EP1911716B1 - Grue - Google Patents

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Publication number
EP1911716B1
EP1911716B1 EP07017698A EP07017698A EP1911716B1 EP 1911716 B1 EP1911716 B1 EP 1911716B1 EP 07017698 A EP07017698 A EP 07017698A EP 07017698 A EP07017698 A EP 07017698A EP 1911716 B1 EP1911716 B1 EP 1911716B1
Authority
EP
European Patent Office
Prior art keywords
travelling
crane
guides
articulations
head support
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
EP07017698A
Other languages
German (de)
English (en)
Other versions
EP1911716A2 (fr
EP1911716A3 (fr
Inventor
Peter Lerchenmüller
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.)
Hans Kuenz GmbH
Original Assignee
Hans Kuenz 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 Hans Kuenz GmbH filed Critical Hans Kuenz GmbH
Priority to PL07017698T priority Critical patent/PL1911716T3/pl
Publication of EP1911716A2 publication Critical patent/EP1911716A2/fr
Publication of EP1911716A3 publication Critical patent/EP1911716A3/fr
Application granted granted Critical
Publication of EP1911716B1 publication Critical patent/EP1911716B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B66C19/00—Cranes comprising trolleys or crabs running on fixed or movable bridges or gantries
    • B66C19/002—Container cranes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/16—Centre bearings or other swivel connections between underframes and bolsters or bogies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C5/00—Base supporting structures with legs
    • B66C5/02—Fixed or travelling bridges or gantries, i.e. elongated structures of inverted L or of inverted U shape or tripods
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C9/00—Travelling gear incorporated in or fitted to trolleys or cranes
    • B66C9/16—Travelling gear incorporated in or fitted to trolleys or cranes with means for maintaining alignment between wheels and track

Definitions

  • the invention relates to a crane, crane, comprising for traveling along rails a chassis with several chassis groups, each having at least two spaced apart in the longitudinal direction of the respective rail on a subframe rotatably mounted wheels, wherein a respective chassis group with a respective head carrier of the crane via a central joint, which has at least degrees of freedom for rotating the chassis group relative to the head support about a vertical axis and for pivoting the chassis group relative to the head support about a horizontal axis perpendicular to the rails, and further connected via two links which in the transverse direction of the seen on opposite sides of the central joint.
  • Landing gears of cranes movable on rails comprise at least two landing gear groups, each having at least one wheel for moving the crane and of which some or all are equipped with at least one drive motor for moving the crane.
  • a landing gear group is arranged on each of the four legs of a gantry crane.
  • the individual chassis groups with only one degree of freedom, namely a pivot about a horizontal axis transverse to the rails axis with a head support of the steel structure connected to the crane.
  • the pivot axis of the respective chassis group receiving holes in the head carrier must be very accurate, especially with regard to the axial position transverse to the road. These holes are interfaces between the mechanical engineering of the chassis group and the steel structure of the crane scaffolding, which have often proven to be problematic in practice.
  • An inclination of the axes can also be caused by solar radiation, which heats the head carrier unevenly, whereby the axis positions change.
  • a construction using a ball or roller slewing ring is technically perfect, but has a very large width and is very unfavorable in terms of cost.
  • the use of a likewise already known sliding bearing with an additional counter-holder for receiving tilting forces has the disadvantage that very large rotational resistances must be overcome.
  • the bearing forces can be, for example, 150 t or more. Due to the large tilting forces, especially in relieved cranial corners, in addition very elaborate countermounts are provided.
  • a central joint in the form of a spherical thrust bearing is provided for connecting the chassis group to the head carrier, which receives the support force.
  • the tilting forces resulting from the horizontal forces transverse to the rail are caused by tie rods, which are on both sides of the central joint between head carrier and suspension group are arranged, added.
  • the disadvantage here is, inter alia, that resulting from the tilting moment high bearing forces, since the tie rods can only absorb tensile forces.
  • a connection of a chassis group with a head carrier protrudes beyond a central joint, by means of which the chassis group can be pivoted relative to the head carrier about a horizontal axis lying at right angles to the rails.
  • a further exemplary embodiment shows a pivotable connection about a horizontal axis lying at right angles to the rails by means of arms which are arranged in a V-shaped manner and are mounted pivotably on the elements to be connected to each other about a horizontal axis lying at right angles to the rails.
  • the object of the invention is to provide a connection of the chassis groups of the crane chassis to the head carrier, wherein in an advantageous power transmission, a cost-effective design is achieved. According to the invention, this is achieved by a crane having the features of claim 1.
  • the central joint is formed according to the invention in the vertical direction as a floating bearing, i. no vertical forces are transmitted by him.
  • Vertical compressive and tensile forces are thus transmitted exclusively via the two handlebars, which are each connected on the one hand to the chassis group and on the other hand to the head carrier by superimposed joints.
  • these joints are in the form of spherical joints. Since the mobility with respect to the aligned parallel to the rail axis must be very small, it would for example also conceivable and possible to form the degree of freedom with respect to this lying parallel to the rail axis by a corresponding game of an axis perpendicular to the rail axis pivotable bearing or plain bearing ,
  • the central joint is in the form of a spherical joint.
  • the training with a first part of the joint, which has only one degree of freedom for pivoting about an axis perpendicular to the rail, and a second partial joint, which has only one degree of freedom for pivoting about a vertical axis.
  • a crane according to the invention can be designed, for example, in the form of a gantry crane.
  • a training in the form of a bridge crane is conceivable and possible, for example.
  • the crane is designed in the form of a gantry crane, which is mounted on one of two spaced-apart rails 1 formed roadway is movable.
  • a gantry crane usually has four legs 2, 3, 4, 5. Also constructions with three legs are known.
  • two supports can be provided.
  • the legs 2 - 5 or supports support the cross member 6 or 7, along which a trolley 8 is movable or which are provided with a different type of movable or fixed lifting device. In the case of training with two or more cross members 6, 7 run between these connection carrier. 9
  • a connecting this head carrier 10 is attached.
  • a head carrier 10 is also referred to as a "chassis carrier” or "moving beam”.
  • the head carrier 10 serve to connect the steel structure of the crane with the individual chassis groups 11 of the crane chassis. Below each of the legs 2 - 5, such a chassis group 1 is arranged.
  • Pro rail 1 are preferably at least two spaced apart in the longitudinal direction of the rail 1 chassis groups 11 are present. An arrangement below a respective leg 2 - 5 is preferred.
  • a respective chassis group 11 has eight wheels 12 which are spaced apart from one another in the longitudinal direction of the rails 1.
  • the axes 13 of the wheels 12 are aligned at right angles to the rails 1.
  • a respective wheel 12 may have two spaced apart in the transverse direction of the rail 1 connected by an axis 13 flanges 14, 15, as shown in Fig. 1 is indicated schematically.
  • the two rockers 17 are connected to a common rocker 19, wherein they are each pivotable relative to the rocker 19 about a horizontal, perpendicular to the rail 1 axis 20.
  • drive motors 21 which drive the respective wheels 12.
  • more or fewer such drive motors 21 may be present.
  • the respective head carrier 10 is connected to the respective chassis group 11 in a manner such that the chassis group 11 is pivotable relative to the head carrier 10 about a horizontal, at right angles to the respective rail 1 axis and is rotatable about a vertical axis.
  • a connecting device is provided, which has a central joint 22. This has at least the following degrees of freedom: a degree of freedom for rotating the chassis group 11 relative to the head carrier 10 about a vertical axis 23 and a degree of freedom for pivoting the chassis group 11 relative to the head carrier 10 about a horizontal, in particular perpendicular to the respective rail 1 lying horizontal axis 24th
  • the central joint 22 comprises a bearing pin 25 connected to the rocker 19, a bearing bush 26 connected to the head support 10, an inner ring 27 arranged on the bearing journal 25 with a spherical or spherical outer surface and an outer ring 28 arranged in the bearing bush 26 with a spherical or spherical segment-shaped inner surface which cooperates with the spherical outer surface of the inner ring 27.
  • the joint could also be arranged "reversed", ie the bearing pin 25 with the head carrier 10 and the bearing bush 26 connected to the rocker 19.
  • the central joint 22 is formed in the vertical direction as a floating bearing, i. has a game in this direction in the assembled state. Thus, no vertical forces are transmitted from this central joint 22. By contrast, forces acting in the horizontal direction are transmitted, both in the direction of the respective rail 1 and at right angles thereto.
  • a respective connecting device between the respective head carrier 10 and the respective chassis group 11 comprises two arms 29, 30, which are arranged on both sides of the central joint 22 in the direction at right angles to the rail 1.
  • Each of the two links 29, 30 is hinged to both the head carrier 10 and the rocker 19.
  • These superimposed joints 31, 32 of the links 29, 30 are in this case designed such that both pressure and tensile forces between the respective head support 10 and the respective chassis group 11 can be transmitted via the links 29, 30.
  • these joints 31, 32 have at least the following degrees of freedom: a degree of freedom for pivoting the respective link 29, 30 both relative to the head support 10 and to the rocker 19 about an axis 33 perpendicular to the respective rail 1 and a degree of freedom for pivoting the respective Handlebar 29, 30 both with respect to the head support 10 and with respect to the chassis group 11 about a horizontal axis 34 lying parallel to the respective rail 1.
  • the joints 31, 32 are in this case in the form of spherical joints or ball joints.
  • a bearing pin 35 is held, on which an inner ring 36 is arranged with a spherical or ball-shaped outer surface.
  • An outer ring 37 with a spherical or spherical section-shaped Inner surface which cooperates with the spherical outer surface of the inner ring 36 is disposed in a respective bore of the handlebar 29, 30.
  • a zero position shown in the figures of a respective chassis group 11 with respect to a rotation about the vertical axis 23 are the two joints 31, 32 of a respective arm 29, 30 exactly vertically above the other.
  • the links 29, 30 are straight and their longitudinal axes are aligned in the zero position in the vertical direction.
  • the joints 31, 32 of a respective arm 29, 30 are thus no longer exactly one above the other vertically.
  • the required angles of rotation about the vertical axis 23 and thus the deviations from the vertical orientation of the joints 31, 32 are very small.
  • the connecting lines between the superimposed hinges 31, 32 in all angular positions of the occurring angular range of rotation about the vertical axis 23 are inclined less than 5 °, preferably less than 3 ° with respect to the vertical. In practice, this angle is usually less than 1 °.
  • a deviation from the zero position results in a reduction of the vertical play in the central joint 22, depending on the angle of rotation about the vertical axis 23.
  • the vertical play in the central joint is dimensioned so that it reaches the maximum intended angle of rotation about the vertical axis 23 remains.
  • the links 29, 30 pivot about the horizontal axes 33 of the joints 31, 32.
  • the horizontal axes 33 of the joints 31, 32 are parallel to the horizontal axis 24 of the central Joint 22.
  • the respective chassis group 11 can be rotated relative to the respective head carrier 10 about the vertical axis 23 by at least 1 °.
  • a respective link 29, 30 relative to the respective rocker 19 about the right angle to the rail 1 horizontal axis 33 of the joint 32 to be pivoted by at least 3 °.
  • a respective link 29, 30 relative to the respective rocker 19 about the horizontal axis 34 of the joint 32 lying parallel to the rail 1 can be pivoted by at least 1 °.
  • a respective link 29, 30 relative to the respective head support 10 about the horizontal axis 34 of the joint 31 lying parallel to the rail 1 can be pivoted by at least 1 °.
  • a landing gear assembly according to the invention may also include more or fewer than eight spaced wheels 12 in the direction of travel, wherein at least two spaced apart in the longitudinal direction of the respective rail, on a common subframe 16 rotatably mounted wheels are present.
  • the central joint 22 may be arranged directly between this subframe and the head carrier and the lower joints 32 of the handlebars 29, 30 may also be arranged directly on the subframe.
  • two wheels can be rotatably mounted on a respective subframe and the subframe be connected in the manner described with a rocker 17.
  • the central joint 22 could in this case be arranged directly between the head carrier 10 and this rocker and the lower joints 32 of the links 29, 30 directly between the links 29, 30 and this rocker.
  • FIGS. 7 and 8 Another embodiment of the invention is shown schematically in FIGS. 7 and 8 shown. The differences from the previously described embodiment will be explained below. Incidentally, the training may be the same or analogous as previously described.
  • the links 29, 30 at least without external forces acting on the crane and in an intermediate position of the lifting device of the crane only loaded on pressure, while the load in the embodiment according to the FIGS. 7 and 8 done on train.
  • the joints 31 are for connection to the head support 10 above the joints 32 for connection to the landing gear group 11).
  • this downwardly projecting connecting portions 38 On both sides of a part of the chassis group 11, here the rocker 17, such a connecting portion 38 extends downwards.
  • the connecting portions 38 each carry a joint 31 for articulation of the respective link 29, 30th
  • the connecting sections 38 may, for example, be U-shaped as shown, having two vertical legs 38a, 38b spaced from each other in the longitudinal direction of the rail 1, extending from an overlying portion 39 of the head carrier 10 and at their lower ends by a horizontal web 38c connected to each other. At this web 38 c, the joint 31 is attached.
  • Other embodiments of the connecting portions 38 may be provided. For example, these may also be continuous plate-shaped.
  • the landing gear group 11 is shown with four spaced apart in the direction of travel wheels 12, wherein two wheels 12 are rotatably mounted on a common subframe 16 and the two subframe 16 are pivotally connected to a rocker 17 (in an analogous manner as in the embodiment described above).
  • a training with eight wheels as in the embodiment of Fig. 1 to 6 could be provided.
  • a different number of wheels 12 could be provided, in turn, at least two spaced apart in the direction of travel, on a common subframe 16 rotatably mounted wheels 12 are present.
  • chassis groups of a bridge crane could be connected to a head carrier of the steel structure of the crane.

Claims (7)

  1. Grue qui, pour le déplacement sur une file de rails (1), comporte un train de roulement avec plusieurs groupes de trains de roulement (11), qui comportent chacun au moins deux roues (12), situées à distance l'une de l'autre dans la direction longitudinale des rails (1) respectifs et montées rotatives sur un faux-châssis (16), un groupe de trains de roulement (11) respectif étant relié à un support de tête (10) respectif de la grue par l'intermédiaire d'une articulation centrale (22), qui possède au moins des degrés de liberté pour la rotation du groupe de trains de roulement (11) par rapport au support de tête (10) autour d'un axe vertical (23), ainsi que pour le pivotement du groupe de trains de roulement (11) par rapport au support de tête (10) autour d'un axe horizontal (24), situé perpendiculairement aux rails (1), et en outre par l'intermédiaire de deux bielles (29, 30) qui, par référence à la direction transversale des rails (1) respectifs, sont disposées sur des côtés face à face de l'articulation centrale (22), caractérisée en ce que l'articulation centrale (22) est réalisée sous forme de palier fou dans la direction verticale, sachant que seules des forces horizontales peuvent être transmises par ladite articulation centrale (22),
    et en ce que les bielles (29, 30), disposées sur des côtés face à face de l'articulation centrale (22), sont reliées chacune, d'une part, au groupe de trains de roulement (11) et, d'autre part, au support de tête (10) par des articulations (31, 32) disposées l'une au-dessus de l'autre, par lesquelles peuvent être transmises tant des forces de pression que des forces de traction, et lesquelles comportent au moins des degrés de liberté pour le pivotement des bielles (29, 30) par rapport au groupe de trains de roulement (11) ou par rapport au support de tête (10) autour d'un axe horizontal (33), situé perpendiculairement aux rails (1) respectifs, et autour d'un axe horizontal (34) situé parallèlement aux rails (1) respectifs.
  2. Grue selon la revendication 1, caractérisée en ce que l'articulation centrale (22) est réalisée sous la forme d'une articulation sphérique.
  3. Grue selon la revendication 1 ou 2, caractérisée en ce que les deux articulations (31, 32) de chaque bielle (29, 30) sont disposées verticalement l'une au-dessus de l'autre dans une position neutre du pivotement de l'articulation centrale (22) autour de l'axe vertical (23).
  4. Grue selon l'une quelconque des revendications 1 à 3, caractérisée en ce que les deux articulations (31, 32) de chaque bielle (29, 30) présentent, par rapport à une position verticale superposée, une divergence de 5°, de préférence inférieure à 3°, dans toutes les positions de pivotement de l'articulation centrale (22) autour de l'axe vertical (23).
  5. Grue selon l'une quelconque des revendications 1 à 4, caractérisée en ce que les bielles (29, 30) sont réalisées droites.
  6. Grue selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les articulations (31, 32), par lesquelles les bielles (29, 30) sont reliées au groupe de trains de roulement (11) respectif et au support de tête (10) respectif, sont réalisées sous la forme d'articulations sphériques.
  7. Grue selon l'une quelconque des revendications 1 à 6, caractérisée en ce que les bielles (29, 30) sont articulées, par l'intermédiaire de leurs articulations inférieures (32), contre un bras oscillant (19, 17), qui est porté, directement ou par l'intermédiaire d'au moins un autre bras oscillant (17), par le faux-châssis (16), ou en ce que les bielles (29, 30) sont articulées par l'intermédiaire de leurs articulations inférieures (32) au faux-châssis (16) respectif.
EP07017698A 2006-10-09 2007-09-11 Grue Active EP1911716B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07017698T PL1911716T3 (pl) 2006-10-09 2007-09-11 Dźwig

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006047997A DE102006047997A1 (de) 2006-10-09 2006-10-09 Kran

Publications (3)

Publication Number Publication Date
EP1911716A2 EP1911716A2 (fr) 2008-04-16
EP1911716A3 EP1911716A3 (fr) 2009-08-26
EP1911716B1 true EP1911716B1 (fr) 2010-05-19

Family

ID=38904589

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07017698A Active EP1911716B1 (fr) 2006-10-09 2007-09-11 Grue

Country Status (5)

Country Link
US (1) US7793594B2 (fr)
EP (1) EP1911716B1 (fr)
AT (1) ATE468297T1 (fr)
DE (2) DE102006047997A1 (fr)
PL (1) PL1911716T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2832678A1 (fr) 2013-07-30 2015-02-04 Hans Künz GmbH Ensemble de mécanisme sur rail

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DE102006047997A1 (de) * 2006-10-09 2008-04-10 Hans Künz GmbH Kran
AT507333B1 (de) * 2008-10-09 2011-09-15 Hans Kuenz Ges M B H Portalkran
CN101934941A (zh) * 2010-08-17 2011-01-05 李燕飞 车载遥控式铁道便梁快速装卸机
CN102275825A (zh) * 2011-06-30 2011-12-14 中船江南重工股份有限公司 一种大型龙门起重机自动纠偏装置
CN102409612B (zh) * 2011-08-16 2013-09-18 中铁十七局集团第二工程有限公司 横跨既有铁路线的悬臂龙门吊转换平台架梁工艺
CN102320523B (zh) * 2011-08-17 2013-04-17 大连博瑞重工有限公司 带有折线形刚性腿的造船门式起重机
CN103204434B (zh) * 2012-01-11 2014-08-20 上海振华重工(集团)股份有限公司 船厂龙门式起重机的刚性腿纠偏复位方法
US9062419B2 (en) 2013-03-12 2015-06-23 Konecranes Plc Rail system for jacking tower
CN104370217B (zh) * 2013-08-12 2017-04-19 湖北鄂南起重运输机械有限公司 一种桥梁板面铺设用门式起重机
CN103663159A (zh) * 2013-12-31 2014-03-26 太原重工股份有限公司 一种具有分载结构的起重机
CN104528535A (zh) * 2015-01-18 2015-04-22 河南省路港起重机有限公司 单主梁小车门式起重机
GB201503159D0 (en) * 2015-02-25 2015-04-08 Fosbel Inc Methods and apparatus for constructing glass furnace structures
US20160332846A1 (en) * 2015-05-13 2016-11-17 Mi-Jack Products, Inc. Uniform footprint multi-wheel end truck for a crane
CN105600684A (zh) * 2016-03-29 2016-05-25 苏州倍特罗智能科技有限公司 一种桥式起重机
CN106241614B (zh) * 2016-09-28 2018-11-13 山东大学 一种盾构机装配与出渣两用龙门吊
CN106744349B (zh) * 2017-02-13 2018-07-06 金祝英 一种可全方位起吊的起重机
CN106882709B (zh) * 2017-03-23 2018-03-30 合肥迅达电器有限公司 一种防打结的电动单梁起重机
CN107381366B (zh) * 2017-08-04 2019-01-11 合力叉车有限公司 汽修用轮毂摆放架
CN107585680A (zh) * 2017-10-21 2018-01-16 黄河勘测规划设计有限公司 小行程多工位起升小车行走驱动方法
CN109835809A (zh) * 2019-02-28 2019-06-04 安徽恒源煤电股份有限公司五沟煤矿 一种安装拆除硐室用的起吊行车及其起吊方法
CN113479769B (zh) * 2021-06-16 2022-03-04 中国矿业大学 一种基于内棘轮机构的单轨吊双向防溜车装置

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2832678A1 (fr) 2013-07-30 2015-02-04 Hans Künz GmbH Ensemble de mécanisme sur rail

Also Published As

Publication number Publication date
DE502007003831D1 (de) 2010-07-01
EP1911716A2 (fr) 2008-04-16
US20080083688A1 (en) 2008-04-10
EP1911716A3 (fr) 2009-08-26
ATE468297T1 (de) 2010-06-15
PL1911716T3 (pl) 2010-10-29
DE102006047997A1 (de) 2008-04-10
US7793594B2 (en) 2010-09-14

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