EP2651812B1 - Mobil-teleskopkran - Google Patents

Mobil-teleskopkran Download PDF

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Publication number
EP2651812B1
EP2651812B1 EP11797252.1A EP11797252A EP2651812B1 EP 2651812 B1 EP2651812 B1 EP 2651812B1 EP 11797252 A EP11797252 A EP 11797252A EP 2651812 B1 EP2651812 B1 EP 2651812B1
Authority
EP
European Patent Office
Prior art keywords
boom
jib
telescopic crane
crane according
mobile 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.)
Active
Application number
EP11797252.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2651812A1 (de
Inventor
Alexander Knecht
Peter Kleinhans
Tobias Ebinger
Andreas Hofmann
Martin Lottes
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.)
Tadano Faun GmbH
Original Assignee
Tadano Faun GmbH
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Filing date
Publication date
Application filed by Tadano Faun GmbH filed Critical Tadano Faun GmbH
Publication of EP2651812A1 publication Critical patent/EP2651812A1/de
Application granted granted Critical
Publication of EP2651812B1 publication Critical patent/EP2651812B1/de
Active 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B66C23/42—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes with jibs of adjustable configuration, e.g. foldable
    • 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
    • B66C23/707—Jibs constructed of sections adapted to be assembled to form jibs or various lengths telescopic guiding devices for telescopic jibs
    • 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 mobile telescopic crane according to the preamble of claim 1.
  • a mobile telescopic crane which has two brackets arranged on the boom and inclined to the rocker plane.
  • the guy supports are connected to increase the load capacity of the mobile telescopic crane via guy ropes with the free end of the boom and the superstructure.
  • laterally acting on the boom loads that can represent the traglastbesky criterion in an operating position of the boom can be better absorbed.
  • a disadvantage of this mobile telescopic crane that the guy supports represent a significant additional weight. The guy supports must therefore be transported separately on a truck to the site and mounted there on the boom. This is associated with a considerable cost and time.
  • the boom is composed of two juxtaposed sub-arms.
  • a material handling machine having a traveling machine frame and a telescoping boom pivotally mounted thereon.
  • the boom is constructed of a plurality of boom sections, wherein a receiving fork for a load to be moved is disposed on the outermost boom section.
  • the boom sections are telescopically formed so that the boom is retractable and retractable about the take-up fork with the one located thereon Load to and from the machine frame.
  • at least one boom section is made of a composite material. As a result, the weight of the boom and thus the Tipping moment around the front axle minimized.
  • the outermost boom section is constructed, for example, of three partial boom sections of composite material.
  • the invention has for its object to provide a mobile telescopic crane, which allows a simple way to increase the load.
  • a mobile telescopic crane with the features of claim 1.
  • the area moment of inertia of the boom is significantly increased.
  • the area moment of inertia which is a measure of the bending stiffness, results, according to Steiner's theorem, from the own shares of the sub-cantilevers and their Steiner shares.
  • the boom Due to the rigid connecting elements that connect the sub-boom sections of the sub-boom to boom sections, the boom is extremely rigid, so that the cross-sectional area remains substantially flat under load of the boom, whereby the Steiner shares in the calculation of the area moment of inertia substantially with their theoretical Values, possibly reduced by reduction factors, can be applied.
  • the at least four sub-arms can be arranged polygonal, wherein over the width and height of the boom, the stiffness with respect to perpendicular to the rocker plane and acting in the rocker bending forces is adjustable.
  • the at least four sub-arms can be triangular or quadrangular, in particular rectangular, trapezoidal or diamond-shaped be arranged. This applies if the boom has exactly four or more than four sub-arms.
  • the boom according to the invention Due to the significant increase in the area moment of inertia or the area moments of inertia of the boom according to the invention can be completely different dimensions than conventional boom, so that in comparison to a conventional boom with guy supports a corresponding increase in the load with a lower additional weight can be achieved.
  • the sub-arms are constructed of telescoping part-boom sections in the longitudinal direction, the boom can be brought from a transport position to an operating position with little effort.
  • Due to the lower additional weight of the mobile telescopic crane according to the invention - drive within a certain load class - with the full boom on public roads to the site, so that in contrast to a boom with guy supports no separate transport and no complex installation is required.
  • the inventive mobile telescopic crane thus enables a simple way to increase the load.
  • the boom according to the invention can be dimensioned such that in comparison to a conventional boom with guy supports again a significant increase in the load can be achieved.
  • the boom according to the invention also has a considerable weight, so that the mobile telescopic crane with the boom according to the invention may no longer be able to participate fully in public traffic. Individual sub-cantilevers or a group of sub-cantilevers or the entire boom must then be transported separately to the site and mounted there. In the described Dimensioning of the boom according to the invention is thus the advantage in increasing the load.
  • the boom according to the invention can be optimized in terms of its bending stiffness perpendicular to and / or parallel to the rocker plane and / or in terms of weight.
  • the boom according to the invention can be optimized with regard to its weight and / or with regard to its bending stiffness or load capacity.
  • the mobile telescopic crane according to the invention preferably has a boom with at least three, in particular at least four, and in particular at least five boom sections or respective partial boom sections.
  • a mobile telescopic crane according to claim 2 ensures a high rigidity of the boom against bending loads.
  • the respective partial cross-sectional area comprises the material cross-sectional area as well as the cavity cross-sectional area bounded by the material of the sub-arm.
  • a mobile telescopic crane according to claim 3 has an increased rigidity against bending forces acting perpendicular to the rocker plane.
  • the width B A is a maximum width of the boom or the respective boom section.
  • a mobile telescopic crane according to claim 4 has an increased rigidity against bending forces acting in the rocker plane.
  • the height H A is a maximum height of the boom or the respective boom section.
  • a mobile telescopic crane according to claim 5 ensures a similar stiffness behavior of the boom in the positive and negative lateral direction.
  • a mobile telescopic crane according to claim 6 allows an optimization of the rigidity of the boom in relation to its weight.
  • these can be arranged in particular as a rectangle, trapezoid, rhombus or kite quadrangle.
  • a mobile telescopic crane according to claim 7 ensures a compact transport position of the boom.
  • the possible change in the height of the boom if necessary, ensures, in particular, that the mobile telescopic crane does not exceed a maximum permissible height when driving.
  • the at least four partial arms can be linearly displaceable or pivotable relative to one another.
  • the sub-arms are fixable to each other in a displaced operating position. This is done in particular by means of mechanical locking units.
  • the mechanical locking units are arranged, for example, on the connecting elements.
  • a mobile telescopic crane according to claim 8 ensures in the extended operating position of the boom high rigidity by the mechanical locking of each adjacent Auslagerabroughe, since the built-up of the sub-boom sections sub-arms are extremely rigid by the lock.
  • each adjacent sub-boom sections of each sub-boom are mechanically locked to each other.
  • the locking takes place for example by means of locking bolts, the hydraulically, pneumatically or electromechanically actuated are.
  • the locking can be done by means of a bayonet-type locking mechanism.
  • a mobile telescopic crane according to claim 9 ensures a telescopability of the boom part.
  • a mobile telescopic crane according to claim 10 is simple.
  • the partial boom sections have a circular cross section.
  • a mobile telescopic crane according to claim 11 ensures a high rigidity of the boom, so that the cross-sectional area remains flat under load of the boom and the Steiner shares in the calculation of the area moment of inertia can be set approximately with their theoretical values.
  • a mobile telescopic crane according to claim 12 allows a simple way of mechanical locking adjacent sub-boom sections.
  • the respective locking bolt is hydraulically, pneumatically or electromechanically actuated, for example.
  • all adjacent sub-boom sections of each sub-boom are mechanically locked to each other by means of at least one locking bolt.
  • a mobile telescopic crane according to claim 13 allows rapid mechanical locking of adjacent sub-boom sections. Every locking bolt must be performed only by two associated locking holes of the adjacent sub-boom sections to lock them mechanically to each other. The distance to be traversed for locking the respective locking bolt is low. Because the respective locking bolt only has to be guided by two associated locking bores, a comparatively low accuracy in the alignment of the respective locking bolt is required. Preferably, exactly two locking bolts are provided, which are arranged opposite to each other and can be actuated in opposite directions.
  • a mobile telescopic crane according to claim 14 ensures a high rigidity against bending forces acting perpendicular to the rocker plane. If the at least two sub-arms with the greatest distance to the rocker plane would be arranged on an underside of the jib facing the undercarriage, so that the width of the jib would decrease from its underside to its upper side, then the at least two lower-part jibs would Both due to acting in the rocker bending forces and due to acting perpendicular to the rocker bending forces are charged to pressure. Such a construction of the boom would lead to an undesirable load limitation of the boom or the mobile telescopic crane due to the double pressure load according to the Euler kinks.
  • the at least two sub-arms are arranged with the greatest distance to the rocker plane on the side facing away from the undercarriage or upper side of the boom, so acting in the rocker plane bending forces substantially to a tensile load of at least two upper part boom lead, whereas perpendicular to the rocker plane acting bending forces to a pressure load of the upper one Lead partial boom.
  • the pressure load on the furthest to the rocker plane spaced sub-arms can thus be significantly reduced.
  • the area moment of inertia is thus increased on the one hand in accordance with the invention, but on the other hand avoided a double pressure load.
  • the width of the boom can be dimensioned at the top in wide areas as needed. If the jib has exactly four sub-jibs which are arranged in a triangular shape, then a lower sub-jib facing the undercarriage is arranged in the jockey plane and three upper sub-jibs facing away from the undercarriage are arranged at a distance from the rocking plane or in the rocker plane, so that the width of the boom increases from the lower boom to the upper boom and the upper side, respectively.
  • the jib has exactly four partial jibs which are arranged trapezoidally, then the width of the jib increases, starting from two lower jib sections facing the undercarriage, to two upper sub-jibs facing away from the undercarriage.
  • the lower part boom thus have a smaller distance to the rocker plane, as the upper part boom. Since the pressure load due to acting perpendicular to the rocker plane bending forces decreases with the distance to the rocker plane, the bending stiffness is optimized with respect to perpendicular to the rocker plane acting bending forces even with a boom with trapezoidally arranged sub-arms.
  • the width of the boom increases from a lower, in the rocker plane arranged sub-boom to two spaced apart from the rocker plane arranged upper part arms, whereby the described advantages are achieved.
  • the arranged in the rocker plane, upper part boom is not loaded due to both acting in the rocker bending forces and due to acting perpendicular to the rocker bending forces on pressure. A reduction of the width of the boom, starting from the spaced apart to the rocker plane, upper part boom to the arranged in the rocker plane, upper part boom is thus not disadvantageous.
  • a mobile telescopic crane according to claim 15 ensures a high rigidity of the boom relative to the rocker acting bending forces.
  • By the end-side locking adjacent sub-boom sections laterally acting bending forces are derived directly into the entire boom and absorbed by this. This is ensured, in particular, by the fact that the respective at least one locking bolt is fastened or displaceably mounted directly on the associated or adjacent connecting element.
  • a mobile telescopic crane according to claim 16 ensures a high flexural rigidity against bending forces acting in the rocker plane. Due to its partial cross-sectional area, the at least one partial boom facing the undercarriage can absorb high bending forces acting in the seesaw plane. The flexural rigidity of the boom is thus correspondingly high.
  • the partial cross-sectional area of the at least one lower partial cantilever corresponds in each case to at least one and a half times, and at least twice the partial cross-sectional area of the further partial cantilevers. Preferably, the further sub-arms on the same part-cross-sectional areas.
  • the at least one of the undercarriage facing part-boom serve as a receiving space for the hydraulic cylinder for telescoping the boom.
  • a mobile telescopic crane according to claim 17 allows in a simple and space-saving manner a telescoping of the boom.
  • the at least one partial boom preferably has a larger partial cross-sectional area compared to the other partial cantilevers.
  • the hydraulic cylinder is preferably arranged in this sub-boom.
  • all sub-arms are arranged at a distance from the rocker plane, a hydraulic cylinder is preferably arranged in one of the sub-arms.
  • a plurality of hydraulic cylinders, preferably two hydraulic cylinders may be arranged in sub-arms, which are arranged symmetrically to the rocker plane.
  • a mobile telescopic crane according to claim 18 has a relatively stiff and simply constructed boom.
  • a mobile telescopic crane according to claim 19 enables a simple and space-saving cable guide.
  • a mobile telescopic crane according to claim 20 ensures in the usual way the lifting of loads by means of a supporting cable.
  • the carrying cable is guided from a free end of the boom to a cable winch arranged on the superstructure.
  • the carrying cable is preferably guided in the cable guide channel.
  • a mobile telescopic crane 1 has a mobile undercarriage 2, on which an uppercarriage 3 with a counterweight 4 are arranged.
  • the undercarriage 2 is designed in the usual way for driving on public roads.
  • the undercarriage 2 on a base frame 5, on which several axes 6 with it arranged wheels 7 are mounted, which are drivable and steerable in the usual way.
  • the uppercarriage 3 and the counterweight 4 arranged thereon are mounted rotatably on the undercarriage 2 about a rotation axis 8 extending perpendicular to the base frame 5.
  • a boom 9 is arranged, which is by means of a hydraulic cylinder 10 in a rocking plane W pivotally and in a longitudinal direction L telescopic.
  • the boom 9 has for this purpose three boom sections 11 to 13, which are by means of a hydraulic cylinder 14 and telescoped out and so can be transferred from a retracted transport position to an extended operating position.
  • the first boom section 11 is pivoted at the end about a horizontal pivot axis 15 pivotally mounted on the uppercarriage 3.
  • the pivoting of the boom 9 in the rocker W is carried out by means of the hydraulic cylinder 10, which is articulated starting from the superstructure 3 spaced from the pivot axis 15 to the boom section.
  • the boom 9 has four sub-arms 16, 17, 18, 19, which are each telescopically constructed of three sub-boom sections 20 to 22, 23 to 25, 26 to 28 and 29 to 31.
  • the hydraulic cylinder 14 is disposed within a receiving space of the sub-boom 16, which is formed to form the receiving space as a hollow cylinder.
  • a hydraulic cylinder 14 may be arranged within a receiving space of the sub-arm 17, which is designed to form the receiving space as a hollow cylinder.
  • the sub-arms 16 to 19 are arranged transversely to the longitudinal direction L at a distance from each other and connected by four rigid connecting elements 32 to 35 together.
  • the connecting elements 32 and 33 are each end to the sub-boom sections 20, 23, 26 and 29 arranged and form with these the first boom section 11.
  • the connecting element 34 is in turn arranged on the first boom section 11 facing away from the end of the boom sections 21, 24, 27 and 30 and forms with these the second boom section 12. Accordingly, the connecting element 35 is remote from the boom section 12 End of the sub-boom sections 22, 25, 28 and 31 arranged and forms with these the third boom section 13.
  • Another connecting element 36 is disposed on the sub-boom sections 20, 23, 26 and 29 and between the connecting elements 32 and 33. On the connecting element 36, the hydraulic cylinder 10 is pivotally articulated.
  • the boom 9 is constructed symmetrically to the rocker W and has a designated as a heavy line and lying in the rocker plane W boom central longitudinal axis 37.
  • the sub-arms 16 to 19 correspondingly have associated sub-boom center longitudinal axes 38 to 41, which are arranged polygonal or square and symmetrical to the rocker plane W.
  • the sub-boom center longitudinal axes 38 to 41 are arranged in particular trapezoidal.
  • the boom central longitudinal axis 37 is located in the rocker plane W.
  • the sub-boom center longitudinal axes 38, 39 have perpendicular to the rocker W equal distances b 1 and b 2 and parallel to the rocker W equal distances h 1 and h 2 to the boom Center longitudinal axis 37 on.
  • the undercarriage 2 facing, lower part boom 16, 17 form an underside of the boom 9, whereas the side facing away from the undercarriage 2, upper part boom 18, 19 form an upper side of the boom 9.
  • the boom 9 has perpendicular to the rocker W a width B, which increases starting from the lower part arms 16, 17 in the direction of the upper part boom 18, 19 up to a maximum width B A. This is in Fig. 7 illustrated.
  • the partial boom sections 20 to 31 are designed as hollow cylinders and have a circular cross-section.
  • Fig. 7 illustrates the cross-sectional shape of the sub-boom sections 20, 23, 26 and 29 of the first boom section 11 and the position of these sub-boom sections 20, 23, 26 and 29 relative to each other and to the rocking plane W.
  • the sub-boom sections 20 and 23 have equal outside radii R 1 and R 2 , which are larger than the same outer radii R 3 and R 4 of the sub-boom sections 26 and 29.
  • the boom 9 thus has in the region of the boom section 11 a height or a maximum height H A , which results from the sum of R 1 , R 3 , h 1 and h 3 .
  • the boom 9 in the region of the boom section 11 has a width or a maximum width B A , which results from the sum of R 3 , R 4 , b 3 and b 4 .
  • adjacent partial boom sections 20 to 31 of each sub-boom 16 to 19 are guided into each other so as to be displaceable in the longitudinal direction L.
  • the boom sections 20, 23, 26 and 29 have perpendicular to the rocker W partial cross-sectional areas A 1 to A 4 , each resulting from the circular area with the associated outer radius R 1 to R 4 .
  • the cross-sectional area A A is in Fig.
  • the area moments of inertia provide a measure of the rigidity of the boom 9 relative to the respective bending forces. Due to the Steiner shares, the area moments of inertia are considerably increased compared to conventional cantilevers.
  • the connecting elements 32 to 36 are each essentially formed of a bottom plate or a lower connecting element part 42 facing away from the undercarriage 2 and an upper plate or an upper connecting element part 43 facing away from the undercarriage 2, which can be displaced relative to one another in the direction of the rocker plane W. and each other can be fixed.
  • the connecting elements 33 to 36 each have four passage openings 44 to 47 for the sub-boom sections 20 to 31 of the sub-boom 16 to 19, wherein the passage openings 44, 45 for the sub-boom 16, 17 respectively in the lower plate 42 and the passage openings 46, 47 for the sub-arms 18, 19 are each formed in the upper plate 43.
  • the lower plates 42 each have the upper part arms 18, 19 facing recesses 48, 49, in which the upper part boom 18, 19 are at least partially receivable.
  • the upper plates 43 each have the lower part arms 16, 17 facing recesses 50, 51, in which the lower part boom 16, 17 are at least partially receivable.
  • the connecting elements 32 to 36 each have a through opening 52 formed by the respective plates 42, 43, which form a cable guide channel 53 for guiding a supporting cable 54.
  • the support cable 54 is guided in a conventional manner from the free end of the boom 9 to a winch 55 arranged on the uppercarriage 3.
  • the support cable 54 is guided at the free end of the arm 9 via two deflection rollers 56, 57, which are rotatably supported by a support frame 58 at the free end of the arm 9.
  • the sub-arms 18 and 19 are displaceable relative to the sub-arms 16 and 17 parallel to the rocker plane W.
  • two hydraulic cylinders 59 are fixedly arranged thereon and connected to the upper plate 43 of the connecting element 32.
  • two hydraulic cylinders 60 which are connected to the upper plate 43 of the connecting element 33, are fastened at the end to the partial boom sections 20 and 23.
  • locking units 61 are provided for the displacement of the sub-arms 18, 19 and for fixing these sub-arms 18, 19 relative to the sub-arms 16, 17 .
  • two locking units 61 are arranged on a respective upper plate 43.
  • Each locking unit 61 has a locking pin 62 which is feasible for locking or unlocking in an associated locking hole 63.
  • the respective locking bolt 62 is hydraulically, pneumatically or electromechanically actuated, for example.
  • the respective guide pin 62 is slidably mounted on the respective upper plate 43, whereas the associated locking hole 63 is formed in the associated lower plate 42.
  • two associated locking holes 63 are formed for each locking pin 62, which serve for locking and unlocking of the plates 42, 43 in a retracted transport position and an extended operating position of the boom 9.
  • the locking units 61 are arranged on each of the connecting elements 32 to 35 and also on the connecting element 36.
  • the hydraulic cylinders 59, 60 and the locking units 61 of the boom 9 can be transferred from a transport position to an operating position and vice versa.
  • the cross-sectional area A and the height H A of the boom 9 is reduced compared to the operating position, whereby the mobile telescopic crane 1 has a smaller overall height.
  • the reduction of the overall height is required, for example, in order not to exceed a maximum permitted height in road traffic.
  • locking units 64 to 67 are provided, which are arranged in the region of the connecting elements 33 and 34.
  • the locking units 64 to 67 are directly mounted on the respectively associated connecting element 33, 34, so that adjacent partial boom sections 20 and 21, 21 and 22, 23 and 24, 24 and 25, 26 and 27, 27 and 28, 29 and 30 and 30 and 31 are mutually mechanically lockable end.
  • the locking units 64 to 67 each have two oppositely disposed locking pins 68 which are guided by respectively associated locking holes 69, 70.
  • the locking bolts 68 are hydraulically, pneumatically or electromechanically actuated, for example.
  • the Fig. 1 to 3 show the mobile telescopic crane 1 in the intended state for driving.
  • the boom 9 is in a fully retracted transport position.
  • the locking units 64 to 67 are unlocked and the boom sections 11 to 13 einteleskopiert.
  • the sub-arms 18 and 19 are completely lowered by means of the hydraulic cylinders 59, 60, so that the sub-arms 18, 19 in the recesses 48, 49 and the sub-arms 16, 17 are arranged in the recesses 50, 51.
  • the mobile telescopic crane 1 has the lowest possible total height, so that the maximum permitted height in the road is not exceeded.
  • Fig. 3 illustrates the transport position of the boom 9 based on a cross section through the boom section 13th
  • Fig. 4 and 5 show the mobile telescopic crane 1 in an operating position with the fully erected and austeleskop faced boom 9.
  • the locking elements 64 to 67 associated with the connecting elements 33 and 34 are also mechanically locked, so that the boom 9 has a high rigidity.
  • Fig. 6 shows a cross section through the belonging to the connecting element 34 locking units 64 to 67th
  • the boom 9 according to the invention has a high rigidity against bending forces perpendicular and parallel to the rocker plane W due to the high area moments of inertia. This can be achieved in relation to the weight of the boom 9, a significant increase in load capacity.
  • no separate transport and no complex assembly is required compared to a conventional boom with guy supports.
  • the sub-arms 16a to 19a of the boom 9a are arranged in the shape of a kite quadrangle.
  • the partial cross-sectional area A 1 of the sub-arm 16 a is greater than the respective partial cross-sectional area A 2 to A 4 .
  • the sub-arms 16a to 19a have a circular cross-section.
  • the boom 9a thus has in the region of the boom section 11a a maximum height H A , which results from the sum of R 1 , h 1 , h 4 and R 4 . Furthermore, the boom 9a in the region of the boom section 11a has a maximum width B A , which results from the sum of R 2 , b 2 , b 3 and R 3 .
  • the receiving space formed by the sub-boom 19a serves as a cable guide channel 53a.
  • the lower plates 42a of the connecting elements 33a to 35a each have a centrally arranged recess 48a, in which the uppermost part of the boom 19a is receivable.
  • the upper plates 43a each have a centrally disposed recess 50a, in which the lower part boom 16a is receivable.
  • the uppermost boom 19a can be displaced relative to the other partial arms 16a to 18a according to the first embodiment and fixed in the retracted transport position and the extended operating position by means of the locking units 16a.
  • the boom 9a and the boom sections 11a to 13a and the sub-boom sections 20a to 31a and the associated locking units 64a to 67a including the locking pin 68a and the associated locking holes 69a, 70a is referred to the first embodiment.
  • the following is based on the Fig. 14 and 15 A third embodiment of the invention described.
  • the partial boom 19b by means of the connecting elements 32b to 35b fixedly disposed on the sub-arms 16b to 18b and not displaceable relative to these. If this is the maximum allowable height of the mobile telescopic crane 1b is not exceeded, so a simplification of the structure of the boom 9b is possible.
  • the connecting elements 32b to 35b are fixedly arranged on the sub-arm 19b and are not constructed of mutually displaceable plates, the hydraulic cylinders 59a, 60a, the recesses 48a and 50a and the locking units 61a with the locking pin 62a and the associated locking holes 63a omitted.
  • the receiving space formed by the sub-boom 19b serves as a cable guide channel 53b.
  • boom 9b and the boom sections 11b to 13b and the boom sections 20b to 31b and the associated lock units 64b to 67b including the lock pins 68b and the associated lock holes 69b, 70b are formed in accordance with the second embodiment.
  • the features of the boom 9 to 9b are basically combined in any way to a boom according to the invention.
  • the boom 9 to 9b according to the invention further advantages over a conventional boom with guy supports on.
  • the booms 9 to 9b according to the invention can be optimized separately in each boom section 11 to 13b for the bending forces acting, so that they are received continuously along the boom 9 to 9b and not only at the end of the boom.
  • both the transfer of the boom 9 to 9b in the operating position and their operation is extremely simple.
  • the boom according to the invention allow 9 to 9b at a predefined weight a significant increase in load over conventional booms. In particular, a significantly easier handling of the boom 9 to 9b with respect to transport and installation or transfer to the operating position over conventional booms with guy supports is possible with the same load.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
EP11797252.1A 2010-12-17 2011-12-16 Mobil-teleskopkran Active EP2651812B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010063456 2010-12-17
PCT/EP2011/073024 WO2012080455A1 (de) 2010-12-17 2011-12-16 Mobil-teleskopkran

Publications (2)

Publication Number Publication Date
EP2651812A1 EP2651812A1 (de) 2013-10-23
EP2651812B1 true EP2651812B1 (de) 2014-12-03

Family

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EP11797251.3A Active EP2504267B1 (de) 2010-12-17 2011-12-16 Mobil-teleskopkran
EP11797252.1A Active EP2651812B1 (de) 2010-12-17 2011-12-16 Mobil-teleskopkran

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EP11797251.3A Active EP2504267B1 (de) 2010-12-17 2011-12-16 Mobil-teleskopkran

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US (2) US9637358B2 (ja)
EP (2) EP2504267B1 (ja)
JP (2) JP5953315B2 (ja)
CN (2) CN103261083B (ja)
DE (1) DE202011110230U1 (ja)
RU (2) RU2547492C2 (ja)
WO (2) WO2012080452A1 (ja)

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Also Published As

Publication number Publication date
WO2012080455A1 (de) 2012-06-21
EP2504267B1 (de) 2013-07-10
US20140158657A1 (en) 2014-06-12
JP5953315B2 (ja) 2016-07-20
US20150008206A1 (en) 2015-01-08
US9376292B2 (en) 2016-06-28
JP2013545691A (ja) 2013-12-26
RU2548652C2 (ru) 2015-04-20
RU2013125916A (ru) 2015-01-27
CN103261083A (zh) 2013-08-21
EP2504267A1 (de) 2012-10-03
JP2013545690A (ja) 2013-12-26
JP5934717B2 (ja) 2016-06-15
RU2013125915A (ru) 2015-01-27
WO2012080452A1 (de) 2012-06-21
DE202011110230U1 (de) 2013-02-13
US9637358B2 (en) 2017-05-02
CN103269970A (zh) 2013-08-28
EP2651812A1 (de) 2013-10-23
CN103261083B (zh) 2015-04-29
CN103269970B (zh) 2015-04-29
RU2547492C2 (ru) 2015-04-10

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