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EP0668238B1 - Profil de flèche - Google Patents

Profil de flèche Download PDF

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Publication number
EP0668238B1
EP0668238B1 EP95102263A EP95102263A EP0668238B1 EP 0668238 B1 EP0668238 B1 EP 0668238B1 EP 95102263 A EP95102263 A EP 95102263A EP 95102263 A EP95102263 A EP 95102263A EP 0668238 B1 EP0668238 B1 EP 0668238B1
Authority
EP
European Patent Office
Prior art keywords
profile
gravity
centre
jib
horizontal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95102263A
Other languages
German (de)
English (en)
Other versions
EP0668238A1 (fr
Inventor
Ernst Kaspar
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.)
Compact Truck AG
Original Assignee
Compact Truck AG
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 Compact Truck AG filed Critical Compact Truck AG
Publication of EP0668238A1 publication Critical patent/EP0668238A1/fr
Application granted granted Critical
Publication of EP0668238B1 publication Critical patent/EP0668238B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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

Definitions

  • the invention relates to cantilever profiles in the preambles of claims 1 and 3 specified genera.
  • Such boom profiles are from DE-U-92 10 902.0 or known from DE-A-23 17 595.
  • the telescopic boom has a base and at least one telescopic Part, the cross-sectional profiles of the individual telescopic members mostly in are of the same shape but are of different sizes.
  • the telescopic boom must be lifted when it is under load.
  • the boom is subjected to a load as a bending beam, i.e. tensile stresses on the top of the boom and on the underside of the The cantilevers predominate under load.
  • Telescopic booms predominantly have rectangular profiles, since the rectangular shape is particularly well suited for the transmission of transverse forces between the individual telescopic members and also for absorbing different bending moments.
  • the demand for weight savings led to particularly thin-walled rectangular profiles, which, however, then no longer proved to be sufficiently resilient.
  • undesirable bulges have occurred on the underside, but also in the central regions of the side sections.
  • the known boom sections of the generic type have semicircular, lower sections or semi-elliptical, lower sections. Have these known boom profiles a fairly good dent resistance in its lower section, but have one comparatively low moment of resistance against bending under load.
  • the invention is therefore based on the object of an improved boom profile provide genus mentioned at the beginning, in which the tendency to bulge is reduced and the stiffness especially in the lower and lower lateral profile area is better adapted to the load requirements of a telescopic boom.
  • the at least one flat wall section with decreasing tendency to bulge the neighboring, rounded section in its lateral extent reduced.
  • there are more ground points of the lower section of the profile are on the side below, So closer to the bottom corners of an imaginary conventional one Rectangular profile and thus the overall profile additionally a large moment of resistance to bending is own.
  • the boom profile according to the invention allows by the appropriate choice of the included Angle between the rounded, lower profile section and a lateral, oblique fold or between the lateral, oblique bend and the top chord belonging lateral vertical web the vulnerability of the lateral Reduce vertical web against bulging.
  • the upper section (Top chord) half box-shaped is the upper section (Top chord) half box-shaped.
  • This Design is a particularly advantageous form of the profile in relation to the utilization of the maximum possible section modulus given against bending. Because in the upper profile area the cantilever tension of the boom must prevail in upper, semi-box-shaped profile area does not occur unwanted bulges can be expected.
  • the profile is made by joining of two half-shells, namely the upper chord and lower chord manufactured.
  • the top chord is made in a conventional manner manufactured by folding. The least is with the lower chord a round section formed by polygonal bevelling.
  • the side folds are replaced by a subsequent one reached two times, causing the lower Area of the boom profile advantageously right is insensitive to manufacturing deficiencies, especially with regard to dimensional deviations at the bottom Bending radius. If dimensional deviations have occurred, leave it this by appropriate choice of the angle between the sideways beveled bevel and the subsequent rounded Balance the section in a simple way. So is the desired width of the lower flange can be exactly maintained and adjustable to the width of the top chord.
  • Cantilever profile in which each other in the lower profile area opposite, flat bends in the side sections and also one that intersects the vertical axis of gravity Horizontal web are provided, are the advantages of Rectangular profile and the advantages of the round profile in particular horr combined.
  • top chord i.e. the upper part of the Boom profile
  • the top chord is formed from an upper, horizontal, flat surface Web section, which is angled downwards by 90 °, rounded corners thigh-like and on both sides of the upper web section into two vertical, flat web sections is transferred.
  • the different embodiments differ in the lateral length of the Top chord vertical webs and in the training of the lower ends of the vertical webs adjoining lower rounded ones Sections of the overall profile.
  • the lateral vertical web belonging to the upper chord is continued with a laterally oblique, flat bevel 15 of length x 1 , which is inclined downward to the vertical axis of gravity Iy.
  • the fold is preferably arranged at a height of the vertical web in such a way that the fold overlaps with the horizontal axis of gravity Ix.
  • a lower horizontal web section 17 with the length M 1 is arranged at the lower horizontal outlet of the circular arc 16. This lower horizontal web section 17 connects the lower ends of the left-hand circular arc section 16 and a right-hand, mirror-symmetrical circular arc section 16 ', the center point of which is designated K11.
  • the two ends of the lower horizontal section 17 go tangentially into the adjacent circular arc sections 16 and 16 'over.
  • the center points K1 and K11 of the two circular arc sections 16 and 16 ' are both of the same kind Major axes Iy and Ix spaced apart, the two centers on both sides of the vertical axis of gravity Iy and provided below the horizontal axis of gravity Ix are.
  • the center point K1 lies vertically above the left-hand side End of the horizontal web 17 and the center K11 lies vertically above the right-hand end of the Horizontal web 17. Consequently, the length M1 is equal to that Distance between the center points K1 and K11.
  • a particular advantage of this cantilever profile according to FIG. 1 can be seen in the fact that many mass points of the lower profile section are at a large distance from the axis of gravity Iy and thus a large moment of resistance against bending about the bending axis Ix is ensured. Furthermore, there is an advantageous introduction of force into the lower profile section, since the membrane effect can come into play at the rounded force introduction points. Finally, a further optimization of the sensitivity of the lateral vertical web assigned to the upper chord against bulging, which is appropriate to the user wishes, is possible by varying the length of the arc sections 16 and 16 'and the length x 1 of the oblique fold 15.
  • FIG. 2 A second embodiment of the boom profile is shown in Fig. 2.
  • a laterally inclined, flat bevel 25 with the length x 2 does not directly adjoin (see FIG. 1). Rather, the vertical web and the bevel 25 are connected to one another via a rounding 28 in such a way that there is no bend edge.
  • a circular arc section 26 with the radius R 2 is then arranged at the lower end of the lateral, oblique fold 25.
  • the center points K 2 (left-hand side) and K 22 (right-hand side) of the circular arc sections 26 (left-hand side) and 26 '(right-hand side) are arranged in relation to the major axes Iy, Ix in such a way that their distances from both major axes are the same.
  • the two circular arc sections 26 and 26 ' are connected to one another with the aid of a flat horizontal web 27.
  • the length of the horizontal web 27 is designated M 2 .
  • the length M 2 corresponds to the distance between the center points K2 and K22 from one another.
  • a third embodiment of the cantilever profile (according to FIG. 3) is derived from the second embodiment.
  • a first difference is that the rounded region 28 crosses the horizontal axis of gravity Ix in the second embodiment, while a similar rounded section 38 of the third embodiment is only set below the horizontal axis of gravity Ix.
  • the center points K 3 and K 33 of the left and right sides of the circular arc sections 36 and 36 'on the left and right sides are arranged similarly to FIG. 2 below the horizontal axis of gravity Ix, however, these center points K 3 , K 33 are so positions that their distances from the horizontal axis of gravity Ix are shorter than from the vertical axis of gravity Iy.
  • the laterally oblique bend 35 adjoining the upper chord vertical section downwards has the length x 3
  • the arc section 36 (or 36 ') has the radius R 3
  • the horizontal, flat web section 37 has the length M 3 .
  • the flat section 37 connects the left and right-hand rounded sections 36 and 36 'to one another.
  • the length M 3 corresponds to the distance between the center points K3 and K33 from one another.
  • a particular advantage of the third embodiment is a large section modulus against the (bending) axis Ix, since large parts of the mass points of the lower section are located relatively far from the axis of gravity Iy. Furthermore, there is an advantageous introduction of force into the arc sections 36 and 36 'due to their membrane action. Furthermore, no moments are to be expected at the transition point between the section 38 and the vertical web section of the upper chord 34 which adjoins upwards. Since no buckling edge is formed between these two sections, circumferential stresses generated by the radial introduction of forces can essentially not result in corresponding moments. Thus there is a slight tendency of the lower horizontal web portion 37 to bulge. The buckling behavior in the area of the lateral vertical web can be influenced by the length x 3 of the flat, obliquely bent edge 35.
  • the third embodiment essentially combines the advantages of the two previous embodiments.
  • a fourth embodiment of the cantilever profile shown in FIG. 4 initially provides, similarly to the first exemplary embodiment, a laterally oblique, flat fold 45 with the length x 4 , which intersects the horizontal axis of gravity Ix, following the upper chord vertical section. Similar to the previous three embodiments, the fold is identical to the tangent which is formed at the upper end of the arc section 46 adjoining at the bottom, ie there is no fold edge below the fold 45, as in the previous three embodiments as well.
  • the arc section 46 with the radius R 4 now connects the left fold 45 with the right fold 45 'of the cantilever profile.
  • the center point K 4 of the arc section 46 is provided above the horizontal axis of gravity Ix, but on the vertical axis of gravity Iy. If necessary, the arc radius of the arc section 46 immediately adjacent to the folds 45, 45 'may be smaller than R 4 , so that the entire arc 46 is composed of three individual arcs.
  • the tangential transitions between the oblique fold 45 and the arc section 46 advantageously prevent the formation of moments due to circumferential stresses.
  • This embodiment allows the height of the vertical web belonging to the upper chord and thus its buckling behavior by varying the radius of the arc 46 which is present at the bend 45, as well as the arc length caused by this radius and by varying the length x 4 of the bend 45 according to the to determine the respective static requirements. Forming the curved section 46 with two different radii results in a particularly favorable buckling behavior in the lower profile section 43.
  • FIG. 5 A fifth embodiment of the cantilever profile is shown in FIG. 5.
  • the laterally inclined, flat bevel 55 which adjoins the vertical web belonging to the upper web and is arranged below the horizontal axis of gravity Ix.
  • the bevel has the length x 5 .
  • the lower end of this left-sided bevel 55 is connected by an arc section 56 to the lower end of a mirror-symmetrical, right-hand, flat bevel 55 '.
  • the arc section 56 has a radius R 5
  • the associated circular arc center K 5 is similar to the fourth exemplary embodiment above the horizontal axis of gravity Ix and the vertical axis Iy intersecting.
  • a relatively large radius R 5 of the arc section 56 ensures a large moment of resistance of the boom against bending against the horizontal axis Ix.
  • the angular position and the length x 5 in the force application area of the folds 55 can be determined flexibly according to the user requirements with regard to the lateral and lateral lower sensitivity to bulging.
  • the sixth embodiment of the cantilever profile according to FIG. 6 represents a variation of the fifth embodiment.
  • the main difference is that a larger radius R 6 (cf. radius R 5 of the circular arc section 56 in the fifth embodiment) was selected for a circular arc section 66 , Accordingly, the associated circular arc center K 6 is arranged significantly higher above the axis of gravity Ix on the vertical axis Iy, the vertical web 64 belonging to the upper flange, in particular below the axis of gravity Ix, is longer and the lateral fold 65 between the vertical web 64 and the arc section 66 is stronger inclined to the vertical axis of gravity Iy.
  • a seventh embodiment of the cantilever profile is shown in FIG. Instead, the vertical web belonging to the upper chord is transferred directly into the curved section 76.
  • the transition from vertical web to arch section is preferably arranged essentially at the level of the horizontal axis of gravity Ix.
  • the left-hand arc section 76 has a radius R 7 with a circular arc center K7 at the intersection of the two major axes.
  • the radius R 7 preferably corresponds essentially to the distance between the vertical center of gravity Ix and the vertical web 74 belonging to the upper chord.
  • the web section 77 has the length M 4 .
  • the transition between circular arc section 76 and web section 77 is designed in such a way that no kink edge is formed by means of a transition arc with a small radius.
  • the seventh embodiment advantageously adjusts large moment of resistance against bending against the axis Ix ready because a large part of the mass points of the lower profile section a large distance from the vertical axis of gravity Iy has.
  • the rounded sections ensure as a result the membrane effect a particularly favorable force transmission in the overall profile. Furthermore, essentially none occur Moments in the transition area to the lateral vertical bars because the circumferential stresses of the arc section 76 or 76'directed directly or tangentially into the vertical webs become.
  • FIG. 1 An eighth embodiment is shown in FIG. This embodiment largely corresponds to the first embodiment shown in FIG. 1, but has no laterally inclined bends. At the lower ends of the vertical webs assigned to the upper chord, an arc section 86 with the radius R 8 is connected on the left side and an arc section 86 ′ with the radius R 8 on the right side. Between the two circular arc sections 86 and 86 'there is a lower horizontal section 87 with a comparable length M 5 . As in the first, second and third embodiment, the center points K 8 and K 88 are each equally spaced to the side of the vertical axis of gravity Iy and equally spaced below the horizontal axis of gravity Ix.
  • the length M 5 of the horizontal section 87 corresponds to the distance between the center points K 8 and K 88 from one another.
  • the membrane tension state is also ensured in the eighth embodiment by the tangential transitions of the circular arc section 86, 86 ′ into the horizontal web section 87.
  • the eighth embodiment advantageously adjusts large moment of resistance against bending against the Ix axis ready because a large part of the mass points of the lower profile section a large distance from the vertical axis of gravity Iy has.
  • the rounded sections ensure as a result the membrane effect a particularly favorable force transmission, both in the two vertical webs and in the horizontal web 87.
  • the length dimensions X of the bevels on the side is preferred in all embodiments of the invention 5 to 28%, based on the total profile height (Y-direction).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)

Claims (8)

  1. Profil de flèche, en particulier pour des flèches télescopiques de grues et de véhicules grutiers, avec une section supérieure, sensiblement en forme de demi-caisson, ayant des parois latérales s'étendant parallèlement à l'axe de la gravité vertical (ly) du profil de flèche, et une section de profil inférieure présentant au moins une section en forme d'arc de cercle, qui est relié aux extrémités des parois latérales parallèles de la section supérieure, caractérisé en ce que les zones, reliées aux extrémités des parois latérales parallèles de la section de profilé supérieure, de la section de profil inférieure, sont configurées en étant opposées les unes les autres, sous forme de chanfreins obliques (15, 25, 35, 45, 55, 65), symétriques, plans, orientés obliquement vers l'intérieur, faisant, avec les parois latérales parallèles de la section de profilé supérieure, chaque fois un angle "alpha", et en ce qu'une section (16, 16', 26, 26', 36, 36', 46, 56, 76, 76', 86, 86') en forme d'arc de cercle, se raccorde aux extrémités inférieures de ces chanfreins plans tournés vers l'intérieur.
  2. Profil de flèche selon la revendication 1, caractérisé en ce que, dans la section de profilé inférieure, est prévue une nervure horizontale (17, 27, 37, 77, 87), divisée centralement par l'axe vertical de gravité (ly) du profil de flèche, nervure s'étendant parallèlement à l'axe horizontal de gravité (lx), une section (16, 16', 26, 26', 36, 36', 76, 76', 86, 86'), en forme d'arc de cercle, de la section de profil inférieure étant raccordée aux deux extrémités de cette nervure horizontale.
  3. Profil de flèche, en particulier pour des flèches télescopiques de grues ou de véhicules grutiers, avec une section supérieure, sensiblement en forme de demi-caisson, avec des parois latérales s'étendant parallèlement à l'axe de gravité vertical (ly), une section de profil inférieure, présentant deux sections en forme d'arc de cercle, reliée aux extrémités des parois latérales de la section supérieure, et avec une nervure horizontale (77, 87) divisée centralement par l'axe de gravité (ly) vertical du profil de flèche, nervure s'étendant parallèlement à l'axe de gravité horizontal (lx) du profil de flèche, à chacune des deux extrémités de la nervure horizontale étant raccordée l'une des sections (76, 76', 86, 86') en forme d'arc de cercle, caractérisé en ce que les rayons (R7, R8), des deux sections (76, 76', 86, 86') en forme d'arc de cercle, sont nettement plus grands que les rayons d'arrondis situés dans la zone de la section de profil supérieure, et en ce que, tant la section de profil supérieure, que la section de profil intérieure, sont chacune réalisées d'une seule pièce.
  4. Profil de flèche selon la revendication 3, caractérisé en ce que les rayons (R7) des deux sections (76, 76') en forme d'arc de cercle, se coupent au point d'intersection de l'axe de gravité vertical (ly) et de l'axe de gravité horizontal (lx).
  5. Profil de flèche selon la revendication 3, caractérisé en ce que les centres (K8, K88) des deux sections (86, 86') en forme d'arc de cercle sont également espacés de l'axe de gravité vertical (ly) et, chaque fois, également espacés au-dessous de l'axe de gravité horizontal (lx), la longueur de la section horizontale (87) étant égale à l'espacement mutuel entre les centres d'arc de cercle (K8, K88).
  6. Profil de flèche selon la revendication 1 ou 3, caractérisé en ce que les rayons des sections (16, 16', 26, 26', 36, 36', 86, 86') en forme d'arc de cercle ont leurs centres de cercle (K1, K11, K2, K22, K3, K33, R4, R5, R6, R8) situés au-dessous de l'axe de gravité horizontal (lx) du profil de flèche.
  7. Profil de flèche selon la revendication 1 ou 3, caractérisé en ce que les sections de paroi (16, 16', 26, 26', 36, 36', R8) en forme d'arc de cercle ont leurs centres de cercle au même espacement vis-à-vis de l'axe de gravité vertical (ly) et de l'axe de gravité horizontal (lx), mais au-dessous de l'axe de gravité horizontal.
  8. Profil de flèche selon la revendication 1, caractérisé en ce que la section (46, 56, 66) en forme d'arc de cercle a son centre de cercle (K4, K5, K6) situé au-dessus de l'axe de gravité horizontal (lx) sur l'axe de gravité vertical (ly).
EP95102263A 1994-02-18 1995-02-17 Profil de flèche Expired - Lifetime EP0668238B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9402692U 1994-02-18
DE9402692U DE9402692U1 (de) 1994-02-18 1994-02-18 Auslegerprofil

Publications (2)

Publication Number Publication Date
EP0668238A1 EP0668238A1 (fr) 1995-08-23
EP0668238B1 true EP0668238B1 (fr) 2003-01-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95102263A Expired - Lifetime EP0668238B1 (fr) 1994-02-18 1995-02-17 Profil de flèche

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EP (1) EP0668238B1 (fr)
DE (2) DE9402692U1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100893929B1 (ko) * 2001-12-12 2009-04-21 그로우브 유.에스. 엘.엘.씨. 차량형 크레인용 신축식 지브

Families Citing this family (13)

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Publication number Priority date Publication date Assignee Title
DE19624312C2 (de) * 1996-06-18 2000-05-31 Grove Us Llc Teleskopausleger für Fahrzeugkrane
DE19711975B4 (de) * 1997-03-12 2006-09-07 Terex-Demag Gmbh & Co. Kg Teleskopausleger für Fahrzeugkrane
DE19755355C2 (de) * 1997-12-12 1999-12-23 Grove Us Llc Teleskopauslegerlagerung mit Prägungen
DE10056799A1 (de) * 2000-11-14 2002-05-29 Atecs Mannesmann Ag Bodenabstützung für fahrbare Krane, Bagger und dergleichen
US6499612B1 (en) 2001-07-27 2002-12-31 Link-Belt Construction Equipment Co., L.P., Lllp Telescoping boom assembly with rounded profile sections and interchangeable wear pads
DE102006014573B3 (de) * 2006-03-29 2007-07-19 Manitowoc Crane Group France SAS, Teleskopkran-Auslegerteil mit schwächer und stärker gekrümmten Querschnittssegmenten im oberen Profilteil und im unteren Profilteil
CN101827773A (zh) * 2007-09-05 2010-09-08 帕尔芬杰尔股份有限公司 起重机臂的断面形状
DE102008032976B4 (de) 2007-09-12 2018-02-22 Manitowoc Crane Group France Sas Teleskopkran-Auslegerteil
JP2010089919A (ja) * 2008-01-09 2010-04-22 Kobelco Cranes Co Ltd 伸縮ブーム
DE202010006624U1 (de) 2010-05-10 2010-08-05 Manitowoc Crane Group France Sas Kranausleger, insbesondere Mobilkranausleger, mit vorgespannten Zugelementen
US9290363B2 (en) 2011-07-21 2016-03-22 Manitowoc Crane Companies, Llc Tailor welded panel beam for construction machine and method of manufacturing
RU190009U1 (ru) * 2019-03-22 2019-06-14 Открытое акционерное общество «Челябинский механический завод» Стрела телескопическая
SI26016B (sl) * 2020-06-19 2024-05-31 Tajfun Liv, Proizvodnja In Razvoj D.O.O. Nosilni sklop teleskopskega kraka pri mobilnem hidravličnem dvigalu in mobilno hidravlično dvigalo, obsegajoče tovrsten sklop

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BE733510A (fr) * 1969-05-23 1969-11-03
DE2317595A1 (de) * 1973-04-07 1974-10-31 Kaspar Klaus Teleskopierbare einheit, insbesondere fuer hebezeuge
DE9210902U1 (de) * 1992-08-14 1992-12-24 Liebherr-Werk Ehingen Gmbh, 7930 Ehingen Teleskopausleger für Fahrzeugkrane o.dgl.
DE9308993U1 (de) * 1993-06-16 1993-08-12 Ec Engineering + Consulting Spezialmaschinen Gmbh, 89079 Ulm Teleskopierbarer Ausleger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100893929B1 (ko) * 2001-12-12 2009-04-21 그로우브 유.에스. 엘.엘.씨. 차량형 크레인용 신축식 지브

Also Published As

Publication number Publication date
EP0668238A1 (fr) 1995-08-23
DE9402692U1 (de) 1994-04-14
DE59510537D1 (de) 2003-02-27

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