EP0702661B1 - Telescopic boom - Google Patents

Telescopic boom Download PDF

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Publication number
EP0702661B1
EP0702661B1 EP94920945A EP94920945A EP0702661B1 EP 0702661 B1 EP0702661 B1 EP 0702661B1 EP 94920945 A EP94920945 A EP 94920945A EP 94920945 A EP94920945 A EP 94920945A EP 0702661 B1 EP0702661 B1 EP 0702661B1
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EP
European Patent Office
Prior art keywords
bearing
boom according
area
slide
liner
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.)
Expired - Lifetime
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EP94920945A
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German (de)
French (fr)
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EP0702661A1 (en
Inventor
Ernst Kaspar
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Compact Truck AG
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Compact Truck AG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/64—Jibs
    • B66C23/70—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
    • 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
    • B66C23/707—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic guiding devices for telescopic jibs

Definitions

  • the invention relates to a telescopic boom with at least one outer slider and at least one inner slider, which are each designed as a hollow profile with an upper chord and lower chord, the upper chord having a half-box shape in cross-section with two corner rounds, to which the lower chord with one in Connects cross-section substantially U-shaped shell, and each Schübling is mounted on the neighboring Schübling via a front and a rear bearing point.
  • Jibs of this type are known from practice, for example from mobile cranes.
  • a load is attached to the front end of an extended inner slide, so that the inner slide loads the front end portion of the lower belt of the outer slide with its lower flange.
  • the rear end of the inner slide with its upper belt loads the upper belt of the outer slide.
  • front denotes the direction to the load-bearing free end of the boom and “rear” denotes the direction to the end opposite the free boom end.
  • the collars of the inner pupils are in generally consistently formed over the cross-sectional shape of the slider and together form the border for the sliding elements, while the collars of the front bearing points are usually attached to the outside of the outer slider and consist of solid material with a dimension of 150 to 300 mm in the longitudinal direction of the boom.
  • the collars thus reduce the usable extension length of the affected child.
  • the inner pushers cannot be fully inserted into each other because they are hindered by the inner collars. The same occurs in the area of the front bearing with the outer collars.
  • DE-OS 1531174 proposes a roller bearing for telescopic booms with a polygonal cross section.
  • an outer roller is assigned to each corner of the lower flange and an inner roller to each corner of the upper flange.
  • the outer and inner rollers each interfere when the pushers are moved into one another, so that the usable extension length of the pushers is reduced by at least the sum of the diameters of the rollers arranged next to one another.
  • the inner rollers take up a lot of space in the hollow profile cross section of the inner slider, so that there is only little space available for the telescopic cylinder unit arranged therein for extending the boom.
  • the invention has for its object to provide a telescopic boom of the type mentioned, which can absorb high forces and is characterized by a safe storage of the pushers and a large usable extension length.
  • This object is achieved in that the front bearing in the area between the lower chords has a sliding element only in the area of the curvature, and the rear bearing in the area between the upper chords only has a separate plain bearing shell in the area of each corner round.
  • the forces between two adjacent thrust blocks are only transmitted via rounded areas which are considerably stiffer than the straight surface of the bearing blocks which is customary in the prior art. This prevents bulging of the surfaces and the deformation of the profile cross-section.
  • the function of the collar can essentially be limited to preventing the slug from expanding at its end. Since the collar no longer has to absorb the supporting forces in full, it can be made much shorter in the longitudinal direction of the pushers. In practice, the collar can be reduced to a length of approx. 50 mm. This means that the individual pushers, as shown in Fig. 5, can be moved much further into one another, so that a larger usable boom length is available.
  • the sliding element and the slide bearing shells can be made much thinner. While thicknesses of 40 to 50 mm are still necessary in the prior art, the thickness can be reduced to less than 20 mm in the solution according to the invention. This means that there is more space available in an outer pusher for additional inner pusher, which yield a profit of the usable boom length. With the storage according to the invention, 7 pushers can be pushed into one another without any problems, the cross section of the outermost pushbar not exceeding the outer cross section of conventional telescopic booms. With the bearings according to the prior art, it was previously only possible to arrange a maximum of 5 slides one inside the other.
  • the tolerances of the sliding element and the slide bearing shells can be adapted to the corner rounds and the lower flange shape, respectively, almost exactly.
  • the storage leaves little Deformations of the straight areas of the cross section, while the rounded areas guarantee the exact positioning of the sliders in one another. It is therefore also possible to dispense with additional tolerance compensation elements, as were usually necessary in the prior art.
  • the sliding element and the sliding bearing shells advantageously center themselves on the rounded areas. It is therefore not necessary to define them in the circumferential direction of the cross section.
  • the rear bearing point in the area between the lower chords has at least one shell-shaped sliding element, which extends at least in regions into each of the curved sides of the lower chords adjoining the upper chords.
  • This arrangement is particularly favorable for absorbing lateral forces that arise, for example, when turning a mobile crane.
  • the cup-shaped sliding element prevents torsion of the cross-section of the boom.
  • the rear bearing has two separate sliding jaw elements in the area between the lower chords, one of which is arranged in each of the curved sides of the lower chords adjoining the upper chords.
  • the shell-shaped sliding element is thus divided into two separate sliding jaw elements, each of which absorbs the torsional forces. There is no need for support in the lower U-point of the lower flange. This simplifies the manufacture of the profile cross-sections in this area, since precise tolerance information can be dispensed with.
  • the front bearing point in the area between the top chords has a separate plain bearing shell only in the area of each corner round. These additional ones too Plain bearing shells on the corner rounds prevent the cross-sections from twisting.
  • the slide jaw element and slide bearing shells of the rear bearing point are preferably fixed to the inner slide.
  • the sliding element (s) and the sliding bearing shells of the front bearing point can be fixed on the outer slide.
  • the radial distance between the inner and outer pushers is greater in the area of the corner rounds than in the straight areas of the upper chord. This allows the plain bearing shells to be made somewhat thicker in the area of the corner rounds, so that they can transmit greater forces. The remaining space in the straight areas is minimized to save space.
  • the center point of the outer corner round and the center point of the inner corner round of the front bearing point and / or the rear bearing point can possibly be arranged spaced apart from one another, the center point of the outer corner round being arranged closer to the corner rounds than the center point of the inner corner round. This creates an increase in the space for the plain bearing shells in the rounded area, the distance in the subsequent straight areas can be kept small.
  • the plain bearing shells of the corner rounds and / or the sliding elements in the lower chord area of the front and / or rear bearing point extend beyond the curved areas into the straight areas of the upper chords, the plain bearing shells or the sliding elements on the side of the slide moving relative to them only touch this slide in the curved area.
  • This is the support of the plain bearing shells or the sliding elements on relatively moving Schübling limited to the stable, curved areas. This prevents the pushbuttons from jamming, since the end of the force introduction zone (curvature) does not meet the end edge of the slide bearing shell.
  • the sliding element On the slide, on which the sliding element is fixed, for example, it extends into the straight region, so that it positions itself automatically in the circumferential direction of the profile cross section at the transition from the curved and straight region.
  • the sliding bearing shells in the straight upper chord region and / or the sliding elements in the lower chord region on the side of the relative movement are advantageously spaced apart from the slide at an angle ⁇ from the straight side. This sloping start-up zone prevents particularly well the jamming of the pupils.
  • the outer slide in the area of the front bearing point can have a front collar and the inner slide in the area of the rear bearing point can have a rear collar, which serve as axial contact of the sliding element, slide bearing shells or sliding jaw elements.
  • the collars reinforce the profile and prevent the pushers from expanding or pressing in at their ends, while at the same time the sliding bodies are positioned on the collars.
  • the sheet thickness of the front and rear collars is 1.2 to 2.5 times the sheet thickness of the respective boom profile.
  • the sheet thickness of the upper chord is different from the sheet thickness of the lower chord.
  • the U-shaped shell of the lower flange has two round shells which are spaced apart from one another and which are connected to one another via a straight web arranged between them.
  • This special profile cross section the U-shape has proven to be particularly suitable because it has a large moment of resistance to bending.
  • the transverse forces are introduced according to the invention in the curved zones of the profile, namely via the round shells into the lower flange, so that the entire profile is very resistant to dents due to the shell effect of the curved regions.
  • the membrane effect of a shell is used.
  • the length of the web preferably corresponds to a ratio of 1: 3 to the profile width.
  • the profile width is to be understood as the distance between the straight sides between the top flange and bottom flange of a slider.
  • the front bearing point have a separate sliding element in the area between the lower chords in the area of each round shell.
  • the forces are transmitted only via the rounded areas. Due to the separate, divided arrangement of the sliding elements, tolerances in the width of the individual sliders can be compensated for well. Furthermore, no moments occur in the transition area to the straight sides of the upper flange or to the straight web, since the circumferential stresses are introduced tangentially.
  • the radial distance between the inner and outer slugs can be greater in the area of the round shells than in the straight areas of the lower flange.
  • the center of the outer round shell and the center of the inner round shell of the front bearing point are arranged spaced apart from one another, the center of the outer round shell being arranged closer to the round shells than the center of the inner round shell.
  • the ratio of profile width to profile height is preferably approximately 1: 1.15 to 1: 1.4.
  • the ratio of the length of the straight side between a corner round of the upper flange and the subsequent curved region of the lower flange to the profile height can be approximately 1: 1.6 to 1: 2.
  • an outer slide 14 and an inner slide 16 are shown.
  • the inner slide 16 is located with a partial length inside a front section of the outer slide 14.
  • Each slide consists of two bent sheet metal half-shells which are connected to one another by longitudinal weld seams.
  • the top chords 1 of each Schüblinges have a U-shaped shape with quarter-circular corner curves R.
  • Ri the two corner curves of the inner slide 16
  • Ra the two corner curves of the outer slide 14 are designated by Ra.
  • the corner curves extend over 60 to 90o.
  • the lower chords 2 of the two slugs 14 and 16 have a semicircular shape with a radius which is equal to half the width (b) of the associated upper chord. It goes without saying that the radius of the lower flange 2 of the inner slide 16 is smaller than the radius of the lower flange of the outer slide 16.
  • the upper and lower flange can have different sheet thicknesses.
  • the welded upper and lower belts have a front collar 7 at their longitudinal ends and a rear collar 8 in the form of welded-on metal sheets at their rear ends. These collars are corrosion-resistant and serve as bearing points.
  • Each lower flange 2 is assigned a front bearing 3 and each upper flange 1 a rear bearing 4.
  • the two collars 7 and 8 also form a stop for the sliding element 10 and the slide bearing shells 12 made of plastic, which are provided at least in the area of the bearing points between the inner slide and the outer slide.
  • a sliding element 10 made of plastic, preferably of polyamide, is provided in the area of each bearing point 3 associated with the lower flange, the shape of which is semicircular
  • bearing bushes 12 are provided at least in the two spaces between the inner upper flange and the outer upper flange in the region of the two corner curves Ri and Ra, as shown in FIG. 3.
  • the semicircular sliding element 10 advantageously extends up to the horizontal line labeled C in FIGS. 2 and 3.
  • the sliding element 10 and the slide bearing shells 12 are each fixed to the outer slide 14.
  • a force F acts on the inner slide 16
  • this causes a moment M, which in turn causes transverse forces Qv and Qh.
  • the shear force Qv deforms the lower flange of the inner slider oval.
  • the transverse force Qv is introduced into the outer slide 14 via the sliding element 10, whereupon its cross section is also deformed oval.
  • the cross section becomes longer in the vertical direction and shorter in the horizontal direction. This shortening in the transverse direction leads to an advantageous stabilization of the bearing 3 by a barrel eye effect as a result of the pressure exerted on the inner slide. Furthermore, bulging is prevented by the large-area contact mediated by the lubricant element 10.
  • the undesired bulging is also prevented by the fact that the transverse force Qv acts on the semicircular lower flange, so that the membrane effect of a shell can be exploited. As a result, the sheet thickness may be small, which leads to a reduction in the dead weight.
  • the rear bearing force Qh loads the inner surface of the outer slide 14 in the area of the rear bearing point 4.
  • the two inner corner rounding areas Ri are connected to the two outer corner rounding areas Ra by means of the two slide bearing shells 12 , wherein the inner corner rounding areas belong to the inner slide 16 and the outer corner rounding areas belong to the outer slide.
  • the plain bearing shells 12 are not supported on a separate collar, as in the prior art, but are supported by the curved plate of the inner slide 16. As a result, the disc effect of the flanges is simultaneously utilized when the load is introduced.
  • the sheet thickness of the front collar 7 as well as the sheet thickness of the rear collar 8 is preferably 1.2 to 2.5 times the sheet thickness of the sheet used for the respective boom profile.
  • the front collar 7 can in the spaces between the outer corner curves Ra and the inner corner curves Ri each have a slide bearing shell 18 made of plastic, as shown in FIG. 2. Instead of the two slide bearing shells 18 shown in FIG. 2, only a single sliding element can be provided.
  • the slide bearing shells 18 must be designed and arranged in such a way that the inner slide 16 is prevented from tilting inside the outer slide 14.
  • the bearing point assigned to the slide bearing shells 18 is not permanently subjected to forces.
  • sliding shoe elements 15 made of plastic can be provided in the area of the rear collar 8, specifically in the lower chord area thereof, as shown in FIG. 3, sliding shoe elements 15 made of plastic can be provided. These sliding jaw elements 15 are arranged between the semicircular lower flange of the inner slide 16 and the semicircular lower flange of the outer slide 14. Advantageously, they extend with their upper ends to the horizontal line C. Instead of the two-part design of the sliding jaw elements 15 shown in FIG. 3, they can also be formed in one piece. Basically, slide jaw elements 15 are to be designed and arranged such that the inner slide 16 does not tip inside the outer slide 16, since the latter slide elements are particularly stressed when a lateral force or a transverse force component acts on the inner slide.
  • a plain bearing shell 12 which is shown between two corner rounds Ri, Ra of the upper chords 1 at the rear end of an inner slide 16.
  • the corner rounds Ri, Ra have spaced-apart centers Ma, Mi, with the center Ma of the corner round Ra closer to the plain bearing shell 12 or the corner rounds Ri, Ra is arranged.
  • the figure shows the center point Ma in each case by two radii ra drawn in and, analogously, the center point Mi by the two radii ri.
  • the slide bearing shell 12 is fixed to the inner slide 16 so that it performs a relative movement relative to the corner round Ra of the outer slide.
  • the slide bearing shell 12 extends into the straight areas adjoining the corner rounds Ri, Ra, it also abutting the inner slide 16 in the straight area.
  • the slide bearing shell 12 withdraws from the outer slide 14 starting at the transitions to the straight regions at an angle ⁇ . As a result, it only rests on the outer slide 14 in the area of the corner round Ra.
  • the slide bearing shells 18 of the front end are designed. In this case, the plain bearing shells 18 also abut the outer slide 14 in the straight region and recede from the upper flange 1 in the straight regions of the inner slide 16 at an angle ⁇ .
  • a collapsed boom with three sliders is shown.
  • a sectional view of the rear slide bearing shells 12 is placed. They rest on one side on the narrow rear collar 8 and are bordered on the other side by an edge 20. The edge 20 is limited over the circumference to the area of the slide bearing shells 12.
  • the slide bearing shells 12 of the neighboring pushbuttons partially overlap and can therefore be pushed very far into one another.
  • Fig. 6 three Schüblinge are shown in the retracted state according to a bearing arrangement of the prior art.
  • the slugs are supported one inside the other by an all-round bearing, the bearing elements 30 each being received in a half-box-shaped bearing block 31, which is offset to the inside with respect to the associated slider.
  • the bordering of the bearing block 31 is formed in each case by two collars 32 which are continuous over the cross section of the slider.
  • the continuous collar 32 which are necessary for stability, a further insertion of the inner slider 16, so that the rear ends of the slider 16 must be arranged side by side.
  • the bearing elements 30 are substantially thicker in the radial direction than the sliding elements 12 according to the invention (FIG. 5).
  • FIG. 7 shows a telescopic boom according to the invention with eight pushers, in which the U-shaped shell of each lower flange 2 is formed from two quarter-circular round shells 33 arranged at a distance from one another.
  • a straight web 34 is arranged between the round shells 33 and extends parallel to the straight region of the upper chord 1 between the corner rounds Ri, Ra.
  • a substantially quarter-circle-shaped sliding element 10 is arranged between the round shells 33 of two adjacent slugs.
  • the sliding element 10 is adapted to the respective shape of the rounded areas of the round shells 33.
  • the sliding elements 10 are each fixed to their outer slide 14 and extend on this side in some areas into the straight web 34 or the straight side 35 between the lower flange 2 and the upper flange 1.
  • On the side of the inner slide 16 the sliding elements 10 rest only in the curved region of the round shells 33. In the straight region, the sliding elements 10 are designed analogously to the ends of the sliding bearing shells 12 shown in FIG. 4.
  • the sliding elements on the side of the inner slide 15 depart from the rounded area in an oblique outlet zone at an angle ⁇ from the inner slide.
  • the rear bearing 4 in the lower flange area 2 can also be formed as shown in FIG. 7.
  • the sliding jaw elements 15 are designed like the round shells 33.

Abstract

The invention pertains to a telescopic boom with at least one outer structure (14) and at least one inner structure (16), each of which is designed as a hollow section with upper flange (1) and lower flange (2), the upper flange (1) having a half-basket profile with two rounded edges (Ri, Ra) to which the lower flange (2) is joined with a liner of an essentially U-shaped profile, and each structure being mounted on the adjoining structure with a front and a back bearing (3, 4). To achieve a stable bearing of the structures and a great usable extension length with this boom under high force level, the invention proposes that the front bearing (3) has a slide element (10) in the area between the lower flanges (2) only in the region of the curve, and the back bearing (4) has a separate plain bearing half liner (12) in the area between the upper flanges (1) only in the region of each rounded corner (Ri, Ra).

Description

Die Erfindung bezieht sich auf einen teleskopierbaren Ausleger mit wenigstens einem äußeren Schübling und wenigstens einem inneren Schübling, welche jeweils als Hohlprofile mit Obergurt und Untergurt ausgebildet sind, wobei der Obergurt im Querschnitt eine Halbkastenform mit zwei Eckrunden aufweist, an den sich der Untergurt mit einer im Querschnitt im wesentlichen U-förmigen Schale anschließt, und jeder Schübling an dem benachbarten Schübling über eine vordere und eine hintere Lagerstelle gelagert ist.The invention relates to a telescopic boom with at least one outer slider and at least one inner slider, which are each designed as a hollow profile with an upper chord and lower chord, the upper chord having a half-box shape in cross-section with two corner rounds, to which the lower chord with one in Connects cross-section substantially U-shaped shell, and each Schübling is mounted on the neighboring Schübling via a front and a rear bearing point.

Ausleger dieser Gattung sind aus der Praxis, beispielsweise von Mobilkränen her, bekannt. Dabei wird an das vordere Ende eines ausgefahrenen inneren Schüblings eine Last angehängt, so daß der innere Schübling mit seinem Untergurt den vorderen Endabschnitt des Untergurts des äußeren Schüblings belastet. Geichzeitig belastet das hintere Ende des inneren Schüblings mit seinem Obergurt den Obergurt des äußeren Schüblings. Im Rahmen dieser Erfindung bezeichnet "vorn" die Richtung zum lastaufnehmenden freien Ende des Auslegers und bezeichnet "hinten" die Richtung zu dem freien Auslegerende gegenüberliegenden Ende.Jibs of this type are known from practice, for example from mobile cranes. In this case, a load is attached to the front end of an extended inner slide, so that the inner slide loads the front end portion of the lower belt of the outer slide with its lower flange. At the same time, the rear end of the inner slide with its upper belt loads the upper belt of the outer slide. In the context of this invention, “front” denotes the direction to the load-bearing free end of the boom and “rear” denotes the direction to the end opposite the free boom end.

In Folge der hohen zu übertragenden Kräfte muß besondere Sorgfalt auf die Ausbildung der vorderen und hinteren Lagerstelle gerichtet werden. Diese sollen neben einer sicheren Lagerung auch gleichzeitig unerwünschten Verformungen der Profilquerschnitte entgegenwirken. Üblicherweise wird hierfür eine Rundum-Lagerung von Gleitelementen an der vorderen und hinteren Lagerstelle angestrebt. Dabei sind die Gleitelemente jeweils an einem der Schüblinge auf einem ebenflächig, seitlich eingefaßten Lagerblock fixiert und stützen sich gegenüberliegend am benachbarten Schübling ab. Zur Aufnahme der auf die Gleitelemente und die Lagerblöcke wirkenden Kräfte sind verstärkende Abstützmittel in Form von Kragen notwendig. Die Kragen der inneren Schüblinge werden in der Regel durchgehend über die Querschnittsform des Schüblings ausgebildet und bilden zusammen die Einfassung für die Gleitelemente, während die Kragen der vorderen Lagerstellen in der Regel außen am äußeren Schübling angebracht sind und aus Vollmaterial mit einer Abmessung von 150 bis 300 mm in Längsrichtung des Auslegers bestehen. Damit vermindern die Kragen die nutzbare Ausfahrlänge des betroffenen Schüblings. Wie in Fig. 6 (Stand der Technik) gezeigt, können die inneren Schüblinge nicht vollständig ineinandergefahren werden, da sie von den inneren Kragen behindert werden. Das gleiche tritt analog im Bereich der vorderen Lagerstelle mit den äußeren Kragen auf.As a result of the high forces to be transmitted, special care must be taken to design the front and rear bearing points. In addition to secure storage, these are also intended to counteract undesirable deformations of the profile cross sections. Usually, all-round storage of sliding elements at the front and rear bearing point is aimed for. The sliding elements are each fixed to one of the sliders on a flat, laterally edged bearing block and are supported opposite each other on the neighboring slider. To absorb the forces acting on the sliding elements and the bearing blocks, reinforcing support means in the form of a collar are necessary. The collars of the inner pupils are in generally consistently formed over the cross-sectional shape of the slider and together form the border for the sliding elements, while the collars of the front bearing points are usually attached to the outside of the outer slider and consist of solid material with a dimension of 150 to 300 mm in the longitudinal direction of the boom. The collars thus reduce the usable extension length of the affected child. As shown in Fig. 6 (prior art), the inner pushers cannot be fully inserted into each other because they are hindered by the inner collars. The same occurs in the area of the front bearing with the outer collars.

In der DE-OS 1531174 wird eine Rollenlagerung für Teleskopausleger mit mehreckigem Querschnitt vorgeschlagen. Um die bei Belastung auftretenden Ringspannungen aufzunehmen, ist jeder Ecke des Untergurts eine äußere Rolle und jeder Ecke des Obergurts eine innere Rolle zugeordnet. Ungünstigerweise behindern sich jeweils die äußeren und inneren Rollen, wenn die Schüblinge ineinander gefahren sind, so daß die nutzbare Ausfahrlänge der Schüblinge mindestens um die Summe der Durchmesser der nebeneinander angeordneten Rollen vermindert wird. Zudem beanspruchen die inneren Rollen viel Platz in dem Hohlprofilquerschnitt des inneren Schüblings, so daß für die darin angeordnete Teleskopzylindereinheit zum Ausfahren des Auslegers nur wenig Platz zur Verfügung steht.DE-OS 1531174 proposes a roller bearing for telescopic booms with a polygonal cross section. In order to absorb the ring stresses that occur during loading, an outer roller is assigned to each corner of the lower flange and an inner roller to each corner of the upper flange. Unfortunately, the outer and inner rollers each interfere when the pushers are moved into one another, so that the usable extension length of the pushers is reduced by at least the sum of the diameters of the rollers arranged next to one another. In addition, the inner rollers take up a lot of space in the hollow profile cross section of the inner slider, so that there is only little space available for the telescopic cylinder unit arranged therein for extending the boom.

Der Erfindung liegt die Aufgabe zugrunde, einen teleskopierbaren Ausleger der eingangs genannten Gattung zu schaffen, der hohe Kräfte aufnehmen kann und sich durch eine sichere Lagerung der Schüblinge und eine große nutzbare Ausfahrlänge auszeichnet.The invention has for its object to provide a telescopic boom of the type mentioned, which can absorb high forces and is characterized by a safe storage of the pushers and a large usable extension length.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die vordere Lagerstelle im Bereich zwischen den Untergurten nur im Bereich der Krümmung ein Gleitelement aufweist, und die hintere Lagerstelle im Bereich zwischen den Obergurten nur im Bereich jeder Eckrunde eine separate Gleitlagerschale aufweist.This object is achieved in that the front bearing in the area between the lower chords has a sliding element only in the area of the curvature, and the rear bearing in the area between the upper chords only has a separate plain bearing shell in the area of each corner round.

Durch diese Lagerung werden die Kräfte zwischen zwei benachbarten Schüblingen nur mehr über gerundete Bereiche übertragen, die wesentlich steifer sind als die im Stand der Technik üblichen geraden Fläche der Lagerblöcke. Damit ist einem Ausbeulen der Flächen und der Verformung des Profilquerschnitts vorgebeugt. Die Funktion des Kragens kann im wesentlichen auf das Verhindern des Aufweitens des Schüblings an seinem Ende beschränkt werden. Da der Kragen jetzt nicht mehr die Abstützkräfte in vollem Umfang aufnehmen muß, kann er in Längsrichtung der Schüblinge wesentlich kürzer ausgebildet sein. In der Praxis kann der Kragen bis zu einer Länge von ca. 50 mm reduziert werden. Dies bedeutet, daß die einzelnen Schüblinge, wie in Fig.5 gezeigt, wesentlich weiter ineinander gefahren werden können, so daß eine größere nutzbare Auslegerlänge zur Verfügung steht.As a result of this mounting, the forces between two adjacent thrust blocks are only transmitted via rounded areas which are considerably stiffer than the straight surface of the bearing blocks which is customary in the prior art. This prevents bulging of the surfaces and the deformation of the profile cross-section. The function of the collar can essentially be limited to preventing the slug from expanding at its end. Since the collar no longer has to absorb the supporting forces in full, it can be made much shorter in the longitudinal direction of the pushers. In practice, the collar can be reduced to a length of approx. 50 mm. This means that the individual pushers, as shown in Fig. 5, can be moved much further into one another, so that a larger usable boom length is available.

Zum anderen können das Gleitelement und die Gleitlagerschalen wesentlich dünner ausgebildet werden. Während im Stand der Technik noch Dicken von 40 bis 50 mm notwendig sind, kann die Dicke bei der erfindungsgemäßen Lösung auf unter 20 mm reduziert werden. Dies bedeutet, daß in einem äußeren Schübling mehr Platz für zusätzliche innere Schüblinge zur Verfügung steht, die einen Gewinn der nutzbaren Auslegerlänge erbringen. Mit der erfindungsgemäßen Lagerung können problemlos 7 Schüblinge ineinandergeschoben werden, wobei der Querschnitt des äußersten Schüblings den äußeren Querschnitt herkömmlicher Teleskopausleger nicht überschreitet. Mit den Lagerungen gemäß dem Stand der Technik war es bisher nur möglich, maximal 5 Schüblinge ineinander anzuordnen.On the other hand, the sliding element and the slide bearing shells can be made much thinner. While thicknesses of 40 to 50 mm are still necessary in the prior art, the thickness can be reduced to less than 20 mm in the solution according to the invention. This means that there is more space available in an outer pusher for additional inner pusher, which yield a profit of the usable boom length. With the storage according to the invention, 7 pushers can be pushed into one another without any problems, the cross section of the outermost pushbar not exceeding the outer cross section of conventional telescopic booms. With the bearings according to the prior art, it was previously only possible to arrange a maximum of 5 slides one inside the other.

Darüber hinaus können die Toleranzen des Gleitelements und der Gleitlagerschalen ziemlich genau den Eckrunden bzw. der Untergurtform angepaßt werden. Die Lagerung läßt geringe Verformungen der geraden Bereiche des Querschnitts zu, während die gerundeten Bereiche die exakte Lagerung der Schüblinge ineinander garantieren. Damit kann auch auf zusätzliche Toleranzausgleichselemente, wie sie im Stand der Technik üblicherweise notwendig waren, verzichetet werden.In addition, the tolerances of the sliding element and the slide bearing shells can be adapted to the corner rounds and the lower flange shape, respectively, almost exactly. The storage leaves little Deformations of the straight areas of the cross section, while the rounded areas guarantee the exact positioning of the sliders in one another. It is therefore also possible to dispense with additional tolerance compensation elements, as were usually necessary in the prior art.

Günstigerweise zentrieren sich das Gleitelement und die Gleitlagerschalen an den gerundeten Bereichen selbständig. Damit kann auf ihre Festlegung in Umfangsrichtung des Querschnitts verzichtet werden.The sliding element and the sliding bearing shells advantageously center themselves on the rounded areas. It is therefore not necessary to define them in the circumferential direction of the cross section.

Besonders vorteilhaft weist die hintere Lagerstelle im Bereich zwischen den Untergurten wenigstens ein schalenförmiges Gleitelement auf, das sich wenigstens bereichsweise in jeden der sich an die Obergurte anschließenden gekrümmten Seiten der Untergurte erstreckt. Diese Anordnung ist besonders günstig zur Aufnahme von Seitenkräften, die beispielsweise beim Drehen eines Mobilkrans entstehen. Dabei verhindert das schalenförmige Gleitelement die Torsion des Auslegerquerschnitts.Particularly advantageously, the rear bearing point in the area between the lower chords has at least one shell-shaped sliding element, which extends at least in regions into each of the curved sides of the lower chords adjoining the upper chords. This arrangement is particularly favorable for absorbing lateral forces that arise, for example, when turning a mobile crane. The cup-shaped sliding element prevents torsion of the cross-section of the boom.

Es wird vorgeschlagen, daß die hintere Lagerstelle zwei separate Gleitbackenelemente im Bereich zwischen den Untergurten aufweist, von denen jeweils eines in jeder der sich an die Obergurte anschließenden gekrümmten Seiten der Untergurte angeordnet sind. Damit ist das schalenförmige Gleitelement in zwei separate Gleitbackenelemente aufgeteilt, die jeweils die Torsionskräfte aufnehmen. Dabei kann auf die unterstützende Lagerung im unteren U-Punkt des Untergurtes verzichtet werden. Dies erleichert die Fertigung der Profilquerschnitte in diesem Bereich, da auf genaue Toleranzangaben verzichtet werden kann.It is proposed that the rear bearing has two separate sliding jaw elements in the area between the lower chords, one of which is arranged in each of the curved sides of the lower chords adjoining the upper chords. The shell-shaped sliding element is thus divided into two separate sliding jaw elements, each of which absorbs the torsional forces. There is no need for support in the lower U-point of the lower flange. This simplifies the manufacture of the profile cross-sections in this area, since precise tolerance information can be dispensed with.

Als Variante der Erfindung weist die vordere Lagerstelle im Bereich zwischen den Obergurten nur im Bereich jeder Eckrunde eine separate Gleitlagerschale auf. Auch diese zusätzlichen Gleitlagerschalen an den Eckrunden verhindern die Torsion der Querschnitte.As a variant of the invention, the front bearing point in the area between the top chords has a separate plain bearing shell only in the area of each corner round. These additional ones too Plain bearing shells on the corner rounds prevent the cross-sections from twisting.

Vorzugsweise sind die Gleitbackenelement und Gleitlagerschalen der hinteren Lagerstelle am inneren Schübling fixiert.The slide jaw element and slide bearing shells of the rear bearing point are preferably fixed to the inner slide.

In besonderer Weise können das/die Gleitelement/e und die Gleitlagerschalen der vorderen Lagerstelle am äußeren Schübling fixiert sein.In a special way, the sliding element (s) and the sliding bearing shells of the front bearing point can be fixed on the outer slide.

Als bevorzugte Ausführungsform ist der radiale Abstand zwischen innerem und äußerem Schübling im Bereich der Eckrunden größer als in den geraden Bereichen des Obergurts. Damit können die Gleitlagerschalen im Bereich der Eckrunden etwas dicker ausgestaltet werden, so daß sie größere Kräfte übertragen können. Dabei ist der übrige Zwischenraum in den geraden Bereichen platzsparend minimiert.As a preferred embodiment, the radial distance between the inner and outer pushers is greater in the area of the corner rounds than in the straight areas of the upper chord. This allows the plain bearing shells to be made somewhat thicker in the area of the corner rounds, so that they can transmit greater forces. The remaining space in the straight areas is minimized to save space.

Möglicherweise kann der Mittelpunkt der äußeren Eckrunde und der Mittelpunkt der inneren Eckrunde der vorderen Lagerstelle und/oder der hinteren Lagerstelle beabstandet voneinander angeordnet sein, wobei der Mittelpunkt der äußeren Eckrunde näher an den Eckrunden als der Mittelpunkt der inneren Eckrunde angeordnet ist. Dadurch wird eine Vergrößerung des Platzes für die Gleitlagerschalen im gerundeten Bereich geschaffen, wobei der Abstand in den anschließenden geraden Bereichen klein gehalten werden kann.The center point of the outer corner round and the center point of the inner corner round of the front bearing point and / or the rear bearing point can possibly be arranged spaced apart from one another, the center point of the outer corner round being arranged closer to the corner rounds than the center point of the inner corner round. This creates an increase in the space for the plain bearing shells in the rounded area, the distance in the subsequent straight areas can be kept small.

Vorzugsweise erstrecken sich die Gleitlagerschalen der Eckrunden und/oder die Gleitelemente im Untergurtbereich der vorderen und/oder hinteren Lagerstelle über die gekrümmten Bereiche hinaus in die geraden Bereiche der Obergurte, wobei die Gleitlagerschalen bzw. die Gleitelemente an der Seite der dem relativ zu ihnen bewegten Schübling nur im gekrümmten Bereich an diesem Schübling anliegen. Damit ist die Abstützung der Gleitlagerschalen bzw. der Gleitelemente am relativ bewegten Schübling auf die stabilen, gekrümmten Bereiche beschränkt. Dies beugt einem Verklemmen der Schüblinge vor, da das Ende der Krafteinleitungszone (Krümmung) nicht mit der Endkante der Gleitlagerschale zusammentrifft. An dem Schübling, an dem beispielsweise das Gleitelement fixiert ist, erstreckt es sich in den geraden Bereich hinein, so daß es sich an dem Übergang von gekrümmtem und geraden Bereich selbständig in Umfangsrichtung des Profilquerschnitts positioniert.Preferably, the plain bearing shells of the corner rounds and / or the sliding elements in the lower chord area of the front and / or rear bearing point extend beyond the curved areas into the straight areas of the upper chords, the plain bearing shells or the sliding elements on the side of the slide moving relative to them only touch this slide in the curved area. This is the support of the plain bearing shells or the sliding elements on relatively moving Schübling limited to the stable, curved areas. This prevents the pushbuttons from jamming, since the end of the force introduction zone (curvature) does not meet the end edge of the slide bearing shell. On the slide, on which the sliding element is fixed, for example, it extends into the straight region, so that it positions itself automatically in the circumferential direction of the profile cross section at the transition from the curved and straight region.

Günstigerweise beabstanden sich die Gleitlagerschalen im geraden Obergurtbereich und/oder die Gleitelemente im Untergurtbereich auf der Seite der Relativbewegung von dem Schübling in einem Winkel α von der geraden Seite. Diese schräge Anlaufzone beugt besonders gut dem Verklemmen der Schüblinge vor.The sliding bearing shells in the straight upper chord region and / or the sliding elements in the lower chord region on the side of the relative movement are advantageously spaced apart from the slide at an angle α from the straight side. This sloping start-up zone prevents particularly well the jamming of the pupils.

In besonderer Weise kann der äußere Schübling im Bereich der vorderen Lagerstelle einen vorderen Kragen und der innere Schübling im Bereich der hinteren Lagerstelle einen hinteren Kragen aufweisen, die als axiale Anlage von Gleitelement, Gleitlagerschalen bzw. Gleitbackenelementen dienen. Die Kragen verstärken das Profil und verhindern ein Aufweiten oder Eindrücken der Schüblinge an ihren Enden, wobei gleichzeitig die Gleitkörper an den Kragen positioniert werden.In a special way, the outer slide in the area of the front bearing point can have a front collar and the inner slide in the area of the rear bearing point can have a rear collar, which serve as axial contact of the sliding element, slide bearing shells or sliding jaw elements. The collars reinforce the profile and prevent the pushers from expanding or pressing in at their ends, while at the same time the sliding bodies are positioned on the collars.

Es wird vorgeschlagen, daß die Blechdicke der vorderen und hinteren Kragen das 1,2- bis 2,5-fache der Blechdicke des jeweiligen Auslegerprofils beträgt.It is proposed that the sheet thickness of the front and rear collars is 1.2 to 2.5 times the sheet thickness of the respective boom profile.

Als Variante der Erfindung ist die Blechdicke des Obergurts verschieden von der Blechdicke des Untergurts.As a variant of the invention, the sheet thickness of the upper chord is different from the sheet thickness of the lower chord.

Besonders vorteilhaft weist die U-förmige Schale des Untergurts zwei beabstandet voneinander angeordnete Rundschalen auf, die über einen zwischen ihnen angeordneten geraden Steg miteinander verbunden sind. Dieser besondere Profilquerschnitt der U-Form hat sich als besonders geeignet erwiesen, da er ein großen Widerstandsmoment gegen Biegen aufweist. Auch hierbei werden die Querkräfte erfindungsgemäß in den gekrümmten Zonen des Profils, nämlich über die Rundschalen in den Untergurt eingeleitet, so daß das gesamte Profil sehr widerstandsfähig gegen Beulen aufgrund der Schalenwirkung der gekrümmten Bereiche ist. Dabei wird die Membranwirkung einer Schale ausgenutzt.Particularly advantageously, the U-shaped shell of the lower flange has two round shells which are spaced apart from one another and which are connected to one another via a straight web arranged between them. This special profile cross section the U-shape has proven to be particularly suitable because it has a large moment of resistance to bending. Here, too, the transverse forces are introduced according to the invention in the curved zones of the profile, namely via the round shells into the lower flange, so that the entire profile is very resistant to dents due to the shell effect of the curved regions. The membrane effect of a shell is used.

Vorzugsweise entspricht die Länge des Stegs zu der Profilbreite etwa einem Verhältnis von 1:3. Als Profilbreite ist in diesem Sinn der Abstand der geraden Seiten zwischen Obergurt und Untergurt eines Schüblings zu verstehen.The length of the web preferably corresponds to a ratio of 1: 3 to the profile width. In this sense, the profile width is to be understood as the distance between the straight sides between the top flange and bottom flange of a slider.

Es wird vorgeschlagen, daß die vordere Lagerstelle im Bereich zwischen den Untergurten im Bereich jeder Rundschale ein separates Gleitelement aufweist. Dadurch werden auch im Untergurtbereich der vorderen Lagerstelle die Kräfte allein über die gerundeten Bereiche übertragen. Durch die separate, geteilte Anordnung der Gleitelemente können Toleranzen in der Breite der einzelnen Schüblinge gut ausgeglichen werden. Ferner treten keine Momente im Übergangsbereich zu den geraden Seiten des Obergurts bzw. zu dem geraden Steg auf, da die Umfangsspannungen tangential eingeleitet werden.It is proposed that the front bearing point have a separate sliding element in the area between the lower chords in the area of each round shell. As a result, even in the lower chord area of the front bearing point, the forces are transmitted only via the rounded areas. Due to the separate, divided arrangement of the sliding elements, tolerances in the width of the individual sliders can be compensated for well. Furthermore, no moments occur in the transition area to the straight sides of the upper flange or to the straight web, since the circumferential stresses are introduced tangentially.

Günstigerweise kann der radiale Abstand zwischen innerem und außerem Schübling im Bereich der Rundschalen größer sein als in den geraden Bereichen des Untergurts.Conveniently, the radial distance between the inner and outer slugs can be greater in the area of the round shells than in the straight areas of the lower flange.

Als bevorzugte Ausführungsform sind der Mittelpunkt der äußeren Rundschale und der Mittelpunkt der inneren Rundschale der vorderen Lagerstelle beabstandet voneinander angeordnet, wobei der Mittelpunkt der äußeren Rundschale näher an den Rundschalen als der Mittelpunkt der inneren Rundschale angeordnet ist.As a preferred embodiment, the center of the outer round shell and the center of the inner round shell of the front bearing point are arranged spaced apart from one another, the center of the outer round shell being arranged closer to the round shells than the center of the inner round shell.

Vorzugsweise beträgt das Verhältnis von Profilbreite zu Profilhöhe etwa 1:1,15 bis 1:1,4.The ratio of profile width to profile height is preferably approximately 1: 1.15 to 1: 1.4.

In besonderer Weise kann das Verhältnis von der Länge der geraden Seite zwischen einer Eckrunde des Obergurts und dem anschließenden gekrümmten Bereich des Untergurts zu der Profilhöhe etwa 1:1,6 bis 1:2 betragen.In a special way, the ratio of the length of the straight side between a corner round of the upper flange and the subsequent curved region of the lower flange to the profile height can be approximately 1: 1.6 to 1: 2.

Die Erfindung wird im folgenden anhand von Ausführungsbeispielen sowie unter Bezug auf die Zeichnung näher erläutert. In dieser zeigt:

Fig. 1
eine vereinfachte, teilweise geschnittene Darstellung eines Teilstücks eines äußeren Schüblings, in welchem ein innerer Schübling teilweise aufgenommen ist,
Fig. 2
einen Querschnitt entlang der Linie A-A in Fig. 1,
Fig. 3
einen Querschnitt entlang der Linie B-B in Fig. 1,
Fig. 4
einen vergrößerten Teilquerschnitt entlang der Linie B-B in Fig. 1 mit einem Gleitelement im Eckrundenbereich,
Fig. 5
eine vereinfachte Schnittansicht der hinteren Enden dreier ineinander geschobener Schüblinge eines erfindungsgemäßen Auslegers,
Fig. 6
eine vereinfachte Schnittansicht dreier ineinander geschobener Schüblinge mit breiten hinteren Kragen eines Auslegers gemäß dem Stand der Technik und
Fig. 7
einen Querschnitt durch die vordere Lagerstelle eines erfindungsgemäßen Auslegers mit acht Schüblingen, deren Untergurte zwei voneinander beabstandete Rundschalen aufweisen.
The invention is explained in more detail below on the basis of exemplary embodiments and with reference to the drawing. In this shows:
Fig. 1
a simplified, partially sectioned representation of a section of an outer slide, in which an inner slide is partially accommodated,
Fig. 2
2 shows a cross section along the line AA in FIG. 1,
Fig. 3
2 shows a cross section along the line BB in FIG. 1,
Fig. 4
2 shows an enlarged partial cross section along the line BB in FIG. 1 with a sliding element in the corner round region,
Fig. 5
FIG. 2 shows a simplified sectional view of the rear ends of three nested pushers of an extension arm according to the invention,
Fig. 6
a simplified sectional view of three nested pushers with wide rear collars of a boom according to the prior art and
Fig. 7
a cross section through the front bearing point of a boom according to the invention with eight pushers, the lower chords of which have two spaced-apart round shells.

In den Fig. 1 bis 3 sind jeweils ein äußerer Schübling 14 und ein innerer Schübling 16 dargestellt. Der innere Schübling 16 befindet sich mit einer Teillänge im Inneren eines vorderen Teilabschnittes des äußeren Schüblinges 14. Jeder Schübling besteht aus zwei gebogenen Blechhalbschalen, die durch Längsschweißnähte miteinander verbunden sind. Die Obergurte 1 eines jeden Schüblinges haben eine U-förmige Gestalt mit viertelkreisförmigen Eckrundungen R. In den Figuren 2 und 3 sind die beiden Eckrundungen des inneren Schüblings 16 mit Ri bezeichnet, und sind die beiden Eckrundungen des äußeren Schüblings 14 mit Ra bezeichnet. Die Eckrundungen erstrecken sich über 60 bis 90o.1 to 3, an outer slide 14 and an inner slide 16 are shown. The inner slide 16 is located with a partial length inside a front section of the outer slide 14. Each slide consists of two bent sheet metal half-shells which are connected to one another by longitudinal weld seams. The top chords 1 of each Schüblinges have a U-shaped shape with quarter-circular corner curves R. In Figures 2 and 3, the two corner curves of the inner slide 16 are denoted by Ri, and the two corner curves of the outer slide 14 are designated by Ra. The corner curves extend over 60 to 90o.

Die Untergurte 2 der beiden Schüblinge 14 und 16 besitzen eine halbkreisförmige Gestalt mit einem Radius, der gleich der Hälfte der Breite (b) des zugehörigen Obergurtes ist. Es versteht sich, daß dementsprechend der Radius des Untergurtes 2 des inneren Schüblings 16 kleiner ist als der Radius des Untergurtes des äußeren Schüblings 16. Ober- und Untergurte können verschiedene Blechdicken aufweisen.The lower chords 2 of the two slugs 14 and 16 have a semicircular shape with a radius which is equal to half the width (b) of the associated upper chord. It goes without saying that the radius of the lower flange 2 of the inner slide 16 is smaller than the radius of the lower flange of the outer slide 16. The upper and lower flange can have different sheet thicknesses.

Die zusammengeschweißten Ober- und Untergurte weisen an ihren längsseitigen Enden einen vorderen Kragen 7 und an ihren hinteren Enden einen hinteren Kragen 8 in Form aufgeschweißter Bleche auf. Diese Kragen sind korrosionssteif ausgebildet und dienen als Lagerstellen. Dabei ist jedem Untergurt 2 eine vordere Lagerstelle 3 und jedem Obergurt 1 eine hintere Lagerstelle 4 zugeordnet.The welded upper and lower belts have a front collar 7 at their longitudinal ends and a rear collar 8 in the form of welded-on metal sheets at their rear ends. These collars are corrosion-resistant and serve as bearing points. Each lower flange 2 is assigned a front bearing 3 and each upper flange 1 a rear bearing 4.

Die beiden Kragen 7 und 8 bilden zugleich einen Anschlag für das Gleitelement 10 und die Gleitlagerschalen 12 aus Kunststoff, welche zumindest im Bereich der Lagerstellen zwischen innerem Schübling und äußerem Schübling vorgesehen sind. Dabei ist im Bereich jeder dem Untergurt zugeordneten Lagerstelle 3 ein Gleitelement 10 aus Kunststoff, vorzugsweise aus Polyamid, vorgesehen, dessen Gestalt dem halbkreisförmigen Zwischenraum zwischen dem Untergurt des inneren Schüblings 16 und dem Untergurt des äußeren Schüblings 14 entspricht. Ferner sind im Bereich jeder dem Obergurt 1 zugeordneten Lagerstelle 4 tragende Gleitlagerschalen 12 wenigstens in den beiden Zwischenräumen zwischen innerem Obergurt und äußerem Obergurt im Bereich der beiden Eckrundungen Ri und Ra vorgesehen, wie in Fig. 3 dargestellt. Das halbkreisförmige Gleitelement 10 erstreckt sich vorteilhafterweise nach oben bis zu der in den Figuren 2 und 3 mit C bezeichneten Horizontallinie.The two collars 7 and 8 also form a stop for the sliding element 10 and the slide bearing shells 12 made of plastic, which are provided at least in the area of the bearing points between the inner slide and the outer slide. A sliding element 10 made of plastic, preferably of polyamide, is provided in the area of each bearing point 3 associated with the lower flange, the shape of which is semicircular The space between the lower flange of the inner slide 16 and the lower flange of the outer slide 14 corresponds. Furthermore, in the area of each bearing point 4 assigned to the upper flange 1, bearing bushes 12 are provided at least in the two spaces between the inner upper flange and the outer upper flange in the region of the two corner curves Ri and Ra, as shown in FIG. 3. The semicircular sliding element 10 advantageously extends up to the horizontal line labeled C in FIGS. 2 and 3.

Das Gleitelement 10 und die Gleitlagerschalen 12 sind jeweils am äußeren Schübling 14 fixiert.The sliding element 10 and the slide bearing shells 12 are each fixed to the outer slide 14.

Das Zusammenwirken der beiden Lagerstellen 3 und 4 ermöglicht ein Übertragen von Querkräften und Biegemomenten von einem inneren Schübling zum benachbarten äußeren Schübling.The interaction of the two bearing points 3 and 4 enables the transfer of transverse forces and bending moments from an inner slide to the adjacent outer slide.

Greift, wie in Fig. 1 dargestellt, am inneren Schübling 16 eine Kraft F an, so bewirkt diese ein Moment M, welches wiederum Querkräfte Qv und Qh hervorruft. Die Querkraft Qv verformt den Untergurt des inneren Schüblings oval. Über das Gleitelement 10 wird die Querkraft Qv in den äußeren Schübling 14 eingeleitet, worauf sich dessen Querschnitt gleichfalls oval verformt. Insbesondere wird der Querschnitt in Vertikalrichtung länger und in Horizontalrichtung kürzer. Gerade diese Verkürzung in Querrichtung führt zu einer vorteilhaften Stabilisierung der Lagerstelle 3 durch einen Fassdauge-Effekt als Folge des auf den inneren Schübling ausgeübten Druckes. Ferner wird durch den vom Gleitmittelelement 10 vermittelten großflächigen Kontakt ein Ausbeulen verhindert. Dem unerwünschten Ausbeulen wird ferner dadurch vorgebeugt, daß die Querkraft Qv auf den halbkreisförmig gestalteten Untergurt einwirkt, so daß der Membraneffekt einer Schale ausgenutzt werden kann. Folglich darf die Blechstärke klein sein, was zu einer Verringerung des Eigengewichtes führt.If, as shown in FIG. 1, a force F acts on the inner slide 16, this causes a moment M, which in turn causes transverse forces Qv and Qh. The shear force Qv deforms the lower flange of the inner slider oval. The transverse force Qv is introduced into the outer slide 14 via the sliding element 10, whereupon its cross section is also deformed oval. In particular, the cross section becomes longer in the vertical direction and shorter in the horizontal direction. This shortening in the transverse direction leads to an advantageous stabilization of the bearing 3 by a barrel eye effect as a result of the pressure exerted on the inner slide. Furthermore, bulging is prevented by the large-area contact mediated by the lubricant element 10. The undesired bulging is also prevented by the fact that the transverse force Qv acts on the semicircular lower flange, so that the membrane effect of a shell can be exploited. As a result, the sheet thickness may be small, which leads to a reduction in the dead weight.

Die hintere Lagerkraft Qh belastet die Innenoberfläche des äußeren Schüblings 14 im Bereich der hinteren Lagerstelle 4. Wie in Fig. 3 dargestellt, sind im Bereich der hinteren Lagerstelle 4 die beiden inneren Eckrundungsbereiche Ri mit Hilfe der beiden Gleitlagerschalen 12 mit den beiden äußeren Eckrundungsbereichen Ra verbunden, wobei die inneren Eckrundungsbereiche zum inneren Schübling 16 und die äußeren Eckrundungsbereiche zum äußeren Schübling gehören. Zu beachten ist an dieser hinteren Lagerstelle 4, daß die Gleitlagerschalen 12 nicht auf einem separaten Kragen gelagert sind, wie im Stand der Technik, sondern durch das gewölbte Blech des inneren Schüblings 16 abgestützt werden. Hierdurch wird gleichzeitig die Scheibenwirkung der Flansche bei der Lasteinleitung ausgenutzt. Daraus wiederum folgt, daß bei dem teleskopierbaren Ausleger nach der Erfindung die Breite der Gleitlagerschalen 12 und des Gleitelements 10 (d.h. deren Abmessung in Auslegerlängsrichtung) unabhängig ist von der Breite des zugeordneten Kragens 8. Wie bereits erwähnt, ergibt sich aus dieser Konstruktion wiederum ein Zuwachs an nutzbarer Auslegerlänge.The rear bearing force Qh loads the inner surface of the outer slide 14 in the area of the rear bearing point 4. As shown in FIG. 3, in the area of the rear bearing point 4 the two inner corner rounding areas Ri are connected to the two outer corner rounding areas Ra by means of the two slide bearing shells 12 , wherein the inner corner rounding areas belong to the inner slide 16 and the outer corner rounding areas belong to the outer slide. It should be noted at this rear bearing point 4 that the plain bearing shells 12 are not supported on a separate collar, as in the prior art, but are supported by the curved plate of the inner slide 16. As a result, the disc effect of the flanges is simultaneously utilized when the load is introduced. From this in turn it follows that in the telescopic boom according to the invention the width of the slide bearing shells 12 and the sliding element 10 (ie their dimension in the longitudinal direction of the boom) is independent of the width of the associated collar 8. As already mentioned, this construction in turn results in an increase of usable boom length.

Die Blechdicke des vorderen Kragens 7 wie auch die Blechdicke des hinteren Kragens 8 beträgt vorzugsweise das 1,2-bis 2,5-fache der Blechdicke des für das jeweilige Auslegerprofil benutzten Bleches.The sheet thickness of the front collar 7 as well as the sheet thickness of the rear collar 8 is preferably 1.2 to 2.5 times the sheet thickness of the sheet used for the respective boom profile.

Dem vorderen Kragen 7 kann in den Zwischenräumen zwischenden äußeren Eckrundungen Ra und den inneren Eckrundungen Ri jeweils eine Gleitlagerschale 18 aus Kunststoff zugeordnet sein, wie in Fig. 2 dargestellt. Statt der zwei in Fig. 2 dargestellten Gleitlagerschalen 18 kann lediglich ein einziges Gleitelement vorgesehen sein. Die Gleitlagerschalen 18 müssen so ausgebildet und angeordnet sein, daß der innere Schübling 16 daran gehindert ist, im Inneren des äußeren Schüblings 14 zu kippen.The front collar 7 can in the spaces between the outer corner curves Ra and the inner corner curves Ri each have a slide bearing shell 18 made of plastic, as shown in FIG. 2. Instead of the two slide bearing shells 18 shown in FIG. 2, only a single sliding element can be provided. The slide bearing shells 18 must be designed and arranged in such a way that the inner slide 16 is prevented from tilting inside the outer slide 14.

Die den Gleitlagerschalen 18 zugeordnete Lagerstelle wird nicht permanent mit Kräften beaufschlagt.The bearing point assigned to the slide bearing shells 18 is not permanently subjected to forces.

Im Bereich des hinteren Kragens 8 und zwar im Untergurtbereich desselben können, wie in Fig. 3 dargestellt, Gleitbackenelemente 15 aus Kunststoff vorgesehen sein. Diese Gleitbackenelemente 15 sind zwischen dem halbkreisförmigen Untergurt des inneren Schüblings 16 und dem halbkreisförmigen Untergurt des äußeren Schüblings 14 angeordnet. Vorteilhafterweise erstrecken sie sich mit ihren oberen Enden bis an die Horizontallinie C. Anstelle der in Fig. 3 gezeigten zweiteiligen Ausbildung der Gleitbackenelemente 15 können dieselben auch einstückig ausgebildet sein. Grundsätzlich sind Gleitbackenelemente 15 so auszubilden und anzuordnen, daß der innere Schübling 16 nicht im Inneren des äußeren Schüblings 16 kippt, da die letztgenannten Gleitelemente besonders bei Einwirkung einer Seitenkraft bzw. einer Querkraftkomponente auf den inneren Schübling beansprucht wird.In the area of the rear collar 8, specifically in the lower chord area thereof, as shown in FIG. 3, sliding shoe elements 15 made of plastic can be provided. These sliding jaw elements 15 are arranged between the semicircular lower flange of the inner slide 16 and the semicircular lower flange of the outer slide 14. Advantageously, they extend with their upper ends to the horizontal line C. Instead of the two-part design of the sliding jaw elements 15 shown in FIG. 3, they can also be formed in one piece. Basically, slide jaw elements 15 are to be designed and arranged such that the inner slide 16 does not tip inside the outer slide 16, since the latter slide elements are particularly stressed when a lateral force or a transverse force component acts on the inner slide.

Die zuvor erörterten Gleitlagerschalen 18 (Fig. 2) werden nur im maximal austeleskopierten Zustand, d.h. nur bei minimaler Einspannlänge des inneren Schüblings, belastet, um denselben gegen ein seitliches Ausweichen (Kippen) abzustützen.The previously discussed plain bearing shells 18 (Fig. 2) are only in the maximum telescoped state, i.e. only with a minimum clamping length of the inner slide, loaded to support it against lateral deflection (tipping).

In Fig. 4 ist eine Gleitlagerschale 12, die zwischen zwei Eckrunden Ri, Ra der Obergurte 1 am hinteren Ende eines inneren Schüblings 16 dargestellt. Im Bereich der Eckrunden Ri, Ra ist der Abstand zwischen den beiden Obergurten 1 größer als in den gerade verlaufenden Bereichen des Obergurtes 1. Die Eckrunden Ri, Ra haben beabstandet voneinander angeordnete Mittelpunkte Ma, Mi, wobei der Mittelpunkt Ma der Eckrunde Ra näher der Gleitlagerschale 12 bzw. den Eckrunden Ri, Ra angeordnet ist. Der Figur ist der Mittelpunkt Ma jeweils durch zwei eingezeichnete Radien ra und analog dazu der Mittelpunkt Mi durch die zwei Radien ri dargestellt.In Fig. 4, a plain bearing shell 12, which is shown between two corner rounds Ri, Ra of the upper chords 1 at the rear end of an inner slide 16. In the area of the corner rounds Ri, Ra, the distance between the two upper chords 1 is greater than in the straight areas of the upper chord 1. The corner rounds Ri, Ra have spaced-apart centers Ma, Mi, with the center Ma of the corner round Ra closer to the plain bearing shell 12 or the corner rounds Ri, Ra is arranged. The figure shows the center point Ma in each case by two radii ra drawn in and, analogously, the center point Mi by the two radii ri.

Die Gleitlagerschale 12 ist am inneren Schübling 16 fixiert, so daß es relativ zu der Eckrunde Ra des äußeren Schüblings eine Relativbewegung ausführt. Die Gleitlagerschale 12 erstreckt sich in die an die Eckrunden Ri, Ra angrenzenden geraden Bereiche hinein, wobei es auch im geraden Bereich am inneren Schübling 16 anliegt. Bezüglich des äußeren Schüblings 14 weicht die Gleitlagerschale 12 beginnend an den Übergängen zu den geraden Bereichen im Winkel α von dem äußeren Schübling 14 zurück. Demzufolge liegt sie nur im Bereich der Eckrunde Ra an dem äußeren Schübling 14 an. Analog zu Fig. 4 sind die Gleitlagerschalen 18 des vorderen Endes ausgebildet. Hierbei liegen die Gleitlagerschalen 18 auch im geraden Bereich an dem äußeren Schübling 14 an und weichen in den geraden Bereichen des inneren Schüblings 16 unter dem Winkel α von dessen Obergurt 1 zurück.The slide bearing shell 12 is fixed to the inner slide 16 so that it performs a relative movement relative to the corner round Ra of the outer slide. The slide bearing shell 12 extends into the straight areas adjoining the corner rounds Ri, Ra, it also abutting the inner slide 16 in the straight area. With regard to the outer slide 14, the slide bearing shell 12 withdraws from the outer slide 14 starting at the transitions to the straight regions at an angle α. As a result, it only rests on the outer slide 14 in the area of the corner round Ra. Analogously to FIG. 4, the slide bearing shells 18 of the front end are designed. In this case, the plain bearing shells 18 also abut the outer slide 14 in the straight region and recede from the upper flange 1 in the straight regions of the inner slide 16 at an angle α.

In Fig. 5 ist ein zusammengeschobener Ausleger mit drei Schüblingen dargestellt. In den Vertikalschnitt ist jeweils eine Schnittansicht der hinteren Gleitlagerschalen 12 gelegt. Sie liegen mit einer Seite an dem schmalen hinteren Kragen 8 an und sind an der anderen Seite von einem Rand 20 eingefaßt. Der Rand 20 ist über den Umfang auf den Bereich der Gleitlagerschalen 12 beschränkt. In dem dargestellten eingeschobenen Zustand überlappen sich die Gleitlagerschalen 12 der benachbarten Schüblinge teilweise und können dadurch sehr weit ineinander eingeschoben werden.In Fig. 5 a collapsed boom with three sliders is shown. In the vertical section, a sectional view of the rear slide bearing shells 12 is placed. They rest on one side on the narrow rear collar 8 and are bordered on the other side by an edge 20. The edge 20 is limited over the circumference to the area of the slide bearing shells 12. In the inserted state shown, the slide bearing shells 12 of the neighboring pushbuttons partially overlap and can therefore be pushed very far into one another.

In Fig. 6 sind drei Schüblinge in zusammengefahrenem Zustand gemäß einer Lageranordnung des Standes der Technik dargestellt. Hier sind die Schüblinge ineinander durch eine Rundumlagerung abgestützt, wobei die Lagerelemente 30 jeweils in einem halbkastenförmigen Lagerblock 31 aufgenommen sind, der gegenüber dem zugehörigen Schübling zur Innenseite versetzt ist. Die Einfassung des Lagerblocks 31 wird jeweils durch zwei über den Querschnitt des Schüblings durchgehende Kragen 32 gebildet. Wie aus Fig. 6 ersichtlich, behindern die durchgehenden Kragen 32, die zur Stabilität notwendig sind, ein weiteres Einschieben der inneren Schüblinge 16, so daß die hinteren Enden der Schüblinge 16 nebeneinander angeordnet werden müssen. Zudem ist in der Zeichnung dargestellt, daß die Lagerelemente 30 in radialer Richtung wesentlich dicker als die Gleitelemente 12 gemäß der Erfindung (Fig. 5) sind.In Fig. 6 three Schüblinge are shown in the retracted state according to a bearing arrangement of the prior art. Here, the slugs are supported one inside the other by an all-round bearing, the bearing elements 30 each being received in a half-box-shaped bearing block 31, which is offset to the inside with respect to the associated slider. The bordering of the bearing block 31 is formed in each case by two collars 32 which are continuous over the cross section of the slider. As can be seen from Fig. 6, the continuous collar 32, which are necessary for stability, a further insertion of the inner slider 16, so that the rear ends of the slider 16 must be arranged side by side. In addition, it is shown in the drawing that the bearing elements 30 are substantially thicker in the radial direction than the sliding elements 12 according to the invention (FIG. 5).

In Fig. 7 ist ein erfindungsgemäßer teleskopierbarer Ausleger mit acht Schüblingen dargestellt, bei dem die U-förmige Schale jedes Untergurts 2 aus zwei beabstandet voneinander angeordneten viertelkreisförmigen Rundschalen 33 gebildet ist. Zwischen den Rundschalen 33 ist ein gerader Steg 34 angeordnet, der sich parallel zu dem geraden Bereich des Obergurts 1 zwischen den Eckrunden Ri, Ra erstreckt.7 shows a telescopic boom according to the invention with eight pushers, in which the U-shaped shell of each lower flange 2 is formed from two quarter-circular round shells 33 arranged at a distance from one another. A straight web 34 is arranged between the round shells 33 and extends parallel to the straight region of the upper chord 1 between the corner rounds Ri, Ra.

Zwischen den Rundschalen 33 zweier benachbarter Schüblinge ist jeweils ein im wesentlichen viertelkreisförmiges Gleitelement 10 angeordnet. Das Gleitelement 10 ist der jeweiligen Form der gerundeten Bereiche der Rundschalen 33 angepaßt. Die Gleitelemente 10 sind jeweils an ihrem äußeren Schübling 14 fixiert und erstrecken sich an dieser Seite bereichsweise in den geraden Steg 34 bzw. die gerade Seite 35 zwischen Untergurt 2 und Obergurt 1 hinein. Auf der Seite des inneren Schüblings 16 liegen die Gleitelemente 10 nur im gekrümmten Bereich der Rundschalen 33 an. Im geraden Bereich sind die Gleitelemente 10 analog zu den Enden der in Fig. 4 dargestellten Gleitlagerschalen 12 ausgebildet. Die Gleitelemente weichen auf der Seite des inneren Schüblings 15 ausgehend vom gerundeten Bereich in einer schrägen Auslaufzone in einem Winkel α von dem inneren Schübling zurück.A substantially quarter-circle-shaped sliding element 10 is arranged between the round shells 33 of two adjacent slugs. The sliding element 10 is adapted to the respective shape of the rounded areas of the round shells 33. The sliding elements 10 are each fixed to their outer slide 14 and extend on this side in some areas into the straight web 34 or the straight side 35 between the lower flange 2 and the upper flange 1. On the side of the inner slide 16, the sliding elements 10 rest only in the curved region of the round shells 33. In the straight region, the sliding elements 10 are designed analogously to the ends of the sliding bearing shells 12 shown in FIG. 4. The sliding elements on the side of the inner slide 15 depart from the rounded area in an oblique outlet zone at an angle α from the inner slide.

Selbstverständlich kann auch die hintere Lagerstelle 4 im Untergurtbereich 2 wie in Fig. 7 dargestellt, ausgebildet sein. In diesem Fall sind die Gleitbackenelemente 15 wie die Rundschalen 33 ausgebildet.Of course, the rear bearing 4 in the lower flange area 2 can also be formed as shown in FIG. 7. In this case, the sliding jaw elements 15 are designed like the round shells 33.

Es versteht sich, daß bei dem in Fig. 7 dargestellten Querschnitt im Obergurtbereich 1 dieselbe Anordnung der Gleitlagerschalen 18 im Bereich der Eckrunden Ri, Ra, gewählt werden kann, wie bei den in den übrigen Figuren geschilderten Ausführungsbeispielen.It goes without saying that, in the cross section shown in FIG. 7 in the upper chord region 1, the same arrangement of the slide bearing shells 18 in the region of the corner rounds Ri, Ra can be selected as in the exemplary embodiments described in the remaining figures.

Claims (20)

  1. Telescopic boom comprising at least one outer structure (14) and at least one inner structure (16), each of which is designed as a hollow section with upper flange (1) and lower flange (2), said upper flange (1) having a half-basket profile with two rounded edges (Ri, Ra) to which the lower flange (2) is joined with a liner of an essentially U-shaped profile, and each structure being mounted on the adjoining structure with a front and a back bearing (3, 4), characterized in that said front bearing (3) has a slide element (10) in the area between said lower flanges (2) only in the region of the curvature, and said rear bearing (4) has a separate plain bearing half liner (12) in the area between said upper flanges (1) only in the region of each rounded edge (Ri, Ra).
  2. The boom according to claim 1, characterized in that in the area between said lower flanges (2) said rear bearing (4) has at least one liner-shaped slide element (15) which extends at least portionwise in each of the curved sides of said lower flanges (2) which adjoin said upper flanges (1).
  3. The boom according to claim 1 or 2, characterized in that said rear bearing (4) comprises two separate sliding block elements (15) in the area between said lower flanges (2), one of said sliding block elements being respectively arranged in each of the curved sides of said lower flanges (2) which adjoin said upper flanges (1).
  4. The boom according to any of the preceding claims, characterized in that said front bearing (3) in the area between said upper flanges (1) comprises a separate plain bearing half liner (18) only in the region of each rounded edge (Ri, Ra).
  5. The boom according to any of the preceding claims, characterized in that said sliding block elements (15) and plain bearing half liners (12) of said rear bearing (4) are fixed onto said inner structure (16).
  6. The boom according to any of the preceding claims, characterized in that said slide element(s) (10) and said plain bearing half liners (18) of said front bearing (3) are fixed to said outer structure (14).
  7. The boom according to any of the preceding claims, characterized in that the radial distance between said inner and outer structures (14, 16) in the area of said rounded edges (Ri,Ra) is greater than in the straight portions of said upper flange (1).
  8. The boom according to any of the preceding claims, characterized in that the center point (Ma) of said outer rounded edge (Ra) and the center point (Mi) of said inner rounded edge (Ri) of said front bearing (3) and/or said rear bearing (4) are spaced apart from each other, with the center point (Ma) of said outer rounded edge (Ra) being arranged closer to the rounded edges (Ri, Ra) than the center point (Mi) of said inner rounded edge (Ri).
  9. The boom according to any of the preceding claims, characterized in that said plain bearing half liners (12, 18) of said rounded edges (Ri, Ra) and/or said slide elements (10, 15) in said lower flange portion (2) of said front and/or rear bearings (3, 4) extend beyond the curved portions into the straight portions, with said slide elements (10, 15) and said plain bearing half liners (12, 18) adjoining, at the side of said structure moved relative thereto, said structure only in the curved region.
  10. The boom according to claim 9, characterized in that said plain bearing half liners (12, 18) in the straight upper flange portion (1) and/or said slide elements (10, 15) in the lower flange portion (2) are spaced apart at the side of the relative movement from said structure at an angle (α) from the straight side.
  11. The boom according to any of the preceding claims, characterized in that said outer structure (16) in the area of said front bearing (3) has a front collar (7) and said inner structure (14) in the area of said rear bearing (4) has a rear collar (8), said collars serving as an axial abutment of slide element (10), plain bearing half liners (12, 18) and sliding block elements (15).
  12. The boom according to any of the preceding claims, characterized in that the sheet thickness of said front and rear collars (7, 8) is 1.2 to 2.5 times the sheet thickness of the respective boom profile.
  13. The boom according to any of the preceding claims, characterized in that the sheet thickness of said upper flange (1) differs form the sheet thickness of said lower flange (2).
  14. The boom according to any of the preceding claims, characterized in that the U-shaped liner of said lower flange (2) comprises two spaced-apart round liners (33) which are interconnected via a straight web (34) arranged thereinbetween.
  15. The boom according to claim 14, characterized in that the length of said web (34) relative to the profile width corresponds approximately to the ratio of 1:3.
  16. The boom according to claim 14 or 15, characterized in that said front bearing (3) in the area between said lower flanges (2) has a separate slide element (10) in the region of each round liner (33).
  17. The boom according to any of claims 14 to 16,
    characterized in that the radial distance between inner and outer structures (14, 16) in the area of said round liners (33) is greater than in the straight portions (34) of said lower flange (2).
  18. The boom according to any of claims 14 to 17,
    characterized in that the center point of said outer round liner (33) and the center point of said inner round liner (33) of said front bearing (3) are spaced apart, the center point of said outer round liner (33) being arranged closer to said round liners (33) than the center point of said inner round liner (33).
  19. The boom according to any of the preceding claims, characterized in that the ratio of profile width to profile height is about 1:1.15 to 1:1.4.
  20. The boom according to any of the preceding claims, characterized in that the ratio of the length of said straight side (35) between a rounded edge (Ri, RA) of said upper flange (1) and the adjoining curved portion (33) of said lower flange (2) to the profile height is about 1:1.6 to 1:2.
EP94920945A 1993-06-16 1994-06-16 Telescopic boom Expired - Lifetime EP0702661B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE9308993U DE9308993U1 (en) 1993-06-16 1993-06-16
DE9308993U 1993-06-16
PCT/EP1994/001965 WO1994029212A1 (en) 1993-06-16 1994-06-16 Telescopic boom

Publications (2)

Publication Number Publication Date
EP0702661A1 EP0702661A1 (en) 1996-03-27
EP0702661B1 true EP0702661B1 (en) 1997-12-17

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EP94920945A Expired - Lifetime EP0702661B1 (en) 1993-06-16 1994-06-16 Telescopic boom

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EP (1) EP0702661B1 (en)
JP (1) JP2828779B2 (en)
CN (1) CN1127497A (en)
DE (2) DE9308993U1 (en)
WO (1) WO1994029212A1 (en)

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EP2184251A1 (en) * 2008-11-07 2010-05-12 Kobelco Cranes Co., Ltd. Telescopic boom

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DE19624312C2 (en) * 1996-06-18 2000-05-31 Grove Us Llc Telescopic boom for mobile cranes
FR2759687B1 (en) * 1997-02-14 1999-04-23 Fdi Sambron GUIDE PAD FOR TELESCOPIC BOOM AND TELESCOPIC BOOM PROVIDED WITH SUCH A GUIDE
KR100659686B1 (en) * 2003-03-07 2006-12-21 히다치 겡키 가부시키 가이샤 Telescopic boom device
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DE102005009348B4 (en) 2005-03-01 2013-05-29 Manitowoc Crane Group France Sas Adaptable sliding bearing for telescopic crane jib
JP4959148B2 (en) * 2005-04-21 2012-06-20 株式会社タダノ Telescopic boom for aerial work platforms
JP5222489B2 (en) * 2007-04-23 2013-06-26 株式会社タダノ Telescopic boom slide device
DK2185462T3 (en) * 2007-09-05 2011-05-23 Palfinger Ag Profile shape for a crane arm
DE102008032976B4 (en) * 2007-09-12 2018-02-22 Manitowoc Crane Group France Sas A telescopic crane jib part
JP2010089919A (en) 2008-01-09 2010-04-22 Kobelco Cranes Co Ltd Telescopic boom
JP2010235250A (en) * 2009-03-31 2010-10-21 Tadano Ltd Structure of telescopic boom and crane
JP5166352B2 (en) * 2009-06-01 2013-03-21 コベルコクレーン株式会社 Multistage telescopic boom
JP5625309B2 (en) * 2009-10-13 2014-11-19 コベルコクレーン株式会社 boom
ITMI20110856A1 (en) * 2011-05-17 2012-11-18 Cifa Spa TELESCOPIC ARM FOR CRANES AND CRANE INCLUDING SUCH ARM
CN104495648B (en) * 2014-11-05 2016-11-30 中联重科股份有限公司 Crane arm handling method and crane arm
JP7220346B2 (en) * 2018-08-07 2023-02-10 株式会社タダノ slide device
CN111891945A (en) * 2020-07-16 2020-11-06 三一汽车起重机械有限公司 Crane boom and crane
CN114873528B (en) * 2022-04-22 2023-10-03 江苏徐工工程机械研究院有限公司 Design method of telescopic arm of aerial working machine

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Publication number Priority date Publication date Assignee Title
EP2184251A1 (en) * 2008-11-07 2010-05-12 Kobelco Cranes Co., Ltd. Telescopic boom

Also Published As

Publication number Publication date
WO1994029212A1 (en) 1994-12-22
JPH09501384A (en) 1997-02-10
DE59404835D1 (en) 1998-01-29
DE9308993U1 (en) 1993-08-12
CN1127497A (en) 1996-07-24
EP0702661A1 (en) 1996-03-27
JP2828779B2 (en) 1998-11-25

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