EP2331446A1 - Grue à portique - Google Patents

Grue à portique

Info

Publication number
EP2331446A1
EP2331446A1 EP09740248A EP09740248A EP2331446A1 EP 2331446 A1 EP2331446 A1 EP 2331446A1 EP 09740248 A EP09740248 A EP 09740248A EP 09740248 A EP09740248 A EP 09740248A EP 2331446 A1 EP2331446 A1 EP 2331446A1
Authority
EP
European Patent Office
Prior art keywords
gantry crane
chassis
rail
group
vertical 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.)
Granted
Application number
EP09740248A
Other languages
German (de)
English (en)
Other versions
EP2331446B1 (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.)
HANZ 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 PL09740248T priority Critical patent/PL2331446T3/pl
Publication of EP2331446A1 publication Critical patent/EP2331446A1/fr
Application granted granted Critical
Publication of EP2331446B1 publication Critical patent/EP2331446B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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 gantry crane, which has a serving for moving the gantry crane along a rectilinear, formed by parallel rails roadway, which comprises a plurality of chassis groups, each having at least two spaced apart in the longitudinal direction of the respective rail on a subframe rotatably mounted wheels and of which at least two, preferably all, are rotatably connected to a head support of the gantry about a vertical axis, wherein for at least one of the associated head carrier about the vertical axis rotatably connected chassis group, preferably for all with the respectively associated head support to the respective vertical Axle rotatably connected chassis groups, at least one measuring device from which the tracking of at least one of the wheels of the chassis group with respect to the rail on which it rolls, can be detected and a respective track position corresponding track position value can be output ,
  • Trolleys of rail cranes movable on rails comprise landing gear groups for a respective leg of the gantry crane.
  • the chassis groups have wheels for moving the crane, some or all of which are equipped with drive motors.
  • the individual chassis groups are connected to a head support of the steel structure of the crane with only one degree of freedom, namely a pivotability about a horizontal axis transverse to the rails.
  • this results in more or less large inclinations of the axes with respect to their exact alignments perpendicular to the longitudinal extent of the rail, due to tolerances and deformations of the components.
  • the resulting horizontal forces and their unfavorable distribution on the individual wheels lead to suspension restrictions and thus to an increased wear of the wheel flanges of the wheels and also the wheel treads and the rails.
  • the chassis group drives a sinusoidal curve, whereby the wheel flanges of the wheels start alternately with relatively low forces on both rail flanks.
  • non-generic corner bogies are also known, which serve for moving a crane along a roadway which has at least one bend.
  • a synchronization device In chassis of overhead cranes, a synchronization device is known, in which a preceding wheel is scanned and the drives associated with the two rails are controlled in such a way that the desired alignment of the crane undercarriage with the rails is achieved.
  • Such a synchronization device is made possible by the usually rigid design of overhead cranes.
  • the object of the invention is to achieve a substantial cost reduction over the service life of the gantry crane. According to the invention, this is achieved by a gantry crane having the features of claim 1.
  • an actuator is provided for at least one of the associated head carrier rotatably connected to the vertical axis group, of which the chassis group with a torque which is determined by the control of the actuator by means of a control device to the vertical Axis can be acted upon. It is therefore a force-controlled actuator, which causes a torque about the vertical axis about which the chassis group is rotatable, according to its force generated by it.
  • at least one force-controlled actuator acts on each of the chassis groups, which are rotatable about a vertical axis relative to the associated head carrier.
  • a tracking value is the position of the wheel relative to the rail with respect to the direction at right angles to the longitudinal extent of the rail.
  • tracking value the track position value
  • this is set by this the moment-loading of the force acting on this chassis group actuator.
  • the force acting on the vertical axis, caused by the actuator torque thus represents the manipulated variable of the control loop.
  • the track of the measuring device for the front wheel for the respective direction of travel is detected.
  • the wheel flanges of the wheels can be kept at a distance from the rail flanks, completely or at least substantially (for example over more than 90% of the driving distance).
  • a substantial reduction in wear is achieved, and in a very simple manner without carrying out a positive control that compulsorily sets the rotational position of a chassis group relative to the vertical axis.
  • the torque application of a respective chassis group is effected by a control, wherein the actual value of the tracking of the detected by the measuring device for the present direction of travel wheel is used as a controlled variable.
  • the torque exerted by the actuator on the chassis group of the control device on the Value 0 is set, ie no torque is applied to the chassis group by the actuator. exerted or the landing gear group is released with respect to a rotation about the vertical axis. If, during the process of the gantry crane, the track position of the wheel comes to lie on one side outside this middle range, a torque is exerted on the chassis group by the actuator.
  • the amount of torque exerted is a constant value, regardless of how far the track position of the wheel is outside this middle range.
  • the direction of the force exerted by the actuator is reversed, ie, the direction of rotation of the torque is reversed.
  • the amount of applied torque may be the same as or different than the left and right deviations from the middle range. In this way, a very simple control can be achieved.
  • Fig. 1 and Fig. 2 is a front view and a plan view of a gantry crane according to an embodiment of the invention, highly schematic and simplified; 3 shows a side view (viewing direction A in FIG. 1) of a chassis group connected to a head carrier with the rail; Fig. 4 shows a portion of the head carrier and connected to the head carrier
  • FIG. 5 shows a schematic enlarged representation of a section of a subframe in the region of the measuring device, in a side view corresponding to FIG. 3 (without the drive motor);
  • Fig. 6 is a schematic representation of the measuring device in view (corresponding to the viewing direction B in Fig. 3);
  • FIG. 7 shows a schematic representation of a part of the front wheel for the respective direction of travel with an upper section of the rail, in a view corresponding to the viewing direction B in FIG. 3;
  • FIG. 8 is a schematic representation of the control loop in a possible embodiment
  • 9 shows exemplary diagrams of the track position versus time (diagram above) and the torque exerted by the actuator versus time (diagram below) to illustrate the control.
  • An exemplary embodiment of a gantry crane designed in accordance with the invention is shown in the figures.
  • the gantry crane is movable on a straight roadway, which is formed by two mutually spaced, parallel rails 1.
  • the gantry crane has four legs 2, 3, 4, 5 in the illustrated embodiment. Also constructions with three legs are known.
  • two supports can be provided.
  • the legs 2-5 and supports support the cross member 6 or 7, along which a trolley 8 is movable or which are provided with another 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 shows exemplary diagrams of the track position versus time (diagram above) and the torque exerted by the actuator versus time (diagram below) to illustrate the control.
  • a connecting this head carrier 10 is attached at the lower ends of the arranged on a respective side of the portal legs 2, 3; 4, 5, 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.
  • the crane chassis is a straight-ahead chassis for moving along the rectilinear rails 1.
  • a landing gear group 1 is arranged directly below each of the legs 2-5. It would also be conceivable and possible, for example, to provide a separate head carrier 10 for each leg 2-5.
  • 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.
  • All wheels 12 of a respective chassis group 11 are arranged one behind the other on a straight line formed by the rail 1.
  • the axes 13 of the wheels 12 are aligned approximately at right angles to the rails 1 (the deviation in all possible rotational positions of the chassis group 11 with respect to the below explained vertical axis 23, for example, less than 3 °, which value depends on the geometry of the chassis group, deviations the axial positions of the wheels 12 of a chassis group 11 with respect to their orientations parallel to one another are preferably less than 0.05 °).
  • a respective chassis group 11 has eight wheels 12 which are spaced apart from one another in the longitudinal direction of the rail 1. In each case two longitudinally of the rails one behind the other wheels 12 are rotatably mounted on a subframe 16. In the exemplary embodiment shown, four subframes 16 located one behind the other in the longitudinal direction of the rails are thus present per chassis group.
  • the two rockers 17 are connected to a common rocker 19, wherein they are each pivotable relative to the rocker 19 about a horizontal, parallel to the axes 13 of the wheels 12 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 such a manner that the chassis group 11 is pivotable relative to the head carrier 10 about a horizontal, perpendicular to the respective rail 1 axis 24 and about a vertical axis 23 is rotatable.
  • a connecting device 25 is provided, which can be designed according to the aforementioned prior art.
  • Particularly preferred is an embodiment, as known from EP 1 911 716 A2, wherein a central, preferably designed in the form of a ball joint, joint 22 is present and further between the respective head carrier 10 and the respective chassis group 11 two arms 29, 30th are arranged, which are seen in the direction perpendicular to the rail 1 on both sides of the central joint 22.
  • 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 each have a degree of freedom for pivoting the respective link 29, 30 relative to the head carrier 10 or against the rocker 19th about a plane parallel to the axes 13 of the wheels 12 axis 33 and a degree of freedom for pivoting the respective link 29, 30 relative to the head support 10 and with respect to the chassis group 11 about a perpendicular to the axes 13 of the wheels 12 standing horizontal axis 34.
  • the central joint 22 is designed as a loose bearing in the vertical direction, ie has a clearance in this direction in the mounted state.
  • a chassis group 11 of a gantry crane constructed in accordance with the invention may also comprise more or less than eight wheels 12 spaced apart in the direction of travel, wherein at least two wheels 12, spaced apart from one another in the longitudinal direction of the respective rail 1, are rotatably mounted on a common subframe 16.
  • the connecting device 25 can be arranged directly between this subframe 16 and the head carrier 10.
  • two wheels on a respective subframe 16 may be rotatably mounted and the subframe 16 about horizontal parallel to the axes 13 of the wheels 12 axes pivotally connected to a rocker 17.
  • the connecting device 25 could be arranged directly between the head carrier 10 and this rocker 17 in this case.
  • the wheels 12 are rigid within the chassis groups 11 with respect to rotations about vertical axes, i. apart from the rotatability of the chassis group 1 1 as a whole about the vertical axis 23 are no rotations about vertical axes, e.g. of individual wheels 12, given.
  • the intermediate wheels 12 may be equipped with flanges 14, 15. Instead, trackless wheels could be used for the intermediate wheels 12.
  • a derailment protection (which may be formed by stops arranged on the subframe which cooperate with the rail flanks, as is known) is advantageously provided, whereby cost savings can be achieved in comparison to wheels with flanges.
  • trackless wagons with derailment protection could also be used for the foremost wheels in relation to the two directions of travel, although wheels with flanges are preferred for safety reasons. are awarded.
  • wheels 12 with flanges 14, 15 and wheels 12 could be used with tracking rollers, which are also known.
  • tracking rollers which are also known.
  • chassis groups 11 For each of the rotatable about the vertical axes 23 chassis groups 11 two measuring devices 26 are available. Of these, the positions of the front wheels 12 with respect to the two directions of travel are detected with respect to their orientations in the direction perpendicular to the rail 1.
  • the orientation of a wheel 11 with respect to the rail 1 with respect to its position perpendicular to the longitudinal extent of the rail 1 is referred to as tracking in the context of this document.
  • the tracking value a indicates the offset of the wheel from the central orientation on the rail 1.
  • the distance between one of the wheel flanges 14, 15 with respect to the adjacent rail flank 27 could also be used as the track position value a.
  • the tracking of the foremost wheel 12 of a drive group 11 relative to the respective direction of travel is largely determinative of the positions of the wheels 12 of the chassis group 11 relative to the rails and of the forces with which wheel flanges of the wheels 12 start on the rail flanks.
  • the measuring device could in principle also detect the tracking position of another of the wheels lying in front of the vertical axis 23 about which the chassis group 11 is rotatable. Which are relative to the respective direction of travel in front of the vertical axis 23 about which the chassis group 11 is rotatable, lying wheels are the respective "leading" wheels.
  • FIGS. 5 and 6 An example of a possible embodiment of a measuring device 26 can be seen in particular from FIGS. 5 and 6.
  • a yoke 35 slidably bears with sliding linings 36 on the two rail flanks 27.
  • the yoke 35 is pivotally mounted on first and second pivot arms 37, 38 about horizontal axes perpendicular to the axes 13 of the wheels 12, 39, 40.
  • the pivot arms 37, 38 are further pivotally mounted above the axes 39, 40 about horizontal, perpendicular to the axes 13 of the wheels 12 stationary axes 41, 42 which are fixedly mounted on the subframe 16, preferably in the region of the end of the subframe sixteenth
  • the distance of the yoke 35 from the axis 13 of the frontmost wheel 12 with respect to the direction of travel in question is relatively small, preferably smaller than the diameter of this wheel 12.
  • the first pivot arm 37 has an extension arm 43 which projects upwards relative to the axle 41. is formed by a two-armed lever.
  • the pivoting position of the extension arm 43 is detected by, for example, inductive measuring sensors 44, 45.
  • inductive measuring sensors 44, 45 In the simplest case, it would be conceivable and possible to design the two measuring sensors 44, 45 as switches which can be actuated mechanically by the extension arm 43.
  • an actuator 28 which is for example formed as shown in the form of a piston-cylinder unit. This is arranged between a connection bracket 46 attached to the head carrier 10 and a connection tab 47 attached to the rocker 19. By a force exerted by the actuator 28, a force acting around the vertical axis 23 torque m is exerted on the chassis group 11.
  • the actuator 28 is controlled by a control device 48, 49 in response to the output by the measuring device 26 tracking position value.
  • a force variable is set as the controlled variable on the actuator 28.
  • An exemplary embodiment of the entire control loop is shown schematically in FIG. 8.
  • the control device has a control unit 48, which is supplied to the tracking position value detected by the measuring device 26, and an actuator drive device 49.
  • the actuator drive means 49 is formed in the illustrated embodiment of hydraulic elements.
  • a feed pump 50 in this case conveys hydraulic oil from a reservoir 51. By means of a pressure relief valve 52, the maximum, prevailing in the hydraulic line 53 pressure is set.
  • Directional valve 54 is controlled by the control unit 48. Depending on the position of the 4/3-way valve 54, the actuator 28 is released or by the actuator 28, a force is exerted in one or the other direction, ie on the chassis group 11, a force acting in one or the other direction of rotation torque m is exercised.
  • This torque m represents the manipulated variable of the control loop.
  • the controlled system as shown schematically in FIG. 8, is formed by the running gear group 1 1 running on the rail 1.
  • the manipulated variable can take only three values, namely, a torque 0, a torque acting in the one direction of rotation with an amount m x or in the other direction of rotation acting torque with the amount m y exerted.
  • the amount m x or m y of the torque is preset here, in the illustrated embodiment by adjusting the pressure value of the pressure relief valve 52.
  • the default can be done after the gantry crane is completed, according to the horizontal forces caused by the deviations of the axles 13 of the wheels 12 of a chassis group 11 with respect to their mutually parallel orientations.
  • the torque value 0 is set by means of the control device, ie in the embodiment shown by setting the corresponding position of the 4/3-way valve 54 by the control unit 48.
  • This middle region corresponds to a tracking value a which is between a value a , and a 2 lies.
  • the flanges 14, 15 are spaced from the rail flanks 27.
  • the distances of the flanges 14, 15 of the rail flanks are each 20mm, so the distance of the flange 14 of the rail flange 27 in tracking position a, eg 5mm and when tracking value a 2, for example 35mm.
  • the 4/3-way valve 54 is correspondingly adjusted by the control unit 48, so that one of the further approach or removal of the flange 14 to the rail edge 27 and of the rail edge 27th counteracting torque ⁇ m x or -m y is exerted on the chassis group 11.
  • the control unit 48 has a comparator part.
  • the control unit 48 has a control part.
  • the front wheel 12 of the chassis group 11, which is the front wheel in relation to the direction of travel, has, for example, the mean track position a 0 at the beginning of the method of the gantry crane.
  • a change in the track position occurs in the method of the crane, in the exemplary embodiment shown in the direction of the value a.
  • Factors for the horizontal force occurring are in particular the total non-compensating deviations of the axial positions of the wheels 12 of a respective chassis group 11 with respect to their orientations parallel to each other, and wind loads occurring.
  • the chassis group 11 is acted upon by the torque m x .
  • the distance a from the rail edge 27 thereby increases again. If an intended tracking value a is reached, for example, when the center position a 0 is reached again, the Fahrwerscade 11 is again unlocked. The described control process is repeated in the sequence.
  • a feed pump 50 could be used for this purpose, the delivery pressure is adjustable.
  • hydraulically acting actuators 28 and other actuators could be used, for example, mechanically or electromechanically acting actuators.
  • this could be controlled directly by the control part of the control unit 48.
  • the measuring device 26 could also be designed in another way as shown.
  • a cooperating only with a rail edge 27, rotatably mounted relative to the subframe 16 part could be present.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Carriers, Traveling Bodies, And Overhead Traveling Cranes (AREA)

Abstract

L'invention concerne une grue à portique qui comporte un mécanisme de roulement servant à déplacer la grue à portique le long d'une voie rectiligne formée de rails parallèles (1), lequel comprend plusieurs groupes de mécanismes de roulement (11) qui comportent respectivement au moins deux roues (12) montées à rotation sur un faux-châssis (16), espacées l'une de l'autre dans la direction longitudinale du rail (1) concerné et dont au moins deux, de préférence toutes, sont reliées à rotation autour d'un axe vertical (23) à un support de tête (10) de la grue à portique. Pour au moins un groupe de mécanismes à roulement (11) relié à rotation autour d'un axe vertical (23) au support de tête (10), il y au moins un dispositif de mesure (26) par lequel la position sur la voie d'au moins une des roues (12) du groupe de mécanismes de roulement (11) par rapport au rail (1) sur lequel elle roule peut être détectée et une valeur (a) correspondant à la position en question peut être fournie. Un organe de réglage (28) agissant entre le groupe de mécanismes de roulement (11) et le support de tête (10) associé est commandé par un dispositif de réglage (48, 49) auquel la valeur (a) fournie par le dispositif de mesure (26) est transmise. Le groupe de mécanismes de roulement (11) peut être soumis par l'organe de réglage (28) à un couple de rotation (m) déterminé par cette commande autour d'un axe vertical (23).
EP09740248A 2008-10-09 2009-09-08 Grue à portique Active EP2331446B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09740248T PL2331446T3 (pl) 2008-10-09 2009-09-08 Suwnica bramowa

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0157708A AT507333B1 (de) 2008-10-09 2008-10-09 Portalkran
PCT/AT2009/000352 WO2010040157A1 (fr) 2008-10-09 2009-09-08 Grue à portique

Publications (2)

Publication Number Publication Date
EP2331446A1 true EP2331446A1 (fr) 2011-06-15
EP2331446B1 EP2331446B1 (fr) 2013-04-03

Family

ID=41402412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09740248A Active EP2331446B1 (fr) 2008-10-09 2009-09-08 Grue à portique

Country Status (5)

Country Link
US (1) US20110180506A1 (fr)
EP (1) EP2331446B1 (fr)
AT (1) AT507333B1 (fr)
PL (1) PL2331446T3 (fr)
WO (1) WO2010040157A1 (fr)

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FI123819B (fi) * 2011-02-03 2013-11-15 Konecranes Oyj Valvontajärjestelmä ja menetelmä sekä tietokoneohjelmatuote
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RU2502665C1 (ru) * 2012-04-18 2013-12-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Брянский государственный технический университет" Способ ограничения перекоса мостового крана
EP2824058A1 (fr) * 2013-07-12 2015-01-14 HF Holding S.A. Rail pour charnière de flèche de grue
CN103738847A (zh) * 2014-01-08 2014-04-23 中山市公路钢结构制造有限公司 一种用于龙门吊的同步纠偏装置
CN113786939A (zh) * 2021-10-09 2021-12-14 山东天益环保测控有限公司 一种用于仪表控制柜的喷漆设备

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Also Published As

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AT507333A1 (de) 2010-04-15
PL2331446T3 (pl) 2013-09-30
WO2010040157A1 (fr) 2010-04-15
AT507333B1 (de) 2011-09-15
US20110180506A1 (en) 2011-07-28
EP2331446B1 (fr) 2013-04-03

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