EP1031531A2 - Grue à porteé variable - Google Patents

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Publication number
EP1031531A2
EP1031531A2 EP99125403A EP99125403A EP1031531A2 EP 1031531 A2 EP1031531 A2 EP 1031531A2 EP 99125403 A EP99125403 A EP 99125403A EP 99125403 A EP99125403 A EP 99125403A EP 1031531 A2 EP1031531 A2 EP 1031531A2
Authority
EP
European Patent Office
Prior art keywords
luffing
crane
jib
luffing jib
pivot axis
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.)
Withdrawn
Application number
EP99125403A
Other languages
German (de)
English (en)
Other versions
EP1031531A3 (fr
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.)
MAN Wolffkran GmbH
Original Assignee
MAN Wolffkran GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Wolffkran GmbH filed Critical MAN Wolffkran GmbH
Publication of EP1031531A2 publication Critical patent/EP1031531A2/fr
Publication of EP1031531A3 publication Critical patent/EP1031531A3/fr
Withdrawn legal-status Critical Current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
    • B66C23/82—Luffing gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • B66C23/72—Counterweights or supports for balancing lifting couples
    • B66C23/74—Counterweights or supports for balancing lifting couples separate from jib
    • B66C23/76—Counterweights or supports for balancing lifting couples separate from jib and movable to take account of variations of load or of variations of length of jib
    • 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
    • B66C23/88—Safety gear
    • B66C23/92—Snubbers or dashpots for preventing backwards swinging of jibs, e.g. in the event of cable or tackle breakage

Definitions

  • the invention relates to a luffing crane.
  • Construction cranes are usually designed as tower cranes on which Horizontal jib for the horizontal load shifting of a trolley is led.
  • the crane swept by the jib Be free of obstacles.
  • a crane tower In the Steep position is the radial extension of that swept by the boom Rotation range very small, so that obstacles lying radially outside can be avoided.
  • the luffing jib has one in its Length adjustable cable system to one arranged at the crane base Tensioned winch.
  • the problem with such rocker drives is the determination of the steep end position of the luffing jib if unintentional Fold back the raised luffing jib with safety should be prevented. This is especially true if the superscript The luffing jib is still exposed to wind forces.
  • the luffing jib of which is simple and precise on its End positions, in particular on the steep position is adjustable.
  • the invention is based on a luffing crane with a crane base, one between a flat position and a steep position pivotable on the Crane base mounted luffing jib and one in a first articulated connection at a distance from the swivel axis of the luffing jib on the Crane base and in a second articulation at a distance from the Swivel axis on the luffing jib attacking luffing drive and is thereby characterized in that the seesaw drive has at least one between the two Piston-cylinder hydraulic power unit attacking articulated connections having.
  • the position of the piston is determined in its retracted position and in its extended position immediately the position of the luffing jib, with which the steep position and the Flat position of the luffing jib can be defined mechanically without that it needs to be adjusted limit switch or the like.
  • Conveniently is the one above the swivel axis of the luffing jib Hydraulic power device both tensile and compressive with the Crane base and the luffing jib connected. This can cause wind power Fold up the luffing jib or even fold back over the Steep position can be prevented.
  • an information signal which more or less accurately represents the magnitude of the load torque.
  • the deviation, with which the hydraulic pressure represents the load torque be kept comparatively small if the distance of the first Articulated connection from the swivel axis of the luffing jib by less than 20%, but preferably less than 10% larger than that vertical distance of the connecting line of the two articulated connections from this pivot axis.
  • the Line of action of the hydraulic power device is substantially tangential a circle around the pivot axis of the luffing jib with the result that the force exerted by the power device on the luffing jib and accordingly the hydraulic pressure in the power unit proportional to the load torque of the luffing jib.
  • the luffing crane is preferably a tower luffing crane, at which the crane base a crane tower and one the luffing jib counter jib protruding from the upper end of the crane tower has, on which the luffing jib in turn pivotable is stored.
  • the hydraulic power device is advantageously above
  • the pivot axis of the luffing jib is arranged and connects the luffing jib with the counter jib.
  • it is one Tower luffing crane can also be a top-slewing crane but a rotating tower luffing crane for reasons of easier and dismantling in construction crane operation preferred.
  • the counter jib is expediently approximately parallel to the Pivot axis extending pivot axis pivotable with the Crane tower connected and anchored to the lower end of the crane tower.
  • effective stops are provided on the counter jib and the crane tower. These stops prevent the luffing jib in the steep position in case of wind load, it tilts backwards together with the counter jib.
  • the crane base is usually on the side facing away from the luffing jib
  • a counterweight body is arranged on the side of its pivot axis.
  • this counterweight body is transverse to Swivel axis movably guided and with the luffing jib over a Coupled drive connection, such that the counterweight body in the Steep position of the luffing jib is closer to the swivel axis than in the flat position.
  • the weight of the counterweight body can be done in this way reduce.
  • the counterweight body is attached Leadership of the crane base with increasing approach of the luffing jib down to the steep position in the vertical direction shifted.
  • the one via the drive connection which is preferably a mechanical drive connection, in particular a cable connection acts, provides counterweight body connected to the luffing jib at least approximately for a compensation of the luffing jib Cantilever torque rotating flat and thus that of the Hydraulic power device to be applied when lifting the luffing jib Powers.
  • the conditions can be such that the luffing jib and the counterweight body mechanically coupled with it with respect to the swivel axis of the luffing jib almost in equilibrium are and accordingly only of the hydraulic power device additional forces required to lift the load are provided have to.
  • the counterweight body When guiding the counterweight body, it can be lever or Act handlebars.
  • the guide is designed as an inclined surface guide, along the the counterweight body between one of the flat positions of the Upper luffing jib assigned to the swivel axis Position and one of the steep position of the luffing jib assigned to the Swivel axis closer lower position is movable.
  • the counterweight body is attached to both the upper counter jib, but also in the area of the lower end of the tower on a platform of the Slewing gear can be arranged.
  • FIG. 1 shows a construction crane in the form of a rotating tower crane.
  • the Crane has a stationary, but possibly mobile lower platform 1, on which an upper platform 3 by means of a rotating mechanism 5 vertical axis of rotation 7 is rotatably mounted.
  • On the upper platform 3 is a tower 9 designed as a tube or lattice structure is attached to the its upper end one between a flat position (shown with solid lines) and a steep position (shown with dash-dotted lines Lines) about a horizontal pivot axis 11 pivoting luffing jib 13 wears.
  • the radius of the crane changes, i.e.
  • the end of the Luffing jib 13 in a joint forming the pivot axis 11 a counter jib 15 mounted, which in turn about a to the pivot axis 11 parallel folding axis 17 articulated on the upper end of the Tower 9 is stored.
  • the counter jib 15, like the luffing jib 13, can be designed as a framework or lattice construction, is opposite to the luffing jib in relation to the pivot axis 11 13 and is via a guy 19 to the upper platform 3 braced.
  • the upper platform 3 carries on the rest of the tower 9th opposite side of the axis of rotation 7 a counterweight body 21, the Weight is such that it is in the flat position of the crane Keep the luffing jib 13 in balance at the maximum permissible load can. Stops 23 assigned to one another at the upper end of the tower 9 on the one hand and on the counter jib 15 on the other hand prevent the Counter jib 15 to the side of the guying 19 around the folding axis 17 folds around, for example when the luffing jib 13 in its Steep position is exposed to a wind load from the front, through which the Guy 19 would otherwise be claimed for pressure.
  • a hydraulic power device 29 in Form of a double-acting hydraulic cylinder built in so that that between the hinge connections 25, 27 both compressive forces can also absorb tensile forces.
  • the power device 29 has a cylinder 31, which at the same time end stops for a displaceable in the cylinder 31 Piston 33 forms.
  • the construction is such that the piston 33 in its one end position, here its extended end position Flat position of the luffing jib 13 defines and in its other End position, here its retracted end position, the steep end position of the Jib boom 13 sets. Additional limit switches for operation are not mandatory; the end position is due to the mechanical construction of the strength device 29 determined. Since the power device 29 also in the steep position Can absorb pressure forces, it also prevents the folding Luffing jib beyond the steep end position, for example when there is a wind load.
  • the force device 29 is individual Piston-cylinder unit shown. It is understood that several such units can be provided working in parallel to each other. Multiple piston-cylinder units can also be used to increase the stroke Row be arranged.
  • the crane construction is designed for a predetermined maximum load moment on the luffing jib.
  • the load that can be attached to the crane hook 14 is in a predetermined position range of the luffing jib 13 in the area of its flat position inversely proportional to the outreach of the luffing jib 13, ie the distance of the load hook 14 from the axis of rotation 7 of the crane.
  • the maximum load moment M is shown as a hyperbolic limit curve of the load L as a function of the projection s.
  • the maximum load capacity of the crane is determined not by the load moment M but by a line of constant maximum load L max .
  • the limit curve determined by M constant and L max must not be exceeded during the operation of the crane and what is monitored by suitable monitoring circuits.
  • force measuring devices are provided on the crane hook 15 or on the lifting mechanism of the crane, not shown in any more detail. In principle, the load moment monitoring in the flat position of the luffing jib could also be monitored by force measuring devices of this type, which operate depending on the luffing angle of the luffing jib.
  • suitable dimensioning of the kinematics of the power device 29 ensures that the hydraulic pressure in the power device 29 is at least approximately a measure of the load torque.
  • the distance between one of the articulated connections 25 or 27, here the articulated connection 27 of the counter jib 15, from the pivot axis 11 is only slightly larger than the vertical distance of the pivot axis 11 from the connecting line of the two articulated connections 25, 27, ie only slightly larger is the moment arm of the direction of force of the force device 29.
  • the moment arm changes only slightly depending on the momentary outreach of the luffing jib 13 and accordingly the load moment curve M is approximated by a curve of constant hydraulic pressure F shown in dashed lines in FIG.
  • a pressure limit indicator is indicated at 35 in FIG. 2; the limit transmitter 35 can, however, also be provided at any suitable point in the hydraulic generating system, provided that it is ensured that a pressure representing the pressure in the hydraulic power device 29 is detected.
  • Figure 3 several luffing positions of the luffing jib 13 are shown. The illustration shows that at a distance of the joint suspension 27 from the pivot axis 11, which in the flat position is less than 10% of the vertical distance of the pivot axis 11 from the line of action of the force device 29, the load torque constant by less than 10% from a curve Hydraulic pressure deviates.
  • the crane explained above is a rotating tower crane. It is understood that the principles of the invention can also be used with an overhead rotating tower crane.
  • FIGS. 5 and 6 show an overhead rotating tower crane Luffing jib 13a in the flat position of luffing jib 13a (FIG. 5) and in a position approximating the steep position (FIG. 6).
  • the luffing jib 13a is in turn in a swivel joint 11a Counter jib 15a rockable about a horizontal pivot axis, and the Counter jib 15a is in turn by means of one indicated at 5a Slewing gear rotatable about a vertical axis 7a.
  • For the rocker drive is again a piston-cylinder hydraulic power device 29a between one Articulated connection 25a of the luffing jib 13a on the one hand and an articulated connection 27a of the counter jib 15a connected on the other hand.
  • the Counterweight body 21 a In contrast to the embodiment of Figures 1 and 2 is the Counterweight body 21 a not stationary, i.e. with fixed radial Distance to the axis of rotation 7a, arranged, but along an oblique guide 37 of the counter jib 15a can be moved.
  • the inclined guide 37 is of the Axis of rotation 7a directed radially away and increases with increasing distance from the axis of rotation 7a.
  • a pull rope 41 guided over deflection rollers 39 connects the counterweight body 21 a with the luffing jib 13a in the Way that the counterweight body 21a in the flat position of the The luffing jib 13a has a maximum distance from the axis of rotation 7a and itself is in its highest position.
  • the steep position of the luffing jib 13a approaches Counterweight body 21a of the axis of rotation 7a with simultaneous lowering on.
  • the counterweight body 21a forms a balance weight, which is the own weight of the luffing jib 13a at least partially compensated. Since the counterweight body 21 a with growing Approach of the luffing jib 13a at its steep position Axis of rotation 7a approaches, it is also achieved that the overall center of gravity of the crane regardless of the luffing position of the luffing jib 13a remains at least approximately stationary with respect to the axis of rotation 7a. This benefits the stability of the crane and allows use lighter counterweight body.
  • FIGS. 5 and 6 show a variant of a luffing crane with radial to the axis of rotation movable counterweight body.
  • FIGS. 5 and 6 are a rotating tower crane, similar to the tower crane of Figures 1 and 2.
  • the counterweight body 21 b is in turn on a radially extending to the axis of rotation 7b and inclined guide 37b of the upper, rising from the axis of rotation 7b the tower 3b supporting platform 3b movable and via a rope 41b, the via deflection rollers 39b of the platform 3b or the counter-jib 15b is guided, tensile connected to the luffing jib 13b.
  • the counterweight body 21b for balancing the luffing jib 13b while largely maintaining the overall focus of the crane.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
EP99125403A 1999-02-26 1999-12-20 Grue à porteé variable Withdrawn EP1031531A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1999108485 DE19908485A1 (de) 1999-02-26 1999-02-26 Wippkran
DE19908485 1999-02-26

Publications (2)

Publication Number Publication Date
EP1031531A2 true EP1031531A2 (fr) 2000-08-30
EP1031531A3 EP1031531A3 (fr) 2004-06-16

Family

ID=7899047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99125403A Withdrawn EP1031531A3 (fr) 1999-02-26 1999-12-20 Grue à porteé variable

Country Status (2)

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EP (1) EP1031531A3 (fr)
DE (1) DE19908485A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1749790A3 (fr) * 2005-08-01 2008-01-23 Liebherr-Werk Biberach GmbH Système pour régler une flèche de grue relevable
FR2909366A1 (fr) * 2006-12-04 2008-06-06 Mobilev Engin de levage
DE102010008155A1 (de) * 2010-02-16 2011-08-18 Wolffkran Holding Ag Wippausleger-Turmkran
ES2374015A1 (es) * 2009-02-05 2012-02-13 Linden Comansa, S.L. Grúa torre sin cúspide.
WO2013078813A1 (fr) * 2011-11-30 2013-06-06 湖南三一智能控制设备有限公司 Limiteur de moment anti basculement vers l'arrière pour une flèche
WO2013178480A1 (fr) * 2012-05-31 2013-12-05 Wolffkran Holding Ag Dispositif électrohydraulique pour la commande d'une flèche
CN104071710A (zh) * 2014-07-01 2014-10-01 徐工集团工程机械股份有限公司 一种起重机及其无级变幅副臂装置
CN109678070A (zh) * 2019-02-22 2019-04-26 沈阳建筑大学 一种动臂塔式起重机移动配重实现机构
CN116290993A (zh) * 2022-05-18 2023-06-23 国网山西送变电工程有限公司 摇臂与平臂通用型抱杆

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7967158B2 (en) 2006-10-27 2011-06-28 Manitowoc Crane Companies, Llc Mobile lift crane with variable position counterweight
US9278834B2 (en) 2009-08-06 2016-03-08 Manitowoc Crane Group, LLC Lift crane with moveable counterweight
DE102012010760A1 (de) 2012-05-31 2013-12-05 Wolffkran Holding Ag Elektrohydraulische Vorrichtung mit Drehstromasynchronmotor zur Verstellung eines Ausleger
US10183848B2 (en) 2014-01-27 2019-01-22 Manitowoc Crane Companies, Llc Height adjustment mechanism for an auxiliary member on a crane
WO2015113048A1 (fr) 2014-01-27 2015-07-30 Manitowoc Crane Companies, Llc Grue de levage à contrepoids mobile amélioré
DE102020107417A1 (de) 2020-03-18 2021-09-23 Liebherr-Werk Biberach Gmbh Turmkran mit verstellbarem Gegenballast

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1091725B (de) * 1958-06-06 1960-10-27 Gerhard Wiese Wippkran mit horizontalem Lastweg
US3149730A (en) * 1962-06-08 1964-09-22 Bucyrus Erie Co Convertible crane
DE2461773C2 (de) * 1974-12-30 1982-09-30 Grisebach, Hans-Theodor, 4750 Unna Stellgerät als einbaufähige Baueinheit mit Spindelmuttertrieb
DE3545185C1 (en) * 1985-12-20 1987-07-23 Krupp Gmbh Luffing-crane jib
EP0708053A1 (fr) * 1994-08-26 1996-04-24 Hiab Export A/S Système de protection contre la surcharge pour grues hydrauliques à flèche, spécialement celles montées sur des véhicules à moteur
GB2326629A (en) * 1997-06-26 1998-12-30 Baesema Ltd Nuclear Safety Crane with Extendible Boom and Isolation from Seismic Loading

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1749790A3 (fr) * 2005-08-01 2008-01-23 Liebherr-Werk Biberach GmbH Système pour régler une flèche de grue relevable
FR2909366A1 (fr) * 2006-12-04 2008-06-06 Mobilev Engin de levage
EP1953112A1 (fr) * 2006-12-04 2008-08-06 Mobilev Engin de levage
ES2374015A1 (es) * 2009-02-05 2012-02-13 Linden Comansa, S.L. Grúa torre sin cúspide.
US8955702B2 (en) 2010-02-16 2015-02-17 Wolffkran Holding Ag Luffing-jib tower crane with jib angle error control
DE102010008155B4 (de) * 2010-02-16 2013-02-28 Wolffkran Holding Ag Wippausleger-Turmkran
DE102010008155A1 (de) * 2010-02-16 2011-08-18 Wolffkran Holding Ag Wippausleger-Turmkran
WO2013078813A1 (fr) * 2011-11-30 2013-06-06 湖南三一智能控制设备有限公司 Limiteur de moment anti basculement vers l'arrière pour une flèche
WO2013178480A1 (fr) * 2012-05-31 2013-12-05 Wolffkran Holding Ag Dispositif électrohydraulique pour la commande d'une flèche
US9873596B2 (en) 2012-05-31 2018-01-23 Wolffkran Holding Ag Electro-hydraulic device for moving a jib
CN104071710A (zh) * 2014-07-01 2014-10-01 徐工集团工程机械股份有限公司 一种起重机及其无级变幅副臂装置
CN109678070A (zh) * 2019-02-22 2019-04-26 沈阳建筑大学 一种动臂塔式起重机移动配重实现机构
CN109678070B (zh) * 2019-02-22 2024-01-30 沈阳建筑大学 一种动臂塔式起重机移动配重实现机构
CN116290993A (zh) * 2022-05-18 2023-06-23 国网山西送变电工程有限公司 摇臂与平臂通用型抱杆

Also Published As

Publication number Publication date
EP1031531A3 (fr) 2004-06-16
DE19908485A1 (de) 2000-08-31

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