EP0499208A2 - Flèche télescopique pour grues mobiles ou analogue - Google Patents

Flèche télescopique pour grues mobiles ou analogue Download PDF

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Publication number
EP0499208A2
EP0499208A2 EP92102268A EP92102268A EP0499208A2 EP 0499208 A2 EP0499208 A2 EP 0499208A2 EP 92102268 A EP92102268 A EP 92102268A EP 92102268 A EP92102268 A EP 92102268A EP 0499208 A2 EP0499208 A2 EP 0499208A2
Authority
EP
European Patent Office
Prior art keywords
telescopic boom
boom according
shots
profile
telescopic
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.)
Granted
Application number
EP92102268A
Other languages
German (de)
English (en)
Other versions
EP0499208A3 (en
EP0499208B1 (fr
EP0499208B2 (fr
Inventor
Rudolf Becker
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.)
Liebherr Werk Ehingen GmbH
Original Assignee
Liebherr Werk Ehingen GmbH
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.)
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Publication date
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Priority claimed from DE9102552U external-priority patent/DE9102552U1/de
Priority claimed from DE9113981U external-priority patent/DE9113981U1/de
Application filed by Liebherr Werk Ehingen GmbH filed Critical Liebherr Werk Ehingen GmbH
Priority to DE9218841U priority Critical patent/DE9218841U1/de
Publication of EP0499208A2 publication Critical patent/EP0499208A2/fr
Publication of EP0499208A3 publication Critical patent/EP0499208A3/de
Publication of EP0499208B1 publication Critical patent/EP0499208B1/fr
Application granted granted Critical
Publication of EP0499208B2 publication Critical patent/EP0499208B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • 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
    • B66C23/70—Jibs constructed of sections adapted to be assembled to form jibs or various lengths
    • B66C23/701—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic
    • B66C23/705—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic telescoped by hydraulic 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
    • B66C23/70—Jibs constructed of sections adapted to be assembled to form jibs or various lengths
    • B66C23/701—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic
    • B66C23/708—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic locking devices for telescopic jibs

Definitions

  • the invention relates to a telescopic boom for vehicle cranes or the like, consisting of an outer link piece pivotally mounted on the vehicle or its superstructure, in which a plurality of telescopically collapsible and extendable telescopic sections are held, each section being provided with bearings for the section guided therein and can be locked with this shot and wherein a hydraulic pressure medium piston-cylinder unit is provided for extending and retracting the individual shots.
  • the individual telescopic sections have an essentially box-like profile, the lower straps of the individual sections having flat V-shaped profiles or flat channel-shaped profiles, which are formed by a flat middle one Web part angled legs are formed.
  • These lower belts are welded to the edge areas of the downward facing legs of U-shaped profile parts with rounded corner areas between their web parts and legs to form box-shaped profiles, in the area of Welded connections can also be welded in bracing strut-like sheets.
  • the individual telescopic sections are mounted one inside the other on the trough-shaped lower chords according to the pressure distribution ratio known from DE-PS 21 48 966, the bearing forces being transmitted in the region of the upper rounded corners of the box profiles by rollers or appropriately shaped bearing shoes.
  • bulge stiffeners with U-shaped profiles are welded onto the inside or outside of the legs of the profile.
  • the lower flange which is mainly subjected to bending forces, is stiffened by its V-shape or the two longitudinal bends that form the channel shape and secured against dents.
  • Telescopic boom in spite of the welded-in buckling stiffeners and the buckling lines, is not only sensitive to dents, it can also be produced only with increased effort because of its complicated cross-sectional shape. Telescopic booms are not only loaded on bends, but also on torsion.
  • the bearing elements arranged in the lower flange with a channel-shaped or V-shaped cross section counteract a rotation. But if the telescopic boom is provided with a luffing needle, this is via a rear A-frame or the like.
  • the object of the invention is a telescopic boom of the beginning to create specified type, which is characterized by a great flexural strength of its individual shots by a simple and economically producible construction.
  • this object is achieved in that the individual shots have round profiles.
  • Round profiles of this type can be produced in a simple and economical manner by known tube production processes. Round profiles not only have favorable moments of inertia and resistance, so that they have great flexural rigidity, they also provide great security against dents due to their round cross-section, without the profiles having to be additionally protected against dents. Round profiles can be provided with all-round bearings in a favorable way, so that good positions of the individual shots in one another are guaranteed even if the telescopic booms are provided with luffing needles and are additionally braced. In addition, the required torsional rigidity is ensured by locking or bolting the individual shots together, both when retracted and when extended.
  • the individual shots can have circular profiles.
  • shots with elliptical profiles that have large moments of inertia in the direction of their long axis, which are arranged vertically, are particularly advantageous.
  • the ratio of the long to the short axes of the profiles expediently decreases from shot to shot from the outside to the inside, so that lateral crescent-shaped spaces are formed between the individual shots, in which lines serving to supply energy can be laid.
  • the outer wefts can have a circular profile.
  • an arrangement can be selected as is known from the older, but not previously published utility model G 90 13 210.6.
  • the piston rod of the piston-cylinder unit can thus be articulated on the boom link piece and a driver device for the individual shots can be arranged in the region of the end of the cylinder from which the piston rod emerges.
  • a driver device for the individual shots can be arranged in the region of the end of the cylinder from which the piston rod emerges.
  • only such a large length of the telescopic cylinder is buckled that corresponds to the extended part of the piston rod plus the necessary clamping length.
  • the receptacles for the coupling pieces of the driver device can be arranged at the inner ends of the telescopic shots.
  • the receptacles for the coupling pieces of the driver device are expediently provided on annular frame parts at the inner ends of the telescopic sections. These recordings are expediently arranged in pairs opposite one another. They can be made from holes or bushings exist for retractable bolts.
  • the receptacles can advantageously be arranged in common planes parallel to the center line of the shots.
  • a pressure medium piston cylinder unit provided with an anti-rotation device has only a limited torsional stiffness due to its elasticity
  • a free-running profile tube articulated on the boom articulation piece is non-rotatably articulated, the length of which is the length of the outer one Shot corresponds and on which the inner shots are guided longitudinally displaceably, but non-rotatably.
  • the individual shots, the bolts of which, at the same time, also serve as an anti-rotation lock, are thus held on this profile tube so that they cannot rotate against one another during extension and retraction.
  • the control used ensures that the shots detached from each other are only completely pushed off the twist-preventing profile tube when they are bolted to the twist or shots to prevent them from rotating.
  • the profile serving as an anti-rotation device is expediently a square tube or a triangular tube.
  • bolts which can be actuated hydraulically or by compressed air and suspension are expediently provided on their collar-like thickened end regions.
  • the bolts can be provided with conical or beveled centerings, which correct slight twists during the extension and retraction of individual shots when locking.
  • the object is achieved in that the articulation piece and the shots consist of profiles, each of which has a lower round and an upper semi-box-shaped part in the horizontal (pivoted onto the vehicle) position, the opposing legs connected to each other are.
  • an upper semi-box-shaped profile is thus connected to a lower round profile in a horizontal parting plane.
  • the lower round profile can for example be a semicircular profile.
  • the lower profile part preferably has approximately the shape of a half ellipse with the apex formed by the small radius.
  • the profile according to the invention thus consists of different profile parts with respect to its horizontal axis, while it is symmetrical about its vertical axis.
  • the profile according to the invention is particularly favorable meet the requirements of a telescopic boom.
  • the profiles of the individual shots of a telescopic boom are primarily subjected to tension in their upper area and to pressure in their lower area during operation, so that the lower area is highly susceptible to buckling.
  • stiffening sheets were welded into the profile inside and / or outside to increase the buckling stiffness.
  • the profile according to the invention meets the demands of a telescopic boom in a particularly favorable manner, because the lower region, which is highly sensitive to buckling, consists of a round profile, which is much less sensitive to buckling than box-shaped profiles.
  • the buckling sensitivity of the lower profile part increases with the increasing compressive stress, i.e. in the direction of the lower apex line. It is therefore particularly favorable to design the lower profile part in the form of a semi-ellipse because this has the smallest radius of curvature in its apex region and therefore has the least sensitivity to buckling in the region with the greatest compressive stress.
  • the legs of the upper profile part can be at right angles to the straight web part forming the upper chord. Since the upper profile part is subjected to tension, the risk of buckling is low, so that the straight profile legs are accepted.
  • the legs of the upper profile part form an obtuse angle with the straight web part. Due to this obtuse angle, the round profile part extends into the upper area of the overall profile, so that in particular the middle profile part is less sensitive to dents.
  • the lateral stress curve is namely highest in the middle of the profile, which increases the compressive stress in this area. The curvature is over Continuing the profile center upwards, the buckling stiffness is improved in this area.
  • the legs of the upper profile part enclose acute angles with the straight web part.
  • This embodiment takes into account the lateral stress curve, the corresponding risk of buckling in the lateral area, if necessary, being taken into account by appropriate measures. For example, larger sheet thicknesses can be selected or buckling stiffeners can be welded in.
  • the legs of the lower round profile part connect tangentially to the straight legs of the upper profile part.
  • the legs of the upper profile part are expediently connected to the straight web part by rounded regions.
  • This embodiment makes it possible to arrange bearings for guiding and holding the telescopic shots in the rounded regions.
  • top shell of each shot can be folded in one piece in its entire length, so that none in the draft zone Welds and in particular no transverse welds are present.
  • Such a one-piece design is particularly difficult in the case of round and oval profile shapes due to the manufacturing facilities to be provided.
  • the round lower shell on the other hand, can be composed of several parts, which are welded together, in accordance with the production facilities to be provided. This can be accepted because weld seams are less problematic in pressure areas than in tension areas.
  • the upper shell When manufacturing the boom sections, the upper shell can be placed on a straight plate and does not need to be held in special facilities, as is the case with a complete oval boom profile.
  • the semi-box-shaped upper profile part creates additional advantages, which consist in the fact that the hoisting rope can lay down on the wide top chord without slipping sideways. Furthermore, the flat upper web part of the upper profile part is also useful for maintenance purposes, since it can be walked on safely. The upper profile part can also be sprayed with a rough covering, so that the necessary sliding security is given when walking on.
  • the arrangement of the bearings in the rounded area between the upper straight web part and the legs of the upper profile part makes it possible to keep the straight side profile walls free of bearings, so that they can be painted for corrosion protection and labeled.
  • the outer link 1 of the telescopic boom 2 is provided with a joint piece 3, by means of which it is attached to the superstructure of a crane, crane vehicle or the like. is articulated.
  • the piston rod of a hydraulic piston-cylinder unit 5 is articulated in the joint 4.
  • a square profile 6 is articulated in a torsion-proof manner above it on the boom link piece 4.
  • the articulation piece and the further telescopic shots are provided in the region of their ends with collar-like stiffeners 8-10, on which pressure medium piston cylinder units provided with locking bolts are arranged.
  • the innermost telescopic shot is, as can be seen from Fig. 1, provided at its outer end with a roller head.
  • FIG. 2 shows an enlarged cross section through the collapsed shots of the telescopic boom.
  • the inner sections 12, 13, 14, which have an elliptical shape, can be telescoped out of the outer bracket articulation piece 1, which in the exemplary embodiment shown has a circular cross section, the ratio of their long to their short axes increasing from the outside inwards.
  • crescent-shaped spaces 16 are formed between the side walls of the telescopic sections, in each of which profile boxes 17 with longitudinal slots for caterpillar-like chains (not shown) can be arranged, which serve to guide and hold supply lines, for example hydraulic and electrical lines.
  • the long axes of the elliptical profiles are reduced from shot to shot by approximately the same and relatively small amounts, so that the bending stiffness of the shots only decreases by smaller amounts from shot to shot, since the area moment of inertia determining the bending stiffness is essentially determined by the long axes.
  • the piston rod of the single-stage hydraulic cylinder 18 is articulated on the lower fastening frame 3 of the boom articulation piece 1 in FIG. 1.
  • the hydraulic cylinder is provided in the region of its outlet end of the piston rod with a collar-like widening 19 from which the locking bolts 20 can be extended. These locking bolts move into receptacles 21 which are provided on each telescopic shot.
  • FIGS. 1-3 and the associated description of the utility model G 19 13 210.6 For a more detailed configuration of this arrangement, reference is made to FIGS. 1-3 and the associated description of the utility model G 19 13 210.6.
  • the box section 6 is pivotally but non-rotatably articulated on the lower mounting frame 3 of the boom link piece 1.
  • the individual telescopic ones Shots 12-15 are provided with slide bearings 24 which are arranged on all lower telescopic shots at their lower frame ends.
  • the box section 6 is guided in these slide bearings.
  • the slide bearings 24 have only a relatively small axial length, so that they are close together in the axial direction when the telescopic sections are inserted.
  • the individual shots are provided in the manner shown in FIGS. 3 and 4 or 3 a and 4 a with all-round bearings, which consist of individual bearing segments 26 which are adapted to the cross-sectional shape and which are made of a suitable plastic, such as polyamide, for example. or other suitable storage materials or can also consist of composite materials.
  • a suitable plastic such as polyamide, for example. or other suitable storage materials or can also consist of composite materials.
  • bearings formed from individual bearing segments instead of bearings formed from individual bearing segments, continuous all-round bearings can also be provided.
  • An all-round bearing arrangement is arranged on the inside of the end-side collar 27 that closes off the individual shots. Further bearings are located on the inner frame end of each telescopic shot, as can be seen from FIGS. 8 and 9.
  • 27 hydraulic cylinders 28, 29 are arranged on opposite sides of the upper half of each stiffening collar, the pistons 30, 31 of which form or carry locking bolts.
  • the individual telescopic shots are provided in a known manner with holes for the locking bolts 30,31.
  • FIG. 5 shows a cross section through the round profiles of the telescopic shots.
  • All telescopic shots could also consist of round profiles in the manner shown in FIG. 6.
  • these round profiles provide evidence of the elliptical profiles Fig. 5 the disadvantage that larger, the bending stiffness greatly reducing diameter gradations would have to be provided if supply lines are to be arranged in the annular spaces between the individual shots.
  • the individual shots can be stored one inside the other with almost no play, which is advantageous for the operation of the crane.
  • This anti-rotation profile is expediently a large-volume square tube or triangular tube, which has a large polar moment of inertia, so that the remaining torsional elasticity is negligible.
  • a square tube any other shape can also be selected, for example a triangular or hexagonal tube.
  • Shots consisting of round tubes can be inexpensively manufactured in a known manner. Also leave the elliptical cross sections can be produced in a simple manner, for example, in that a round tube is then laterally pressed by hydraulic presses in such a way that the desired elliptical shape is produced.
  • the diameters of the wefts decrease relatively strongly if sufficiently large annular spaces are to be created for the arrangement of supply lines. This distance can be reduced to a favorable ratio if externally arranged cable drums are used, which, however, must additionally be protected against the weather.
  • the plastic bearing for the elliptical cross sections of the wefts can be produced, for example, by copy milling. Circular bearings are easier to produce by turning. The bearings can also be poured into molds or pressed.
  • the elliptical design of the individual shots also has the advantage that the buckling radius is smaller in the highly stressed lower and upper pressure areas and thus the buckling safety is greater.
  • the larger buckling radius is in the middle, more neutral load zones.
  • both the boom articulation piece and the shots that can be telescoped from it can have similar elliptical profiles, so that between the individual shots, elliptical annular spaces with the same width are formed over their entire circumference.
  • the individual shots are now axially displaceable by bearings of the type shown in FIGS. 3, 8 and 9, the required torsional rigidity is already ensured, so that the box section serving as a guide can be dispensed with. Due to the given non-rotatable guidance of the individual shots into one another, such an embodiment can also be locked of the individual shots can be dispensed with.
  • Fig. 12 the cross section through a telescopic section or an outer link of a telescopic boom can be seen, which consists of a lower semi-elliptical profile part 40 and an upper semi-box-shaped profile part 41, the legs of which are welded together in a horizontal parting plane by welds 42, 43.
  • the legs 44, 45 of the upper half-box-shaped profile part are connected to the upper web part 46 by curved regions 47, 48 with the bending radius RL.
  • the lower profile part 40 is formed by a shell with a semi-elliptical cross section, wherein the profile shape can be described by the three radii ri, Rmi and Ri with close approximation to an ellipse.
  • a simplification can be made if the cross-sectional shape is defined only by the two radii ri and Rmi.
  • the shape of the ellipse changes only slightly as a result of the simplifications described in the production, although from a static point of view these can even be favorable under certain circumstances.
  • This is because the area of the bulge-resistant shell with the radius ri or the angle Ey2 becomes larger and the radius Rmi can be guided almost to the middle of the profile.
  • the larger and thus less dent-proof area with the radius Ri is omitted.
  • the lower shell 40 is overall more rigid, since the buckling security decreases linearly with the increase in the radii.
  • the profile acc. Fig. 13 differs from that of FIG. 12 only in that the upper profile shell 41 'with half-box-shaped profile legs 44' and 45 ', which include the obtuse angle with the web part 46'.
  • the profile acc. Fig. 14 has an upper shell 41 ⁇ consisting of a semi-box-shaped profile, the profile legs 44 ⁇ and 45 ⁇ enclose acute angles with the web part 46 ⁇ .
  • the lower part has the shape of a half ellipse, which also forms the lower structural profile shell.
  • the lower part can be extended upwards by dimension V, which means that dimension H2 of the upper shell is shortened accordingly.
  • the compressive stress (-) is often the most critical stress in thin-walled hollow profiles due to the risk of buckling.
  • the greatest bending compressive stress arises from the main load of the boom around the axis X-X (X direction) in the lower vertex of the radius ri. This is according to the three profiles. 12 to 14 the same.
  • the lateral load or deflection of the boom about the axis Y-Y (Y direction) in both directions causes compressive or tensile stresses in the side walls of the profile, the size of which results in relation to the distance to the axis of inertia Y-Y.
  • profile acc. Fig. 12 is the least by the uniform, lateral stress curve in the upper profile half or the upper shell, the build-up of the compressive stress in the upper bulging side wall.
  • the production of this profile is easier than that of the profiles acc. 13 and 14, since the legs 44, 45 form right angles with the web part of the upper shell, which are easier to control in steel construction because of the existing aids.
  • the lateral stress curve is highest in the middle of the profile, as a result of which an increase in the compressive stress compared to the profile according to FIG. 12 occurs in this area.
  • the radius Ri continues upward beyond the center of the profile, the buckling stiffness is thereby improved, so that this is not disadvantageous.
  • the lateral stress curve has the highest value at the point at which the radius RL begins. Since the curvature by the radius R has already ended below the center of the profile, the flat profile side, which is not stiff against bulging, is larger and also shifted downwards. This area receives higher compressive stresses due to these influences. The less favorable buckling behavior may have to be compensated for by appropriate measures (larger sheet thickness or buckling strips).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
EP92102268A 1991-02-11 1992-02-11 Flèche télescopique pour grues mobiles ou analogue Expired - Lifetime EP0499208B2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE9218841U DE9218841U1 (de) 1991-02-11 1992-02-11 Teleskopausleger für Fahrzeugkrane o. dgl.

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE9101533 1991-02-11
DE9101533U 1991-02-11
DE9102552U DE9102552U1 (fr) 1991-02-11 1991-03-04
DE9102552U 1991-03-04
DE9113981U 1991-11-11
DE9113981U DE9113981U1 (fr) 1991-11-11 1991-11-11

Publications (4)

Publication Number Publication Date
EP0499208A2 true EP0499208A2 (fr) 1992-08-19
EP0499208A3 EP0499208A3 (en) 1993-05-19
EP0499208B1 EP0499208B1 (fr) 1995-06-14
EP0499208B2 EP0499208B2 (fr) 2001-10-17

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ID=27208262

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92102268A Expired - Lifetime EP0499208B2 (fr) 1991-02-11 1992-02-11 Flèche télescopique pour grues mobiles ou analogue

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Country Link
EP (1) EP0499208B2 (fr)
AT (1) ATE123743T1 (fr)
DE (1) DE59202474D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661234A1 (fr) * 1993-12-28 1995-07-05 Liebherr-Werk Ehingen GmbH Grue mobile avec un flèche télescopique
JPH10157980A (ja) * 1996-06-18 1998-06-16 Kidde Ind Inc クレーン用伸縮ブーム
US6098824A (en) * 1997-03-12 2000-08-08 Mannesmann Ag Telescopic crane boom section and a process for making sure
US6216895B1 (en) * 1998-03-18 2001-04-17 Grove U.S. L.L.C. Lateral jib locking device
US6499612B1 (en) 2001-07-27 2002-12-31 Link-Belt Construction Equipment Co., L.P., Lllp Telescoping boom assembly with rounded profile sections and interchangeable wear pads
EP1321425A1 (fr) * 2001-12-12 2003-06-25 Grove U.S. LLC Flèche télescopique pour grue mobile
DE102006014573B3 (de) * 2006-03-29 2007-07-19 Manitowoc Crane Group France SAS, Teleskopkran-Auslegerteil mit schwächer und stärker gekrümmten Querschnittssegmenten im oberen Profilteil und im unteren Profilteil

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006021877A (ja) * 2004-07-08 2006-01-26 Tadano Ltd 伸縮ブーム
JP2010089919A (ja) 2008-01-09 2010-04-22 Kobelco Cranes Co Ltd 伸縮ブーム
US20180297825A1 (en) * 2015-10-13 2018-10-18 Tadano Ltd. Operating machine boom

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Publication number Priority date Publication date Assignee Title
LU40776A1 (fr) * 1960-11-10 1962-01-03
DE1170134B (de) * 1962-05-11 1964-05-14 Focke Wulf Ges Mit Beschraenkt Hoehenverstellbare Arbeitsbuehne
FR1415329A (fr) * 1964-12-01 1965-10-22 Ver Flugtechnische Werke Plate-forme de travail réglable en hauteur
US3250182A (en) * 1963-08-01 1966-05-10 Harold K Nansel Multiple extension apparatus
DE2362338A1 (de) * 1972-12-15 1974-06-20 Harnischfeger Corp Kran
DE2148966B2 (de) * 1971-09-30 1978-03-30 Liebherr-Werk Ehingen Gmbh, 7930 Ehingen Teleskopausleger, insbesondere für straBenverfahrbare Krane
FR2513978A1 (fr) * 1981-10-02 1983-04-08 Coles Cranes Ltd Fleche telescopique et appareil de levage la comportant
DE3216427A1 (de) * 1982-05-03 1983-11-10 Heinrich H. Klüssendorf GmbH & Co KG, 1000 Berlin Einrichtung zur fuehrung zweier axial ineinander beweglicher stangen- oder/und roehrenartiger elemente
FR2560864A1 (fr) * 1984-03-12 1985-09-13 Oesa Ab Montage de fleches telescopiques
DE3510710A1 (de) * 1985-03-23 1986-10-02 Fried. Krupp Gmbh, 4300 Essen Teleskopkran
US4688690A (en) * 1986-03-07 1987-08-25 Harnischfeger Corporation Method and apparatus for extending fly section of crane boom
DE9013210U1 (fr) * 1990-09-18 1991-01-03 Liebherr-Werk Ehingen Gmbh, 7930 Ehingen, De

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU40776A1 (fr) * 1960-11-10 1962-01-03
DE1170134B (de) * 1962-05-11 1964-05-14 Focke Wulf Ges Mit Beschraenkt Hoehenverstellbare Arbeitsbuehne
US3250182A (en) * 1963-08-01 1966-05-10 Harold K Nansel Multiple extension apparatus
FR1415329A (fr) * 1964-12-01 1965-10-22 Ver Flugtechnische Werke Plate-forme de travail réglable en hauteur
DE2148966B2 (de) * 1971-09-30 1978-03-30 Liebherr-Werk Ehingen Gmbh, 7930 Ehingen Teleskopausleger, insbesondere für straBenverfahrbare Krane
DE2362338A1 (de) * 1972-12-15 1974-06-20 Harnischfeger Corp Kran
FR2513978A1 (fr) * 1981-10-02 1983-04-08 Coles Cranes Ltd Fleche telescopique et appareil de levage la comportant
DE3216427A1 (de) * 1982-05-03 1983-11-10 Heinrich H. Klüssendorf GmbH & Co KG, 1000 Berlin Einrichtung zur fuehrung zweier axial ineinander beweglicher stangen- oder/und roehrenartiger elemente
FR2560864A1 (fr) * 1984-03-12 1985-09-13 Oesa Ab Montage de fleches telescopiques
DE3510710A1 (de) * 1985-03-23 1986-10-02 Fried. Krupp Gmbh, 4300 Essen Teleskopkran
US4688690A (en) * 1986-03-07 1987-08-25 Harnischfeger Corporation Method and apparatus for extending fly section of crane boom
DE9013210U1 (fr) * 1990-09-18 1991-01-03 Liebherr-Werk Ehingen Gmbh, 7930 Ehingen, De

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661234A1 (fr) * 1993-12-28 1995-07-05 Liebherr-Werk Ehingen GmbH Grue mobile avec un flèche télescopique
US5628416A (en) * 1993-12-28 1997-05-13 Liebherr-Werk Ehingen Traveling crane with telescoping boom
JPH10157980A (ja) * 1996-06-18 1998-06-16 Kidde Ind Inc クレーン用伸縮ブーム
US6098824A (en) * 1997-03-12 2000-08-08 Mannesmann Ag Telescopic crane boom section and a process for making sure
US6216895B1 (en) * 1998-03-18 2001-04-17 Grove U.S. L.L.C. Lateral jib locking device
US6499612B1 (en) 2001-07-27 2002-12-31 Link-Belt Construction Equipment Co., L.P., Lllp Telescoping boom assembly with rounded profile sections and interchangeable wear pads
EP1321425A1 (fr) * 2001-12-12 2003-06-25 Grove U.S. LLC Flèche télescopique pour grue mobile
EP1496006A3 (fr) * 2001-12-12 2005-02-02 Grove U.S. LLC Flèche télescopique pour grue mobile
CN1319846C (zh) * 2001-12-12 2007-06-06 格罗夫美国有限责任公司 轮式起重机的伸缩臂
DE102006014573B3 (de) * 2006-03-29 2007-07-19 Manitowoc Crane Group France SAS, Teleskopkran-Auslegerteil mit schwächer und stärker gekrümmten Querschnittssegmenten im oberen Profilteil und im unteren Profilteil

Also Published As

Publication number Publication date
EP0499208A3 (en) 1993-05-19
ATE123743T1 (de) 1995-06-15
EP0499208B1 (fr) 1995-06-14
EP0499208B2 (fr) 2001-10-17
DE59202474D1 (de) 1995-07-20

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