tower crane 1 also comprises a mast 3 having a first mast section 31 and a second mast section 32, articulated in rotation relative to each other around a mast rotation axis 321 .
  • This mast is supported by a chassis 4, intended to rest on a ground, the second mast section 32 being articulated in rotation relative to the chassis 4 around an axis of rotation of the chassis 41.
  • the first boom section 21 extends between a first end 211 and a second end 214 in a boom direction F, and the first mast section 31 extends in a mast direction M.
  • the first boom section 21 and the first mast section are also articulated in rotation relative to each other around a main axis of rotation 311.
  • first boom rotation axis 221, the second boom rotation axis 231, the mast rotation axis 321 and the chassis rotation axis 41 are parallel to each other and also parallel to each other. the main axis of rotation 311.
  • the tower crane 1 In its transport configuration, the tower crane 1 has a very compact shape and is therefore very easily transportable.
  • the tower crane 1 In its working configuration, the tower crane 1 is adapted to move a load fixed to a hook C, itself connected to a block O designed to be movable along the boom 2.
  • the block O is also connected to a lifting cable 5 comprising a first end 51 fixed on the third boom section 23 and a second end 52 connected to a winding device 53 secured to the second mast section 32.
  • This winding device 53 (for example, consisting of a winch actuated by a motor) is designed to alternately increase or decrease a cable length of the lifting cable 5, measured between the first end 51 and the second end 52, (for example example, by winding or unwinding said lifting cable 5), in order to make respectively raise or lower the block O in the mast direction M, and thus move a load fixed to the hook C in the vertical direction when the tower crane 1 is in working configuration.
  • the winding device 53 is therefore adapted to exert a tension force T of variable intensity on this same lifting cable 5.
  • the tower crane 1 also includes a punch 6, articulated in rotation with the first end 211 of the first boom section 21 around a secondary axis of rotation 61, and extending the boom 2 beyond the main axis of rotation 311 .
  • This punch 6 is also connected to a rear retainer 7, formed of several connecting rods 71, 72, 73 and 74 articulated together and connecting the punch 6 to the chassis 4 extending along the mast 2.
  • this rear retainer 7 allows, via the punch 6, to maintain the boom 2 in its horizontal position at the top of the mast 2.
  • the punch 6 comprises in particular two ribs 62 articulated in rotation with the first arrow section 21 around the secondary axis of rotation 61 and joined at a junction point 63.
  • these frames 62 are thus movable relative to the first boom section 21 between a working position of the punch 6 (as illustrated in the figures 2 to 7 ) and a transport position (as shown in the Figure 9 ).
  • the ribs 62 define a plane parallel to the arrow direction F.
  • the ribs 62 define a plane substantially perpendicular to the arrow direction F.
  • the punch 6 In its transport position, the punch 6 abuts against the first boom section 6, thereby improving the overall compactness of the tower crane 1 in its transport configuration.
  • the punch 6 follows a folding movement when it moves from its working position to its transport position, and an unfolding movement when it moves from its transport position to his working position.
  • the punch 6 is connected, at the junction point 63 to the rear retainer 7: the junction point being located at a maximum distance of the main axis of rotation 311, this characteristic makes it possible to increase the lever arm of the forces exerted on the punch by the rear retainer 7.
  • the secondary axis of rotation 61 is positioned at a lower limit of the first boom section 21 defined by lower boom ribs 212.
  • the tower crane 1 also includes a line of upper tie rods 64 joining the junction point 63 of the punch 6 to the first boom section 21, at the level of an upper limit of said first boom section 21 defined by upper boom chords 213 .
  • the punch 6 extends obliquely with respect to the arrow direction F, the junction point 63 being located (in the transverse direction 33) at the level of the mast 3, while the articulation of the frames 62 with the first boom section 21 is located at said first boom section.
  • the punch cooperates with the lifting cable 5 via a return system 8.
  • the return system 8 makes it possible to transmit the tension force T exerted on the lifting cable 5 by the winding device 53 between a first portion 54 of the lifting cable 5, extending along the mast 3, and a second portion 55 of the lifting cable 5, extending along the arrow 2.
  • This return system 8 therefore cooperates with an intermediate portion 56 of the lifting cable, said intermediate portion 56 joining said first portion 54 and second portion 55.
  • the return system 8 is well suited to transmit the tension force T between the first portion 54 and the second portion 55 of the lifting cable 5.
  • the pulleys of the secondary return element 81, of the main return element 82 and of the tertiary return elements 83 are advantageously arranged so as not to introduce torsional forces into the lifting cable 5.
  • this return system 8 As previously, many other embodiments are possible concerning this return system 8, the structure of which is necessarily adapted to that of the tower crane 1.
  • this return system 8 cooperates with the punch 6; in particular, it is necessary that the return system 8 is configured to be able to transmit the tension force T, exerted on the lifting cable 5, to the punch 6.
  • THE figures 5 to 10 describe the different stages of a method of folding the tower crane 1 according to the invention, that is to say a method allowing it to pass from its transport configuration to its transport configuration.
  • This folding process begins with a step of folding the arrow 2 on itself, by stacking (visible on the figure 5 ) of the first boom section 21, second boom section 22 and third boom section 23, by rotation around a first boom rotation axis 221 and the second boom rotation axis 231.
  • the mast is then also folded on itself, by a rotational movement of the first mast section 31 around the mast rotation axis 321 and of the second mast section 32 around the frame rotation axis 41.
  • the rear retainer 7 is also connected in an articulated manner to the chassis 4 (by means of a connecting rod 71, said connecting rod 71 also being telescopic) to the punch 6 (by means of a connecting rod 72), to the first mast section 31 ( by means of a connecting rod 73) and to the second mast section 32 (by means of a connecting rod 74), this rear retainer is deformed under the effect of the folding movement of the mast 2: under the effect of the action of the V cylinder, the rear retainer makes it possible to control the folding kinetics of the tower crane 1.
  • these steps of folding the boom 2 and the mast 3 cause a release of the lifting cable 5: during all the previous steps, the winding device 53 was controlled, by means of a control system whose operation will be described in more detail below, so as to reduce the cable length of the lifting cable 5, in order to compensate for the relaxation of the lifting cable 5 and thus maintain a tension force in the lifting cable 5 of relatively constant intensity .
  • the winding device 53 continues to be controlled by the control system so as to wind the lifting cable 5 (that is to say so as to reduce the cable length).
  • the lifting cable 5 exerts on the main return element 82 of the return system a tension force T directed towards the secondary return element 81.
  • This folding force P has an intensity which depends in particular on the relative positions of the main return element 82, of the return element secondary 81 and the tertiary return element 83' (in particular, positioning the tertiary return element 83' near the upper limit of the first boom section 21 makes it possible to maximize the intensity of the folding force P), and mechanical friction exerted by these same return elements 81, 82 and 83' on the lifting cable 5.
  • the folding force P thus exerts on the punch 6 a folding moment making it possible to cause the punch 6 to rotate relative to the first arrow section 21 around the secondary axis of rotation 61.
  • the punch 6 is thus moved from its working position (in Figure 7 ) to its transport position (in Figure 9 ) under the effect of the tension force T and the folding force P.
  • the secondary return element 82 arranged near the upper limit of the first boom section 21 (defined by the upper boom ribs 213), relative to the secondary axis of rotation, arranged near the lower limit of the first boom section 21 (defined by the lower boom chords 212), and relative to the main return element 82, disposed between said upper limit and said lower limit.
  • the folding force P tends to bring the junction point 63 closer to this upper limit, that is to say it tends to “raise” the punch 6 relative to the arrow direction F.
  • FIG 8 illustrates an intermediate position of the punch 6, between its working position and its transport position, during its rotational movement around the secondary axis 61 under the effect of the tension force T.
  • FIG. 9 illustrates this same punch 6 after it has reached its transport position: the punch 6 is then positioned abutting against the first end 211 of the first boom section 21, and the frames 62 are then substantially orthogonal to the boom direction F.
  • first mast section 31 and the second mast section 32 are folded on top of each other and both extend horizontally.
  • boom 2 is folded on itself in contact with the first mast section 31 and also extends horizontally.
  • the tower crane is in a very compact form and occupies a small volume, which makes it easily transportable by usual means of transport.
  • the fact of having moved the punch 6 towards its transport position, abutting against the first boom section 21, makes it possible to reduce the bulk of the tower crane 1 in its transport configuration: the folding of the punch 6 makes it possible to reduce a length L occupied by the tower crane 1 by a length L' of the frames 62 (measured between the junction point 63 and the secondary axis of rotation 61.
  • the tower crane 1 includes a control system making it possible to control the winding device 53 so as to control the intensity of the tension force T in the lifting cable 5 during the folding movement of the punch 6. More precisely, this control system is capable of measuring a value of a characteristic quantity representative of the intensity of the tension force T, undergoing the same variations over time as the intensity of the tension force.
  • the characteristic quantity can correspond to an intensity of the supply current of this motor, or even a value of a resistive torque exerted on the motor shaft of this one.
  • This characteristic quantity can also correspond to the intensity of the tension force T itself, for example measured using a dynamometer.
  • the control system is designed to regularly compare the value of this characteristic quantity to a previously defined threshold value and to command the winding device 53 to increase the cable length when the value of this characteristic quantity is greater than this threshold value, and command the winding device 53 to reduce the cable length when the value of this characteristic quantity is less than this threshold value.
  • control system makes it possible to automatically and continuously maintain the value of the characteristic quantity approximately equal to the threshold value throughout the folding or unfolding movements of the tower crane 1, and therefore to exert on the lifting cable 5 a tension force T of substantially constant intensity.
  • the winding device 53 performs regular winding of the lifting cable 5 in order to maintain the intensity of the tension force T at a high level.
  • the tension force T must therefore have a sufficiently large intensity so that the folding force P can overcome the weight of the punch 6 and the rear retainer 7, in order to cause the folding movement of the punch 6.
  • a process for unfolding the tower crane 1, making it possible to move the latter from its transport configuration to its working configuration, can be carried out in a manner similar to the folding process previously described.
  • This unfolding process can thus be described by the same figures 5 to 10 , traveled in the opposite direction to the folding process, that is to say the unfolding process begins with the transport configuration of the tower crane 1 illustrated by the Figure 10 and ends with the working configuration of tower crane 1 shown in Figure 5 .
  • the mast is deployed by means of the cylinder V, controlled so as to increase the distance separating the first mast section 31 from the second mast section 32.
  • the punch 6 is in its transport position, abutting against the first boom section 21.
  • the rear retainer 7 exerts mechanical forces on the punch 6 at the junction point 63, resulting in the application on the punch 6 of a mechanical torque allowing the initiation of a unfolding movement of the punch 6, towards its working position.
  • the punch 6 is then subjected to the effects of its own weight, which tends to move it towards its working position: the unfolding movement of the punch 6 is thus achieved thanks to the rear retainer 7 and the weight of the punch 6.
  • the control system of the winding device 53 makes it possible, by continuously controlling the value of the intensity of the tension force T during the unfolding movement of the punch 6, to control the kinematics of said punch 6.
  • the unfolding of the punch 6 results in an increase in the cable length of the lifting cable 5: the control system controls the winding device 53 so that it unwinds the lifting cable 5 little by little and in a controlled manner, in order to to slow down the movement of the punch 6.
  • the arrow 2 is also rotated (under the effect of the rear retainer 7 and via the punch 6) relative to the first mast section 31 around the main axis of rotation 311 and moved to a horizontal position, until the tower crane 1 reaches its working configuration illustrated in figure 1 , in which the arrow 2 is perpendicular to the vertical mast 3.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Jib Cranes (AREA)

Claims (16)

  1. Turmdrehkran (1), vom Typ der zwischen einer Arbeitskonfiguration und einer Transportkonfiguration zusammenklappbar und aufklappbar ist, umfassend einen Ausleger (2), der in Bezug auf einen Mast (3) um eine Hauptdrehachse (311) drehbar angelenkt ist, wobei der Turmdrehkran (1) eine hintere Halterung umfasst, die an einem Rahmen (4), der den Mast (3) trägt, und an einer Stütze (6) befestigt ist, wobei die Stütze (6) dazu vorgesehen ist, den Ausleger (2) nach hinten von der Hauptdrehachse (311) zu verlängern, und dazu ausgelegt, in Bezug zum Ausleger (2) zwischen einer Arbeitsposition und einer Transportposition verschiebbar zu sein,
    wobei der Turmdrehkran (1) dadurch gekennzeichnet ist, dass er ein Hubseil (5) umfasst, das mit einer Aufwickelvorrichtung (53) verbunden ist, die dazu ausgelegt ist, auf das Hubseil (5) eine Zugkraft (T) auszuüben, wobei die Zugkraft (T) durch ein Rückholsystem (8), das dazu ausgelegt ist, mit dem Hubseil (5) zusammenzuwirken, auf die Stütze (6) ausgeübt wird, um eine Verschiebung der Stütze (6) von ihrer Arbeitsposition in ihre Transportposition zu bewirken.
  2. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das Rückholsystem (8) mindestens ein Hauptrückholelement (82) umfasst, in das das Hubseil (5) eingreift, wobei das Hauptrückholelement (82) an der Stütze (6) befestigt ist.
  3. Turmdrehkran (1) nach einem der vorhergehenden Ansprüche, wobei die Stütze (6) um eine sekundäre Drehachse (61) drehbar mit einem ersten Auslegersegment (21) verbunden ist, das sich in einer Richtung (F) des Auslegers erstreckt, wobei die Stütze (6) durch eine Drehbewegung in Bezug zum ersten Auslegersegment (21) um die sekundäre Drehachse (61) zwischen seiner Arbeitsposition und seiner Transportposition verschiebbar ist.
  4. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei die Stütze (6) einen Stützenkörper aufweist, der sich in einer Richtung der Stütze zwischen einem ersten Ende, das mit dem ersten Auslegersegment (21) verbunden ist, und einem zweiten gegenüberliegenden Ende erstreckt, wobei das Hauptrückholelement (82) des Rückholsystems (8) nahe dem zweiten Ende angeordnet ist.
  5. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei die Richtung der Stütze (6) parallel zur Richtung (F) des Auslegers ist, wenn sich die Stütze (6) in ihrer Arbeitsposition befindet, und wobei die Richtung der Stütze (6) orthogonal zur Richtung des Auslegers (F) ist, wenn sich die Stütze (6) in ihrer Transportposition befindet.
  6. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das erste Auslegersegment (21) mindestens einen oberen Steg (213) und einen unteren Steg (212) aufweist, die jeweils in einer Richtung senkrecht zur Richtung (F) des Auslegers eine obere Grenze und eine untere Grenze des ersten Auslegersegments (21) definieren, wobei die sekundäre Drehachse (61) auf der Höhe der unteren Grenze positioniert ist,
    und wobei das Rückholsystem (8) mindestens ein sekundäres Rückholelement (81) umfasst, das nahe der oberen Grenze positioniert ist, wobei das Hubseil (5) nacheinander in das sekundäre Rückholelement (81) und dann in das Hauptrückholelement (82) eingreift,
    so dass die Zugkraft (T) am Hauptrückholelement (82) eine Faltkraft (P) erzeugt, die auf das sekundäre Rückholelement (81) gerichtet ist und eine Verschiebung der Stütze (6) von ihrer Arbeitsposition in ihre Transportposition ermöglicht.
  7. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das sekundäre Rückholelement (81) am Mast (3) befestigt und über einen ersten Abschnitt (54) des Hubseils (5), der zur Verlängerung der Länge des Masts (3) vorgesehen ist, mit der Aufwickelvorrichtung (53) verbunden ist,
    wobei das sekundäre Rückholelement (81) und das Hauptrückholelement (82) in Richtung (F) des Auslegers auf beiden Seiten der sekundären Drehachse (61) positioniert sind, wenn die Stütze (6) sich in ihrer Arbeitsposition befindet.
  8. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das Rückholsystem (8) ein oder mehrere tertiäre Rückholelemente (83, 83') umfasst, die am Mast (3), an der Stütze (6) oder am ersten Auslegersegment (21) befestigt sind, wobei das Hubseil (5) in die tertiären Rückholelemente (83, 83') eingreift, um die Zugkraft (T) des Hauptrückholelements (82) zu einem zweiten Abschnitt (55) des Hebeseils (5) zu übertragen, wobei der zweite Abschnitt dazu vorgesehen ist, die Länge des ersten Auslegersegments (21) zu verlängern.
  9. Turmdrehkran (1) nach einem der vorhergehenden Ansprüche, wobei die Aufwickelvorrichtung (53) einen Aktuator umfasst, der dazu ausgelegt ist, eine Intensität der von der Aufwickelvorrichtung (53) auf das Hubseil (5) ausgeübten Zugkraft (T) zu variieren.
  10. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das Hubseil (5) sich zwischen einem ersten Ende (51), das am Ausleger (2) befestigt ist, und einem zweiten Ende (52), das mit der Aufwickelvorrichtung (53) verbunden ist, erstreckt, wobei die Aufwickelvorrichtung (53) am Mast (3) fixiert ist,
    und wobei der Aktuator der Aufwickelvorrichtung (53) dazu ausgelegt ist, eine Seillänge des Hubseils (5), gemessen zwischen dem ersten Ende und der Aufwickelvorrichtung (53), zu variieren, um die Intensität der Zugkraft (T) zu variieren.
  11. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei die Aufwickelvorrichtung (53) ein Steuersystem umfasst, das ausgelegt ist zum:
    - Bestimmen eines Werts einer charakteristischen Größe, die repräsentativ für die Intensität der Zugkraft (T) ist,
    - Vergleichen des Werts mit einem zuvor definierten Schwellenwert, und
    - Ansteuern des Aktuators der Aufwickelvorrichtung (53), um die Seillänge zu erhöhen, wenn der Wert größer ist als der Schwellenwert, und
    - Ansteuern des Aktuators der Aufwickelvorrichtung (53), um die Seillänge zu reduzieren, wenn der Wert kleiner ist als der Schwellenwert.
  12. Turmdrehkran (1) nach dem vorhergehenden Anspruch, wobei das Steuerungssystem dazu ausgelegt ist, den Wert der charakteristischen Größe, die repräsentativ für die Intensität der Zugkraft (T) ist, durch mindestens einer der folgenden Messungen zu bestimmen:
    - Eine direkte Messung der Intensität der Zugkraft (T) durch einen Dynamometer,
    - eine Messung einer Stärke eines elektrischen Stroms, der den Aktuator der Aufwickelvorrichtung (53) mit Strom versorgt, oder
    - eine Messung eines Drehmoments oder einer mechanischen Kraft innerhalb des Aktuators.
  13. Verfahren zum Auf- und Zusammenklappen eines Turmdrehkrans (1) nach einem der vorhergehenden Ansprüche, umfassend:
    - Eine Aufklappphase, während der der Turmdrehkran (1) von seiner Transportkonfiguration in seine Arbeitskonfiguration übergeht und während der die Stütze (6) unter der Wirkung einer hinteren Halterung (7), die dazu ausgelegt ist, die Stütze (6) mit einem den Mast (3) tragenden Rahmen zu verbinden, von ihrer Transportkonfiguration in ihre Arbeitskonfiguration verschoben wird, und
    - eine Zusammenklappphase, während der der Turmdrehkran (1) von seiner Arbeitskonfiguration in seine Transportkonfiguration übergeht und während der die Stütze (6) unter der Wirkung der Zugkraft (T), die von der Aufwickelvorrichtung (53) auf das Hubseil (5) ausgeübt wird, von ihrer Arbeitskonfiguration in ihre Transportkonfiguration verschoben wird.
  14. Verfahren nach dem vorhergehenden Anspruch, wobei während der Aufklappphase die Zugkraft (T) an der Stütze (6) eine Faltkraft (P) erzeugt, die eine Verschiebung der Stütze (6) von ihrer Arbeitsposition in ihre Transportposition bewirkt, wobei die Faltkraft (P) derart ist, dass sie in vertikaler Richtung dem Gewicht (PO) der Stütze (6) unter der Wirkung der Schwerkraft entgegenwirkt.
  15. Verfahren nach einem der Ansprüche 13 und 14, wobei der Turmdrehkran (1) Anspruch 10 entspricht, wobei die Zusammenklappphase einen Schritt des Ansteuerns des Aktuators der Aufwickelvorrichtung (53) durch das Steuersystem umfasst, um die Seillänge zu reduzieren, um die Verschiebung der Stütze (6) in ihre Transportkonfiguration zu bewirken.
  16. Verfahren nach einem der Ansprüche 13 bis 15, wobei der Drehturmkran (1) Anspruch 11 entspricht, wobei die Aufklappphase zumindest einen Schritt umfasst, während dem das Steuersystem den Wert der charakteristischen Größe, die für die Intensität der Zugkraft (T) repräsentativ ist, mit einem Schwellenwert des Aufklappens vergleicht, und wobei die Zusammenklappphase mindestens einen Schritt umfasst, während dem das Steuersystem den Wert der charakteristischen Größe, die für die Intensität der Zugkraft (T) repräsentativ ist, mit einem Schwellenwert des Zusammenklappens vergleicht,
    wobei der Schwellenwert des Zusammenklappens größer ist als der Schwellenwert des Aufklappens.
EP20204539.9A 2019-10-31 2020-10-29 Turmkran mit automatisch ein- und ausklappbarem gegenausleger Active EP3816091B1 (de)

Applications Claiming Priority (1)

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FR1912237A FR3102763B1 (fr) 2019-10-31 2019-10-31 Grue à tour avec poinçon à pliage et dépliage automatiques

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EP3816091B1 true EP3816091B1 (de) 2023-10-11

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RU2817662C1 (ru) * 2023-11-17 2024-04-17 Общество с ограниченной ответственностью "Дигинавис" Складной башенный кран

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USD1019048S1 (en) * 2021-07-01 2024-03-19 Liebherr-Werk Biberach Gmbh Crane
CN113772548B (zh) * 2021-07-29 2024-01-19 余姚太平洋称重工程有限公司 一种基于双分量称重传感器的钢丝绳补偿方法

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CH499455A (de) * 1969-04-24 1970-11-30 Wetzel Kg Turmdrehkran
US5016768A (en) * 1989-11-02 1991-05-21 David C. Kennard, Jr. Pickup truck derrick with traveling sheaves
FR2790252B1 (fr) * 1999-02-26 2001-04-06 Potain Sa Dispositif de depliage ou repliage simultane d'elements de pointe de fleche de grue
FR2834505B1 (fr) 2002-01-09 2004-05-07 Potain Sa Procede et dispositif de commande/controle securise du depliage et repliage d'une grue a tour
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RU2817662C1 (ru) * 2023-11-17 2024-04-17 Общество с ограниченной ответственностью "Дигинавис" Складной башенный кран
RU226627U1 (ru) * 2024-04-16 2024-06-14 Общество с ограниченной ответственностью "Дигинавис" Устройство для вертикального перемещения стрелы башенного крана

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FR3102763A1 (fr) 2021-05-07
US11420851B2 (en) 2022-08-23
US20210130141A1 (en) 2021-05-06
PT3816091T (pt) 2024-01-05
EP3816091A1 (de) 2021-05-05

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