WO2005026036A1 - Engin de levage - Google Patents
Engin de levage Download PDFInfo
- Publication number
- WO2005026036A1 WO2005026036A1 PCT/CH2004/000577 CH2004000577W WO2005026036A1 WO 2005026036 A1 WO2005026036 A1 WO 2005026036A1 CH 2004000577 W CH2004000577 W CH 2004000577W WO 2005026036 A1 WO2005026036 A1 WO 2005026036A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- dart
- jib
- boom
- lifting device
- counterweight
- Prior art date
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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
- B66C23/62—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 machine for lifting and handling loads with an adjustable and articulated distributing jib, comprising a pylon with a rotating pivot, an articulated jib comprising a jib foot, articulated at its first end at the top of the pylon by an axis of horizontal rotation, a dart articulated in rotation by a horizontal articulation axis at the second end of the boom foot, a boom retention assembly comprising at least one punch, a boom retention sling and a mobile counterweight connected to the boom by said retaining sling
- Cranes with lifting distributing jibs have the advantage, compared to horizontal jib cranes, of being able to bring loads to greater heights, at comparable pylon heights.
- the deadweight effort of a boom operating in lifting mode varies considerably between the positions of the boom close to the horizontal and the raised position close to the vertical. This is why this type of crane is sometimes provided with a mobile counterweight, the position of which varies as a function of the angle made by the boom with the horizontal.
- the document DE 3438937 describes a lifting jib crane, with a platform at the top of the pylon, carrying a counterweight disposed at one end of a swinging arm.
- the position of the arm is controlled by the angular position of the boom, attached to the other end of the swingarm, so that the counterweight is near the axis of rotation of the pylon when the boom is raised, and moves away in a pendulum motion when the boom s' tilt to the horizontal.
- This device does little to assist the lifting operation for large lifting angles.
- This type of crane always requires a high torque lifting motor device.
- Document EP 379448 describes a lifting jib crane comprising a rotating pivot, on which the jib is mounted, a platform carrying the jib lifting and lifting mechanisms as well as a mobile counterweight, fixed at the rear of the pivot, opposite the arrow.
- the counterweight is mounted rolling on rectilinear longitudinal members of the platform, which have a slight slope directed towards the axis of the pylon.
- the counterweight is connected by a retaining tie to the jib, via a deflection pulley, so as to move away from the pylon when the jib lowers horizontally and to approach the pylon when the jib is raised.
- This device compensates for the moment of the dead weight of the boom on the pylon structure, but the lifting requires a mechanism providing a very high torque.
- Document DE 1260733 describes a crane of this type and proposes to reduce or even eliminate the counterweight and to use a distribution booster cable, fixed to the end of the dart tip, cooperating with an arrow retaining cable acting on the end of the counter-dart, via punches and deflection pulleys, these two cables being actuated by winches.
- the implementation of these winches requires very high torque motors.
- Patent FR 2605619 describes a folding lifting device which combines the effects of an articulated distributing jib crane with those of a lifting distributing jib crane, thus giving it a certain versatility.
- this crane due to the design of the articulations of the distributing jib, this crane always has a significant minimum reach.
- the height gain under hook when the tip of the arrow is raised remains relatively small, not being able to exceed an angular amplitude equivalent to 30 ° relative to the horizontal.
- Patent application EP 1057776 of the applicant describes a folding lifting device with an adjustable distributing jib capable of working in articulated mode or in lifting mode.
- the arrow consists of a boom foot, the first end of which is mounted at the top of the pylon, and a dart mounted in articulation on the second end of the boom foot, this dart being delimited by this articulation in two parts, with know a counter-dart and a dart point.
- the counter-dart and the part of the jib foot close to this articulation are shaped so that the jib foot and the dart can come into alignment in liftable working mode, which increases both the horizontal reach and the height maximum under hook of the machine.
- This device uses a distribution cable not maintained by guides over a long length when the boom is almost fully deployed, hence problems of stability in rotation and distribution under load and headwind.
- Patent application WO 02/04336 by the applicant describes folding lifting devices and tower cranes with jibs swiveling, articulated, lifting and tilting dart distributors.
- the part of the jib foot adjacent to the dart and the counter-dart have conjugate shapes allowing the dart point to come into position aligned with the jib foot in the lifting work mode.
- a system of jacks is arranged at the articulation between the boom foot and the dart to ensure the deployment and the folding of the boom in horizontal or tilted articulated working mode.
- a mobile counterweight system allows the crane to be balanced in all working positions: this system comprises in combination a fixed counterweight, for example at the end of the mechanism platform, a main pendulum counterweight and a second oscillating counterweight corrector.
- the adjustment of the masses and positions of the three counterweights allows these cranes to be optimally balanced in the different lifting, tilting and articulated working modes.
- the object of the present invention is to provide a lifting device of the defined type of input which does not have the drawbacks mentioned above.
- the object of the present invention is in particular to propose a lifting machine having the same character of versatility of use as that described in the document WO 02/04336 while lowering the manufacturing cost, by simplifying the implementation and, moreover, by reducing the space requirement below the platform.
- the mobile counterweight exerts, simply via the boom retaining sling (s), a pull on this boom, the intensity of which depends on the local slope of the guide track at the position of the counterweight.
- the mobile counterweight also exerts a bearing force on the guide track, which results in a torque exerted on the structure of the machine secured to the guide track, this couple being a function of the distance between counterweight and axis of the pylon , and also the local slope at the position of the counterweight.
- the boom retaining assembly of the lifting device according to the invention may comprise only one retaining sling. It is however preferable to use a set of two slings and two punches with their respective deflection pulleys, the slings being arranged and attached on either side of the boom, arranged symmetrically with respect to the plane of symmetry thereof .
- the description below describes, for the sake of educational simplicity, a lifting machine equipped with a retaining sling. It applies mutatis mutandis to a machine fitted with two slings.
- the guide track according to the invention is arranged opposite the arrow, that is to say that seen in vertical projection on a horizontal plane, it extends in the opposite direction of the projection of the arrow, relative to the axis of rotation of the pylon.
- the guide track in side view, it has a curved profile, the slope variations being chosen by the manufacturer according to the forces required by the boom.
- the guide track has in its first portion, the closest to the pylon, a slight slope, lower than the slope of a second portion of the track, further from the pylon.
- the guide track may have two or more portions of constant but different slopes, preferably connected to each other by a rounding.
- the guideway may have a more complex profile.
- the guide track may have a curvilinear profile, in particular a sigmoidal profile.
- the mobile counterweight is provided with rolling means, such as wheels or rollers, and the guide track can comprise one or more rails on which said rolling means roll.
- rolling means such as wheels or rollers
- the guide track can comprise one or more rails on which said rolling means roll.
- Such a track can be produced by means of a pair of curved rails, parallel to each other, and the counterweight can consist of a roller carriage, movable on these rails, and of ballast elements carried by said cart.
- the guide track could also consist of a plurality of rollers on which the mobile counterweight slides, or of any equivalent mechanical system.
- a counterweight of weight P placed on the guide track when it is located at a distance x from the axis of the pylon, in an area where the guide track has an angle ⁇ with the horizontal, exerts on the one hand a restoring force F on the boom via the retaining sling and the return pulleys, and on the other hand a bearing force on the guide track which generates a torque C exerted on the structures of the crane, opposing the torque exerted by the dead weight of the boom and the lifting load on the pylon.
- these forces correspond to the two components of the vector P, respectively parallel and perpendicular to the guide track, and
- ⁇ varies as a function of x, the function ⁇ (x) being determined by the choice of the curvilinear profile of the guideway made by the manufacturer of the crane.
- the distance x of the counterweight relative to the axis of the pylon being itself a decreasing function of the angle made by the jib foot with the horizontal, due to the connection via the retaining sling, the choice of profile of the guideway according to the invention makes it possible to modulate a deflection component of the boom, so that all of the restoring and supporting forces automatically balance the crane during the movements of the crane in articulated work, and can assist the mechanism (s) operating the deployment and folding of the boom, such as jacks, motors and winches. If the crane is operating in lifting mode, this recall component automatically assists the boom lifting mechanism.
- variable return component in the lifting, articulated or tilting dart working mode allows the use of mechanical lifting devices offering a lower maximum torque and maximum power.
- the use of this variable return component of the counterweight also allows the use of less powerful, lighter and more economical devices than a system of hydraulic jacks, for example electric winches, to operate the boom in articulated working mode. for horizontal load distribution.
- reaction time of a system with electric motors is faster than that of a system based on hydraulic cylinders, which is penalized by the long length of the pipes.
- the use of an electric motor system therefore improves the comfort of the crane operator. Finally, maintenance is also reduced and easier.
- the counterweight system according to the invention can be applied - to lifting devices with articulated distributing jib, or - to lifting jib machines, or - to articulated and lifting jib machines, or - to articulated, lifting boom and tilting jib.
- the counterweight system according to the invention can in particular be used for machines whose arrow comprises a jib foot articulated at the top of the pylon by its first end, a dart articulated in rotation at the second end of the jib foot, the so-called dart comprising on either side of its axis of articulation at the foot of the arrow respectively a dart point and a counter-dart, the said second end of the arrow foot and the counter-dart having conjugate shapes allowing the point of the dart to come into position aligned with the jib foot in the lifting working position, the end of the jib retaining sling being fixed to the dart.
- the counterweight system according to the invention can be used not only for tower cranes, but also for lifting machines with collapsible, self-erecting pylons.
- the counter-dart and the second end of the jib foot may have conjugated prismatic profiles and come into contact with one another when the jib foot and dart are aligned.
- the second end of the boom foot can have the shape of a fork with two branches and the counter-dart is housed in the space between the two branches.
- the jib foot is made up of two parallel beams and the counter-dart is received in the space between the two beams.
- the jib may include a jib foot / dart blocking device such as those described in document WO 02/04336.
- the rotation of the dart around the second end of the jib foot is carried out by means of a system of opposing cables wound and unwound by means of electric winches.
- these winches, part of the cables and their deflection pulleys can be housed in the jib foot. More precisely, the winches are housed at the base of the jib foot to obtain a better balance of the crane by reducing as much as possible the self-weight of the winches towards the center of the pylon. This location improves maintenance due to the fact that the winches are located close to the turning pivot, i.e. the platform.
- the rotation of the dart around the end of the jib foot is carried out by means of a gear system comprising a motor, a pinion and a toothed segment.
- the motor is fixed to the jib foot and drives, via a pinion, a circular toothed segment secured to the dart.
- - fig. 1 shows two schematic views, in profile in front and in lb, of a construction crane according to the invention, mounted on a crawler, boom folded and raised, the dart being folded against the boom foot;
- - fig. 2 is a schematic profile view of a counterweight guide track
- - fig. 4 is a side view of a counterweight
- - fig. 5 is a front view of a counterweight
- - figs. 6a and 6b are two schematic side views of a lifting jib crane
- figs. 7a, 7b and 7c are three schematic side views of an articulated jib crane
- FIGS. 7a, 7b and 7c are detailed views illustrating the operation of the crane of FIGS. 7a, 7b and 7c;
- - figs. 9a, 9b are two schematic side views of a crane operating in a tiltable jib working mode;
- FIG. 10a 10b and 10c are three schematic views illustrating another embodiment of an articulated jib crane
- - fig. 11 is an overall view, in profile, of an exemplary embodiment of a tower crane.
- Fig. 2 is a schematic view, in profile, of an embodiment of the guide track 1 of the counterweight 100.
- the guide track consists of two curvilinear and parallel rails 2, 3, which are both visible, in section, in FIG. 5.
- only one rail is shown.
- the guide 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 from 2 ° to 25 °.
- the slope increases.
- B in fig. 2 the guide track can form an angle ⁇ B of the order of 15 ° to 85 ° with the horizontal.
- C close to the distal end of the guideway relative to the axis of the pylon, the slope decreases again, the track forming an angle ⁇ c from 2 ° to 45 °.
- 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 greater.
- this restoring force corresponds approximately to the component of the weight P parallel to this guide track, ie Fb.
- zone C slightly less steep, this restoring force decreases again.
- the slope remains constant and equal to the maximum value reached in zone B, the restoring force would keep in zone C the maximum value of F b reached in the zone B.
- Fig. 3 represents the restoring force as a function of the distance between counterweight and pylon for three different counterweight systems. In all three systems, the total mass of the counterweight is 20 tonnes.
- Curve (b) represents the restoring force of a pendulum counterweight, attached to the end of a 12 meter long swing arm, which is bulky, the movement taking place in the space below the platform.
- Curve (c) represents the restoring force obtained by means of a guide track according to the invention similar to that of FIG. 2, for which the slope is 3 ° near the pylon, then increases to a maximum of 53 ° at a distance of 9 meters, to then decrease, the slope being of the order of 30 ° at the end of the way.
- the profile of the curve (c) is determined by the choice of the profile of the guideway, that is to say by the variations in slope between the zones A, B and C shown in FIG. 2.
- Figs. 4 and 5 show, respectively in profile and from the front, an embodiment of the counterweight according to the invention.
- the carriage is generally designated by 101.
- the chassis of the carriage consists of four longitudinal beams, two external beams 102 and two internal beams 103, connected by four transverse beams 104.
- Each beam 102, 103 carries two rolling devices with rollers 105 which roll on the two curvilinear rails 2 and 3 constituting the track.
- the outer longitudinal beams 102 each carry three substantially vertical support beams, namely an upper beam 106 and two lower beams 107, constituting three support points.
- Each longitudinal beam 102 also carries two support arms 108, 109.
- These support arms are preferably mounted inclined to eliminate the play between ballast elements, which come to bear against each other, and against the points of support .
- the support arms and the corresponding fixing means of the ballast elements are arranged so that the level of the center of gravity of the counterweight is close to, and preferably coincides substantially with the level of the track at the location where the carriage is located, to avoid swaying when the crane is moving.
- the support arms can be mounted on articulations allowing them to be folded, in order to reduce the size of the carriage during transport.
- Each pair of unfolded arms 108, 109 receives one or more ballast mass (s) 110. As shown in FIGS.
- these ballast masses may consist of concrete plates provided with two holes allowing them to be hung on the support arms 108 and 109.
- the holes 111 can be produced in the form of two squares turned angularly by 90 ° l one with respect to the other and spaced from each other so that the support arms 108 and 109 are placed in the corners as shown in FIG. 2.
- this arrangement 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 prevents the masses from tilting and the corresponding shocks when the mobile carriage moves between zone A and zones B and C of the track.
- the installation of weights on the carriage is completed by the installation of a set of bars 113 and safety cables 112 between support arm and support beams of the carriage.
- the ballast plates 110 provide the lateral wind with a large surface. The action of the wind on it therefore generates a torque which partially compensates for the torque that the wind exerts on the boom. This arrangement and this conformation of the ballast plates therefore assists the horizontal rotation of the rotating part above the pivot, that is to say the distribution of the loads.
- FIG. 5 shows an articulated jib crane, jib foot raised to the maximum and dart folded against the jib foot, on a rolling chassis. In the position where the boom foot is fully raised, the ballast masses come very close to the pylon, framing it on both sides, as shown in fig. lb.
- Cylinders 33 can be used to lift and adjust the level of the crane during such a movement.
- Figs. 6a and 6b show the operation of the counterweight on a lifting machine whose boom operates in liftable working mode.
- Fig. 6a shows the machine, the arrow 10 being almost horizontal, in the maximum range position.
- the counterweight 100 represented in a simplified manner by a square ballast and a set of rollers, rolls on the guide track 1 and is connected to the boom only by the retaining sling (s) 11, so that its movement is controlled by the movement of the boom simply and only by this (these) sling (s) 11.
- the counterweight 100 is located in the distal zone of the track 1 relative to the axis of the tower.
- the arrow 10 is raised to the minimum reach position.
- the boom retaining sling 11 is fixed at its first end to the counterweight 100. It passes over a deflection pulley 9 arranged at the distal end of the guide track and over a second deflection pulley 8 arranged at the top of the punch 7.
- the other end of the retaining sling 11 is fixed at 12 to the boom, at the same level as the easel 13.
- the easel 13 serves as an attachment point to the lifting device.
- the lifting device can consist of several parts, namely a lifting rod 14, connecting the lifting bridge to a pulley or a block 16, and a lifting cable 15, which can make several strands of block.
- the lifting cable 15 is connected to a winch linkage 17, the coil of which is arranged on the platform integral with the guide track.
- the boom retaining sling 11 cooperates with the lifting motor device to raise the boom.
- the counterweight system according to the invention therefore makes it possible to reduce the maximum nominal torque of the lifting device. If it is desired to obtain a return component F assisting the lifting device to the maximum in the positions close to that of FIG. 6a, the guide track can have its steepest slope in its distal portion.
- FIGS. 6a and 6b can be a rigid boom or an articulated boom like that of FIG. 7c.
- Figs. 7a, 7b and 7c illustrate the operation of an articulated boom operating in horizontal articulated distribution mode.
- Fig. 7a similar to fig. la, shows the arrow in the minimum reach position, dart 18 folded against the boom foot 19.
- FIG. 7c shows the arrow 10 in a position similar to that of FIG. 6a, in the maximum reach position, the jib foot and the dart being aligned.
- Fig. 7b shows the arrow in an intermediate deployment position.
- the counterweight 100 is approximately halfway and that the traction component on the retaining sling 11 of the boom is large.
- the arrow linkage rod 14 attached to the easel 13 passes over the end 21 of the counter-dart 20 which returns it.
- the articulation 32 formed by a horizontal axis of rotation between the jib foot 19 and the dart 18 delimits the latter between dart point 22 and counter-dart 20. It is at this level that 12 is attached to the sling 11.
- the rotation of the dart around the hinge pin 32 is carried out using two counter cables 23 and 24.
- the point of attachment of the counter cable 23 is located at the end of the counter dart 20 in order to obtain the largest lever arm relative to the joint 32, in order to reduce the forces in the cable 23 as well as the required power of the electric winch 25 which actuates it.
- the point of attachment of the cable 24 on the dart 22 is situated approximately at the same distance as the cable 23 relative to the joint 32.
- a pulley 29 for deflecting the cables 23, 24 is arranged in the jib foot, in an area close to the joint 32 between the jib foot and the dart, as illustrated in FIG. 7b.
- the winding winches 25, 26 of the cables 23 and 24 are arranged in the jib foot near the articulation 27 of the first end of the jib foot at the top of the pylon in order to obtain a better balance of the crane in bringing the self-weight of the different elements of the winches 25 and 26 as close as possible to the center of the pylon. This location also improves maintenance due to the fact that the winches are close to the turning pivot.
- the attachment point 12 of the sling 11, located on the jib 18, describes an arc around the articulation axis 32 to optimize the movement of the counterweight in order to improve the balance of the crane.
- FIGS. 8a, 8b, 8c, 8d and 8e The operation of the horizontal distribution from the minimum range (fig. 7a) to the maximum range, fig. 7c, in articulated working mode is illustrated in more detail by FIGS. 8a, 8b, 8c, 8d and 8e.
- Fig. 8a shows the area of the arrow surrounding the 32 foot articulation of arrow / dart in the position of fig. 7a.
- the boom retaining slings (s) pass (s) a little below and to the right of the hinge 32 jib / dart joint; the lifting cable 15 and the lifting linkage 14 of the boom pass over the end 21 of the counter-dart and are located a little to the left of the joint 32 between the boom foot and the dart.
- Cables 23 and 24 have antagonistic effects. From this position, the upper cable 23 is controlled by the crane operator and the lower cable 24 is unwound. The upper cable 23 is deflected by the upper rod 30.
- the upper cable 23 always pulls on the counter-dart, in order to continue the deployment movement, but the upper rod 30 no longer deflects the upper cable 23.
- the lower cable 24 is always driven by the upper cable.
- the upper cable 23 always pulls on the counter-dart, in order to continue deploying the boom, and the lower cable 24 is always driven by the upper cable. It will be noted that the lower cable 24 comes into contact with the lower rod 31 and that the retaining sling 11 has passed the joint 32 between the jib foot and the dart.
- the lifting rod 14 is no longer in contact with the end 21 of the counter-dart.
- the lower rod 31 increases the angle of traction of the lower cable 24 in order to reduce the efforts of this and to ensure the stability of the elements around the joint 32.
- the return force contribution F of the boom retaining sling 11 decreases in favor of the torque C.
- the distal zone of the guideway 1 indicated as zone C on the fig. 2 may have a slope less than the slope of zone B.
- Figs. 9a and 9b illustrate the tilting jib working mode of the articulated boom previously described in relation to the groups in FIG. 7 and 8.
- the jib foot 19 does not move, it is in abutment against a stop device 33.
- stop devices are known in the state of the art.
- the mobile counterweight 100 is located in the two positions in an area of slight slope of the track, near the pylon.
- this attachment point 12 describes an arc of a circle around the articulation 32 of the boom, causing the counterweight in a limited displacement.
- the stability of the end of the boom is ensured by an electro-mechanical brake with no current installed on the motors of cables 23 and 24.
- the set of opposing cables 24 and 23 with their winding and unwinding winches 25, 26 arranged in the jib foot is replaced by a gear system 200, composed of a motor 201, a pinion 202 and a toothed segment 203, arranged at the joint 232 between the jib foot 204 and the dart 205.
- the electric motor 201 is fixed on the jib foot, it drives a pinion 202 which itself meshes with a circular toothed segment 203 secured to the dart, to ensure the rotation of the dart around the joint 232 between the foot of the arrow and the dart.
- the arrangement and function of the boom retaining slings 11 and the lifting tie rod 14 are the same as those of the embodiments described above.
- Fig. 11 schematically illustrates an exemplary embodiment of a tower crane according to the invention.
- the basic chassis has a 5 x 5 meter wheelbase and carries a basic ballast of 46 tonnes.
- the basic chassis is surmounted by a tower having a cabin height of 31 meters and a rotating pivot. This carries the platform, the cabin and the boom as well as the guide track on which the mobile ballast circulates.
- the total weight of the empty crane in working order is 111.6 tonnes.
- the guide track integral with the pivot rotating at the top of the pylon extends from the pylon up to a distance of 12 meters from the latter. It consists of a pair of rails connected by spacers. Each rail comprises a first straight portion with a slope of 5 °, extending from the rotating pivot to a distance of 6 meters, a second straight portion with a slope of 29 °, extending from a distance of 6 meters to at a distance of 8 meters from the pylon, and a third straight portion with a 43 ° slope, corresponding to the last two meters of the track. Between the first and second straight portions on the one hand and the second and third straight portions on the other are located two curved intermediate portions, forming the rounded rails, which are therefore generally curvilinear.
- the guide track which also constitutes the platform, carries the boom lifting winch which has a power of 22 kW.
- the guide track is surmounted by a set of punches and punch rods carrying the return pulleys. The whole rises to a height of about 41.6 meters.
- the boom foot accommodates, near its articulation with the rotating pivot of the pylon, the boom deployment / folding winches in articulated working mode with a power of 7.5 kW and the load lifting winch d '' a power of 45 kW.
- the corresponding return pulleys are also housed in the jib foot near the joint with the dart.
- the operating mode of the articulated boom has been described above in relation to FIGS. 6a to 8e.
- the crane can distribute a maximum load of 12 tonnes at reduced speed, or a load of 10 tonnes at normal speed, in an area of 2 to 20 meters from the foot of the pylon.
- the distributable load decreases at a greater distance from the base of the pylon.
- the maximum load is 5.6 tonnes at reduced speed and 4.7 tonnes at normal speed at the maximum working range, that is to say at 47 meters.
- the dispensing speed can vary from 0 to 60 meters per minute.
- the maximum distributable load is 12 tonnes when the range is included between 5 and 20 meters.
- the maximum load is reduced to 5.6 tonnes at a maximum range of 47 meters.
- the maximum height under hook in lifting mode is 80 meters.
- the speed of movement in liftable mode can vary from 0 to 30 meters per minute.
- the crane When the crane is dismantled, it can be transported in parts by means of five trailers of lengths between 6 and 12 meters, each of the trailers carrying a set of parts from 19.5 to 25 tonnes.
- the boom lifting winch can be removed and the lifting block is replaced by two metal tie rods. This reduces the selling price of the crane as well as the number of parts.
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/571,982 US7331476B2 (en) | 2003-09-15 | 2004-09-14 | Lifting appliance |
CA002539014A CA2539014A1 (fr) | 2003-09-15 | 2004-09-14 | Engin de levage |
EP04761917A EP1667931B1 (fr) | 2003-09-15 | 2004-09-14 | Engin de levage |
AT04761917T ATE446275T1 (de) | 2003-09-15 | 2004-09-14 | Hebevorrichtung |
AU2004272136A AU2004272136A1 (en) | 2003-09-15 | 2004-09-14 | Lifting appliance |
DE602004023738T DE602004023738D1 (de) | 2003-09-15 | 2004-09-14 | Hebevorrichtung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03405677.0 | 2003-09-15 | ||
EP03405677A EP1514832A1 (fr) | 2003-09-15 | 2003-09-15 | Engin de levage |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005026036A1 true WO2005026036A1 (fr) | 2005-03-24 |
Family
ID=34130421
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CH2004/000577 WO2005026036A1 (fr) | 2003-09-15 | 2004-09-14 | Engin de levage |
Country Status (7)
Country | Link |
---|---|
US (1) | US7331476B2 (fr) |
EP (2) | EP1514832A1 (fr) |
AT (1) | ATE446275T1 (fr) |
AU (1) | AU2004272136A1 (fr) |
CA (1) | CA2539014A1 (fr) |
DE (1) | DE602004023738D1 (fr) |
WO (1) | WO2005026036A1 (fr) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1916220A1 (fr) * | 2006-10-27 | 2008-04-30 | Manitowoc Crane Companies, Inc. | Seuil de levage mobile et contrepoids de position variable |
US7967158B2 (en) | 2006-10-27 | 2011-06-28 | Manitowoc Crane Companies, Llc | Mobile lift crane with variable position counterweight |
US9278834B2 (en) | 2009-08-06 | 2016-03-08 | Manitowoc Crane Group, LLC | Lift crane with moveable counterweight |
US9440824B2 (en) | 2012-03-30 | 2016-09-13 | Manitowoc Crane Group France Sas | Vehicle crane with decouplable counterweight assembly |
US10179722B2 (en) | 2014-01-27 | 2019-01-15 | Manitowoc Crane Companies, Llc | Lift crane with improved movable counterweight |
US10183848B2 (en) | 2014-01-27 | 2019-01-22 | Manitowoc Crane Companies, Llc | Height adjustment mechanism for an auxiliary member on a crane |
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CN102259801B (zh) * | 2011-04-28 | 2013-06-05 | 上海三一科技有限公司 | 桁架臂履带起重机用折叠臂架 |
US9102507B2 (en) * | 2011-06-29 | 2015-08-11 | Liebherr-Werk Ehingen Gmbh | Method of operating a crane and crane |
CN102756978A (zh) * | 2012-07-20 | 2012-10-31 | 辽宁抚挖重工机械股份有限公司 | 一种履带起重机折叠臂 |
NO2694106T3 (fr) * | 2012-09-12 | 2018-05-12 | ||
CN103318781B (zh) * | 2012-11-01 | 2015-05-13 | 上海振华重工(集团)股份有限公司 | 用于码头的折臂大梁起重机 |
CN102942125B (zh) * | 2012-12-12 | 2014-10-22 | 中联重科股份有限公司 | 副臂尾架及包含该副臂尾架的副臂、起重设备 |
JP6816647B2 (ja) * | 2017-05-26 | 2021-01-20 | コベルコ建機株式会社 | ジブ引込装置およびジブ引込方法 |
CN107717949A (zh) * | 2017-11-23 | 2018-02-23 | 苏州夏木自动化科技有限公司 | 地面移动式助力机械手 |
CN115611173A (zh) * | 2022-09-08 | 2023-01-17 | 三一海洋重工有限公司 | 一种前大梁俯仰机构及岸桥 |
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- 2004-09-14 WO PCT/CH2004/000577 patent/WO2005026036A1/fr active Search and Examination
- 2004-09-14 EP EP04761917A patent/EP1667931B1/fr not_active Not-in-force
- 2004-09-14 DE DE602004023738T patent/DE602004023738D1/de active Active
- 2004-09-14 CA CA002539014A patent/CA2539014A1/fr not_active Abandoned
- 2004-09-14 US US10/571,982 patent/US7331476B2/en not_active Expired - Fee Related
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Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
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US10336589B2 (en) | 2006-10-27 | 2019-07-02 | Manitowoc Crane Companies, Llc | Mobile lift crane with variable position counterweight |
US7967158B2 (en) | 2006-10-27 | 2011-06-28 | Manitowoc Crane Companies, Llc | Mobile lift crane with variable position counterweight |
US8511489B2 (en) | 2006-10-27 | 2013-08-20 | Manitowoc Cranes, Llc | Mobile lift crane with variable position counterweight |
US8985353B2 (en) | 2006-10-27 | 2015-03-24 | Manitowoc Crane Companies, Llc | Mobile lift crane with variable position counterweight |
US7546928B2 (en) | 2006-10-27 | 2009-06-16 | Manitowoc Crane Companies, Inc. | Mobile lift crane with variable position counterweight |
US11884522B2 (en) | 2006-10-27 | 2024-01-30 | Grove U.S. L.L.C. | Mobile lift crane with variable position counterweight |
EP1916220A1 (fr) * | 2006-10-27 | 2008-04-30 | Manitowoc Crane Companies, Inc. | Seuil de levage mobile et contrepoids de position variable |
US11261064B2 (en) | 2009-08-06 | 2022-03-01 | Manitowoc Cranes, Llc | Lift crane with moveable counterweight |
US9278834B2 (en) | 2009-08-06 | 2016-03-08 | Manitowoc Crane Group, LLC | Lift crane with moveable counterweight |
US10457530B2 (en) | 2009-08-06 | 2019-10-29 | Manitowoc Cranes, Llc | Lift crane with moveable counterweight |
US9440824B2 (en) | 2012-03-30 | 2016-09-13 | Manitowoc Crane Group France Sas | Vehicle crane with decouplable counterweight assembly |
US11208303B2 (en) | 2014-01-27 | 2021-12-28 | Manitowoc Crane Companies, Llc | Lift crane with improved movable counterweight |
US10183848B2 (en) | 2014-01-27 | 2019-01-22 | Manitowoc Crane Companies, Llc | Height adjustment mechanism for an auxiliary member on a crane |
US10179722B2 (en) | 2014-01-27 | 2019-01-15 | Manitowoc Crane Companies, Llc | Lift crane with improved movable counterweight |
Also Published As
Publication number | Publication date |
---|---|
DE602004023738D1 (de) | 2009-12-03 |
US20060283826A1 (en) | 2006-12-21 |
AU2004272136A1 (en) | 2005-03-24 |
EP1514832A1 (fr) | 2005-03-16 |
EP1667931A1 (fr) | 2006-06-14 |
CA2539014A1 (fr) | 2005-03-24 |
US7331476B2 (en) | 2008-02-19 |
ATE446275T1 (de) | 2009-11-15 |
EP1667931B1 (fr) | 2009-10-21 |
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